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WO2025052936A1 - Unité de source de chaleur - Google Patents

Unité de source de chaleur Download PDF

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Publication number
WO2025052936A1
WO2025052936A1 PCT/JP2024/029749 JP2024029749W WO2025052936A1 WO 2025052936 A1 WO2025052936 A1 WO 2025052936A1 JP 2024029749 W JP2024029749 W JP 2024029749W WO 2025052936 A1 WO2025052936 A1 WO 2025052936A1
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WO
WIPO (PCT)
Prior art keywords
refrigerant
liquid
heat source
gas
pipe
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.)
Pending
Application number
PCT/JP2024/029749
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English (en)
Japanese (ja)
Inventor
健人 奥澤
啓 竹中
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.)
Daikin Industries Ltd
Original Assignee
Daikin Industries Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Daikin Industries Ltd filed Critical Daikin Industries Ltd
Priority to EP24801460.7A priority Critical patent/EP4545876A4/fr
Publication of WO2025052936A1 publication Critical patent/WO2025052936A1/fr
Pending legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • 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
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • 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
    • F25B41/24—Arrangement of shut-off valves for disconnecting a part of the refrigerant cycle, e.g. an outdoor part
    • 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
    • F25B45/00—Arrangements for charging or discharging refrigerant
    • 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
    • F25B2345/00—Details for charging or discharging refrigerants; Service stations therefor
    • F25B2345/001—Charging refrigerant to a cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/12—Inflammable refrigerants
    • F25B2400/121—Inflammable refrigerants using R1234
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/16—Receivers

Definitions

  • This disclosure relates to a heat source unit for an air conditioner that uses a non-azeotropic refrigerant mixture.
  • the heat source unit of the first aspect is a heat source unit configured to form a refrigerant circuit by connecting to a utilization unit via piping at an installation location.
  • the refrigerant filled into the heat source unit is a non-azeotropic refrigerant having a temperature glide of 1°C or more during evaporation and condensation.
  • the heat source unit is pre-filled with the amount of refrigerant required for the refrigerant circuit when the length of the piping is a first length that makes it unnecessary to fill the refrigerant circuit with additional refrigerant.
  • the heat source unit of the second aspect is the heat source unit of the first aspect, and is configured to form a refrigerant circuit by connecting one utilization unit.
  • the heat source unit of the third aspect is the heat source unit of the first aspect, configured so that a refrigerant circuit is formed by connecting multiple utilization units in parallel.
  • the heat source unit of the fourth aspect is any one of the heat source units of the first aspect to the third aspect, in which the temperature glide during evaporation and condensation of the refrigerant is 5°C or more.
  • the heat source unit of the fifth aspect is any one of the heat source units of the first aspect to the fourth aspect, and is configured to be connected to a piping of 2.5 minutes or more (outer diameter 7.93 mm) through which a liquid refrigerant or a gas-liquid mixed refrigerant flows.
  • the heat source unit of the sixth aspect is the heat source unit of the fifth aspect, in which the piping through which the liquid refrigerant or the gas-liquid mixed refrigerant flows is a 2.5-section pipe (outer diameter 7.93 mm).
  • the heat source unit of the seventh aspect is any one of the heat source units of the first aspect to the sixth aspect, in which the amount of refrigerant pre-filled in the heat source unit is two to three times the amount of R32 refrigerant required in the entire refrigerant circuit when R32 refrigerant is filled in the refrigerant circuit whose piping is set to the first length.
  • Some non-azeotropic refrigerants require a charging amount two to three times that of R32 refrigerant, which has a zero temperature glide, and there is a high risk that the composition ratio of such refrigerants will change when they are charged on-site. Therefore, with this heat source unit, there is a great advantage in that the composition ratio of the non-azeotropic refrigerant is maintained by charging the refrigerant in advance into the heat source unit.
  • the heat source unit of the eighth aspect is any one of the heat source units of the first aspect to the seventh aspect, and has a first length of 30 m.
  • the heat source unit of the ninth aspect is any one of the heat source units of the first aspect to the eighth aspect, and includes a first shut-off valve, a second shut-off valve, and a heat source circuit.
  • the heat source circuit is a refrigerant flow path from the first shut-off valve to the second shut-off valve, and is configured to form part of the refrigerant circuit.
  • the heat source circuit includes a compressor, a heat exchanger, and a pressure reducer. The compressor, the heat exchanger, and the pressure reducer are connected in sequence.
  • the heat source circuit further includes a high-pressure receiver connected between the heat exchanger and the pressure reducer.
  • the amount of refrigerant that can be pre-charged can include an amount equivalent to the internal volume of the high-pressure receiver.
  • the heat source unit of the tenth aspect is the heat source unit of the ninth aspect, in which the volume ratio of the high-pressure receiver to the heat exchanger is within the range of 0.04 to 0.6.
  • FIG. 1 is a circuit diagram of a refrigerant circuit of an air conditioning apparatus according to a first embodiment of the present disclosure.
  • 4 is a table showing the composition ratio and temperature glide of the non-azeotropic refrigerant mixture used in the present embodiment.
  • FIG. 6 is a circuit diagram of a refrigerant circuit of an air-conditioning apparatus according to a second embodiment of the present disclosure.
  • First Embodiment 1 is a circuit diagram of a refrigerant circuit 10 of an air conditioner 1 according to a first embodiment of the present disclosure.
