WO2008013093A1 - Conditionneur d'air - Google Patents

Conditionneur d'air Download PDF

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Publication number
WO2008013093A1
WO2008013093A1 PCT/JP2007/064235 JP2007064235W WO2008013093A1 WO 2008013093 A1 WO2008013093 A1 WO 2008013093A1 JP 2007064235 W JP2007064235 W JP 2007064235W WO 2008013093 A1 WO2008013093 A1 WO 2008013093A1
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WO
WIPO (PCT)
Prior art keywords
refrigerant
amount
compressor
temperature
circuit
Prior art date
Application number
PCT/JP2007/064235
Other languages
English (en)
Japanese (ja)
Inventor
Tadafumi Nishimura
Shinichi Kasahara
Manabu Yoshimi
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.
Publication of WO2008013093A1 publication Critical patent/WO2008013093A1/fr

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Classifications

    • C—CHEMISTRY; METALLURGY
    • C09—DYES; PAINTS; POLISHES; NATURAL RESINS; ADHESIVES; COMPOSITIONS NOT OTHERWISE PROVIDED FOR; APPLICATIONS OF MATERIALS NOT OTHERWISE PROVIDED FOR
    • C09K—MATERIALS FOR MISCELLANEOUS APPLICATIONS, NOT PROVIDED FOR ELSEWHERE
    • C09K5/00—Heat-transfer, heat-exchange or heat-storage materials, e.g. refrigerants; Materials for the production of heat or cold by chemical reactions other than by combustion
    • C09K5/02—Materials undergoing a change of physical state when used
    • C09K5/04—Materials undergoing a change of physical state when used the change of state being from liquid to vapour or vice versa
    • C09K5/041—Materials undergoing a change of physical state when used the change of state being from liquid to vapour or vice versa for compression-type refrigeration systems
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/005—Arrangement or mounting of control or safety devices of safety devices
    • C—CHEMISTRY; METALLURGY
    • C10—PETROLEUM, GAS OR COKE INDUSTRIES; TECHNICAL GASES CONTAINING CARBON MONOXIDE; FUELS; LUBRICANTS; PEAT
    • C10N—INDEXING SCHEME ASSOCIATED WITH SUBCLASS C10M RELATING TO LUBRICATING COMPOSITIONS
    • C10N2040/00—Specified use or application for which the lubricating composition is intended
    • C10N2040/30—Refrigerators lubricants or compressors lubricants
    • 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
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
    • F25B2313/02741—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using one four-way valve
    • 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
    • F25B2400/13—Economisers
    • 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
    • F25B2600/21—Refrigerant outlet evaporator temperature
    • 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
    • F25B2700/04—Refrigerant level

Definitions

  • the present invention relates to a function for determining the suitability of the amount of refrigerant in the refrigerant circuit of an air conditioner, in particular, by connecting a compressor, a heat source side heat exchanger ⁇ , an expansion mechanism, and a user side heat exchanger.
  • the present invention relates to a function of determining whether or not the amount of refrigerant in a refrigerant circuit of an air conditioner configured is appropriate.
  • Patent Document 1 Japanese Patent Laid-Open No. 2000-304388
  • the inventor of the present application uses a relational expression between the refrigerant amount of each part and the operating state quantity of the refrigerant or component equipment flowing through the refrigerant circuit when the refrigerant circuit is divided into a plurality of parts, and A method of calculating the refrigerant amount of each part from the refrigerant flowing through the circuit or the operating state quantity of the component equipment, and using the refrigerant amount of each part obtained by this calculation to determine the suitability of the refrigerant quantity in the refrigerant circuit
  • the suitability of the refrigerant amount in the refrigerant circuit can be determined with high accuracy while suppressing the calculation load (see # 112005-363732).
  • the amount of refrigerant dissolved in the refrigerating machine oil In particular, it is necessary to ascertain as accurately as possible the amount of refrigerant dissolved in the refrigerating machine oil accumulated in the oil reservoir inside the compressor and reflect it in the calculation of the refrigerant amount. In order to accurately grasp the amount of refrigerant dissolved in the refrigerating machine oil accumulated in such an oil reservoir, the oil reservoir It is necessary to detect the pressure and temperature of the accumulated refrigeration oil and use it to calculate the solubility of the refrigerant in the refrigeration oil.
  • the refrigerating machine oil accumulated in the oil reservoir inside the compressor has a temperature distribution in the refrigerating machine oil due to the temperature of the refrigerant in contact with the refrigerating machine oil and the temperature of the wall of the compressor casing that forms the oil reservoir. It is difficult to detect the exact temperature of the refrigerating machine oil accumulated in the oil reservoir, resulting in a large calculation error in the solubility of the refrigerant in the refrigerating machine oil accumulated in the oil reservoir. In particular, it is not possible to improve the accuracy of determining the appropriateness of the refrigerant amount. In order to solve such problems, it may be possible to provide a large number of temperature sensors inside the compressor to accurately detect the temperature of the refrigeration oil. However, the cost increases due to additional calories from the sensors. It will be.
  • An object of the present invention is to accurately grasp the amount of refrigerant inside the compressor without adding sensors inside the compressor and to determine whether the amount of refrigerant in the refrigerant circuit is appropriate or not with high accuracy. .
  • An air conditioner includes a refrigerant circuit configured by connecting a compressor, a heat source side heat exchange, an expansion mechanism, and a utilization side heat exchanger, and a refrigerant or a configuration flowing through the refrigerant circuit.
  • a refrigerant amount determining means for determining whether or not the refrigerant amount in the refrigerant circuit is appropriate based on the operating state quantity of the device, and the refrigerant circuit is weakly compatible or incompatible with the refrigerant together with the refrigerant. Refrigerating machine oil is enclosed.
  • the air conditioner according to the first invention uses an HFC refrigerant as the refrigerant and an alkylbenzene oil or mineral oil as the refrigerating machine oil.
  • An air conditioner according to a third invention is the air conditioner according to the second invention, wherein R41OA is used as a refrigerant.
  • the air conditioner according to the fourth invention uses the R407C as a refrigerant in the air conditioner according to the second invention.
  • the air conditioner according to the fifth invention uses the Rl 34a as a refrigerant in the air conditioner according to the second invention!
  • An air conditioner according to a sixth aspect of the present invention is the air conditioner according to any of the first to fifth aspects of the present invention, based on the refrigerant flowing through the refrigerant circuit or the operating state quantity of the component equipment.
  • Refrigerant amount calculating means for calculating the amount of refrigerant in the refrigerant circuit including the amount of dissolved refrigerant that is the amount of refrigerant dissolved in the refrigerating machine oil is further provided.
  • the refrigerant amount determination means determines whether or not the refrigerant amount in the refrigerant circuit is appropriate based on the refrigerant amount calculated by the refrigerant amount calculation means.
  • FIG. 1 is a schematic configuration diagram of an air conditioner according to an embodiment of the present invention.
  • FIG. 2 is a schematic longitudinal sectional view of a compressor.
  • FIG. 3 is a control block diagram of the air conditioner.
  • FIG. 4 is a flowchart of a test operation mode.
  • FIG. 5 is a flowchart of an automatic refrigerant charging operation.
  • FIG. 6 is a schematic diagram showing the state of refrigerant flowing in the refrigerant circuit in the refrigerant quantity determination operation (illustration of a four-way switching valve and the like is omitted).
  • FIG. 7 is a flowchart of a pipe volume determination operation.
  • FIG. 8 is a Mollier diagram showing the refrigeration cycle of the air conditioner in the pipe volume judgment operation for the liquid refrigerant communication pipe.
  • FIG. 9 is a Mollier diagram showing the refrigeration cycle of the air conditioner in the pipe volume judgment operation for the gas refrigerant communication pipe.
  • FIG. 10 is a flowchart of an initial refrigerant quantity determination operation.
  • FIG. 11 is a flowchart of a refrigerant leak detection operation mode.
  • FIG. 1 is a schematic configuration diagram of an air-conditioning apparatus 1 according to one embodiment of the present invention.
  • air The harmony device 1 is a device used for air conditioning in a building or the like by performing a vapor compression refrigeration cycle operation.
  • the air conditioner 1 mainly includes an outdoor unit 2 as a single heat source unit, and indoor units 4 and 5 as a plurality of (two in this embodiment) usage units connected in parallel to the outdoor unit 2.
  • the liquid refrigerant communication pipe 6 and the gas refrigerant communication pipe 7 are provided as refrigerant communication pipes connecting the outdoor unit 2 and the indoor units 4 and 5.
  • the outdoor unit 2 the indoor units 4, 5, the liquid refrigerant communication pipe 6 and the gas refrigerant communication pipe 7 are connected. It is constituted by.
  • an HFC refrigerant such as R407C, R410A, or R134a is sealed in the refrigerant circuit 10 as a refrigerant.
  • the indoor units 4 and 5 are installed by being embedded or suspended in the ceiling of a room such as a building or by hanging on the wall surface of the room.
  • the indoor units 4 and 5 are connected to the outdoor unit 2 via the liquid refrigerant communication pipe 6 and the gas refrigerant communication pipe 7 and constitute a part of the refrigerant circuit 10.
  • the configuration of the indoor units 4 and 5 will be described. Since the indoor unit 4 and the indoor unit 5 have the same configuration, only the configuration of the indoor unit 4 will be described here, and the configuration of the indoor unit 5 indicates each part of the indoor unit 4 respectively. Instead of the 40's code, the 50's code is used, and the description of each part is omitted.
  • the indoor unit 4 mainly includes an indoor refrigerant circuit 10a (in the indoor unit 5, the indoor refrigerant circuit 10b) that constitutes a part of the refrigerant circuit 10.
  • the indoor refrigerant circuit 10a mainly has an indoor expansion valve 41 as an expansion mechanism and an indoor heat exchange 42 as a use side heat exchanger.
  • the indoor expansion valve 41 is an electric expansion valve connected to the liquid side of the indoor heat exchanger 42 in order to adjust the flow rate of the refrigerant flowing in the indoor refrigerant circuit 10a.
  • the indoor heat exchange is a cross-fin type fin 'and' tube heat exchanger composed of heat transfer tubes and a large number of fins. It is a heat exchanger that functions as an evaporator and cools the room air, and functions as a refrigerant condenser during heating operation to heat the room air.
  • the indoor unit 4 sucks indoor air into the unit, exchanges heat with the refrigerant in the indoor heat exchanger 42, and then supplies the indoor fan 43 as a blower fan to be supplied indoors as supply air.
  • the indoor fan 43 is a fan capable of changing the air volume Wr of air supplied to the indoor heat exchanger 42, and in this embodiment, the centrifugal fan or the multiblade fan driven by the motor 43a that also has DC fan motor power.
  • the indoor unit 4 is provided with various sensors. On the liquid side of the indoor heat exchanger 42, a liquid side temperature sensor 44 that detects the temperature of the refrigerant (that is, the refrigerant temperature corresponding to the condensation temperature Tc during heating operation or the evaporation temperature Te during cooling operation) is provided. ing. A gas side temperature sensor 45 for detecting the refrigerant temperature Teo is provided on the gas side of the indoor heat exchanger 42. An indoor temperature sensor 46 for detecting the temperature of indoor air flowing into the unit (that is, the indoor temperature Tr) is provided on the indoor air inlet side of the indoor unit 4.
