WO2018073855A1 - Climatiseur - Google Patents

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Publication number
WO2018073855A1
WO2018073855A1 PCT/JP2016/080649 JP2016080649W WO2018073855A1 WO 2018073855 A1 WO2018073855 A1 WO 2018073855A1 JP 2016080649 W JP2016080649 W JP 2016080649W WO 2018073855 A1 WO2018073855 A1 WO 2018073855A1
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WO
WIPO (PCT)
Prior art keywords
compressor
refrigerant
air conditioner
unit
indoor heat
Prior art date
Application number
PCT/JP2016/080649
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English (en)
Japanese (ja)
Inventor
貴玄 中村
齊藤　信
Original Assignee
三菱電機株式会社
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 三菱電機株式会社 filed Critical 三菱電機株式会社
Priority to PCT/JP2016/080649 priority Critical patent/WO2018073855A1/fr
Priority to JP2018545721A priority patent/JP6715945B2/ja
Publication of WO2018073855A1 publication Critical patent/WO2018073855A1/fr

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B13/00—Compression machines, plants or systems, with reversible cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B31/00—Compressor arrangements
    • F25B31/002—Lubrication
    • F25B31/004—Lubrication oil recirculating arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B47/00—Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass
    • F25B47/02—Defrosting cycles
    • F25B47/022—Defrosting cycles hot gas defrosting
    • F25B47/025—Defrosting cycles hot gas defrosting by reversing the 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
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/005—Arrangement or mounting of control or safety devices of safety devices
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/30—Control or safety arrangements for purposes related to the operation of the system, e.g. for safety or monitoring
    • F24F11/32—Responding to malfunctions or emergencies
    • F24F11/38—Failure diagnosis
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/023—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units
    • F25B2313/0233—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units in parallel arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/025—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple outdoor units
    • F25B2313/0253—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple outdoor units in parallel arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
    • F25B2313/02741—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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/031—Sensor arrangements
    • F25B2313/0313—Pressure sensors near the outdoor heat exchanger
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/031—Sensor arrangements
    • F25B2313/0314—Temperature sensors near the indoor heat exchanger
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/031—Sensor arrangements
    • F25B2313/0315—Temperature sensors near the outdoor heat exchanger
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • 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
    • F25B2400/01—Heaters
    • 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
    • F25B2500/00—Problems to be solved
    • F25B2500/26—Problems to be solved characterised by the startup of the refrigeration 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
    • F25B2500/00—Problems to be solved
    • F25B2500/28—Means for preventing liquid refrigerant entering into the compressor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/19—Pressures
    • F25B2700/193—Pressures of the compressor
    • F25B2700/1931—Discharge pressures
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/19—Pressures
    • F25B2700/193—Pressures of the compressor
    • F25B2700/1933—Suction pressures
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2101—Temperatures in a bypass
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2103—Temperatures near a heat exchanger
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2104—Temperatures of an indoor room or compartment
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2105—Oil temperatures
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2106—Temperatures of fresh outdoor air
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2115—Temperatures of a compressor or the drive means therefor
    • F25B2700/21152—Temperatures of a compressor or the drive means therefor at the discharge side of the compressor

Definitions

  • This invention relates to an air conditioner.
  • Patent Document 1 Japanese Patent Laying-Open No. 2013-221661 (Patent Document 1) describes a reference position of an expansion valve when a liquid back is generated in which liquid refrigerant is sucked into the compressor due to an expansion valve control error.
  • An air conditioner configured to calibrate is disclosed.
  • damage to the compressor is prevented in advance by preventing the liquid back from repeatedly occurring due to the control error of the expansion valve.
  • Patent Document 1 cannot prevent the compressor from being damaged for some reason other than the control error of the expansion valve. Therefore, there has been a problem that the progress of the deterioration of the compressor cannot be suppressed.
  • a main object of the present invention is to provide an air conditioner that can suppress the progress of deterioration of the compressor.
  • An air conditioner includes a refrigerant circuit and a control device that controls the refrigerant circuit.
  • the refrigerant circuit includes at least one compressor, at least one outdoor heat exchanger, at least one expansion valve, and at least one indoor heat exchanger, and is configured to circulate the refrigerant.
  • the control device includes a calculation unit, a detection unit, and a control unit. The calculation unit is configured to calculate at least one index used for determining deterioration of at least one compressor based on an operation state quantity representing an operation state of the refrigerant circuit.
  • the detection unit detects forced deterioration of the compressor corresponding to the index when the difference between the initial value and the current value of one index exceeds a threshold value during a stable period in which the operation state of the refrigerant circuit is stable. Configured to do.
  • the control unit is configured to control the refrigerant circuit so as to prevent the liquid refrigerant from being sucked into the compressor in which the forced deterioration is detected by the detection unit.
  • FIG. (Configuration of air conditioner) 1 is a diagram showing a configuration of an air conditioner according to Embodiment 1 of the present invention.
  • the air conditioner includes an outdoor unit 1 and an indoor unit 20.
  • the outdoor unit 1 includes a compressor 2, an oil separator 3, a four-way switching valve 4, an outdoor heat exchanger 5, an outdoor fan 6, a HIC (Heat Inter Changer) 7, an outdoor expansion valve 8, an accumulator 9, and a control device 10.
  • the indoor unit 20 includes an indoor heat exchanger 21, an indoor blower 22, an indoor expansion valve 23, and an operation unit 24.
  • the compressor 2, the oil separator 3, the four-way switching valve 4, the outdoor heat exchanger 5, the HIC 7, the outdoor expansion valve 8, the accumulator 9, the indoor heat exchanger 21, and the indoor expansion valve 23 are connected by pipes P1 to P10.
  • the refrigerant circuit for circulating the refrigerant is configured.
  • the compressor 2 is controlled by the control device 10, sucks and compresses the gas refrigerant, and discharges the high-temperature and high-pressure gas refrigerant.
  • the compressor 2 is a positive displacement compressor capable of controlling the operating frequency.
  • an inverter that converts direct-current power into variable-frequency alternating-current power is provided.
  • the compressor 2 includes a motor that is driven by AC power generated by an inverter, and a main body that is driven by the motor and compresses the refrigerant.
  • the main body of the compressor 2 may be simply abbreviated as the compressor 2.
  • the discharge port of the compressor 2 is connected to the oil separator 3 via the discharge pipe P1.
  • the oil separator 3 separates the lubricating oil from the high-temperature and high-pressure gas refrigerant discharged from the compressor 2 and returns it to the suction port of the compressor 2. Note that the lubricating oil is used to enhance the slidability of the sliding portion of the compressor 2 and has a property of being dissolved in the refrigerant.
  • the discharge port of the compressor 2 is further connected to the other opening of the outdoor heat exchanger 5 via a bypass pipe P10.
  • the bypass pipe P10 is configured to bypass the gas refrigerant discharged from the compressor 2 to the outdoor heat exchanger 5.
  • the bypass pipe P10 is provided with an electromagnetic valve V1. The opening and closing of the electromagnetic valve V1 is controlled by the control device 10.
  • bypass pipe P ⁇ b> 10 is connected between the discharge port of the compressor 2 and the other opening of the outdoor heat exchanger 5, but as shown in FIG. 18, the oil separator 3 and A bypass pipe P ⁇ b> 10 may be connected between the pipe between the four-way switching valve 4 and the other opening of the outdoor heat exchanger 5.