  • an indoor unit 30, which is one utilization unit is connected to an outdoor unit 20, which is a heat source unit, via a liquid refrigerant pipe 5 and a gas refrigerant pipe 6.
  • the refrigerant filled into the refrigerant circuit 10 is a non-azeotropic refrigerant mixture with a temperature glide of 1°C or more during evaporation and condensation.
  • the refrigerant is usually filled after the outdoor unit 20 and the indoor unit 30 are connected via the liquid refrigerant piping 5 and the gas refrigerant piping 6 at the installation site of the air conditioning device 1.
  • the outdoor unit 20 is pre-filled with the amount of refrigerant required for the entire refrigerant circuit 10 when the liquid refrigerant piping 5 and the gas refrigerant piping 6 are set to a predetermined first length L1, regardless of the actual lengths of the liquid refrigerant piping 5 and the gas refrigerant piping 6.
  • Outdoor unit 20 The outdoor unit 20 includes a compressor 11, a four-way switching valve 13, an outdoor heat exchanger 15, a bridge circuit section 17, a liquid-gas heat exchanger 19, a high-pressure receiver 21, an expansion valve 23, a liquid-side shut-off valve 25, a gas-side shut-off valve 26 and an accumulator 27.
  • the compressor 11, four-way switching valve 13, outdoor heat exchanger 15, bridge circuit section 17, liquid-gas heat exchanger 19, high-pressure receiver 21, expansion valve 23, and accumulator 27 are provided in the refrigerant flow path from the liquid-side shut-off valve 25 to the gas-side shut-off valve 26, and constitute the heat source circuit 20a, which is part of the refrigerant circuit 10.
  • the outdoor unit 20 also includes an outdoor fan 29 that generates an airflow to promote heat exchange between the air and the outdoor heat exchanger 15.
  • Compressor 11 The compressor 11 has a suction port 11a and a discharge port 11b.
  • the refrigerant flows into the compressor 11 through the suction port 11a, is compressed to a high temperature and high pressure, and flows out from the discharge port 11b.
  • the four-way switching valve 13 has a first port P1, a second port P2, a third port P3, and a fourth port P4.
  • the first port P1 is connected to the discharge port 11b of the compressor 11.
  • the second port P2 is connected to the outdoor heat exchanger 15.
  • the third port P3 is connected to the suction port 11a of the compressor 11 via the liquid-gas heat exchanger 19 and the accumulator 27.
  • the fourth port P4 is connected to the gas-side shutoff valve 26.
  • Outdoor heat exchanger 15 is an air heat exchanger.
  • the outdoor heat exchanger 15 exchanges heat between the refrigerant flowing inside and the outside air sent from the outdoor fan 29.
  • a fin-and-tube heat exchanger is used as the outdoor heat exchanger 15.
  • the bridge circuit section 17 has four check valves 17a, 17b, 17c, and 17d connected in a bridge configuration.
  • a first connection point S1 between the check valves 17a and 17b is connected to the outdoor heat exchanger 15.
  • a second connection point S2 between the check valves 17a and 17c is connected to the expansion valve 23.
  • a third connection point S3 between the check valves 17c and 17d is connected to the liquid-side stop valve 25.
  • a fourth connection point S4 between the check valves 17b and 17d is connected to the liquid pipe 19a of the liquid-gas heat exchanger 19.
  • Liquid-gas heat exchanger 19 exchanges heat between a high-pressure refrigerant flowing through a liquid pipe 19a and a low-pressure refrigerant flowing through a gas pipe 19b.
  • the liquid-gas heat exchanger 19 is a double-pipe heat exchanger.
  • High-pressure receiver 21 The high-pressure receiver 21 temporarily stores the refrigerant supercooled in the liquid-gas heat exchanger 19 .
  • Expansion valve 23 The expansion valve 23 is disposed between the outlet of the high-pressure receiver 21 and the second connection point S2 of the bridge circuit unit 17. The expansion valve 23 reduces the pressure of the refrigerant flowing from the high-pressure receiver 21 to the second connection point S2 of the bridge circuit unit 17 to a predetermined low pressure.
  • liquid-side shut-off valve 25 is connected between the third connection point S3 of the bridge circuit portion 17 and the indoor heat exchanger 35.
  • the liquid-side shut-off valve 25 and the indoor heat exchanger 35 are connected by the liquid refrigerant piping 5.
  • Gas side shutoff valve 26 The gas-side shut-off valve 26 is connected in series with the four-way switching valve 13 between the four-way switching valve 13 and the indoor heat exchanger 35.
  • the gas-side shut-off valve 26 and the indoor heat exchanger 35 are connected by the gas refrigerant piping 6.
  • Accumulator 27 The accumulator 27 is connected between the four-way switching valve 13 and the suction port 11a of the compressor 11.
  • the accumulator 24 collects the liquid refrigerant that was not gasified in the evaporator, and prevents the liquid refrigerant from flowing into the suction port 11a of the compressor 11.
  • Outdoor fan 29 The outdoor fan 29 generates an air flow to promote heat exchange between the air and the refrigerant flowing inside the outdoor heat exchanger 15.
  • the outdoor fan 29 is a propeller fan.