  • the liquid side temperature sensor 44, the gas side temperature sensor 45, and the room temperature sensor 46 are composed of thermistors.
  • the indoor unit 4 also has an indoor side control unit 47 that controls the operation of each part constituting the indoor unit 4.
  • the indoor control unit 47 includes a microcomputer, a memory, and the like provided for controlling the indoor unit 4, and a remote controller (not shown) for individually operating the indoor unit 4. Control signals etc. can be exchanged with the outdoor unit 2 and control signals etc. can be exchanged with the outdoor unit 2 via the transmission line 8a.
  • the outdoor unit 2 is installed outside a building or the like, and is connected to the indoor units 4 and 5 via the liquid refrigerant communication pipe 6 and the gas refrigerant communication pipe 7. Circuit 10 is configured.
  • the outdoor unit 2 mainly has an outdoor refrigerant circuit 10c that constitutes a part of the refrigerant circuit 10.
  • This outdoor refrigerant circuit 10c mainly includes the compressor 21, the four-way switching valve 22, and the outdoor heat exchange as heat source side heat exchange. 23, an outdoor expansion valve 38 as an expansion mechanism, an accumulator 24, a supercooler 25 as a temperature adjustment mechanism, a liquid side closing valve 26, and a gas side closing valve 27.
  • the compressor 21 is a compressor whose operating capacity can be varied.
  • the compressor 21 is a capacity type compressor driven by a compressor motor 73 whose rotation speed Rm is controlled by an inverter.
  • the number of the compressors 21 is only one, but is not limited to this, and two or more compressors may be connected in parallel according to the number of indoor units connected.
  • FIG. 2 is a schematic longitudinal sectional view of the compressor 21.
  • the compressor 21 is a hermetic compressor in which a compression element 72 and a compressor motor 73 are incorporated in a compressor casing 71 that is a vertical cylindrical container.
  • the compressor casing 71 has a substantially cylindrical body plate 71a, an upper end plate 71b welded and fixed to the upper end of the body plate 71a, and a lower end plate 71c welded and fixed to the lower end of the body plate 71a. .
  • a compression element 72 is mainly disposed at the upper part, and a compressor motor 73 is disposed below the compression element 72.
  • the compression element 72 and the compressor motor 73 are connected by a shaft 74 arranged so as to extend in the up-down direction within the compressor casing 71.
  • the compressor casing 71 is provided with a suction pipe 81 so as to penetrate the upper end plate 71b, and a discharge pipe 82 is provided so as to penetrate the body plate 71a.
  • the compression element 72 is a mechanism for compressing the refrigerant therein.
  • a scroll-type compression element is adopted, and a compressor casing 71 is formed through a suction pipe 81 in the upper part thereof.
  • a suction port 72a for sucking in the low-pressure refrigerant flowing in is formed, and a discharge port 72b for discharging the compressed high-pressure refrigerant is formed in the lower part.
  • a space such as a flow path from the suction pipe 81 to the suction port 72a is a low-pressure space Q1 into which a low-pressure refrigerant flows.
  • the space in the compressor casing 71 where the discharge pipe 82 on the lower side of the compression element 72 communicates is a high-pressure space Q2 into which high-pressure refrigerant flows through the discharge port 72b of the compression element 72.
  • the lower part of the high-pressure space Q2 is necessary for lubrication in the compressor 21 (particularly, the compression element 72).
  • An oil reservoir 71d for storing the refrigerator oil is formed.
  • the refrigerating machine oil an alkylbenzene oil or mineral oil that is weakly compatible or incompatible with the HFC refrigerant is used.
  • the compression element 72 is not limited to the scroll type compression element as in the present embodiment, and various types of compression elements such as a rotary type can be used.
  • the shaft 74 is formed with an oil passage 74a that opens to the oil reservoir 71d and communicates with the inside of the compression element 72. Refrigerating machine oil collected in the oil reservoir 71d is formed at the lower end of the oil passage 74a. Is provided with a pump element 74b for supplying the pressure to the compression element 72.
  • the compressor motor 73 is disposed in the high-pressure space Q2 below the compression element 72, and an annular stator 73a fixed to the inner surface of the compressor casing 71 and a slight gap on the inner peripheral side of the stator 73a. And a rotor 73b accommodated in a freely rotatable manner.
  • the compressor 21 having such a configuration, when the compressor motor 73 is driven, low-pressure refrigerant flows into the compressor casing 71 through the suction pipe 81 and the low-pressure space Q1, and is compressed by the compression element 72 to be high-pressure. Then, the refrigerant flows out from the high-pressure space Q2 of the compressor casing 71 through the discharge pipe 82.
  • the high-pressure refrigerant that has flowed into the high-pressure space Q2 from the discharge port 72b of the compression element 72 is mainly stored in the oil reservoir as shown by the arrow drawn with a two-dot chain line in FIG.
  • Refrigerator accumulated in the section 71d flows so as to come into contact with the oil upper surface, and then rises through the gap between the stator 73a and the rotor 73b between the compressor motor 73 and the compressor casing 71 and passes through the discharge pipe 82. It will flow out of the high pressure space Q2.
  • the refrigerating machine oil accumulated in the oil reservoir 71d is in contact with the refrigerant on its upper surface, so that the refrigerating machine oil near the upper oil surface approaches the temperature of the refrigerant, and the compressor casing forming the oil reservoir 71d Since the refrigeration oil near the wall surface of the lower part of 71 (mainly lower end plate 71c) approaches the temperature of the wall surface, that is, the ambient temperature outside the compressor 21, the refrigeration oil accumulated in the oil sump 71d A temperature distribution corresponding to the temperature difference between the temperature of the refrigerant in contact with the oil upper surface of the portion 71d and the ambient temperature outside the compressor 21 is generated.
  • the refrigerant in contact with the oil upper surface of the oil reservoir 71d is a high-pressure refrigerant that has become hot as it is compressed by the compression element 72, and is higher than the temperature of the indoor air or the temperature of the outdoor air.
  • the temperature outside the compressor 21 The temperature difference from the ambient temperature tends to increase. That is, the air conditioner 1 of the present embodiment is configured such that the temperature difference between the refrigerating machine oil accumulated in the oil reservoir 71d inside the compressor 21 and the refrigerant in contact with the refrigerating machine oil increases.
  • the temperature distribution of the refrigerating machine oil accumulated in the oil reservoir 71 d inside the compressor 21 is likely to occur.
  • the four-way switching valve 22 is a valve for switching the flow direction of the refrigerant.
  • the outdoor heat exchanger 23 serves as a refrigerant condenser compressed by the compressor 21, and the indoor
  • the heat exchangers 42 and 52 to function as an evaporator for the refrigerant condensed in the outdoor heat exchanger 23
  • the discharge side of the compressor 21 and the gas side of the outdoor heat exchanger 23 are connected and the suction side of the compressor 21 ( Specifically, the accumulator 24) and the gas refrigerant communication pipe 7 side are connected (see the solid line of the four-way selector valve 22 in Fig. 1), and the indoor heat exchangers 42 and 52 are connected to the compressor 21 during heating operation.
  • the discharge side of the compressor 21 and the gas refrigerant communication pipe 7 side and the suction side of the compressor 21 and the gas side of the outdoor heat exchange Can be connected (see the dashed line of the four-way selector valve 22 in FIG. 1).
  • the outdoor heat exchange is a cross-fin type fin 'and' tube heat exchanger composed of heat transfer tubes and a large number of fins, and functions as a refrigerant condenser during cooling operation. This is heat exchange that functions as a refrigerant evaporator during heating operation.
  • the outdoor heat exchanger 23 has a gas side connected to the four-way switching valve 22 and a liquid side connected to the liquid coolant communication pipe 6.
  • the outdoor expansion valve 38 is an electric expansion valve connected to the liquid side of the outdoor heat exchanger 23 in order to adjust the pressure and flow rate of the refrigerant flowing in the outdoor refrigerant circuit 10c.
  • the outdoor unit 2 has an outdoor fan 28 as a blower fan for sucking outdoor air into the unit, exchanging heat with the refrigerant in the outdoor heat exchanger 23, and then discharging the air outside.
  • the outdoor fan 28 is a fan capable of changing the air volume Wo of the air supplied to the outdoor heat exchanger ⁇ 23.
  • the outdoor fan 28 is a propeller fan or the like driven by a motor 28a having a DC fan motor power. is there.
  • the accumulator 24 is connected between the four-way switching valve 22 and the compressor 21, and removes excess refrigerant generated in the refrigerant circuit 10 in accordance with fluctuations in the operating load of the indoor units 4 and 5. It is a container that can be stored.
  • the subcooler 25 is a double-pipe heat exchanger, and is provided to cool the refrigerant sent to the indoor expansion valves 41 and 51 after being condensed in the outdoor heat exchanger 23. ing.
  • the supercooler 25 is connected between the outdoor expansion valve 38 and the liquid side closing valve 26.
  • a bypass refrigerant circuit 61 as a cooling source for the subcooler 25 is provided.
  • the part excluding the bypass refrigerant circuit 61 from the refrigerant circuit 10 will be referred to as a main refrigerant circuit for convenience.
  • the bypass refrigerant circuit 61 is provided in the main refrigerant circuit so that a part of the refrigerant sent from the outdoor heat exchanger 23 to the indoor expansion valves 41, 51 is branched from the main refrigerant circuit and returned to the suction side of the compressor 21. It is connected. Specifically, the bypass refrigerant circuit 61 connects a part of the refrigerant sent from the outdoor expansion valve 38 to the indoor expansion valves 41 and 51 so that the positional force between the outdoor heat exchanger and the subcooler 25 also branches. And the junction circuit 61b connected to the suction side of the compressor 21 so as to return to the suction side of the compressor 21 from the outlet of the bypass refrigerant circuit side of the subcooler 25. .
  • the branch circuit 61a is provided with a bypass expansion valve 62 for adjusting the flow rate of the refrigerant flowing through the bypass refrigerant circuit 61.
  • the bypass expansion valve 62 also has an electric expansion valve force.
  • the refrigerant sent from the outdoor heat exchanger 23 to the indoor expansion valves 41 and 51 is cooled by the refrigerant flowing in the bypass refrigerant circuit 61 after being depressurized by the no-pass expansion valve 62 in the supercooler 25. That is, the capacity control of the subcooler 25 is performed by adjusting the opening degree of the bypass expansion valve 62.
  • the liquid side shut-off valve 26 and the gas side shut-off valve 27 are valves provided at connection ports with external devices and pipes (specifically, the liquid refrigerant communication pipe 6 and the gas refrigerant communication pipe 7). .
  • the liquid side closing valve 26 is connected to the outdoor heat exchanger 23.
  • the gas side closing valve 27 is connected to the four-way switching valve 22.