  • the four-way switching valve 4 is controlled by the control device 10 and switches the direction of the refrigerant flow between the cooling operation and the heating operation. Specifically, the four-way switching valve 4 flows the refrigerant gas discharged from the compressor 2 and passed through the oil separator 3 to one opening of the outdoor heat exchanger 5 as indicated by a solid line during cooling operation, A gas refrigerant supplied from one opening of the indoor heat exchanger 21 through the gas pipe P6, the gas side valve 11, and the gas pipe P7 flows to the accumulator 9 through the suction pipe P8.
  • the four-way switching valve 4 causes the refrigerant gas discharged from the compressor 2 and passed through the oil separator 3 to flow into the indoor heat via the gas pipe P7, the gas side valve 11, and the gas pipe P7, as indicated by a broken line during heating operation. While flowing to one opening of the exchanger 21, the refrigerant gas from the outdoor heat exchanger 5 is allowed to flow to the accumulator 9 via the gas pipe P2 and the suction pipe P8.
  • the outdoor heat exchanger 5 exchanges heat between the outside air and the refrigerant, functions as a condenser that condenses and liquefies the refrigerant during the cooling operation, and functions as an evaporator that evaporates the refrigerant and gasifies during the heating operation. To do.
  • the outdoor blower 6 is controlled by the control device 10 and sends outside air to the outdoor heat exchanger 5.
  • the outdoor blower 6 is a fan for blowing air, and is configured by, for example, a centrifugal fan or a multiblade fan driven by a DC motor. The amount of air blown from the outdoor blower 6 can be adjusted.
  • the other opening of the outdoor heat exchanger 5 is connected to the other opening of the indoor heat exchanger 21 via the liquid pipe P3, HIC7, liquid pipe P4, liquid side valve 12, liquid pipe P5, and indoor expansion valve 23. ing.
  • the liquid pipe P4 is connected to the suction pipe P8 via the outdoor expansion valve 8, the bypass of the HIC 7, and the branch pipe P9.
  • the outdoor expansion valve 8 is controlled by the control device 10 and controls the amount of refrigerant flowing from the liquid pipe P4 to the branch pipe P9 via the bypass of the HIC7.
  • an expansion valve for example, an electronic expansion valve that can control the opening degree and can control the flow rate with high accuracy is used.
  • the HIC 7 performs heat exchange between the liquid refrigerant flowing in from the liquid pipe P3 and the gas refrigerant flowed to the bypass from the outdoor expansion valve 8, and supercools the liquid refrigerant from the liquid pipe P3 to flow into the liquid pipe P4.
  • the accumulator 9 separates the liquid refrigerant from the gas refrigerant flowing from the suction pipe P8 and the branch pipe P9 to the compressor 2 and stores the liquid refrigerant.
  • Valves 11 and 12 are normally opened, and are closed during maintenance of the air conditioner, for example.
  • Each of the valves 11 and 12 is configured by a valve capable of opening and closing such as a ball valve, an on-off valve, and an operation valve.
  • the indoor heat exchanger 21 exchanges heat between the indoor air and the refrigerant, functions as an evaporator that evaporates and gasifies the liquid refrigerant during the cooling operation, and condenses and liquefies the gas refrigerant during the heating operation. Functions as a condenser.
  • the indoor blower 22 is controlled by the control device 10 and sends indoor air to the indoor heat exchanger 21.
  • the indoor blower 22 is a blower fan, and is constituted by, for example, a centrifugal fan or a multiblade fan driven by a DC motor. The amount of air blown from the indoor blower 22 can be adjusted.
  • the indoor expansion valve 23 is controlled by the control device 10 and expands the liquid refrigerant by reducing the pressure during the cooling operation.
  • an expansion valve for example, an electronic expansion valve that can control the opening degree and can control the flow rate with high accuracy is used.
  • the operation unit 24 includes a plurality of buttons, a plurality of switches, a liquid crystal display device, and the like, and is operated by a user of the air conditioner.
  • the operation unit 24 is used for turning on and off the power supply of the air conditioner, switching between cooling and heating, setting the room temperature, and the like.
  • the content operated by the operation unit 24 is transmitted to the control device 10 as a command signal.
  • this Embodiment 1 demonstrates the case where the number of indoor units 20 is one, this invention is not limited to such a structure. Two or more indoor units 20 may be provided. Furthermore, the capacity
  • refrigerant Any type of refrigerant can be used as the refrigerant.
  • natural refrigerants such as carbon dioxide, hydrocarbons, and helium may be used, or alternative refrigerants that do not contain chlorine such as R410A, R407C, and R404A may be used.
  • the air conditioner which can provide the four-way switching valve 4 and can switch between cooling operation and heating operation is demonstrated, this invention is not limited to this.
  • the present invention is also applicable to an air conditioner that performs only a cooling operation or only a heating operation without providing the four-way switching valve 4.
  • the outdoor unit 1 includes a high pressure sensor (discharge pressure sensor) S1, a low pressure sensor (suction pressure sensor) S2, a discharge temperature sensor S3, an outdoor intake air temperature sensor (outside air temperature sensor) S4, an outdoor unit outlet temperature sensor S5, and a HIC.
  • An outlet temperature sensor S6 and an HIC bypass outlet temperature sensor S7 are provided.
  • the outdoor unit 1 further includes a power sensor S11, a current sensor S12, and a vibration sensor S13.
  • the high-pressure sensor S1 is installed on the discharge side of the compressor 2 (connected to the gas pipe between the oil separator 3 and the four-way switching valve 4 in FIG. 1), and the gas refrigerant discharged from the compressor 2 is The pressure is detected, and a signal SO1 indicating the detected value is output.
  • the low-pressure sensor S2 is installed on the suction port side of the compressor 2 (in FIG. 1, connected to the suction pipe P8 between the four-way switching valve 4 and the accumulator 9), and the gas refrigerant sucked into the compressor 2 The pressure is detected, and a signal SO2 indicating the detected value is output.
  • the discharge temperature sensor S3 is installed on the discharge port side of the compressor 2 (connected to the discharge pipe P1 in FIG. 1), detects the temperature of the gas refrigerant discharged from the compressor 2, and a signal SO3 indicating the detected value. Is output.
  • the condensing temperature of the refrigeration cycle can be obtained by converting the pressure detected by the high pressure sensor S1 into a saturation temperature. By converting the pressure detected by the low pressure sensor S2 into a saturation temperature, the evaporation temperature of the refrigeration cycle can be obtained.
  • the installation positions of the high pressure sensor S1 and the discharge temperature sensor S3 are not limited to the positions shown in FIG. 1, and any of the sections from the discharge port of the compressor 2 to the four-way switching valve 4 can be used.
  • the position may be
  • the installation position of the low-pressure sensor S2 is not limited to the position shown in FIG. 1, and may be any position in the section from the four-way switching valve 4 to the suction port of the compressor 2.
  • the outdoor intake air temperature sensor S4 detects the air temperature taken into the outdoor heat exchanger 5 (that is, the air temperature around the outdoor unit 1), and outputs a signal SO4 indicating the detected value.
  • the outdoor unit outlet temperature sensor S5 is connected to the liquid pipe P3, detects the temperature of the liquid refrigerant flowing from the outdoor heat exchanger 5 to the HIC 7, and outputs a signal SO5 indicating the detected value.
  • the HIC outlet temperature sensor S6 is connected to the liquid pipe P4, detects the temperature of the liquid refrigerant at the outlet of the HIC 7, and outputs a signal SO6 indicating the detected value.