  • (1-2) Indoor unit 30 An indoor heat exchanger 35 is disposed in the indoor unit 30. Also, an indoor fan 37 that generates an air flow is disposed in the indoor unit 30 to promote heat exchange between the air and the indoor heat exchanger 35.
  • the indoor heat exchanger 35 is an air heat exchanger.
  • the indoor heat exchanger 35 exchanges heat between the refrigerant flowing inside and the indoor air sent from the indoor fan 37.
  • a fin-and-tube heat exchanger is used as the indoor heat exchanger 35.
  • One end of the indoor heat exchanger 35 is connected to the liquid side shutoff valve 25 via the liquid refrigerant piping 5, and the other end is connected to the gas side shutoff valve 26 via the gas refrigerant piping 6.
  • the indoor fan 37 generates an air flow to promote heat exchange between the indoor air and the refrigerant flowing inside the indoor heat exchanger 35.
  • the indoor fan 37 is a sirocco fan.
  • liquid refrigerant pipe 5 and gas refrigerant pipe 6 The liquid refrigerant piping 5 and the gas refrigerant piping 6 connect the outdoor unit 20 and the indoor unit 30 to form a refrigerant circuit 10.
  • the lengths of the liquid refrigerant piping 5 and the gas refrigerant piping 6 are determined depending on the installation positions of the outdoor unit 20 and the indoor unit 30.
  • the gas refrigerant pipe 6 connects the gas side shutoff valve 26 of the outdoor unit 20 to the refrigerant outlet of the indoor heat exchanger 35 of the indoor unit 30 during cooling operation (the refrigerant inlet during heating operation).
  • the diameter of the liquid refrigerant pipe 5 When using a non-azeotropic refrigerant mixture that has a large pressure loss, the diameter of the liquid refrigerant pipe 5 must be large, preferably 2.5 mm or more (outer diameter 7.93 mm). However, the amount of refrigerant charged increases, and the greater the charged amount, the greater the risk that the refrigerant composition ratio will change when charged on-site. Therefore, with this air conditioning device 1, there is a great advantage in that the composition ratio of the non-azeotropic refrigerant mixture is maintained by charging the outdoor unit 20 with the refrigerant in advance.
  • Control Unit 40 controls the operating frequency of the compressor 11, controls the switching of the four-way switching valve 13, and controls the opening degree of the expansion valve 23.
  • the control unit 40 is composed of a microprocessor and a printed circuit board equipped with a memory.
  • the refrigerant used in this embodiment is a non-azeotropic refrigerant mixture.
  • a non-azeotropic refrigerant mixture is a mixture of two or more refrigerants with different boiling points. Since a refrigerant with a higher boiling point condenses before a refrigerant with a lower boiling point, the isotherm of the non-azeotropic refrigerant mixture slopes downward to the right from the saturated liquid line to the saturated vapor line. Therefore, a temperature glide occurs on the saturated liquid line and the saturated vapor line under the same pressure conditions.
  • FIG. 2 is a table showing the composition ratios and temperature glides of the non-azeotropic refrigerant mixtures used in this embodiment.
  • the physical properties of R454B, R454C, and R474A are determined based on the composition ratios shown in FIG. 2.
  • the condensed refrigerant flows through the first connection point S1, the check valve 17b, and the fourth connection point S4 of the bridge circuit section 17 into the liquid pipe 19a of the liquid-gas heat exchanger 19.
  • the refrigerant flowing through the liquid pipe 19a exchanges heat with the refrigerant flowing through the gas pipe 19b and is subcooled.
  • the refrigerant that flows through the liquid pipe 19a is temporarily stored in the high-pressure receiver 21.
  • the refrigerant that flows out of the high-pressure receiver 21 is then reduced in pressure to a predetermined low pressure in the expansion valve 23.
  • the refrigerant reduced in pressure in the expansion valve 23 flows into the indoor heat exchanger 35 via the second connection point S2 of the bridge circuit section 17, the check valve 17c, and the third connection point S3.
  • the refrigerant exchanges heat with the indoor air in the indoor heat exchanger 35 and evaporates.
  • the indoor air that has been cooled by the evaporation of the refrigerant is then blown into the room by the corresponding indoor fan 37, cooling the room.
  • the refrigerant that evaporates in the indoor heat exchanger 35 flows through the gas refrigerant pipe 6 and the four-way switching valve 13 into the gas pipe 19b of the liquid-gas heat exchanger 19.
  • the refrigerant flowing through gas pipe 19b exchanges heat with the refrigerant flowing through liquid pipe 19a and becomes superheated vapor.
  • the refrigerant that has flowed through gas pipe 19b passes through accumulator 27 and is sucked into compressor 11.
  • the refrigerant evaporated in the outdoor heat exchanger 15 flows through the four-way switching valve 13 into the gas pipe 19b of the liquid-gas heat exchanger 19.
  • the refrigerant flowing through the gas pipe 19b exchanges heat with the refrigerant flowing through the liquid pipe 19a and becomes superheated vapor.
  • the refrigerant that has flowed through the gas pipe 19b passes through the accumulator 27 and is sucked into the compressor 11.
  • the heat source circuit 20a of the outdoor unit 20 is pre-filled with an amount of refrigerant corresponding to the amount of refrigerant required in the refrigerant circuit 10 when the liquid refrigerant piping 5 and the gas refrigerant piping 6 have a predetermined first length L1.