  • the outdoor unit 2 is provided with various sensors. Specifically, the outdoor unit 2 includes a suction pressure sensor 29 that detects the suction pressure Ps of the compressor 21, and a compressor 21. A discharge pressure sensor 30 for detecting the discharge pressure Pd, a suction temperature sensor 31 for detecting the suction temperature Ts of the compressor 21, and a discharge temperature sensor 32 for detecting the discharge temperature Td of the compressor 21 are provided. The suction temperature sensor 31 is provided at a position between the accumulator 24 and the compressor 21.
  • the outdoor heat exchanger 23 includes a heat exchange temperature sensor that detects the temperature of the refrigerant flowing in the outdoor heat exchanger 23 (that is, the refrigerant temperature corresponding to the condensation temperature Tc during the cooling operation or the evaporation temperature Te during the heating operation).
  • a liquid side temperature sensor 34 for detecting the temperature Tco of the refrigerant is provided on the liquid side of the outdoor heat exchanger 23 .
  • a liquid pipe temperature sensor 35 that detects the temperature of the refrigerant (that is, the liquid pipe temperature Tip) is provided at the outlet of the subcooler 25 on the main refrigerant circuit side.
  • the junction circuit 6 lb of the no-pass refrigerant circuit 61 is provided with a bypass temperature sensor 63 for detecting the temperature of the refrigerant flowing through the outlet of the subcooler 25 on the bypass refrigerant circuit side.
  • An outdoor temperature sensor 36 for detecting the temperature of the outdoor air flowing into the unit (that is, the outdoor temperature Ta) is provided on the outdoor air inlet side of the outdoor unit 2.
  • the suction temperature sensor 31, the discharge temperature sensor 32, the heat exchange temperature sensor 33, the liquid side temperature sensor 34, the liquid pipe temperature sensor 35, the outdoor temperature sensor 36, and the binos temperature sensor 63 are composed of thermistors.
  • the outdoor unit 2 also has an outdoor control unit 37 that controls the operation of each part constituting the outdoor unit 2.
  • the outdoor control unit 37 includes a microcomputer provided to control the outdoor unit 2, an inverter circuit that controls the memory and the compressor motor 73, and the like. Control signals can be exchanged with the control units 47 and 57 via the transmission line 8a. That is, the indoor side control units 47 and 57, the outdoor side control unit 37, and the transmission line 8a that connects the control units 37, 47, and 57 constitute the control unit 8 that controls the operation of the entire air conditioner 1. Yes.
  • FIG. 3 is a control block diagram of the air conditioner 1. ⁇ Refrigerant piping>
  • Refrigerant communication pipes 6 and 7 are refrigerant pipes that are installed on site when the air conditioner 1 is installed in a building or other location, such as a combination of the installation location or outdoor unit and indoor unit. Depending on the installation conditions, those having various lengths and pipe diameters are used. For this reason, for example, when a new air conditioner is installed, it is necessary to accurately grasp information such as the length of the refrigerant communication pipes 6 and 7 in order to calculate the additional refrigerant charging amount. Although there is information management, the calculation of the refrigerant amount itself is complicated. In addition, when the existing unit is used to update the indoor unit or the outdoor unit, the blueprints such as the length and diameter of the refrigerant communication pipes 6 and 7 may be lost.
  • the indoor side refrigerant circuits 10a and 10b, the outdoor side refrigerant circuit 10c, and the refrigerant communication pipes 6 and 7 are connected to constitute the refrigerant circuit 10 of the air conditioner 1.
  • the refrigerant circuit 10 can be paraphrased as being composed of a bypass refrigerant circuit 61 and a main refrigerant circuit excluding the bypass refrigerant circuit 61.
  • the air conditioner 1 according to the present embodiment is operated by switching the cooling operation and the heating operation by the four-way switching valve 22 by the control unit 8 including the indoor side control units 47 and 57 and the outdoor side control unit 37.
  • the outdoor unit 2 and the indoor units 4 and 5 are controlled according to the operation load of the indoor units 4 and 5.
  • the normal operation mode for controlling the components of the outdoor unit 2 and the indoor units 4 and 5 according to the operation load of the indoor units 4 and 5 is performed.
  • installation of the components and components of the air conditioner 1 specifically, not limited to after the initial installation of the device, for example, after remodeling such as adding or removing components such as indoor units, or failure of the device
  • the normal operation mode mainly includes a cooling operation for cooling the room and a heating operation for heating the room.
  • the refrigerant automatic charging that mainly fills the refrigerant in the refrigerant circuit 10 is performed.
  • Filling operation, piping volume determination operation for detecting the volume of the refrigerant communication pipes 6 and 7, and initial refrigerant amount detection operation for detecting the initial refrigerant amount after the components are installed or the refrigerant circuit is filled with the refrigerant. Is included.
  • the four-way switching valve 22 is in the state indicated by the solid line in FIG. 1, that is, the discharge side of the compressor 21 is the outdoor heat. It is connected to the gas side of the exchanger 23, and the suction side of the compressor 21 is connected to the gas side of the indoor heat exchangers 42 and 52 via the gas side closing valve 27 and the gas refrigerant communication pipe 7. Yes.
  • the outdoor expansion valve 38 is fully opened.
  • the liquid side closing valve 26 and the gas side closing valve 27 are in an open state.
  • the indoor expansion valves 41 and 51 are opened so that the superheat degree SHr of the refrigerant at the outlets of the indoor heat exchangers 42 and 52 (that is, the gas side of the indoor heat exchangers 42 and 52) is constant at the superheat degree target value SHrs.
  • the degree is adjusted! /
  • the degree of superheat SHr of the refrigerant at the outlets of the indoor heat exchangers 42, 52 is the refrigerant temperature value detected by the gas side temperature sensors 45, 55, and the refrigerant temperature sensors 44, 54 also detect the refrigerant temperature value force.
  • a temperature sensor for detecting the temperature of the refrigerant flowing in each of the indoor heat exchangers 42 and 52 is provided and corresponds to the evaporation temperature Te detected by this temperature sensor.
  • the superheat degree SHr of the refrigerant at the outlet of each indoor heat exchanger 42 and 52 is detected. Also good. Further, the bypass expansion valve 62 is adjusted in opening degree so that the superheat degree SHb of the refrigerant at the outlet on the bypass refrigerant circuit side of the supercooler 25 becomes the superheat degree target value SHbs.
  • the output of the bypass refrigerant circuit side of the subcooler 25 is
  • the refrigerant superheat degree SHb at the outlet is obtained by converting the suction pressure Ps of the compressor 21 detected by the suction pressure sensor 29 into a saturation temperature value corresponding to the evaporation temperature Te, and calculating from the refrigerant temperature value detected by the bypass temperature sensor 63. It is detected by subtracting the saturation temperature value of this refrigerant.
  • a temperature sensor is provided at the bypass refrigerant circuit side inlet of the subcooler 25, and the refrigerant temperature value detected by this temperature sensor is detected by the bypass temperature sensor 63.
  • the refrigerant superheat degree SHb at the outlet of the subcooler 25 on the bypass refrigerant circuit side may be detected by subtracting the refrigerant temperature value.
  • a part of the high-pressure liquid refrigerant condensed in the outdoor heat exchange is branched to the bypass refrigerant circuit 61, decompressed by the bypass expansion valve 62, and then returned to the suction side of the compressor 21.
  • a part of the refrigerant passing through the binos expansion valve 62 is evaporated by being reduced to near the suction pressure Ps of the compressor 21.
  • the refrigerant flowing in the direction of the outlet force of the bypass expansion valve 62 of the bypass refrigerant circuit 61 toward the suction side of the compressor 21 passes through the subcooler 25 and from the outdoor heat exchanger 23 on the main refrigerant circuit side. Exchanges heat with high-pressure liquid refrigerant sent to indoor units 4 and 5.
  • the high-pressure liquid refrigerant in a supercooled state is sent to the indoor units 4 and 5 via the liquid-side closing valve 26 and the liquid refrigerant communication pipe 6.
  • the high-pressure liquid refrigerant sent to the indoor units 4 and 5 is decompressed to near the suction pressure Ps of the compressor 21 by the indoor expansion valves 41 and 51 to become a low-pressure gas-liquid two-phase refrigerant and exchanges heat in the room.
  • the heat is exchanged with the indoor air in the indoor heat exchangers 42 and 52 to evaporate and become low-pressure gas refrigerant.
  • This low-pressure gas refrigerant is sent to the outdoor unit 2 via the gas refrigerant communication pipe 7 and flows into the accumulator 24 via the gas side closing valve 27 and the four-way switching valve 22. And The low-pressure gas refrigerant flowing into the accumulator 24 is again sucked into the compressor 21. (Heating operation)
  • the four-way switching valve 22 is in the state indicated by the broken line in FIG. 1, that is, the discharge side of the compressor 21 is connected to the indoor heat exchanger 42 via the gas-side closing valve 27 and the gas refrigerant communication pipe 7. 52, and the suction side of the compressor 21 is connected to the gas side of the outdoor heat exchanger 23.
  • the degree of opening of the outdoor expansion valve 38 is adjusted to reduce the pressure of the refrigerant flowing into the outdoor heat exchanger 23 to a pressure at which the refrigerant can be evaporated in the outdoor heat exchanger (that is, the evaporation pressure Pe). Further, the liquid side closing valve 26 and the gas side closing valve 27 are opened.
  • the indoor expansion valves 41 and 51 are adjusted in opening degree so that the supercooling degree SCr of the refrigerant at the outlets of the indoor heat exchangers 42 and 52 becomes constant at the supercooling degree target value SCrs.
  • the degree of refrigerant supercooling SCr at the outlets of the indoor heat exchangers 42 and 52 is the saturation temperature value corresponding to the condensation temperature Tc, which is the discharge pressure Pd of the compressor 21 detected by the discharge pressure sensor 30.
  • the refrigerant temperature value is detected by subtracting the refrigerant temperature value detected by the liquid side temperature sensors 44 and 54 from the saturation temperature value of the refrigerant.
  • a temperature sensor that detects the temperature of the refrigerant flowing in each indoor heat exchanger 42, 52 is provided, and the refrigerant corresponding to the condensation temperature Tc detected by this temperature sensor.
  • the subcooling degree SCr of the refrigerant at the outlets of the indoor heat exchangers 42, 52 may be detected by subtracting the temperature value from the refrigerant temperature value detected by the liquid side temperature sensors 44, 54. Further, the bypass expansion valve 62 is closed.
  • the high-pressure gas refrigerant sent to the indoor units 4 and 5 is condensed by exchanging heat with the indoor air in the outdoor heat exchangers ⁇ 42 and 52 to become a high-pressure liquid refrigerant.
  • the pressure is reduced according to the opening degree of the indoor expansion valves 41 and 51.
  • the refrigerant that has passed through the indoor expansion valves 41 and 51 passes through the liquid refrigerant communication pipe 6 to the outdoor unit.
  • the pressure is further reduced via the liquid side closing valve 26, the supercooler 25 and the outdoor expansion valve 38, and then flows into the outdoor heat exchanger 23.