  • the HIC bypass outlet temperature sensor S7 is connected to the branch pipe P9, detects the temperature of the gas refrigerant at the bypass outlet of the HIC 7, and outputs a signal SO7 indicating the detected value.
  • the power sensor S11 detects the power consumption of the compressor 2 and outputs a signal SO11 indicating the detected value.
  • the current sensor S12 detects a secondary current generated by rotation of a motor that drives the compressor 2, and outputs a signal SO12 indicating the detected value.
  • the vibration sensor S13 detects the vibration generated by the compressor 2 and outputs a signal SO13 indicating the detected value.
  • a sound sensor that detects the operation sound of the compressor 2 may be provided instead of or in addition to the vibration sensor S13. The sound sensor outputs a signal indicating the detection value.
  • the indoor unit 20 includes an indoor intake air temperature sensor S8, an indoor liquid piping temperature sensor S9, and an indoor gas piping temperature sensor S10.
  • the indoor intake air temperature sensor S8 detects the air temperature taken into the indoor heat exchanger 21 (that is, the air temperature around the indoor unit 20), and outputs a signal SO8 indicating the detected value.
  • the indoor liquid piping temperature sensor S9 detects the temperature of the liquid refrigerant flowing out of the indoor heat exchanger 21 during the heating operation, and outputs a signal SO9 indicating the detected value.
  • the indoor gas pipe temperature sensor S10 detects the temperature of the gas refrigerant flowing out of the indoor heat exchanger 21 during the cooling operation, and outputs a signal SO10 indicating the detected value.
  • the control device 10 controls the entire air conditioner based on the command signal from the operation unit 24 and the output signals SO1 to SO13 of the sensors S1 to S13.
  • Air conditioner operation Next, the operation of the air conditioner will be described.
  • the high-temperature and high-pressure gas refrigerant compressed by the compressor 2 is discharged from the discharge port of the compressor 2 to the discharge pipe P1.
  • the discharged gas refrigerant passes through the oil separator 3 and then flows to the gas pipe P2 side by the four-way switching valve 4.
  • the gas refrigerant that has passed through the gas pipe P2 is subjected to heat exchange with the outside air sent from the outdoor blower 6 in the outdoor heat exchanger 5 to be condensed and liquefied to be liquid refrigerant.
  • This liquid refrigerant is supercooled by exchanging heat with the gas refrigerant adiabatically expanded by the outdoor expansion valve 8 in the process of passing through the HIC 7 via the liquid pipe P3.
  • the liquid refrigerant supercooled by the HIC 7 flows into the indoor expansion valve 23 through the liquid pipe P4, the liquid side valve 12, and the liquid pipe P5.
  • This liquid refrigerant is adiabatically expanded by the indoor expansion valve 23 and flows into the indoor heat exchanger 21 as a gas-liquid two-phase flow.
  • heat is exchanged between the indoor air circulated by the indoor blower 22 and the refrigerant. Thereby, indoor air is cooled and it uses for indoor air_conditioning
  • the refrigerant gasified in the indoor heat exchanger 21 flows into the suction pipe P8 via the gas pipe P6, the gas side valve 11, the gas pipe P7, and the four-way switching valve 4, and joins the gas refrigerant from the branch pipe P9. , Flows into the accumulator 9. In the accumulator 9, the liquid component contained in the gas refrigerant is separated, only the gas component is sucked into the compressor 2, and the refrigerant is compressed again by the compressor 2. The cooling operation is performed by repeating the above refrigeration cycle.
  • the high-temperature and high-pressure gas refrigerant compressed by the compressor 2 is discharged to the discharge pipe P1.
  • the gas refrigerant that has passed through the oil separator 3 is caused to flow toward the gas pipe P7 by the four-way switching valve 4.
  • the gas refrigerant that has passed through the gas pipe P7 flows into the indoor heat exchanger 21 through the gas side valve 11 and the gas pipe P6.
  • the high-temperature and high-pressure gas refrigerant flowing into the indoor heat exchanger 21 is heat-exchanged with the indoor air circulated by the indoor blower 22 in the indoor heat exchanger 21. Thereby, indoor air is heated and it uses for indoor heating.
  • the liquid refrigerant cooled and condensed by room air flows into the liquid pipe P4 through the indoor expansion valve 23, the liquid pipe P5, and the liquid side valve 12.
  • the opening degree of the indoor expansion valve 23 is controlled so that the degree of supercooling of the refrigerant at the outlet of the indoor heat exchanger 21 functioning as a condenser becomes a constant value.
  • Part of the refrigerant liquid flowing into the liquid pipe P4 is adiabatically expanded by the outdoor expansion valve 8 to become a gas refrigerant, and flows into the accumulator 9 through the bypass of the HIC 7 and the branch pipe P9.
  • the remaining portion of the liquid refrigerant that has flowed into the liquid pipe P4 undergoes heat exchange with the refrigerant adiabatically expanded by the outdoor expansion valve 8 in the process of passing through the HIC 7, and is supercooled, and the outdoor heat exchanger via the liquid pipe P3 5 flows into.
  • the refrigerant absorbs heat from the outside air and is evaporated and vaporized.
  • the refrigerant gas merges with the gas refrigerant from the branch pipe P9 from the outdoor heat exchanger 5 through the gas pipe P2, the four-way switching valve 4, and the suction pipe P8, and flows into the accumulator 9.
  • the liquid component contained in the gas refrigerant is separated and only the gas component is sucked into the compressor 2, and the refrigerant is compressed again by the compressor 2.
  • the heating operation is performed by repeating the above refrigeration cycle.
  • the control device 10 opens the electromagnetic valve V1, passes the high-temperature and high-pressure gas refrigerant discharged from the compressor 2 through the bypass pipe P10 via the electromagnetic valve V1, and performs outdoor heat exchange. Into the vessel 5.
  • the high-temperature and high-pressure gas refrigerant that has flowed into the outdoor heat exchanger 5 exchanges heat with the frost attached to the outdoor heat exchanger 5 to melt the frost.
  • the high-temperature and high-pressure gas refrigerant becomes a low-temperature and low-pressure gas refrigerant, and returns to the compressor 2 via the four-way switching valve 4 and the accumulator 9.
  • the control device can perform the defrosting operation by controlling the four-way switching valve 4 to switch from the heating operation to the cooling operation. . That is, the control device causes the high-temperature and high-pressure gas refrigerant discharged from the compressor 2 to flow into the outdoor heat exchanger 5 via the oil separator 3.
  • the defrosting operation is started as the defrosting operation start determination condition.
  • the defrosting operation is stopped when the temperature of the gas refrigerant flowing from the outdoor heat exchanger 5 to the gas pipe P2 becomes a predetermined value or more.
  • the determination condition for the start and end of the defrosting operation is not limited to this.
  • the defrosting operation is started, and when the detected value exceeds the predetermined value. You may make it complete
  • the defrosting operation may be started when the detection value of the low pressure sensor S2 becomes equal to or less than a predetermined value, and the defrosting operation may be terminated when the detection value exceeds a predetermined value.
  • the deterioration diagnosis of the compressor 2 is executed every time the operation state of the refrigerant circuit is stabilized.
  • this deterioration diagnosis it is determined whether or not the degree of deterioration of the compressor 2 has reached the limit level set by the user.
  • This limit level can be set, for example, to a level that is estimated to make it difficult to ensure desired performance in power consumption or air-conditioning capacity if the compressor 2 is continuously used.
  • a signal indicating the determination result is output.