  • the first length L1 is a length that makes it unnecessary to add additional refrigerant to the refrigerant circuit 10 formed by connecting the outdoor unit 20 and the indoor unit 30 via the liquid refrigerant piping 5 and the gas refrigerant piping 6.
  • the first length L1 is set to 30 m.
  • the installation work for the air conditioning device 1 consists of a process in which the outdoor unit 20 and the indoor unit 30 are each installed at the installation location, a process in which the outdoor unit 20 and the indoor unit 30 are connected via the liquid refrigerant piping 5 and the gas refrigerant piping 6, and a process in which the refrigerant filled in the outdoor unit 20 is sent to the refrigerant circuit 10.
  • the outdoor unit 20 and the indoor unit 30 are connected at the installation location via the liquid refrigerant pipe 5 and the gas refrigerant pipe 6 to form a refrigerant circuit 10.
  • the refrigerant filled in the refrigerant circuit 10 is a non-azeotropic refrigerant with a temperature glide of 1° C. or more during evaporation and condensation.
  • the lengths of the liquid refrigerant pipe 5 and the gas refrigerant pipe 6 are determined according to the installation positions of the outdoor unit 20 and the indoor unit 30.
  • the liquid refrigerant pipe 5 is preferably a 2.5-section pipe (outer diameter 7.93 mm) or more.
  • the diameter of the liquid refrigerant pipe 5 must be large, and the amount of refrigerant charged increases. The greater the amount of charge, the greater the risk that the composition ratio of the refrigerant will change during on-site charging. Therefore, in this air conditioning device 1, there is a great advantage in that the composition ratio of the non-azeotropic refrigerant is maintained, by charging the outdoor unit 20 with the refrigerant in advance.
  • the amount of the non-azeotropic refrigerant mixture pre-filled in the outdoor unit 20 is 2 to 3 times the amount of R32 refrigerant required in the entire refrigerant circuit 10 when a single R32 refrigerant is filled into the refrigerant circuit 10 in which the liquid refrigerant piping 5 and the gas refrigerant piping 6 are set to the first length L1.
  • non-azeotropic refrigerants require a charging amount two to three times that of R32 refrigerant, which has a zero temperature glide, and there is a high risk that the composition ratio of such refrigerants will change when charging on-site. Therefore, in this air conditioning system 1, there is a great advantage in that the composition ratio of the non-azeotropic refrigerant is maintained by charging the outdoor unit 20 with the refrigerant in advance.
  • the volume ratio of the outdoor heat exchanger 15 to the indoor heat exchanger 35 is equal to or greater than 3. This allows the amount of refrigerant pre-filled in the outdoor unit 20 to be sufficient for the amount of refrigerant required in the entire refrigerant circuit 10.
  • the high-pressure receiver 21 is connected between the outdoor heat exchanger 15 and the expansion valve 23.
  • the volume ratio of the high-pressure receiver 21 to the outdoor heat exchanger 15 is within a range of 0.04 to 0.6.
  • the amount of refrigerant that can be pre-charged in the outdoor unit 20 can include an amount of refrigerant equivalent to the internal volume of the high-pressure receiver 21.
  • the refrigerant circuit 10 is provided with a liquid-gas heat exchanger 19 for exchanging heat between a high-pressure liquid refrigerant and a low-pressure gas refrigerant.
  • the liquid-gas heat exchanger 19 is a double-pipe heat exchanger.
  • the amount of refrigerant that can be pre-filled into the outdoor unit 20 can include an amount of refrigerant equivalent to the internal volume of the liquid-gas heat exchanger 19.
  • the refrigerant additional charging process is not necessary because the amount of refrigerant charged in the outdoor unit 20 is equal to or greater than the required amount of refrigerant. Therefore, the additional refrigerant charging process is not performed, and the outdoor unit 20 and the indoor unit 30 are connected via the liquid refrigerant piping 5 and the gas refrigerant piping 6, and the installation work is completed.
  • the amount of refrigerant filled in the outdoor unit 20 is equal to or greater than the amount of refrigerant required in the refrigerant circuit 10 when the liquid refrigerant pipe 5 and the gas refrigerant pipe 6 are equal to or less than the first length L1.
  • the refrigerant pre-filled in the outdoor unit 20 is insufficient to meet the required amount of refrigerant, so a process of additionally filling the refrigerant is required.
  • a refrigerant additional charging process is performed, and an amount of refrigerant according to the lengths of the liquid refrigerant piping 5 and the gas refrigerant piping 6 is additionally charged into the refrigerant circuit 10.
  • the refrigerant is additionally charged, for example, from the service port of the liquid side shutoff valve 25 or the gas side shutoff valve 26.
  • FIG. 3 is a circuit diagram of a refrigerant circuit 110 of the air conditioning apparatus 100 according to the second embodiment of the present disclosure.
  • the air conditioning apparatus 100 is a multi-room air conditioning apparatus in which a plurality of indoor units 30a, 30b, 30c, and 30d, which are utilization units, are connected in parallel to one outdoor unit 120, which is a heat source unit.
  • the compressor 11, four-way switching valve 13, outdoor heat exchanger 15, bridge circuit section 17, liquid-to-gas heat exchanger 19, high-pressure receiver 21, expansion valve 23, and the refrigerant to be filled are the same as those in the first embodiment, so a description thereof will be omitted.