  • the low-pressure gas-liquid two-phase refrigerant flowing into the outdoor heat exchanger 23 exchanges heat with the outdoor air supplied by the outdoor fan 28 to evaporate into a low-pressure gas refrigerant.
  • control unit 8 (more specifically, the indoor side control units 47, 57 functioning as normal operation control means for performing normal operation including cooling operation and heating operation. And the transmission line 8a) connecting the outdoor control unit 37 and the control units 37, 47, and 57.
  • Fig. 4 is a flowchart of the test operation mode.
  • the test operation mode first, the automatic refrigerant charging operation in step S1 is performed, then the pipe volume determination operation in step S2 is performed, and further, the initial refrigerant amount detection operation in step S3 is performed. .
  • the outdoor unit 2 pre-filled with the refrigerant and the indoor units 4 and 5 are installed at a place such as a building and connected via the liquid refrigerant communication pipe 6 and the gas refrigerant communication pipe 7.
  • a place such as a building and connected via the liquid refrigerant communication pipe 6 and the gas refrigerant communication pipe 7.
  • the refrigerant circuit 10 is additionally filled with a refrigerant that is insufficient in accordance with the volume of the liquid refrigerant communication pipe 6 and the gas refrigerant communication pipe 7.
  • Step S1 Refrigerant automatic charging operation
  • the liquid side shutoff valve 26 and the gas side shutoff valve 27 of the outdoor unit 2 are opened, and the refrigerant circuit 10 is filled with the refrigerant filled in the outdoor unit 2 in advance.
  • FIG. 5 is a flowchart of the automatic refrigerant charging operation. (Step S11: Refrigerant amount judgment operation)
  • the refrigerant circuit 10 When an instruction to start the automatic refrigerant charging operation is made, the refrigerant circuit 10 is in a state where the four-way switching valve 22 of the outdoor unit 2 is shown by a solid line in FIG. 1 and the indoor expansion valves 41 of the indoor units 4 and 5 51 and outdoor expansion valve 38 are opened, compressor 21, outdoor fan 28 and indoor fans 4 3, 53 are activated, and all indoor units 4, 5 are forcibly cooled (hereinafter referred to as the total number of indoor units). Driving).
  • the high-pressure gas refrigerant compressed and discharged by the compressor 21 is disposed in the flow path from the compressor 21 to the outdoor heat exchange functioning as a condenser.
  • the outdoor heat exchanger 23 that functions as a condenser is in a gas state by heat exchange with the outdoor air.
  • the high-pressure refrigerant that changes phase from liquid to liquid flows (see the hatched and black hatched parts in Fig.
  • FIG. 6 is a schematic diagram showing the state of the refrigerant flowing in the refrigerant circuit 10 in the refrigerant quantity determination operation (illustration of the four-way switching valve 22 and the like is omitted).
  • the following device control is performed to reduce the state of the refrigerant circulating in the refrigerant circuit 10. Shift to the operation to be fixed. Specifically, the indoor expansion valves 41 and 51 are controlled so that the superheat degree SHr of the indoor heat exchangers 42 and 52 functioning as an evaporator becomes constant (hereinafter referred to as superheat degree control). The operation capacity of the compressor 21 is controlled so as to be constant (hereinafter referred to as evaporation pressure control), and the outdoor fan 28 is used for outdoor heat exchange so that the refrigerant condensation pressure Pc in the outdoor heat exchanger 23 is constant.
  • evaporation pressure control the outdoor fan 28 is used for outdoor heat exchange so that the refrigerant condensation pressure Pc in the outdoor heat exchanger 23 is constant.
  • the subcooler is controlled so that the air volume Wo of the outdoor air supplied to the cooler 23 is controlled (hereinafter referred to as condensing pressure control) so that the temperature of the refrigerant sent from the supercooler 25 to the indoor expansion valves 41 and 51 is constant.
  • the indoor fan 43, 53 controls the indoor heat exchanger 42 so that the refrigerant evaporating pressure Pe is controlled stably by the above evaporating pressure control.
  • the air volume Wr of the indoor air supplied to No. 52 is kept constant.
  • the evaporation pressure is controlled by the low-pressure refrigerant in the indoor heat exchangers 42 and 52 functioning as an evaporator while changing phase to a gas-liquid two-phase state gas state by heat exchange with room air.
  • Flowing indoor heat exchange ⁇ 42, 52 (Refer to the part corresponding to the indoor heat exchangers 42, 52 in the latticed hatching and hatching hatched parts in Fig. 6; This is because the amount of refrigerant in (1) greatly affects the evaporation pressure Pe of the refrigerant.
  • the evaporation pressure Pe of the refrigerant in the indoor heat exchangers 42 and 52 is kept constant, and the evaporation The state of the refrigerant flowing in the vessel part C is stabilized, and a state in which the amount of refrigerant in the evaporator C is changed mainly by the evaporation pressure Pe is created.
  • the refrigerant temperature value (corresponding to the evaporation temperature Te) detected by the liquid side temperature sensors 44, 54 of the indoor heat exchangers 42, 52 is the saturation pressure.
  • the operating capacity of the compressor 21 is controlled so that the pressure value becomes constant at the low pressure target value Pes (that is, control for changing the rotational speed Rm of the compressor motor 73 is performed). This is realized by increasing or decreasing the refrigerant circulation amount Wc flowing in the refrigerant circuit 10.
  • the suction of the compressor 21 detected by the suction pressure sensor 29, which is an operation state quantity equivalent to the refrigerant pressure at the refrigerant evaporating pressure Pe in the indoor heat exchangers 42 and 52
  • the pressure Ps is constant at the low pressure target value Pes, or the saturation temperature value (corresponding to the evaporation temperature Te) corresponding to the suction pressure Ps is the low pressure target value T.
  • the operating capacity of the compressor 21 may be controlled to be constant at es, or the refrigerant temperature value detected by the liquid side temperature sensors 44 and 54 of the indoor heat exchangers 42 and 52 (corresponding to the evaporation temperature Te) However, the operating capacity of the compressor 21 may be controlled so that it is constant at the low pressure target value Tes.
  • the refrigerant refrigerant pipe including the gas refrigerant communication pipe 7 and the accumulator 24 from the indoor heat exchangers 42, 52 to the compressor 21 (the hatched lines in FIG. 6).
  • the state of the refrigerant flowing through the indoor heat exchangers 42 and 52 to the compressor 21 (hereinafter referred to as the gas refrigerant circulation section D) is stable and mainly the gas refrigerant circulation section D.
  • a state is created in which the amount of refrigerant in the gas refrigerant circulation portion D is changed by the evaporating pressure Pe (ie, the suction pressure Ps), which is an operation state amount equivalent to the refrigerant pressure at.
  • Condensation pressure control is performed in the outdoor heat exchanger ⁇ 23 in which high-pressure refrigerant flows while the gas state force changes to a liquid state due to heat exchange with the outdoor air (hatched hatched and blacked out in Fig. 6).
  • the condenser portion A which is also the force that greatly affects the refrigerant condensing pressure Pc. Since the refrigerant condensing pressure Pc in the condenser part A changes greatly due to the influence of the outdoor temperature Ta, the air volume Wo of the indoor air supplied from the outdoor fan 28 to the outdoor heat exchanger 23 is controlled by the motor 28a.
  • the condensation pressure Pc of the refrigerant in the outdoor heat exchanger 23 is made constant, and the state of the refrigerant flowing in the condenser section A is stabilized, and mainly the liquid side of the outdoor heat exchanger 23 (hereinafter referred to as the refrigerant).
  • the refrigerant amount in the condenser A is changed by the degree of supercooling SCo at the outlet of the outdoor heat exchanger 23).
  • the compressor 21 detected by the discharge pressure sensor 30 which is an operation state amount equivalent to the refrigerant condensation pressure Pc in the outdoor heat exchanger 23 is used.
  • the discharge pressure Pd or the temperature of the refrigerant flowing in the outdoor heat exchanger 23 detected by the heat exchange temperature sensor 33 that is, the condensation temperature Tc is used.
  • the outdoor expansion valve 38 from the outdoor heat exchange to the indoor expansion valves 41, 51, the main refrigerant circuit side portion of the subcooler 25, and the liquid refrigerant communication pipe Bypass expansion of bypass refrigerant circuit 61 from flow path including 6 and outdoor heat exchange 23
  • High-pressure liquid refrigerant flows through the flow path to the valve 62, and the parts from the outdoor heat exchanger 23 to the indoor expansion valves 41 and 51 and the binos expansion valve 62 (see the black hatched parts in Fig. 6)
  • the pressure of the refrigerant in the liquid refrigerant circulation part B) is also stabilized, and the liquid refrigerant circulation part B is sealed with the liquid refrigerant and becomes stable.
  • the liquid pipe temperature control is performed in the refrigerant pipe including the liquid refrigerant communication pipe 6 from the subcooler 25 to the indoor expansion valves 41 and 51 (the subcooler in the liquid refrigerant circulation section B shown in FIG. 6). This is to prevent the refrigerant density from changing from 25 to the indoor expansion valves 41 and 51).
  • the capacity control of the subcooler 25 is controlled so that the refrigerant temperature Tip detected by the liquid pipe temperature sensor 35 provided at the outlet of the main refrigerant circuit of the subcooler 25 is constant at the liquid pipe temperature target value Tips.
  • the flow rate of the refrigerant flowing through the bypass refrigerant circuit 61 is increased or decreased to adjust the amount of heat exchanged between the refrigerant flowing through the main refrigerant circuit side of the subcooler 25 and the refrigerant flowing through the bypass refrigerant circuit side. Yes.
  • the flow rate of the refrigerant flowing through the bypass refrigerant circuit 61 is increased or decreased by adjusting the opening degree of the bypass expansion valve 62.
  • liquid pipe temperature control is realized in which the refrigerant temperature in the refrigerant pipe including the liquid refrigerant communication pipe 6 extending from the supercooler 25 to the indoor expansion valves 41 and 51 is constant.
  • the refrigerant circuit 10 is filled with the refrigerant, and as the amount of refrigerant in the refrigerant circuit 10 gradually increases, at the outlet of the outdoor heat exchanger 23, Even if the refrigerant temperature Tco (that is, the degree of refrigerant supercooling SCo at the outlet of the outdoor heat exchanger 23) changes, the change in the refrigerant temperature Tco at the outlet of the outdoor heat exchanger 23
  • the influence force and the outlet power of the outdoor heat exchange are also contained only in the refrigerant pipe reaching the subcooler 25, and the refrigerant pipe from the subcooler 25 to the indoor expansion valves 41 and 51 including the liquid refrigerant communication pipe 6 in the liquid refrigerant circulation section B Does not affect the state.
  • the superheat control is performed because the amount of refrigerant in the evaporator section C greatly affects the dryness of the refrigerant at the outlets of the indoor heat exchangers 42 and 52.
  • the degree of superheat SHr of the refrigerant at the outlet of the indoor heat exchanger 52 is controlled by controlling the opening degree of the indoor expansion valves 41 and 51, so that the gas side of the indoor heat exchangers 42 and 52 (hereinafter referred to as refrigerant amount determination operation).