  • FIG. 2 is a Mollier diagram showing the thermodynamic change of the refrigerant in the operation process of the air conditioner shown in FIG.
  • the refrigerant is compressed from the point A to the point Bs in the compression process, cooled from the point Bs to the point C in the condensation process, depressurized from the point C to the point D in the expansion process, and from the point D to the point A in the evaporation process. Basically, it is heated to circulate through the refrigerant circuit.
  • the degree of deterioration of the compressor 2 is determined using the difference (T1 ⁇ T2) between the temperature T1 of the refrigerant discharged from the compressor 2 and the temperature T2 of the refrigerant sucked into the compressor 2 as a determination index ⁇ . Can do.
  • the time when the compressor 2 is installed is set as a reference time, and the determination index ⁇ of the operation state quantity under a predetermined refrigerant condition is set as the determination reference value ⁇ m.
  • the degree of deterioration of the compressor 2 is determined by comparing the operation state quantity determination index ⁇ under the predetermined refrigerant condition with the determination reference value ⁇ m. .
  • the deterioration of the compressor 2 is natural deterioration or forced deterioration based on the increase amount ⁇ of the determination index ⁇ .
  • the “increase amount ⁇ of the determination index ⁇ ” means the increase amount of the determination index ⁇ with respect to the initial value (or the minimum value) of the determination index ⁇ during the period in which the operation state of the refrigerant circuit is stable.
  • the increase amount ⁇ is given by the difference between the initial value of the determination index ⁇ and the current value of the determination index ⁇ .
  • natural degradation means a decrease in performance of a device that occurs when the device is continuously used for a specified service life under specified operating conditions or use conditions.
  • forced degradation means a reduction in the performance of the device over natural degradation caused by some reason within the specified lifetime. The above-mentioned poor lubrication of the sliding portion in the compressor 2 causes forced deterioration of the compressor 2.
  • the control pattern of the refrigerant circuit is changed so as to suppress the progress of deterioration of the compressor 2. Specifically, the control pattern of the refrigerant circuit is changed so as to prevent the occurrence of liquid refrigerant suction (liquid back) into the compressor 2.
  • FIG. 3 is a block diagram showing a configuration of the control device 10 shown in FIG.
  • the control device 10 includes an operation state quantity generation unit 31, a calculation unit 32, a storage unit 33, a determination unit 34, a forced deterioration detection unit 35, a control pattern selection unit 36, a control pattern storage unit 37, and A control unit 38 is included.
  • the operation state quantity generation unit 31 reads the output signals SO1 to SO13 of the sensors S1 to S13 shown in FIG. 1 and the frequency command value Fc for instructing the operation frequency of the compressor 2 at regular intervals.
  • the frequency command value Fc is a value generated in the control unit 38 based on the output signals SO1 to SO13 of the sensors S1 to S13.
  • the operation state quantity generation unit 31 generates an operation state quantity of the refrigerant circuit based on the read output signals SO1 to SO13 and the frequency command value Fc of the sensors S1 to S13.
  • the operating state quantity includes first information for determining whether or not the refrigerant circuit is in a stable state (for example, the operating frequency of the compressor 2, the condensing temperature of the refrigerant, the evaporating temperature of the refrigerant), and the 2nd information (for example, the temperature T1 of the refrigerant
  • the condensation temperature and the evaporation temperature of the refrigerant may be temperatures detected by the temperature sensors S3 to S10, or may be temperatures estimated from the detected values of the pressure sensors S1 and S2 and the temperature sensors S3 to S10.
  • the refrigerant condensing temperature and evaporating temperature during cooling operation are detected by temperature sensors S5 and S8, respectively.
  • the calculation unit 32 determines whether or not the operation state of the refrigerant circuit is stable based on the first information generated by the operation state amount generation unit 31. For example, the operation unit 32 has a value within a certain range of the operating frequency of the compressor 2 for a certain time or more, the refrigerant condensation temperature is within 40 ° C. ⁇ 1 ° C., and the refrigerant evaporation temperature is 0 ° C. ⁇ 1 It is determined that the operating state of the refrigerant circuit is stable when the temperature falls within the temperature.
  • the calculation unit 32 is based on the operation state amount generated by the operation state amount generation unit 31 during the stable period when the operation state of the refrigerant circuit is stable, and the individual difference correction value A1, the outside air temperature correction value A2, the determination index. ⁇ and the determination reference value ⁇ m are calculated at a constant cycle and stored in the storage unit 33.
  • the individual difference correction value A ⁇ b> 1 is a value calculated based on the operation state amount collected in the initial operation immediately after the air conditioner is installed on the site and the standard data stored in the storage unit 33 in advance. It is. That is, in the storage unit 33, a standard air conditioner is installed in a standard building, and a result (standard data) obtained by examining the relationship between the outside air temperature, the room temperature, and the operation state quantity is, for example, a table format. Is stored in. Since there is an individual difference between an air conditioner actually installed on the site and a standard air conditioner, an individual difference correction value A1 for correcting the individual difference is calculated. The individual difference correction value A1 is stored in the storage unit 33.
  • the outside air temperature correction value A2 is used to correct the influence of the temperature difference when the outside air temperature at which the standard data is detected is different from the current outside air temperature.
  • the outside air temperature correction value A2 is stored in the storage unit 33 and updated every time the deterioration diagnosis is performed.
  • the determination index ⁇ is calculated at a constant cycle based on the operation state quantity generated by the operation state quantity generation unit 31 during the stable period in which the operation state of the refrigerant circuit is stable.
  • the determination index ⁇ is used as a value for quantitatively evaluating the degree of deterioration of the current compressor 2.
  • the determination index ⁇ is, for example, a temperature difference (T1 ⁇ T2) between the temperature T1 of the refrigerant discharged from the compressor 2 and the temperature T2 of the refrigerant sucked into the compressor 2.
  • the temperature T1 is, for example, a temperature detected by the temperature sensor S3.
  • the temperature T2 may be a temperature estimated based on a temperature sensor (for example, a temperature sensor S7) provided in a refrigerant circuit on the low pressure side of the compressor 2, or based on the temperature T1 and a detection value of the low pressure sensor S2.
  • the temperature estimated from the evaporation temperature obtained in this way may be used.
  • the determination index ⁇ is stored in the storage unit 33.
  • the determination reference value ⁇ m is a reference value to be compared with the determination index ⁇ .
  • the calculation unit 32 obtains a determination reference value ⁇ m (for example, T1-T2) based on the standard data stored in the storage unit 33.
  • the calculation unit 32 further corrects the determination reference value ⁇ m based on the individual difference correction value A1 and the outside air temperature correction value A2 stored in the storage unit 33, and stores the corrected determination reference value ⁇ m in the storage unit 33. As a result, it is possible to generate the determination reference value ⁇ m that matches the actual condition of the air conditioner installed at the site.
  • the determination unit 34 When D ⁇ Ds, the determination unit 34 maintains the deterioration detection signal ⁇ X at the L (logic low) level of the inactivation level, and when D> Ds, the determination unit 34 sets the deterioration detection signal ⁇ X at the activation level H ( (Logic high) level.
  • H (Logic high) level.
  • a notification device may be provided for notifying that the compressor 2 has deteriorated due to lamp light, buzzer sound, characters on the liquid crystal display device, or the like. The operation may be stopped.
  • the determination index ⁇ read from the storage unit 33 by the determination unit 34 is also given to the forced deterioration detection unit 35.