  • Second expansion valves 24a, 24b, 24c, 24d The four second expansion valves 24a, 24b, 24c, and 24d are connected in parallel, and each of the second expansion valves 24a, 24b, 24c, and 24d is connected in series to a corresponding liquid-side shutoff valve 25a, 25b, 25c, and 25d.
  • Each liquid side shut-off valve 25a, 25b, 25c, 25d is connected in series with the corresponding second expansion valve 24a, 24b, 24c, 24d between the corresponding second expansion valve 24a, 24b, 24c, 24d and the corresponding indoor heat exchanger 35a, 35b, 35c, 35d.
  • the liquid side shutoff valves 25a, 25b, 25c, and 25d are connected to the corresponding indoor heat exchangers 35a, 35b, 35c, and 35d by the corresponding liquid refrigerant pipes 5a, 5b, 5c, and 5d.
  • Indoor units 30a, 30b, 30c, 30d The indoor units 30a, 30b, 30c, and 30d are provided with indoor heat exchangers 35a, 35b, 35c, and 35d, respectively.
  • indoor fans 37a, 37b, 37c, and 37d that generate airflow are provided in each indoor unit 30a, 30b, 30c, and 30d to promote heat exchange between the air and the indoor heat exchangers 35a, 35b, 35c, and 35d.
  • the indoor heat exchangers 35a, 35b, 35c, and 35d are air heat exchangers.
  • the indoor heat exchangers 35a, 35b, 35c, and 35d exchange heat between the refrigerant flowing therethrough and the indoor air sent from the corresponding indoor fans 37a, 37b, 37c, and 37d.
  • fin-and-tube heat exchangers are used as the indoor heat exchangers 35a, 35b, 35c, and 35d.
  • One end of the indoor heat exchanger 35a is connected to the liquid side shut-off valve 25a via the liquid refrigerant pipe 5a, and the other end is connected to the gas side shut-off valve 26.
  • one end of the indoor heat exchanger 35b is connected to the liquid side shut-off valve 25b via the liquid refrigerant pipe 5b, and the other end is connected to the gas side shut-off valve 26 via the gas refrigerant pipe 6.
  • one end of the indoor heat exchanger 35c is connected to the liquid side shut-off valve 25c via the liquid refrigerant pipe 5c, and the other end is connected to the gas side shut-off valve 26 via the gas refrigerant pipe 6.
  • one end of the indoor heat exchanger 35d is connected to the liquid side shut-off valve 25d via the liquid refrigerant pipe 5d, and the other end is connected to the gas side shut-off valve 26 via the gas refrigerant pipe 6.
  • Indoor fans 37a, 37b, 37c, 37d The indoor fans 37a, 37b, 37c, and 37d generate airflows to promote heat exchange between the refrigerant and air flowing inside the corresponding indoor heat exchangers 35a, 35b, 35c, and 35d.
  • the indoor fans 37a, 37b, 37c, and 37d are sirocco fans.
  • the liquid refrigerant pipes 5a, 5b, 5c, and 5d and the gas refrigerant pipe 6 connect the outdoor unit 120 and the indoor units 30a, 30b, 30c, and 30d to form a refrigerant circuit 110.
  • the lengths of the liquid refrigerant pipes 5a, 5b, 5c, and 5d and the gas refrigerant pipe 6 are determined depending on the installation positions of the outdoor unit 120 and the indoor units 30a, 30b, 30c, and 30d.
  • the liquid refrigerant pipes 5a, 5b, 5c, and 5d connect the corresponding liquid-side shutoff valves 25a, 25b, 25c, and 25d of the outdoor unit 120 to the refrigerant inlets of the corresponding indoor heat exchangers 35a, 35b, 35c, and 35d during cooling operation (refrigerant outlets during heating operation).
  • the gas refrigerant pipe 6 connects the gas side shutoff valve 26 of the outdoor unit 120 to the refrigerant outlets of the indoor heat exchangers 35a, 35b, 35d, and 35c during cooling operation (refrigerant inlets during heating operation).
  • the pipe diameter of the liquid refrigerant pipes 5a, 5b, 5c, and 5d must be large, preferably 2.5 mm or more (outer diameter 7.93 mm).
  • the amount of refrigerant charged increases, and the greater the charged amount, the greater the risk that the refrigerant composition ratio will change during on-site charging. Therefore, in this air conditioning device 100, there is a great advantage in that the composition ratio of the non-azeotropic refrigerant mixture is maintained by charging the outdoor unit 120 with the refrigerant in advance.
  • liquid refrigerant pipes 5a, 5b, 5c, and 5d exceeds the first length L1
  • additional refrigerant charging will be required, increasing the risk of a change in the refrigerant composition ratio.
  • the liquid refrigerant pipes 5a, 5b, 5c, and 5d it is appropriate for the liquid refrigerant pipes 5a, 5b, 5c, and 5d to be 2.5-section pipes.
  • Control Unit 40 controls the operating frequency of the compressor 11, the switching control of the four-way switching valve 13, the opening degree of the expansion valve 23, and the opening degree of the second expansion valves 24a, 24b, 24c, and 24d.
  • the control unit 40 is composed of a printed circuit board equipped with a microprocessor and a memory.