  • the superheat degree SHr of the refrigerant in the indoor heat exchangers 42 and 52 is made constant at the superheat target value SHrs (that is, the gas refrigerant at the outlets of the indoor heat exchangers 42 and 52 is used). Excessive The state of the refrigerant flowing in the evaporator section c is stabilized.
  • the state of the refrigerant circulating in the refrigerant circuit 10 is stabilized, and the distribution of the refrigerant amount in the refrigerant circuit 10 becomes constant.
  • the refrigerant begins to be charged, it is possible to create a state in which the change in the refrigerant amount in the refrigerant circuit 10 mainly appears as a change in the refrigerant amount in the outdoor heat exchanger 23 (hereinafter, this operation is performed). Is the refrigerant quantity determination operation).
  • control unit 8 (more specifically, the indoor side control units 47 and 57, the outdoor side control unit 37, and the control unit 37, which functions as a refrigerant amount determination operation control unit that performs the refrigerant amount determination operation.
  • the transmission line 8a) connecting 47 and 57 is performed as the process of step S11.
  • the component device when the outdoor unit 2 is not prefilled with the refrigerant, the component device abnormally stops when performing the above-described refrigerant amount determination operation prior to the processing of step S11. It is necessary to charge the refrigerant until the amount of refrigerant is low enough
  • step S12 additional refrigerant charging is performed in the refrigerant circuit 10 while performing the above-described refrigerant amount determination operation.
  • the additional charging of the refrigerant in step S12 is performed by the control unit 8 functioning as the refrigerant amount calculating means.
  • the refrigerant amount in the refrigerant circuit 10 is calculated from the refrigerant flowing through the refrigerant circuit 10 at the time or the operating state quantity of the component equipment.
  • the refrigerant quantity calculating means calculates the refrigerant quantity in the refrigerant circuit 10 by dividing the refrigerant circuit 10 into a plurality of parts and calculating the refrigerant quantity for each of the divided parts. More specifically, for each of the divided parts, a relational expression between the refrigerant amount of each part and the operating state quantity of the refrigerant flowing through the refrigerant circuit 10 or the component device is set. By using it, the amount of refrigerant in each part can be calculated.
  • the refrigerant circuit 10 includes the four-way switching valve 22 in the state indicated by the solid line in FIG.
  • the discharge side of the compressor 21 is connected to the gas side of the outdoor heat exchanger 23, and ,
  • the suction side of the compressor 21 is the gas side closing valve 27 and an outdoor heat exchanger 2 including a four-way switching valve 22 (not shown in FIG. 6) connected to the outlets of the indoor heat exchangers 42 and 52 via the gas refrigerant communication pipe 7 Up to 3 (hereinafter referred to as high-pressure gas pipe section E), the outdoor heat exchanger 23 section (that is, the condenser section A), and the liquid refrigerant circulation section B from the outdoor heat exchanger 23 to the subcooler.
  • high-pressure gas pipe section E high-pressure gas pipe section
  • the outdoor heat exchanger 23 section that is, the condenser section A
  • the liquid refrigerant circulation section B from the outdoor heat exchanger 23 to the subcooler.
  • the liquid refrigerant communication pipe 6 (hereinafter referred to as the liquid refrigerant communication pipe section B3) and the liquid refrigerant communication pipe 6 in the liquid refrigerant circulation section B through the indoor expansion valves 41 and 51 and the indoor Of the gas refrigerant circulation part D including the exchangers 42 and 52 (that is, the evaporator part C), the part up to the gas refrigerant communication pipe 7 (hereinafter referred to as the indoor unit part F), and the gas refrigerant circulation part D Part of the gas refrigerant communication pipe 7 (hereinafter referred to as the gas refrigerant communication pipe part G) and the gas refrigerant closing part 27 (not shown in FIG.
  • the relational expression between the refrigerant amount Mogl in the high-pressure gas pipe E and the operating state quantity of the refrigerant or the component device flowing through the refrigerant circuit 10 is, for example,
  • This is expressed as a functional expression obtained by multiplying the volume Vogl of the high-pressure gas pipe E of the outdoor unit 2 by the refrigerant density / 0 d in the high-pressure gas pipe E.
  • the volume Vogl of the high-pressure gas pipe E is a known value of the front force at which the outdoor unit 2 is installed at the installation location, and is stored in advance in the memory of the control unit 8.
  • the density of the refrigerant in the high-pressure gas pipe E can be obtained by converting the discharge temperature Td and the discharge pressure Pd.
  • Refrigerant amount Mc in condenser part A and operation of refrigerant or component equipment flowing through refrigerant circuit 10 The relational expression with the state quantity is, for example,
  • Mc kcl XTa + kc2 XTc + kc3 X SHm + kc4 XWc
  • the outdoor temperature Ta, the condensation temperature Tc, the compressor discharge superheat SHm, the refrigerant circulation rate Wc, the saturated liquid density pc of the refrigerant in the outdoor heat exchanger 23, and the refrigerant density P at the outlet of the outdoor heat exchanger 23 It is expressed as a function expression of co.
  • the parameters kcl to kc7 in the above relational expression are obtained by regression analysis of the results of tests and detailed simulations, and are stored in the memory of the control unit 8 in advance.
  • the compressor discharge superheat degree S Hm is the refrigerant superheat degree on the discharge side of the compressor.
  • the discharge pressure Pd is converted to the refrigerant saturation temperature value, and the discharge temperature Td force is subtracted from the refrigerant saturation temperature value.
  • the saturated liquid density pc of the refrigerant can be obtained by converting the condensation temperature Tc.
  • the refrigerant density p co at the outlet of the outdoor heat exchanger 23 is obtained by converting the condensation pressure Pc obtained by converting the condensation temperature Tc and the refrigerant temperature Tco.
  • the relational expression between the refrigerant amount Moll in the high-temperature liquid pipe section B1 and the operating state quantity of the refrigerant flowing through the refrigerant circuit 10 or the component device is, for example,
  • the volume Voll of the high-pressure liquid pipe section B1 is a known value of the front force at which the outdoor unit 2 is installed at the installation location, and is stored in the memory of the control section 8 in advance.
  • the relational expression between the refrigerant quantity Mol2 in the low temperature liquid pipe part B2 and the operating state quantity of the refrigerant flowing through the refrigerant circuit 10 or the component device is, for example,
  • the refrigerant density p lp in the cryogenic liquid pipe section B2 is the refrigerant density at the outlet of the subcooler 25, and is obtained by converting the condensation pressure Pc and the refrigerant temperature Tip at the outlet of the subcooler 25. It is done.
  • volume Vlp of the liquid refrigerant communication pipe 6 is a refrigerant pipe that is installed locally when the liquid refrigerant communication pipe 6 is installed at the installation location of the air conditioner 1 at a place such as a building.
  • Mr krl XTlp + kr2 X AT + kr3 X SHr + kr4 XWr + kr5
  • the refrigerant temperature Tlp at the outlet of the supercooler 25 is expressed as a function expression of the air volume Wr.
  • the parameters krl to kr5 in the above relational expression are obtained by regression analysis of the results of the test and detailed simulation, and are stored in the memory of the control unit 8 in advance.
  • the relational expression of the refrigerant amount Mr is set corresponding to each of the two indoor units 4 and 5, and the refrigerant amount Mr of the indoor unit 4 and the refrigerant amount Mr of the indoor unit 5 are added. As a result, the total amount of refrigerant in the indoor unit F is calculated. If the indoor unit 4 and the indoor unit 5 have different models and capacities, the relational forces S with different values of the parameters krl to kr5 will be used.
  • volume Vgp of the gas refrigerant communication pipe 7 is the refrigerant installed at the site when the gas refrigerant communication pipe 7 installs the air conditioner 1 at the installation location of the building, etc., like the liquid coolant communication pipe 6.
  • the refrigerant density p gp in the gas refrigerant pipe connecting portion G is equal to the refrigerant density P s on the suction side of the compressor 21 and the outlets of the indoor heat exchangers 42 and 52 (that is, the inlet of the gas refrigerant connecting pipe 7). This is the average value with the density p eo of the refrigerant.
  • the refrigerant density ps is obtained by converting the suction pressure Ps and the suction temperature Ts
  • the refrigerant density p eo is obtained by converting the evaporation pressure Pe and the indoor heat exchangers 42 and 52, which are conversion values of the evaporation temperature Te. It is obtained by converting the outlet temperature Teo.
  • the relational expression between the refrigerant amount Mog2 in the low-pressure gas pipe part H and the operating state quantity of the refrigerant or the component device flowing through the refrigerant circuit 10 is, for example,
  • volume Vog2 of the low-pressure gas pipe H in the outdoor unit 2 is a known value of the pre-force that is shipped to the installation location, and is stored in the memory of the controller 8 in advance.
  • the relational expression between the refrigerant amount Mob in the no-pass circuit section I and the operation state quantity of the refrigerant flowing through the refrigerant circuit 10 or the component device is, for example,
  • Mob kobl X co + kob2 X ps + kob3 X Pe + kob4
  • the refrigerant density p co at the outlet of the outdoor heat exchanger 23, the refrigerant density ps at the outlet of the subcooler 25 on the bypass circuit side, and the evaporation pressure Pe are expressed as functional expressions.
  • the parameters kobl to kob3 in the above relational expression are obtained by regression analysis of the results of tests and detailed simulations, and are recorded in the memory of the control unit 8 in advance. It is remembered.
  • the volume Mob of the bypass circuit part I may be smaller than the other parts, and may be calculated by a simpler relational expression. For example,
  • the volume Vob of the bypass circuit section I is also a known value of the front force at which the outdoor unit 2 is installed at the installation location, and is stored in the memory of the control section 8 in advance.
  • the saturated liquid density pe in the portion on the bypass circuit side of the subcooler 25 can be obtained by converting the suction pressure Ps or the evaporation temperature Te.
  • the relational expression between the refrigerant amount Mcomp in the compressor part J and the operating state quantity of the refrigerant or the component equipment flowing through the refrigerant circuit 10 is, for example,
  • the dissolved refrigerant amount Mqo is
  • the solubility ⁇ of the refrigerant in the refrigerating machine oil is expressed as a function of the pressure and temperature of the refrigerating machine oil accumulated in the oil reservoir 71d.
  • the refrigerant is weakly compatible or incompatible with the refrigerant. Because the pressure dependence of the solubility ⁇ of refrigerant in the refrigeration oil is small, the pressure of the refrigeration oil should be, for example, the refrigerant pressure (ie, discharge pressure Pd) in the high-pressure space Q2. Can do.
  • the air conditioner 1 is configured such that the temperature difference between the refrigerating machine oil accumulated in the oil reservoir 71d inside the compressor 21 and the refrigerant in contact with the refrigerating machine oil increases. 21 Force that tends to cause the temperature distribution of the refrigerating machine oil accumulated in the oil reservoir 71d inside.