  • the forced deterioration detection unit 35 maintains the forced deterioration detection signal ⁇ Y at the L level of the inactivation level when ⁇ ⁇ ⁇ TH, and the forced deterioration detection signal ⁇ Y at the H level of the activation level when ⁇ > ⁇ TH.
  • the forced deterioration detection signal ⁇ Y is set to the H level, it can be determined that the forced deterioration of the compressor 2 has occurred.
  • a notification device may be provided for notifying that the forced deterioration of the compressor 2 has been detected by lamp light, buzzer sound, characters of the liquid crystal display device, or the like.
  • the forced deterioration detection signal ⁇ Y is given to the control pattern selection unit 36 and the control unit 38.
  • the control pattern storage unit 37 stores a plurality of control patterns.
  • the control pattern includes the opening time of the electromagnetic valve V1 during the defrosting operation, the change rate of the operating frequency of the compressor 2, the speed at which the opening of the indoor expansion valve 23 changes, and the like.
  • the control pattern selection unit 36 selects an appropriate control pattern based on the detection results of the sensors S1 to S10 and gives the control unit 38 when the air conditioner is actually installed in the building.
  • the control pattern selection unit 36 selects a control pattern that can prevent the occurrence of liquid back from the current control pattern and supplies the control pattern to the control unit 38.
  • control pattern capable of preventing the occurrence of liquid back refers to the refrigerant in the operation state of the refrigerant circuit in which liquid back is likely to occur (when the air-conditioning load fluctuates rapidly, when the compressor 2 is started, etc.). This pattern is aimed at controlling the circuit. By changing the control pattern in the operation state in which liquid back is likely to occur, the occurrence of liquid back can be effectively prevented.
  • an air-conditioning load fluctuates rapidly when an air conditioner returns from a defrost operation to heating operation, when changing the number of operation
  • the control unit 38 Based on the output signals SO1 to SO13 of the sensors S1 to S13, the command signal from the operation unit 24, the forced deterioration detection signal ⁇ Y, the control pattern from the control pattern selection unit 36, etc., the control unit 38 Switch valve 4, compressor 2, expansion valves 8 and 23, blowers 6 and 22, etc.).
  • the control unit 38 includes an inverter that drives the motor of the compressor 2.
  • FIG. 5 is a flowchart showing the operation of the control device 10.
  • control device 10 (operation state quantity generation unit 31) takes in the operation data of the air conditioner and generates an operation state quantity based on the acquired operation data.
  • the operation data includes output signals SO1 to SO13 of the sensors S1 to S13 and a frequency command value Fc for instructing the operation frequency of the compressor 2.
  • the operating state quantity includes first information for determining whether or not the refrigerant circuit is in a stable state, and second information used in the deterioration diagnosis of the compressor 2.
  • step ST2 the control device 10 (arithmetic unit 32) determines whether or not the refrigerant circuit is in a stable state based on the first information in the operation state quantity, and if not, returns to step ST1. In the stable state, the process proceeds to step ST3.
  • step ST3 the control device 10 (calculation unit 32) calculates the individual difference correction value A1 and the outside air temperature correction value A2 based on the operation state quantity generated by the operation state quantity generation unit 31.
  • step ST4 the control device 10 (calculation unit 32) calculates a determination index ⁇ .
  • the determination index ⁇ is a temperature difference (T1 ⁇ T2) between the temperature T1 of the refrigerant discharged from the compressor 2 and the temperature T2 of the refrigerant sucked into the compressor 2.
  • step ST5 the control device 10 (calculating unit 32) generates the determination reference value ⁇ m based on the standard data stored in the storage unit 33, the individual difference correction value A1, and the outside air temperature correction value A2.
  • the deterioration detection signal ⁇ X is set to H level in step ST7 to notify that the degree of deterioration of the compressor 2 has reached the limit level. Thereby, the compressor 2 can be repaired and replaced with a new one.
  • step ST8 the control device 10 (forced deterioration detection unit 35) determines whether or not the increase amount ⁇ of the determination index ⁇ in the stable period exceeds the threshold value ⁇ TH. If ⁇ > ⁇ TH is not satisfied, the process returns to step ST1, and if ⁇ > ⁇ TH, the forced deterioration detection signal ⁇ Y is set to H level and the process proceeds to step ST9.
  • step ST9 the control device 10 (the control unit 38) determines that the forced deterioration has occurred in the compressor 2 when it receives the H level forced deterioration detection signal ⁇ Y.
  • the control device 10 the control unit 38
  • the operation frequency of the compressor 2 is temporarily set. Reduce. At this time, the compressor 2 may be stopped.
  • step ST11 the control device 10 (control pattern selection unit 36) selects a control pattern that can prevent the occurrence of liquid back from the current control pattern, and gives the control pattern to the control unit 38.
  • the control unit 38 controls the refrigerant circuit according to the new control pattern given from the control pattern selection unit 36.
  • step ST12 the control device 10 (the control unit 38) notifies that the compressor 2 has undergone forced deterioration. Specifically, the control device 10 (control unit 38) causes the liquid crystal display device of the operation unit 24 to display a message recommending that the compressor 2 be repaired or replaced with a new one. Or the control apparatus 10 (control part 38) notifies a service center automatically using a communication means.
  • FIG. 6 is a flowchart showing a first mode of changing the control pattern in step ST11 of FIG.
  • control device 10 determines whether or not forced deterioration of compressor 2 has been detected based on forced deterioration detection signal ⁇ Y.
  • the control pattern selection unit 36 determines in step ST21 that the opening time of the electromagnetic valve V1 during the defrosting operation is appropriate based on the detection results of the sensors S1 to S10.
  • the control pattern is selected and given to the control unit 38. Thereby, the control part 38 performs a defrost operation according to the present control pattern.
  • step ST22 the control pattern selection unit 36 has a control pattern in which the opening time of the solenoid valve V1 during the defrosting operation is shorter than the current control pattern. Select and give to the control unit 38. Thereby, the control unit 38 performs the defrosting operation according to the new control pattern given from the control pattern selection unit 36.
  • the new control pattern for example, increases the outdoor air temperature (the air temperature taken into the outdoor heat exchanger 5), which is a condition for determining the start of the defrosting operation, higher than the current control pattern. Thereby, the start timing of a defrost operation is delayed rather than the present control pattern. Or the temperature of the gas refrigerant which flows into the gas piping P2 from the outdoor heat exchanger 5 used as the completion
  • a high-temperature gas refrigerant flows into the outdoor heat exchanger 5 from the bypass pipe P10 and proceeds while melting the frost, but the refrigerant condensed and liquefied by melting the frost is transferred to the outdoor heat exchanger 5. It becomes easy to collect.
  • the liquid refrigerant may return to the compressor 2.
  • Embodiment 2 FIG. In the second embodiment, another method for diagnosing deterioration of the compressor 2 will be described.
  • FIG. 7 is a diagram illustrating a determination index ⁇ used for deterioration diagnosis of the compressor 2 in the air conditioner according to the second embodiment of the present invention.
  • a plurality of determination indices ⁇ are used in the deterioration diagnosis of compressor 2 according to the second embodiment.
  • Each determination index ⁇ is calculated at a constant period based on the operation state quantity generated by the operation state quantity generation unit 31 during the stable period in which the operation state of the refrigerant circuit is stable.
  • the operating state quantity is, as second information used in the deterioration diagnosis of the compressor 2, the temperature T1 of the refrigerant discharged from the compressor 2, the temperature T2 of the refrigerant sucked into the compressor 2, and the power consumption of the compressor 2.