  • the condensed refrigerant flows through the first connection point S1, the check valve 17b, and the fourth connection point S4 of the bridge circuit section 17 into the liquid pipe 19a of the liquid-gas heat exchanger 19.
  • the refrigerant flowing through the liquid pipe 19a exchanges heat with the refrigerant flowing through the gas pipe 19b and is subcooled.
  • the refrigerant that flows through the liquid pipe 19a is temporarily stored in the high-pressure receiver 21.
  • the refrigerant that flows out of the high-pressure receiver 21 passes through the fully open expansion valve 23, and is diverted to each of the second expansion valves 24a, 24b, 24c, and 24d via the second connection point S2, check valve 17c, and third connection point S3 of the bridge circuit section 17, and is reduced to a predetermined low pressure.
  • the refrigerant that has been reduced in pressure by each of the second expansion valves 24a, 24b, 24c, and 24d exchanges heat with the indoor air in the corresponding indoor heat exchanger 35a, 35b, 35c, and 35d, and evaporates.
  • the indoor air that has been cooled by the evaporation of the refrigerant is then blown into the room by the corresponding indoor fan 37a, 37b, 37c, and 37d, cooling the room.
  • each indoor heat exchanger 35a, 35b, 35c, and 35d joins together in the gas refrigerant pipe 6 and flows through the four-way switching valve 13 into the gas pipe 19b of the liquid-gas heat exchanger 19.
  • the refrigerant flowing through gas pipe 19b exchanges heat with the refrigerant flowing through liquid pipe 19a and becomes superheated vapor.
  • the refrigerant that has flowed through gas pipe 19b passes through accumulator 27 and is sucked into compressor 11.
  • the indoor air heated by heat exchange with the refrigerant is blown into the room by the corresponding indoor fans 37a, 37b, 37c, and 37d, heating the room.
  • each indoor heat exchanger 35a, 35b, 35c, 35d flows into the corresponding liquid refrigerant pipes 5a, 5b, 5c, 5d and reaches the corresponding second expansion valves 24a, 24b, 24c, 24d. Since the second expansion valves 24a, 24b, 24c, 24d are fully open, the refrigerant passes through and joins the second expansion valves 24a, 24b, 24c, 24d without being reduced in pressure.
  • the refrigerant passes through the third connection point S3 of the bridge circuit section 17, the check valve 17d, and the fourth connection point S4 and flows into the liquid pipe 19a of the liquid-gas heat exchanger 19.
  • the refrigerant flowing through the liquid pipe 19a exchanges heat with the refrigerant flowing through the gas pipe 19b and is subcooled.
  • the refrigerant that flows through the liquid pipe 19a is temporarily stored in the high-pressure receiver 21.
  • the refrigerant that flows out of the high-pressure receiver 21 is then reduced in pressure to a predetermined low pressure by the expansion valve 23.
  • the reduced-pressure refrigerant passes through the second connection point S2 of the bridge circuit section 17, the check valve 17a, and the first connection point S1 and flows into the outdoor heat exchanger 15.
  • the refrigerant exchanges heat with the outdoor air in the outdoor heat exchanger 15 and evaporates.
  • the refrigerant evaporated in the outdoor heat exchanger 15 flows through the four-way switching valve 13 into the gas pipe 19b of the liquid-gas heat exchanger 19.
  • the refrigerant flowing through the gas pipe 19b exchanges heat with the refrigerant flowing through the liquid pipe 19a and becomes superheated vapor.
  • the refrigerant that has flowed through the gas pipe 19b passes through the accumulator 27 and is sucked into the compressor 11.
  • the refrigerant is charged at the installation location of the air conditioning apparatus 100 after the outdoor unit 120 and the indoor units 30a, 30b, 30c, 30d are connected via the liquid refrigerant pipes 5a, 5b, 5c, 5d and the gas refrigerant pipe 6.
  • the lengths of the liquid refrigerant pipes 5a, 5b, 5c, 5d and the gas refrigerant pipe 6 are determined depending on the installation positions of the outdoor unit 120 and the indoor units 30a, 30b, 30c, 30d.
  • the air conditioning device 100 of this embodiment uses a non-azeotropic refrigerant mixture, and there is a high risk that the composition ratio will change when the refrigerant is charged after installation, so this risk needs to be reduced.
  • the heat source circuit 120a of the outdoor unit 120 is pre-filled with an amount of refrigerant corresponding to the amount of refrigerant required in the refrigerant circuit 110 when the liquid refrigerant pipes 5a, 5b, 5c, 5d and the gas refrigerant pipe 6 have a predetermined first length L1.
  • the first length L1 is a length that makes it unnecessary to add additional refrigerant to the refrigerant circuit 110 formed by connecting the outdoor unit 120 and the indoor units 30a, 30b, 30c, 30d via the liquid refrigerant pipes 5a, 5b, 5c, 5d and the gas refrigerant pipe 6.
  • the first length L1 is set to 30 m.
  • the refrigerant is filled into the outdoor heat exchanger 15, liquid-to-gas heat exchanger 19, high-pressure receiver 21, accumulator 27, and the piping connecting them, which are included in the heat source circuit 120a of the outdoor unit 120.
  • the amount of non-azeotropic refrigerant mixture pre-filled in the outdoor unit 120 is, for example, two to three times the amount of R32 refrigerant required for the entire refrigerant circuit 110 when R32 refrigerant is filled into the refrigerant circuit 110 in which the liquid refrigerant pipes 5a, 5b, 5c, and 5d and the gas refrigerant pipe 6 are set to the first length.