  • a refrigerating machine oil that is weakly compatible or incompatible with the refrigerant is used. Since the temperature dependence of the solubility ⁇ of the refrigerant in the refrigeration oil is small, the temperature of the refrigerant in the high-pressure space Q2 (that is, the discharge temperature Td) can be used as the temperature of the refrigeration oil.
  • the amount of dissolved refrigerant Mqo can be calculated for the known amount of refrigeration oil Moil, discharge pressure Pd, and discharge temperature Td, so special sensors are added to calculate the amount of dissolved refrigerant Mqo. You don't have to.
  • the amount of refrigeration oil Moil changes with the amount of refrigeration oil discharged from the compressor 21 together with the refrigerant, so strictly speaking, it is not a known amount, but the solubility ⁇ of the refrigerant in the refrigeration oil is small. Therefore, even if there is a slight fluctuation in the amount of refrigeration oil Moil, the dissolved refrigerant quantity Mqo can be easily calculated with sufficient accuracy without taking this fluctuation into account. Furthermore, when the determination accuracy necessary for determining the suitability of the refrigerant amount is sufficient to ignore the dissolved refrigerant amount Mqo, the calculation of the dissolved refrigerant amount Mqo as described above becomes unnecessary, The calculation of the refrigerant amount is further facilitated.
  • the total volume Vcomp force of the compressor 21 is also calculated by subtracting the volume Voil of the refrigerating machine oil and the volume Vql of the low pressure space Q1, and multiplying this by the refrigerant density p d as the refrigerant density in the high pressure space Q2.
  • the volume Voil of the refrigeration oil is calculated by dividing the amount Moil of the refrigeration oil by the density p oil of the refrigeration oil.
  • the density p oil of the refrigerating machine oil is expressed as a function of the temperature of the refrigerating machine oil.
  • the discharge temperature Td can be used as in the case of calculating the solubility ⁇ described above. That is, the density of refrigeration oil can be expressed as a function of discharge temperature (ie, poi ⁇ fS CTd)).
  • the refrigerant amount Mq2 in the portion other than the oil reservoir 71d in the high pressure space Q2 in the compressor casing 71 of the compressor 21 is the known volume Vcomp, the known volume Vql, the known amount of refrigerating machine oil Moil and The discharge temperature Td force can also be calculated. [0052]
  • the refrigerant amount Mql is
  • a plurality of refrigerant quantities Mogl, Mc, Moll, Mol2, Mog2, Mob, and Mcomp related to the outdoor unit are present.
  • the relational expression of the refrigerant quantity of each part is set corresponding to each of the outdoor units, and the total refrigerant quantity of the outdoor unit is calculated by adding the refrigerant quantity of each part of the plurality of outdoor units. ing.
  • the relational expression for the refrigerant amount of each part with different parameter values is used.
  • the refrigerant flowing through the refrigerant circuit 10 in the refrigerant quantity determination operation or the operating state quantity of the component device Force refrigerant in each part By calculating the amount, the amount of refrigerant in the refrigerant circuit 10 can be calculated.
  • step S12 Since this step S12 is repeated until the condition for determining whether or not the refrigerant amount is appropriate in step S13, which will be described later, is satisfied, the additional charging of the refrigerant is started and the power is completed until the power is completed.
  • the amount of operating state force when the refrigerant is charged is calculated. More specifically, the refrigerant amount Mo in the outdoor unit 2 and the refrigerant amount Mr in each of the indoor units 4 and 5 necessary for determining whether or not the refrigerant amount is appropriate in step S 13 described later (that is, the refrigerant communication pipe 6,
  • the refrigerant amount of each part of the refrigerant circuit 10 excluding 7 is calculated.
  • the refrigerant amount Mo in the outdoor unit 2 is calculated by adding the refrigerant amounts Mogl, Mc, Moll, Mol2, Mog2, Mob, and Mcomp of each part in the outdoor unit 2 described above.
  • control unit 8 functioning as a refrigerant amount calculating means for calculating the refrigerant amount of each part of the refrigerant circuit 10 from the refrigerant flowing in the refrigerant circuit 10 or the operating state quantity of the component device in the automatic refrigerant charging operation. Then, the process of step S12 is performed.
  • Step S13 Judgment of appropriateness of refrigerant quantity
  • the refrigerant amount is stored in advance in the memory of the control unit 8 as the charging target value Ms, and the refrigerant flowing in the refrigerant circuit 10 in the automatic refrigerant charging operation or the Refrigerant amount value obtained by adding the refrigerant amount Mo of the outdoor unit 2 and the refrigerant amount Mr of the indoor units 4 and 5 to which the operation state quantity force of the component equipment is also calculated until the filling target value Ms is reached.
  • step S13 determines whether or not the refrigerant amount value obtained by adding the refrigerant amount Mo of the outdoor unit 2 and the refrigerant amounts Mr of the indoor units 4 and 5 in the automatic refrigerant charging operation has reached the charging target value Ms. This determination is a process for determining whether or not the amount of refrigerant charged in the refrigerant circuit 10 by additional charging of the refrigerant is appropriate.
  • step S13 additional charging of the refrigerant in which the refrigerant amount value obtained by adding the refrigerant amount Mo of the outdoor unit 2 and the refrigerant amount Mr of the indoor units 4 and 5 is smaller than the charging target value Ms is not completed.
  • the process of step S13 is repeated until the filling target value Ms is reached.
  • the refrigerant amount value obtained by adding the refrigerant amount Mo of the outdoor unit 2 and the refrigerant amount Mr of the indoor units 4 and 5 reaches the charging target value Ms, the additional charging of the refrigerant is completed and the refrigerant automatic Step S1 as the filling operation process is completed.
  • the charging target value Ms is set to the value of the outdoor unit 2 that is not the outdoor unit 2 and the indoor units 4 and 5.
  • the charging target value Ms is set to the value of the outdoor unit 2 that is not the outdoor unit 2 and the indoor units 4 and 5.
  • the control unit 8 functions as a refrigerant amount determination means for determining whether or not the refrigerant amount in the refrigerant circuit 10 in the refrigerant amount determination operation of the automatic refrigerant charging operation is appropriate (that is, whether or not the charging target value Ms has been reached).
  • the control unit 8 performs the process of step S13.
  • Step S2 Pipe volume judgment operation
  • step S1 When the above-described automatic refrigerant charging operation in step S1 is completed, the process proceeds to the pipe volume determination operation in step S2.
  • the control unit 8 performs the processing from step S21 to step S25 shown in FIG.
  • FIG. 7 is a flow chart of the pipe volume judgment operation.
  • Step S21 the indoor unit 100% operation and condensation are performed in the same manner as the refrigerant amount judgment operation in step S11 in the above-described automatic refrigerant charging operation.
  • Perform pipe volume judgment operation for liquid refrigerant communication pipe 6 including pressure control, liquid pipe temperature control, superheat control and evaporation pressure control.
  • the refrigerant temperature at the outlet of the main refrigerant circuit of the subcooler 25 in the liquid pipe temperature control is set as the first target value Tlpsl
  • the refrigerant amount judgment operation is performed with the first target value Tlpsl.
  • the stable state is the first state (see the refrigeration cycle indicated by the line including the broken line in Fig. 8).
  • FIG. 8 is a Mollier diagram showing the refrigeration cycle of the air conditioner 1 in the pipe volume determination operation for the liquid refrigerant communication pipe.
  • the refrigerant amount Mlp in the liquid refrigerant communication pipe part B3 in the second state Will decrease compared to the amount of refrigerant in the first state. Then, the refrigerant reduced from the liquid refrigerant communication pipe part B3 moves to the other part of the refrigerant circuit 10. It will be.
  • the equipment control conditions other than the liquid pipe temperature control are not changed, so that the refrigerant amount Mogl in the high pressure gas pipe E and the refrigerant in the low pressure gas pipe H Amount Mog2, refrigerant amount Mgp in gas refrigerant communication pipe part G and refrigerant quantity Mcomp in compressor part J are kept almost constant, and the refrigerant decreased from liquid refrigerant communication pipe part B3 is the condenser part A, high temperature It moves to liquid pipe part Bl, cryogenic liquid pipe part B2, indoor unit part F and binos circuit part I.
  • the refrigerant amount Mc in the condenser part A, the refrigerant amount Moll in the high temperature liquid pipe part B1, the refrigerant quantity Mol2 in the low temperature liquid pipe part B2, and the indoor unit part F by the amount of refrigerant reduced from the liquid refrigerant communication pipe part B3
  • the refrigerant amount Mr and the refrigerant amount Mob in the bypass circuit section I increase.
  • control unit 8 (more specifically, the indoor side control unit) that functions as a pipe volume determination operation control unit that performs a pipe volume determination operation for calculating the volume Mlp of the liquid refrigerant communication pipe 6.
  • the transmission line 8a) connecting between 47 and 57, the outdoor side control unit 37, and the control units 37, 47 and 57 is performed as the process of step S21.
  • step S22 the liquid cooling medium is utilized by utilizing the phenomenon that the refrigerant is decreased from the liquid refrigerant communication pipe section B3 and moves to the other part of the refrigerant circuit 10 due to the change from the first state to the second state. Calculate the volume Vlp of connecting pipe 6.
  • the amount of refrigerant that has decreased from the liquid refrigerant communication piping section B3 and moved to the other part of the refrigerant circuit 10 by the pipe volume determination operation described above is defined as the refrigerant increase / decrease amount ⁇ Mlp, and each part between the first and second states If the increase / decrease amount of the refrigerant is A Mc, ⁇ ⁇ 11, ⁇ ⁇ 12, A Mr, and ⁇ Mob (here, the refrigerant amount Mogl, the refrigerant amount Mog2 and the refrigerant amount Mgp are kept almost constant, they are omitted), the refrigerant increase / decrease
  • the quantity ⁇ Mlp is, for example,
  • ⁇ Mlp — ( ⁇ Mc + ⁇ Moll + ⁇ ⁇ 12 + ⁇ Mr + ⁇ Mob)
  • a Mc, ⁇ ⁇ 11, ⁇ ⁇ 12, A Mr, and A Mob are used to calculate the refrigerant amount in the first state and the refrigerant amount in the second state using the relational expressions for each part of the refrigerant circuit 10 described above. Further, the amount of refrigerant in the second state is obtained by subtracting the amount of refrigerant in the first state, and the density change amount ⁇ lp is the amount of refrigerant at the outlet of the subcooler 25 in the first state. It is obtained by calculating the density and the density of the refrigerant at the outlet of the subcooler 25 in the second state, and further subtracting the density of the refrigerant in the second state.
  • the volume Vlp of the liquid refrigerant communication pipe 6 can be calculated from the refrigerant flowing through the refrigerant circuit 10 in the first and second states or the operating state quantity of the component equipment using the arithmetic expression as described above.
  • the state is changed so that the second target value Tlps2 in the second state is higher than the first target value Tlpsl in the first state, and the refrigerant in the liquid refrigerant communication pipe section B2 is changed.
  • the amount of refrigerant in the other part is increased by moving the part to the other part, and the volume Vlp of the increased force liquid refrigerant communication pipe 6 is calculated.