  • the secondary current generated in the rotor of the motor that drives the compressor 2 and the vibration (or operation sound) generated by the compressor 2 are included.
  • the power consumption of the compressor 2 is, for example, the power detected by the power sensor S11.
  • the secondary current of the compressor 2 is, for example, a current detected by the current sensor S1.
  • the vibration of the compressor 2 is, for example, vibration detected by the vibration sensor S13.
  • the operation sound of the compressor 2 is a signal detected by a sound sensor, for example.
  • the power consumption and secondary current of the compressor 2 may be values detected by the sensors S11 and S12, or may be values estimated from the detection values of the other sensors S1 to S10.
  • the calculation unit 32 is configured to calculate the individual difference correction value A1, the outside air temperature correction value A2, a plurality of values based on the operation state amount generated by the operation state amount generation unit 31 during the stable period in which the operation state of the refrigerant circuit is stable.
  • the determination index ⁇ and the plurality of determination index reference values ⁇ m are calculated at a constant period and stored in the storage unit 33.
  • the plurality of determination indexes ⁇ are the temperature difference (T1 ⁇ T2) between the temperature T1 of the refrigerant discharged from the compressor 2 and the temperature T2 of the refrigerant sucked into the compressor 2, the power consumption of the compressor 2, and the compression
  • the secondary current of the machine 2 and the vibration (or operation sound) of the compressor 2 are included.
  • the calculating unit 32 calculates a plurality of determination reference values ⁇ m corresponding to the plurality of determination indexes ⁇ , respectively. Specifically, the calculation unit 32 obtains the determination reference value ⁇ m based on the standard data stored in the storage unit 33 for each determination index ⁇ , and the individual difference correction value A1 and the outside air temperature stored in the storage unit 33. The determination reference value ⁇ m is corrected based on the correction value A2, and then stored in the storage unit 33. As a result, for each determination index ⁇ , a determination reference value ⁇ m that matches the actual condition of the air conditioner installed at the site can be generated.
  • each determination index ⁇ increases as the degree of wear of the internal mechanism of the compressor 2 increases. Therefore, when the difference D between any determination index ⁇ and the determination reference value ⁇ m exceeds the limit value Ds, it can be determined that the degree of deterioration of the compressor 2 has reached the limit level.
  • the determination unit 34 maintains the deterioration detection signal ⁇ X at the L level when D> Ds is not satisfied in all the determination indexes ⁇ , and sets the deterioration detection signal ⁇ X at the H level when D> Ds in any of the determination indexes ⁇ . To do.
  • the plurality of determination indexes ⁇ read from the storage unit 33 by the determination unit 34 are also given to the forced deterioration detection unit 35.
  • the forced deterioration detection unit 35 determines whether or not each of the plurality of determination indexes ⁇ is increased during a stable period in which the operation state of the refrigerant circuit is stable.
  • the forced deterioration detection unit 35 calculates, for each determination index ⁇ , an increase amount ⁇ that is the difference between the initial value (or minimum value) of the determination index ⁇ and the current value during the stable period.
  • the amount of increase ⁇ is the amount of increase ⁇ 1 in temperature difference (T1 ⁇ T2), the amount of increase in power consumption ⁇ 2 of the compressor 2, the amount of increase in secondary current ⁇ 3 of the compressor 2, and the vibration (or operating noise) of the compressor 2.
  • Increase amount ⁇ 4 determines whether or not each of the plurality of determination indexes ⁇ is increased by comparing the plurality of increase amounts ⁇ 1 to ⁇ 4 with the plurality of threshold values ⁇ TH1 to ⁇ TH4, respectively.
  • FIG. 8 is a flowchart illustrating a method for detecting forced deterioration of the compressor 2 executed by the control device for the air conditioner according to the second embodiment.
  • control device 10 forced deterioration detection unit 35 determines whether or not the increase amount ⁇ 1 of determination index ⁇ (T1-T2) in the stable period exceeds threshold value ⁇ TH1. If ⁇ 1> ⁇ TH1, the process proceeds to step ST82, and if ⁇ 1> ⁇ TH1, the forced deterioration detection signal ⁇ Y is set to H level and the process proceeds to step ST9.
  • step ST9 the control device 10 (the control unit 38) determines that the forced deterioration has occurred in the compressor 2 when it receives the H level forced deterioration detection signal ⁇ Y.
  • the control unit 38 suspects that the compressor 2 is poorly lubricated, so that the operating frequency of the compressor 2 is once lowered to protect the compressor 2. At this time, the compressor 2 may be stopped.
  • control device 10 control pattern selection unit 36
  • the control unit 38 controls the refrigerant circuit according to the new control pattern given from the control pattern selection unit 36.
  • step ST82 the forced deterioration detection unit 35 determines whether or not the increase amount ⁇ 2 of the determination index ⁇ (power consumption of the compressor 2) exceeds the threshold value ⁇ TH2. If ⁇ 2> ⁇ TH2, the process proceeds to ST83, and if ⁇ 2> ⁇ TH2, the forced deterioration detection signal ⁇ Y is set to H level and the process proceeds to step ST9.
  • step ST82 the forced deterioration detection unit 35 determines in step ST83 whether the increase ⁇ 3 of the determination index ⁇ (secondary current of the compressor 2) exceeds the threshold value ⁇ TH3. If ⁇ 3> ⁇ TH3 is not satisfied, the process proceeds to ST84. If ⁇ 3> ⁇ TH3, the forced deterioration detection signal ⁇ Y is set to the H level, and the process proceeds to step ST9.
  • step ST84 the forced deterioration detecting unit 35 determines whether or not the increase amount ⁇ 4 of the determination index ⁇ (vibration or operating sound of the compressor 2) exceeds the threshold value ⁇ TH4.
  • the process proceeds to ST85, and it is determined that the compressor 2 is naturally deteriorated.
  • the forced deterioration detection signal ⁇ Y is set to H level, and the process proceeds to step ST9.
  • a plurality of determination indexes ⁇ are calculated at a constant period during a stable period in which the operation state of the refrigerant circuit is stable, and the determination index ⁇ in the stable period is calculated in any of the plurality of determination indexes ⁇ .
  • Embodiment 3 In the third to sixth embodiments, another aspect of changing the control pattern of the compressor 2 (step ST11 in FIG. 5) performed by the air conditioner control device 10 according to the present embodiment will be described.
  • FIG. 9 is a diagram showing the configuration of the air conditioner according to the third embodiment of the present invention, and is a diagram contrasted with FIG. Referring to FIG. 9, the air conditioner according to the third embodiment is different from the air conditioner shown in FIG. 1 in that outdoor unit 1 includes heater 25.
  • the temperature of the compressor 2 is lowered, and therefore, a phenomenon that the refrigerant becomes a liquid state and accumulates in the compressor 2 (refrigerant stagnation) may occur.
  • the compressor 2 is started in a state where the refrigerant stagnation occurs, the liquid refrigerant may be sucked into the compressor 2 to cause liquid compression. Further, when a large amount of refrigerant is dissolved in the lubricating oil in the compressor 2, the lubricating oil is diluted and the viscosity is lowered. If the compressor 2 is started in a state where the viscosity of the lubricating oil is low, poor lubrication of the sliding portion in the compressor 2 may occur, and the compressor 2 may be damaged.
  • the heater 2 is provided in the compressor 2, and the compressor 2 is heated by energizing the heater 25.
  • the liquid refrigerant is heated and vaporized, so that the refrigerant stagnation is prevented.