  • the pipe diameter inside the outdoor unit 120 is made larger than the pipe diameter inside the indoor units 30a, 30b, 30c, and 30d.
  • the amount of refrigerant pre-filled in the outdoor unit 120 can more than meet the amount of refrigerant required for the entire refrigerant circuit 110.
  • the installation work of the air conditioning device 100 consists of a process of installing the outdoor unit 120 and the indoor units 30a, 30b, 30c, and 30d at the installation location, a process of connecting the outdoor unit 120 and the indoor units 30a, 30b, 30c, and 30d via the liquid refrigerant pipes 5a, 5b, 5c, and 5d and the gas refrigerant pipes 6, and a process of sending the refrigerant filled in the outdoor unit 120 to the refrigerant circuit 110.
  • liquid side shutoff valves 25a, 25b, 25c, and 25d and the gas side shutoff valve 26 are opened to fill the refrigerant circuit 110.
  • the outdoor unit 120 and the indoor units 30a, 30b, 30c, and 30d are connected to each other via liquid refrigerant pipes 5a, 5b, 5c, and 5d and gas refrigerant pipes 6 at the installation location to form a refrigerant circuit 110.
  • the refrigerant filled in the refrigerant circuit 110 is a non-azeotropic refrigerant having a temperature glide of 1° C. or more during evaporation and condensation.
  • the lengths of the liquid refrigerant pipes 5a, 5b, 5c, and 5d and the gas refrigerant pipes 6 are determined according to the installation positions of the outdoor unit 120 and the indoor units 30a, 30b, 30c, and 30d.
  • the outdoor unit 120 is pre-filled with an amount of refrigerant corresponding to the amount of refrigerant required for the refrigerant circuit 110 when the liquid refrigerant pipes 5a, 5b, 5c, 5d and the gas refrigerant pipe 6 have the first length L1.
  • the outdoor unit 120 is charged with the refrigerant in advance, eliminating the need for on-site charging, thereby maintaining the composition ratio of the non-azeotropic refrigerant mixture.
  • the liquid refrigerant pipes 5a, 5b, 5c, and 5d are preferably 2.5-section pipes (outer diameter 7.93 mm) or more.
  • the diameter of the liquid refrigerant pipes 5a, 5b, 5c, and 5d must be large, and the amount of refrigerant charged increases. The greater the amount of charge, the greater the risk that the composition ratio of the refrigerant will change during on-site charging. Therefore, in this air conditioning device 100, there is a great advantage in pre-charging the outdoor unit 120 with the refrigerant, in terms of maintaining the composition ratio of the non-azeotropic refrigerant.
  • the amount of the non-azeotropic refrigerant mixture pre-filled in the outdoor unit 120 is 2 to 3 times the amount of R32 refrigerant required in the entire refrigerant circuit 110 when a single R32 refrigerant is filled into the refrigerant circuit 110 in which the liquid refrigerant piping 5 and the gas refrigerant piping 6 are set to the first length L1.
  • non-azeotropic refrigerants require a charging amount two to three times that of R32 refrigerant, which has a zero temperature glide, and there is a high risk that the composition ratio of such refrigerants will change when charging on-site. Therefore, in this air conditioning device 100, there is a great advantage in that the composition ratio of the non-azeotropic refrigerant is maintained by charging the outdoor unit 120 with the refrigerant in advance.
  • the ratio of the volume of the outdoor heat exchanger 15 to the total volume of the indoor heat exchangers 35a, 35b, 35c, and 35d is equal to or greater than 3. This allows the amount of refrigerant pre-filled in the outdoor unit 120 to be sufficient for the amount of refrigerant required in the entire refrigerant circuit 110.
  • the high-pressure receiver 21 is connected between the outdoor heat exchanger 15 and the expansion valve 23.
  • the volume ratio of the high-pressure receiver 21 to the outdoor heat exchanger 15 is within a range of 0.04 to 0.6.
  • the amount of refrigerant that can be pre-charged in the outdoor unit 120 can include an amount of refrigerant equivalent to the internal volume of the high-pressure receiver 21.
  • the refrigerant circuit 110 is provided with a liquid-gas heat exchanger 19 that exchanges heat between a high-pressure liquid refrigerant and a low-pressure gas refrigerant.
  • the liquid-gas heat exchanger 19 is a double-pipe heat exchanger.
  • the amount of refrigerant that can be pre-filled into the outdoor unit 120 can include an amount of refrigerant equivalent to the internal volume of the liquid-gas heat exchanger 19.
  • the worker installing the air conditioning apparatus 100 determines whether the lengths of the liquid refrigerant pipes 5a, 5b, 5c, 5d and the gas refrigerant pipe 6 required for the installation work of the air conditioning apparatus 100 are equal to or shorter than the first length L1.
  • the refrigerant additional charging process is not necessary because the amount of refrigerant charged in the outdoor unit 120 is equal to or greater than the required amount of refrigerant. Therefore, the additional refrigerant charging process is not performed, and the outdoor unit 120 and the indoor units 30a, 30b, 30d are connected via the liquid refrigerant pipes 5a, 5b, 5c, 5d and the gas refrigerant pipes 6, and the installation work is completed.