  • the second target value Tlps2 in the second state is Change the state so that the temperature is lower than the first target value Tlpsl in 1 state, and move the refrigerant from the other part to the liquid refrigerant communication pipe part B3 to reduce the amount of refrigerant in the other part, From this decrease, the volume Vlp of the liquid refrigerant communication pipe 6 may be calculated.
  • the volume Vlp of the liquid refrigerant communication pipe 6 is calculated from the refrigerant flowing in the refrigerant circuit 10 in the pipe volume determination operation for the liquid refrigerant communication pipe 6 or the operating state quantity of the component equipment.
  • Pipe for the liquid refrigerant communication pipe The process of step S22 is performed by the control unit 8 functioning as a volume calculation means.
  • Step S23, S24 Pipe volume determination operation and volume calculation for gas refrigerant communication pipe
  • Step S23 all indoor units are operated, condensation pressure control, liquid Pipe volume judgment operation for gas refrigerant communication pipe 7 including pipe temperature control, superheat control and evaporation pressure control is performed.
  • the low pressure target value Pes of the suction pressure Ps of the compressor 21 in the evaporation pressure control is defined as the first target value Pesl.
  • the state in which the refrigerant quantity determination operation is stable at the standard value Pesl is defined as the first state (see the refrigeration cycle indicated by the line including the broken line in FIG. 9).
  • FIG. 9 is a Mollier diagram showing the refrigeration cycle of the air conditioner 1 in the pipe volume determination operation for the gas refrigerant communication pipe.
  • the low pressure target value Pes is different from the first target value Pesl.
  • the second target value Pes2 is a pressure lower than the first target value Pesl.
  • the device control conditions other than the evaporation pressure control are changed, so that the refrigerant amount Mogl in the high-pressure gas pipe section E, the high-temperature liquid pipe section Refrigerant amount Moll in B1, refrigerant amount Mol2 in low temperature liquid pipe B2 and liquid Refrigerant communication pipe part B3 Refrigerant quantity Mlp is kept almost constant and gas refrigerant communication pipe part H, condenser section A, indoor unit section F, bypass circuit section I and compressor section J.
  • the refrigerant amount Mog2 in the low-pressure gas pipe part H, the refrigerant quantity Mc in the condenser part A, the refrigerant quantity Mr in the indoor unit part F, and the bypass circuit part I by the amount of refrigerant reduced from the gas refrigerant communication pipe part G
  • the refrigerant amount Mob in the compressor and the refrigerant amount Mcomp in the compressor part J will increase.
  • control unit 8 (more specifically, indoor side functioning as a pipe volume determination operation control means for performing a pipe volume determination operation for calculating the volume Vgp of the gas refrigerant communication pipe 7. This is performed as the process of step S23 by the control unit 47, 57, the outdoor control unit 37, and the transmission line 8a) connecting the control units 37, 47, 57.
  • step S24 the gas refrigerant communication pipe is changed from the first state to the second state.
  • Part G force also calculates the volume Vgp of the gas refrigerant communication pipe 7 by utilizing the phenomenon that the refrigerant decreases and moves to the other part of the refrigerant circuit 10.
  • the amount of refrigerant that has decreased from the gas refrigerant communication piping part G and moved to the other part of the refrigerant circuit 10 by the pipe volume determination operation described above is defined as the refrigerant increase / decrease amount ⁇ Mgp, and each part between the first and second states
  • the amount of increase / decrease in refrigerant is A Mc, A Mog2, A Mr, A Mob, and A Mcomp (here, the refrigerant amount Mogl, the refrigerant amount Moll, the refrigerant amount Mol2, and the refrigerant amount Mlp are omitted because they are kept almost constant).
  • the refrigerant increase / decrease amount ⁇ Mgp is, for example,
  • a Mgp — (A Mc + A Mog2 + A Mr + A Mob + A Mcomp) can be calculated. Then, by dividing the value of ⁇ Mgp by the refrigerant density change ⁇ p gp between the first and second states in the gas refrigerant communication pipe 7, the volume Vgp of the gas refrigerant communication pipe 7 is calculated. can do. It should be noted that the calculation result of the refrigerant increase / decrease amount ⁇ Mgp is hardly affected, but the above-mentioned function formula may include the refrigerant amount Mogl, the refrigerant amount Moll, and the refrigerant amount Mol2.
  • a Mc, A Mog2, A Mr, A Mob, and A Mcomp calculate the refrigerant amount in the first state and the refrigerant amount in the second state using the relational expressions for each part of the refrigerant circuit 10 described above. Further, the amount of refrigerant in the second state is obtained by subtracting the amount of refrigerant in the first state, and the density change amount ⁇ p gp is the amount of refrigerant on the suction side of the compressor 21 in the first state. It is obtained by calculating the average density of the density ps and the refrigerant density p eo at the outlets of the indoor heat exchangers 42 and 52, and subtracting the average density in the first state from the average density in the second state.
  • the volume Vgp of the gas refrigerant communication pipe 7 can be calculated from the refrigerant flowing through the refrigerant circuit 10 in the first and second states or the operation state quantity of the component equipment in the first and second states using the above arithmetic expression.
  • the state change is performed so that the second target value Pes2 in the second state is lower than the first target value Pesl in the first state and the pressure is changed, and the gas refrigerant communication pipe section
  • the amount of refrigerant in the other part is increased, and this increase
  • the volume force Vlp of the gas refrigerant communication pipe 7 is also calculated, but the state is changed so that the second target value Pes2 in the second state is higher than the first target value Pesl in the first state.
  • step S24 is performed by the control unit 8 functioning as a calculation means.
  • step S25 whether or not the result of the pipe volume determination operation is appropriate, that is, the refrigerant communication pipes 6 and 7 calculated by the pipe volume calculation means. It is determined whether the volume of Vlp and Vgp is reasonable.
  • ⁇ 1 and ⁇ 2 are values that can be varied based on the minimum value and the maximum value of the pipe volume ratio in a feasible combination of the outdoor unit and the indoor unit.
  • step S2 when the volume ratio VlpZVgp satisfies the above numerical range, the processing of step S2 that is involved in the pipe volume determination operation is completed, and when the volume ratio VlpZVgp does not satisfy the above numerical range, The pipe volume determination operation and the volume calculation process in steps S21 to S24 are performed again.
  • step S25 is performed by the control unit 8 functioning as validity determination means for determining whether or not there is.
  • the pipe volume determination operation for the liquid refrigerant communication pipe 6 (steps S21 and S22) is performed first, and then the pipe volume determination operation for the gas refrigerant communication pipe 7 (step S23). S24), but the pipe volume judgment operation for the gas refrigerant communication pipe 7 may be performed first.
  • step S25 when the result of the pipe volume determination operation in steps S21 to S24 is determined a plurality of times as inappropriate, or the volume of the refrigerant communication pipes 6 and 7 is more simply If it is desired to make a determination of Vlp or Vgp, although not shown in FIG. 7, for example, in step S25, after determining that the result of the pipe volume determination operation in steps S21 to S24 is not valid, the refrigerant communication is performed. Estimate the length of the refrigerant communication pipes 6 and 7 from the pressure loss in the pipes 6 and 7, and move to the process of calculating the volume Vlp and Vgp of the refrigerant communication pipes 6 and 7 from the estimated pipe length and the average volume ratio. Then, the volumes Vlp and Vgp of the refrigerant communication pipes 6 and 7 may be obtained.
  • the length of the refrigerant communication pipes 6 and 7 has no information on the pipe diameter, etc.
  • the pipe volume judgment operation is performed on the assumption that the volumes Vlp and Vgp of the refrigerant communication pipes 6 and 7 are unknown.
  • the force described for calculating the volume Vlp and Vgp of the refrigerant communication pipes 6 and 7 When the pipe volume calculation means inputs information such as the diameter of the refrigerant communication pipes 6 and 7, the refrigerant communication pipe If you have the function to calculate the volume Vlp and Vgp of 6 and 7, you can use this function together.
  • the length of the refrigerant communication pipes 6 and 7 is the pipe diameter.
  • the above-mentioned validity judgment means step S25 is used to input the refrigerant If the length of the communication pipes 6 and 7 is sufficient, it may be determined whether or not the information such as the pipe diameter is appropriate.
  • Step S3 Initial refrigerant quantity detection operation
  • step S2 When the pipe volume determination operation in step S2 is completed, the process proceeds to the initial refrigerant amount determination operation in step S3.
  • Fig. 10 shows the initial refrigerant amount test. It is a flowchart of an intellectual driving
  • Step S31 Refrigerant Amount Determination Operation
  • step S31 similar to the refrigerant amount determination operation in step S11 of the above-described automatic refrigerant charging operation, the refrigerant amount determination operation including all indoor unit operations, condensation pressure control, liquid pipe temperature control, superheat degree control, and evaporation pressure control is performed. Is done.
  • control unit 8 functioning as the refrigerant quantity determination operation control means for performing the refrigerant quantity determination operation including the indoor unit total number operation, the condensation pressure control, the liquid pipe temperature control, the superheat degree control, and the evaporation pressure control, performs the step S. 31 processes are performed.
  • control unit 8 that functions as the refrigerant amount calculation means while performing the refrigerant amount determination operation described above, the refrigerant flowing from the refrigerant circuit 10 in the initial refrigerant amount determination operation in step S32 or the operation state amount of the component device is used.
  • the amount of refrigerant in the refrigerant circuit 10 is calculated using a relational expression between the amount of refrigerant in each part of the refrigerant circuit 10 described above and the operating state amount of the refrigerant flowing through the refrigerant circuit 10 or the constituent devices.
  • the volume Vlp and Vgp of the refrigerant communication pipes 6 and 7 that were unknown after the installation of the components of the air conditioner 1 are calculated and known by the above-described pipe volume determination operation.
  • Refrigerant communication pipes 6 and 7 volumes Vlp and Vgp are multiplied by the refrigerant density to calculate refrigerant amounts Mlp and Mgp in refrigerant communication pipes 6 and 7, and the refrigerant quantities in the other parts are calculated.
  • the initial refrigerant amount of the entire refrigerant circuit 10 can be detected.
  • This initial refrigerant quantity is used as a reference refrigerant quantity Mi for the refrigerant circuit 10 as a reference for determining the presence or absence of leakage from the refrigerant circuit 10 in the refrigerant leakage detection operation described later. Is stored in the memory of the control unit 8 as state quantity storage means.
  • step S32 the control that functions as the refrigerant amount calculating means for calculating the refrigerant amount in each part of the refrigerant circuit 10 from the refrigerant flowing in the refrigerant circuit 10 in the initial refrigerant amount detection operation or the operation state quantity of the constituent devices.
  • the process of step S32 is performed by the unit 8.
  • FIG. 11 is a flowchart of the refrigerant leak detection operation mode.
  • it is detected periodically (for example, when it is not necessary to perform air conditioning during holidays, late at night, etc.) whether refrigerant has leaked from the refrigerant circuit 10 due to unforeseen causes.
  • a case will be described as an example.
  • Step S41 Refrigerant amount judgment operation
  • the refrigerant leak detection operation mode is automatically or manually changed from the normal operation mode.