  • the control pattern of the refrigerant circuit is changed so as to prevent refrigerant stagnation.
  • FIG. 10 is a flowchart showing a second mode of changing the control pattern in step ST11 of FIG.
  • control device 10 determines whether or not forced deterioration of compressor 2 has been detected based on forced deterioration detection signal ⁇ Y.
  • the control pattern selection unit 36 performs compression in the period in which the compressor 2 is stopped based on the detection results of the sensors S1 to S10 in step ST23.
  • a control pattern suitable for heating the compressor 2 is selected and given to the control unit 38.
  • the control unit 38 energizes the heater 25 according to the current control pattern before starting the stopped compressor 2.
  • step ST24 the control pattern selection unit 36 selects a control pattern that increases the energization power amount of the heater 25 from the current control pattern and selects the control unit. 38.
  • the control unit 38 energizes the heater 25 in accordance with the new control pattern given from the control pattern selection unit 36 before starting the stopped compressor 2.
  • the new control pattern is a pattern for increasing the energization power amount of the heater 25 than the current control pattern. Specifically, the new control pattern extends the energization time of the heater 25. Alternatively, the new control pattern increases the energization power of the heater 25. Or a new control pattern expands the range of the outdoor air temperature (air temperature taken in by the outdoor heat exchanger 5) which energizes the heater 25. FIG.
  • the refrigerant stagnation can be prevented by increasing the amount of electric power supplied to the heater 25 before starting the compressor 2 according to the new control pattern. Thereby, since liquid compression and the lubrication failure of the sliding part in the compressor 2 can be prevented, the progress of deterioration of the compressor 2 can be suppressed.
  • FIG. 11 is a flowchart showing a third mode of changing the control pattern in step ST11 of FIG.
  • control device 10 determines whether or not forced deterioration of compressor 2 has been detected based on forced deterioration detection signal ⁇ Y.
  • the control pattern selection unit 36 determines the increase rate of the operating frequency when starting the compressor 2 based on the detection results of the sensors S1 to S10 in step ST25.
  • An appropriate control pattern is selected and given to the control unit 38. Thereby, the control part 38 raises an operating frequency at the time of starting of the compressor 2 according to the present control pattern.
  • step ST26 the control pattern selection unit 36 selects a control pattern in which the increase rate of the operating frequency of the compressor 2 is smaller than the current control pattern. This is given to the control unit 38.
  • the control unit 38 increases the operating frequency of the compressor 2 when the compressor 2 is started according to the new control pattern given from the control pattern selection unit 36.
  • the new control pattern is a pattern that makes the increase in operating frequency more gradual when the compressor 2 starts than the current control pattern.
  • FIG. 12 is a flowchart showing a fourth mode of control pattern change in step ST11 of FIG.
  • control device 10 determines whether or not forced deterioration of compressor 2 has been detected based on forced deterioration detection signal ⁇ Y. If the forced deterioration of the compressor 2 is not detected in step ST20, the control pattern selection unit 36 in step ST27 is appropriate for restraint energization of the stopped compressor driving motor based on the detection results of the sensors S1 to S10. The control pattern is selected and given to the control unit 38.
  • Restraint energization refers to the application of a low voltage to the compressor driving motor that generates heat in the motor windings but does not rotate the compressor. By using the heat generated by the motor windings to heat the liquid refrigerant accumulated in the compressor 2, it is possible to eliminate the stagnation of the refrigerant.
  • the controller 38 energizes the stopped compressor driving motor in accordance with the current control pattern.
  • step ST28 the control pattern selection unit 36 selects a control pattern whose energization timing to the compressor driving motor is earlier than the current control pattern. This is given to the control unit 38.
  • the control unit 38 energizes the stopped compressor driving motor in accordance with the new control pattern given from the control pattern selection unit 36.
  • the new control pattern is a pattern that extends the time for energizing the compressor drive motor compared to the current control pattern.
  • FIG. 13 is a diagram showing a configuration of an air conditioner according to Embodiment 6 of the present invention, and is compared with FIG. Referring to FIG. 13, the air conditioner according to the sixth embodiment is a multi-type air conditioner including a plurality of indoor units 20_1 to 20_n (where n is an integer of 2 or more).
  • Each of the indoor units 20_1 to 20_n has the same configuration as the indoor unit 20 shown in FIG. In order to simplify the drawings and description, the illustration of a large number of sensors distributed in the refrigerant circuit is omitted.
  • the control device 10 Based on the command signal from the operation unit 24 of the indoor units 20_1 to 20_n and the output signal of the sensor, the control device 10 sets the room temperature of the n rooms in which the indoor units 20_1 to 20_n are respectively set to the set temperature. Thus, the entire air conditioner is controlled.
  • the air conditioning load of the room in which each indoor unit is installed is usually detected, and the operating frequency of the compressor 2 is controlled in accordance with the detected total air conditioning load. Thereby, the optimal air-conditioning capability corresponding to the sum total of an air-conditioning load is obtained.
  • an expansion valve 23 (electronic expansion valve) is provided in the refrigerant pipe connected to each indoor unit, and each expansion valve is adjusted so that the degree of superheat of the refrigerant in each indoor heat exchanger converges to a constant value. The opening degree of 23 is controlled.
  • the amount of refrigerant diverted from the outdoor unit 1 to each indoor unit is controlled so as to be in an optimum state for each evaporator by the superheat control.
  • the amount of refrigerant that is diverted from the outdoor unit 1 to each indoor heat exchanger may change temporarily during the transition period. For example, by stopping the operation of one indoor unit, the refrigerant flow rate of the indoor heat exchanger 21 may increase rapidly in a different indoor unit being operated, and the refrigerant flow rate may temporarily become excessive. . In this indoor unit, the superheat control cannot catch up with the increase in the refrigerant flow rate, and liquid back may occur.
  • the operating frequency of the compressor 2 when it is determined that forced deterioration has occurred in the compressor 2, when switching the number of operating indoor units, the operating frequency of the compressor 2 is changed. Reduce the rate of change. By reducing the change rate of the operating frequency of the compressor 2, the change in the refrigerant flow rate of each indoor heat exchanger 21 is moderated during the transition period when the number of operating indoor units is switched. Thereby, since it is suppressed that the refrigerant
  • FIG. 14 is a flowchart showing a fifth mode of control pattern change in step ST11 of FIG.
  • control device 10 determines whether or not forced deterioration of compressor 2 has been detected based on forced deterioration detection signal ⁇ Y.
  • the control pattern selection unit 36 controls the change rate of the operation frequency of the compressor 2 appropriately based on the detection results of the sensors S1 to S10 in step ST27.
  • a pattern is selected and given to the control unit 38.
  • the control unit 38 switches the number of indoor units operated according to the current control pattern.
  • step ST28 the control pattern selection unit 36 selects a control pattern that makes the change rate of the operating frequency of the compressor 2 smaller than the current control pattern. To the control unit 38. As a result, the control unit 38 switches the number of indoor units operated according to the new control pattern given from the control pattern selection unit 36.
  • the indoor expansion is performed. It is good also as a structure which makes the speed of the change of the opening degree of the valve 23 slow.
  • the indoor expansion valve 23 in the indoor unit When stopping the indoor unit in operation, the indoor expansion valve 23 in the indoor unit is closed. On the other hand, when operating a stopped indoor unit, the opening of the indoor expansion valve 23 in the indoor unit is increased. In any case, if the opening degree of the indoor expansion valve 23 is suddenly changed, the amount of the refrigerant that is diverted from the outdoor unit 1 to each indoor heat exchanger changes abruptly, which may cause liquid back.