  • the amount of refrigerant filled in the outdoor unit 120 is equal to or greater than the amount of refrigerant required in the refrigerant circuit 110 when the liquid refrigerant pipes 5a, 5b, 5c, and 5d and the gas refrigerant pipe 6 are equal to or shorter than the first length L1.
  • the refrigerant pre-filled in the outdoor unit 120 is insufficient to meet the required amount of refrigerant, so a process of additionally filling the refrigerant is required.
  • a refrigerant additional charging process is performed, and an amount of refrigerant according to the lengths of the liquid refrigerant pipes 5a, 5b, 5c, and 5d and the gas refrigerant pipe 6 is additionally charged into the refrigerant circuit 110.
  • the refrigerant is additionally charged, for example, from the service port of the liquid side shutoff valves 25a, 25b, 25c, and 25d or the gas side shutoff valve 26.
  • Air conditioning device Liquid refrigerant piping (piping) 5a, 5b, 5, 5c Liquid refrigerant piping (piping) 6 Gas refrigerant piping (piping) 10, 110 Refrigerant circuit 11 Compressor 15 Outdoor heat exchanger (heat exchanger) 20, 120 Outdoor unit (heat source unit) 20a, 120a Heat source circuit 21 High pressure receiver 23 Expansion valve (pressure reducer) 24a, 24b, 24c, 24d Second expansion valve (pressure reducer) 25 Liquid side shutoff valve (first shutoff valve) 25a, 25b, 25c, 25d Liquid side shutoff valve (first shutoff valve) 26 Gas side shutoff valve (second shutoff valve) 30 Indoor unit (utilization unit) 30a, 30b, 30c, 30d Indoor units (utilization units) L1 First length

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)

Abstract

L'invention concerne un dispositif de climatisation de type divisé qui réduit le risque d'un changement du rapport de composition d'un mélange de fluide frigorigène non azéotrope au moment de l'installation. Dans un dispositif de climatisation (1), une unité extérieure (20) et une unité intérieure (30) sont reliées par l'intermédiaire d'un tuyau de fluide frigorigène liquide (5) et d'un tuyau de fluide frigorigène gazeux (6) de façon à former un circuit frigorifique (10) au niveau d'un site d'installation. Un fluide frigorigène avec lequel est rempli le circuit frigorifique (10) est un mélange de fluide frigorigène non azéotrope qui présente un glissement de température d'au moins 1 °C pendant l'évaporation et la condensation. La longueur du tuyau de fluide frigorigène liquide (5) et du tuyau de fluide frigorigène gazeux (6) est déterminée en fonction des positions d'installation de l'unité extérieure (20) et de l'unité intérieure (30). Une première longueur (L1), qui rend inutile l'ajout d'un fluide frigorigène au circuit frigorifique (10), est définie à l'avance en tant que longueur du tuyau de fluide frigorigène liquide (5) et du tuyau de fluide frigorigène gazeux (6). L'unité extérieure (20) est remplie à l'avance avec une quantité d'un fluide frigorigène en fonction d'une quantité de fluide frigorigène nécessaire pour le circuit frigorifique (10) lorsque le tuyau de fluide frigorigène liquide (5) et le tuyau de fluide frigorigène gazeux (6) ont la première longueur (L1).
PCT/JP2024/029749 2023-09-07 2024-08-22 Unité de source de chaleur Pending WO2025052936A1 (fr)

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JP2023-145352 2023-09-07
JP2023145352A JP2025038623A (ja) 2023-09-07 2023-09-07 熱源ユニット

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Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2013111180A1 (fr) 2012-01-24 2013-08-01 三菱電機株式会社 Procédé de remplissage en réfrigérant destiné à une unité de climatisation et unité de climatisation
JP2017075760A (ja) * 2015-10-16 2017-04-20 ダイキン工業株式会社 空気調和機
JP2021055958A (ja) * 2019-09-30 2021-04-08 ダイキン工業株式会社 冷凍装置
WO2021106793A1 (fr) * 2019-11-25 2021-06-03 ダイキン工業株式会社 Système à cycle de fluide frigorigène
WO2022244793A1 (fr) * 2021-05-21 2022-11-24 ダイキン工業株式会社 Dispositif à cycle frigorifique

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2002089978A (ja) * 2000-09-11 2002-03-27 Daikin Ind Ltd ペア型の冷凍装置およびマルチ型の冷凍装置
WO2020017522A1 (fr) * 2018-07-17 2020-01-23 ダイキン工業株式会社 Dispositif à cycle de réfrigération

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2013111180A1 (fr) 2012-01-24 2013-08-01 三菱電機株式会社 Procédé de remplissage en réfrigérant destiné à une unité de climatisation et unité de climatisation
JP2017075760A (ja) * 2015-10-16 2017-04-20 ダイキン工業株式会社 空気調和機
JP2021055958A (ja) * 2019-09-30 2021-04-08 ダイキン工業株式会社 冷凍装置
WO2021106793A1 (fr) * 2019-11-25 2021-06-03 ダイキン工業株式会社 Système à cycle de fluide frigorigène
WO2022244793A1 (fr) * 2021-05-21 2022-11-24 ダイキン工業株式会社 Dispositif à cycle frigorifique

Non-Patent Citations (1)

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Title
See also references of EP4545876A4

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