  • the refrigerant quantity judgment operation including the indoor unit total number operation, the condensation pressure control, the liquid pipe temperature control, the superheat degree control, and the evaporation pressure control is performed.
  • This refrigerant quantity determination operation is performed for each refrigerant leakage detection operation.For example, if the condensation pressure Pc is different, refrigerant leakage occurs! Even if the refrigerant temperature Tco at the outlet of the outdoor heat exchanger 23 fluctuates due to the liquid pipe temperature control, the refrigerant temperature Tip in the liquid refrigerant communication pipe 6 is kept constant at the same liquid pipe temperature target value Tips. It will be.
  • control unit 8 functioning as the refrigerant amount determination operation control means for performing the refrigerant amount determination operation including the indoor unit total number operation, the condensation pressure control, the liquid pipe temperature control, the superheat degree control, and the evaporation pressure control, performs step S41. Is performed.
  • control unit 8 that functions as the refrigerant quantity calculation means while performing the refrigerant quantity determination operation described above, the refrigerant from the operating state quantity of the refrigerant flowing through the refrigerant circuit 10 or the component device in the refrigerant leakage detection operation in step S42.
  • the refrigerant amount in the refrigerant circuit 10 is calculated using a relational expression between the refrigerant amount of each part of the refrigerant circuit 10 and the operation state quantity of the refrigerant flowing through the refrigerant circuit 10 or the component device.
  • the volumes Vlp and Vgp of the refrigerant communication pipes 6 and 7 that were unknown after the installation of the components of the air conditioner 1 are calculated by the above-described pipe volume determination operation as in the initial refrigerant amount determination operation. Therefore, the refrigerant volumes Mlp and Mgp in the refrigerant communication pipes 6 and 7 are calculated by multiplying the volumes Vlp and Vgp of the refrigerant communication pipes 6 and 7 by the density of the refrigerant. Refrigerant amount M of refrigerant circuit 10 as a whole by adding the refrigerant amounts of other parts Can be calculated.
  • the liquid refrigerant communication pipe section The refrigerant amount Mlp in B3 is kept constant even when the refrigerant temperature Tco fluctuates at the outlet of the outdoor heat exchanger 23, regardless of the operating conditions of the refrigerant leak detection operation.
  • control unit 8 that functions as the refrigerant amount calculating means for calculating the refrigerant amount of each part of the refrigerant circuit 10 from the refrigerant flowing in the refrigerant circuit 10 or the operating state quantity of the component device in the refrigerant leakage detection operation causes the step S42. Is performed.
  • Steps S43, S44 Judgment of appropriateness of refrigerant amount, warning display
  • the refrigerant amount M of the entire refrigerant circuit 10 calculated in step S42 described above is detected through the initial refrigerant amount detection operation in the case where refrigerant leakage from the refrigerant circuit 10 occurs.
  • the reference refrigerant amount MU is also small and no refrigerant leakage from the refrigerant circuit 10 occurs, the value is almost the same as the reference refrigerant amount Mi.
  • step S43 it is determined whether or not refrigerant has leaked. If it is determined in step S43 that no refrigerant leaks from the refrigerant circuit 10, the refrigerant leak detection operation mode is terminated.
  • step S43 if it is determined in step S43 that refrigerant has leaked from the refrigerant circuit 10, the process proceeds to step S44, and a warning is sent to the warning display unit 9 informing that the refrigerant has been detected. After the display, the refrigerant leak detection operation mode is terminated.
  • the refrigerant amount determination means for detecting the presence or absence of refrigerant leakage by determining whether or not the refrigerant amount in the refrigerant circuit 10 is appropriate while performing the refrigerant amount determination operation in the refrigerant leakage detection operation mode.
  • the processing of steps S42 to S44 is performed by the control unit 8 that functions as one refrigerant leakage detection means.
  • the control unit 8 includes the refrigerant amount determination operation means, the refrigerant amount calculation means, the refrigerant amount determination means, the pipe volume determination operation means, the pipe volume calculation means, By functioning as a validity determination means and a state quantity accumulation means, the refrigerant circuit 10 (3)
  • the refrigerant circuit 10 By functioning as a validity determination means and a state quantity accumulation means, the refrigerant circuit 10 (3)
  • the air conditioner 1 of the present embodiment has the following features.
  • a weakly compatible or incompatible refrigerating machine oil is enclosed with the refrigerant together with the refrigerant, so that sensors for calculating the dissolved refrigerant amount Mqo are not added. Even in this case, it is possible to reduce the calculation error of the dissolved refrigerant amount Mqo due to the influence of the temperature distribution generated in the refrigerating machine oil accumulated in the oil reservoir 71d inside the compressor 21.
  • the refrigerant amount in the refrigerant circuit 10 including the dissolved refrigerant amount Mqo is calculated based on the refrigerant flowing through the refrigerant circuit 10 or the operating state quantity of the constituent devices. Based on this calculated amount of refrigerant, the force that determines whether or not the amount of refrigerant in the refrigerant circuit 10 is appropriate. As described above, the calculation error of the dissolved refrigerant amount Mqo is reduced, so that the compression is reduced. This makes it possible to accurately grasp the amount of refrigerant inside the machine 21 and to reduce the calculation error when calculating the amount of refrigerant in the refrigerant circuit 10 including the dissolved refrigerant amount Mqo. The determination accuracy when determining the suitability of the refrigerant amount in the refrigerant circuit 10 based on the refrigerant amount thus improved improves the suitability of the refrigerant amount with high accuracy.
  • the compressor 21 is a type having the refrigeration oil reservoir 71d in the high pressure space Q2, and the refrigeration oil accumulated in the oil reservoir 71d inside the compressor 21. Therefore, the temperature difference between the refrigerant and the refrigerant in contact with the refrigerating machine oil is increased, so that the temperature distribution of the refrigerating machine oil accumulated in the oil reservoir 71d inside the compressor 21 tends to occur. Even in such cases, it is weakly compatible or incompatible with the refrigerant The above-mentioned effect can be obtained by enclosing the refrigerating machine oil, and the accuracy of determining the suitability of the refrigerant amount in the refrigerant circuit 10 can be dramatically improved.
  • a force indicating an example in which R410A, R407C, and R134a of the HFC refrigerant and an alkylbenzene oil or mineral oil are combined is limited to this.
  • R116, R125, R14, R143a, R23, etc., and mixed refrigerants such as R407A, R407B, R410B, R404A, etc. may be used in combination with alkylbenzene oil or mineral oil.
  • HC refrigerants such as butane, isobutane, and propane
  • natural refrigerants such as carbon dioxide and ammonia may be used in combination with alkylbenzene oils or mineral oils.
  • the present invention is applied to an air conditioner capable of switching between cooling and heating.
  • the present invention is not limited to this, and other air conditioners such as an air conditioner dedicated to cooling are used.
  • the present invention may be applied to.
  • the example in which the present invention is applied to the air conditioner including one outdoor unit has been described.
  • the present invention is not limited to this, and the air conditioner includes a plurality of outdoor units.
  • the present invention may be applied to an apparatus.
  • the present invention is applied to an air conditioner having a compressor of a type having a refrigerating machine oil reservoir in a high-pressure space as a compressor, but the refrigerating machine oil in the low-pressure space.

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  • Chemical & Material Sciences (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • Combustion & Propulsion (AREA)
  • Materials Engineering (AREA)
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  • General Engineering & Computer Science (AREA)
  • Lubricants (AREA)
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Abstract

Selon l'invention, une certaine quantité d'un réfrigérant dans un compresseur est recueillie précisément et le fait qu'une quantité du réfrigérant dans un circuit réfrigérant convient ou non est évalué de façon très précise, sans ajouter de capteur et autre à l'intérieur du compresseur. Un conditionner d'air (1) est muni d'un circuit réfrigérant (10) composé en raccordant un compresseur (21), un échangeur de chaleur extérieur (23), des soupapes de dilatation intérieures (41, 51) et des échangeurs de chaleur intérieurs (42, 52). Le conditionneur d'ère est également muni d'un moyen d'évaluation de quantité de réfrigérant permettant d'évaluer si une certaine quantité de réfrigérant dans le circuit réfrigérant (10) convient ou non, sur la base d'une quantité d'un état de fonctionnement du réfrigérant circulant dans le circuit réfrigérant (10) ou dans celui d'un appareil constitutif. Le circuit réfrigérant (10) est rempli d'une huile incongelable, faiblement miscible ou non miscible avec le réfrigérant, en même temps que le réfrigérant.
PCT/JP2007/064235 2006-07-24 2007-07-19 Conditionneur d'air WO2008013093A1 (fr)

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JP4864110B2 (ja) * 2009-03-25 2012-02-01 三菱電機株式会社 冷凍空調装置
CN212253263U (zh) * 2017-07-27 2020-12-29 三菱电机株式会社 制冷空调装置
US11656015B2 (en) 2017-09-14 2023-05-23 Mitsubishi Electric Corporation Refrigeration cycle apparatus and refrigeration apparatus
WO2019082331A1 (fr) * 2017-10-26 2019-05-02 三菱電機株式会社 Dispositif de climatisation/ réfrigération et dispositif de commande
JP2020159687A (ja) * 2020-07-02 2020-10-01 三菱電機株式会社 冷凍サイクル装置および冷凍装置

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JPH0311278A (ja) * 1989-06-08 1991-01-18 Hitachi Ltd 空気調和機の冷媒封入量不足検出装置
JPH03186170A (ja) * 1989-12-13 1991-08-14 Hitachi Ltd 冷凍装置及び冷凍装置における冷媒量表示方法
JPH04148170A (ja) * 1990-10-12 1992-05-21 Mitsubishi Electric Corp 冷媒封入量演算装置
JP2001032772A (ja) * 1999-07-19 2001-02-06 Daikin Ind Ltd 圧縮機及び冷凍装置
JP2003097443A (ja) * 2001-09-25 2003-04-03 Mitsubishi Heavy Ind Ltd 圧縮機および冷凍装置
JP2005274134A (ja) * 2001-09-28 2005-10-06 Mitsubishi Electric Corp ヒートポンプ床暖房空調装置

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Publication number Priority date Publication date Assignee Title
JPH0311278A (ja) * 1989-06-08 1991-01-18 Hitachi Ltd 空気調和機の冷媒封入量不足検出装置
JPH03186170A (ja) * 1989-12-13 1991-08-14 Hitachi Ltd 冷凍装置及び冷凍装置における冷媒量表示方法
JPH04148170A (ja) * 1990-10-12 1992-05-21 Mitsubishi Electric Corp 冷媒封入量演算装置
JP2001032772A (ja) * 1999-07-19 2001-02-06 Daikin Ind Ltd 圧縮機及び冷凍装置
JP2003097443A (ja) * 2001-09-25 2003-04-03 Mitsubishi Heavy Ind Ltd 圧縮機および冷凍装置
JP2005274134A (ja) * 2001-09-28 2005-10-06 Mitsubishi Electric Corp ヒートポンプ床暖房空調装置

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