  • the opening degree of the indoor expansion valve 23 is changed when the number of operating indoor units is switched. Slow down the rate of change.
  • the change in the refrigerant flow rate of each indoor heat exchanger 21 is moderated in the transitional period when the number of operating indoor units is switched.
  • FIG. 15 is a flowchart showing a sixth mode of control pattern change in step ST11 of FIG.
  • control device 10 determines whether or not forced deterioration of compressor 2 has been detected based on forced deterioration detection signal ⁇ Y.
  • the control pattern selection unit 36 changes the opening of the indoor expansion valve 23 of each indoor unit based on the detection results of the sensors S1 to S10.
  • a control pattern with an appropriate speed is selected and given to the control unit 38.
  • the control unit 38 switches the number of indoor units operated according to the new control pattern given from the control pattern selection unit 36.
  • step ST29 the control pattern selection unit 36 sets a control pattern that makes the change rate of the opening of the indoor expansion valve 23 slower than the current control pattern. Select and give to the control unit 38. As a result, the control unit 38 switches the number of indoor units operated according to the new control pattern given from the control pattern selection unit 36.
  • FIG. FIG. 16 is a diagram showing the configuration of the air conditioner according to the seventh embodiment of the present invention, and is compared with FIG. Referring to FIG. 16, the air conditioner according to the seventh embodiment includes an outdoor device 41 and a plurality (three in FIG. 16) of indoor units 20A to 20C.
  • the outdoor device 41 includes a plurality (two in FIG. 16) of outdoor units 1A and 1B.
  • Each of the indoor units 20A to 20C has the same configuration as the indoor unit 20 shown in FIG.
  • Each of the outdoor units 1A and 1B has the same configuration as the outdoor unit 1 shown in FIG.
  • a common control device 42 is provided in the outdoor units 1A and 1B.
  • the outdoor units 1A and 1B include compressors 2a and 2b, respectively. For simplification of the drawings and description, illustration of a large number of sensors S1 to Sn (where n is an integer of 2 or more) distributed in the refrigerant circuit is omitted.
  • the gas pipe P7 of the outdoor units 1A and 1B is connected to one opening of each indoor heat exchanger 21 of each of the indoor units 20A to 20C via the gas pipe P6.
  • Gas side valves 11 are provided at a plurality of locations of the gas pipe P6.
  • the liquid piping P3 of the outdoor units 1A and 1B is connected to the indoor expansion valve 23 of each of the indoor units 20A to 20C via the liquid piping P5.
  • Liquid side valves 12 are provided at a plurality of locations of the liquid pipe P5.
  • the control device 42 can detect the indoor temperatures of the three rooms in which the indoor units 20A to 20C are respectively arranged.
  • the entire air conditioner is controlled so that each of the temperature reaches a set temperature.
  • FIG. 17 is a block diagram illustrating a configuration of the control device 42, and is a diagram to be compared with FIG.
  • the control device 42 has the same configuration as the control device 10, and includes an operation state quantity generation unit 51, a calculation unit 52, a storage unit 53, a determination unit 54, a forced deterioration detection unit 55, and a control pattern selection. Part 56, control pattern storage part 57, and control part 58.
  • the operation state quantity generation unit 51 takes in the operation data of the air conditioner at a constant cycle, and generates the operation state quantity based on the acquired operation data.
  • the operation data includes output signals SO1 to SOn of the sensors S1 to Sn, Each includes frequency command values Fca and Fcb that command operating frequencies of the two compressors 2a and 2b.
  • the operation state quantity includes first information for determining whether or not the refrigerant circuit is in a stable state, and second information used in the deterioration diagnosis of each of the two compressors 2a and 2b.
  • the frequency command values Fca and Fcb are generated in the control unit 58.
  • the calculation unit 52 determines whether or not the refrigerant circuit is in a stable state based on the first information in the operation state.
  • the calculation unit 52 compresses the individual difference correction value A1 and the outside air temperature correction value A2 into two compressions based on the operation state amount generated by the operation state amount generation unit 51 each time the refrigerant circuit becomes stable.
  • Two determination indexes ⁇ a and ⁇ b corresponding to the machines 2a and 2b are calculated at a constant period.
  • the determination index ⁇ a is, for example, a temperature difference T1a-T2a between the temperature T1a of the refrigerant discharged from the compressor 2a and the temperature T2a of the refrigerant sucked into the compressor 2a.
  • the determination index ⁇ b is, for example, a temperature difference T1b ⁇ T2b between the temperature T1b of the refrigerant discharged from the compressor 2b and the temperature T2b of the refrigerant sucked into the compressor 2b.
  • the calculation unit 52 uses two determination reference values ⁇ ma corresponding to the two compressors 2a and 2b based on the standard data stored in the storage unit 53, the individual difference correction value A1, and the outside air temperature correction value A2. , ⁇ mb.
  • the calculated individual difference correction value A1, outside air temperature correction value A2, determination indices ⁇ a and ⁇ b, and determination reference values ⁇ ma and ⁇ mb are written in the storage unit 53.
  • Determination indexes ⁇ a and ⁇ b and determination reference values ⁇ ma and ⁇ mb written in the storage unit 53 are given to the determination unit 54, and determination indexes ⁇ a and ⁇ b written in the storage unit 53 are given to the forced deterioration detection unit 55.
  • the forced deterioration detection unit 55 determines whether or not the increase amount ⁇ a of the determination index ⁇ a exceeds the threshold value ⁇ THa while the determination unit 54 determines whether or not the compressor 2a has deteriorated, and ⁇ a> In the case of ⁇ THa, the forced deterioration detection signal ⁇ Ya is set to H level to notify that the compressor 2a has undergone forced deterioration.
  • the forced deterioration detection unit 55 determines whether or not the increase amount ⁇ b of the determination index ⁇ b exceeds the threshold value ⁇ THb while the determination unit 54 determines whether or not the compressor 2b is deteriorated, and ⁇ b> In the case of ⁇ THb, the forced deterioration detection signal ⁇ Yb is set to H level to notify that the compressor 2b has undergone forced deterioration.
  • the control unit 58 When the forced deterioration detection signal ⁇ Ya is set to the H level, the control unit 58 temporarily reduces the operating frequency of the compressor 2a in order to protect the compressor 2a.
  • the control pattern selection unit 56 selects a control pattern that can prevent the occurrence of liquid back in the compressor 2a, rather than the current control pattern, and controls the control unit 38. To give.
  • the control pattern selection unit 56 selects, for example, a control pattern that shortens the opening time of the electromagnetic valve V1 of the outdoor unit 1A during the defrosting operation and gives it to the control unit 38, compared to the current control pattern.
  • the control unit 58 When the forced deterioration detection signal ⁇ Yb is set to the H level, the control unit 58 temporarily reduces the operating frequency of the compressor 2b in order to protect the compressor 2b.
  • the control pattern selection unit 56 selects a control pattern that can prevent the occurrence of liquid back in the compressor 2b, rather than the current control pattern, and controls the control unit 38. To give.
  • the control pattern selection unit 56 selects a control pattern that shortens the opening time of the electromagnetic valve V1 of the outdoor unit 1B during the defrosting operation and provides the control unit 38 with the control pattern 38, for example.
  • the forced deterioration detection method according to the second embodiment and the control pattern changing method according to the third to sixth embodiments are also applicable to the air conditioner according to the seventh embodiment.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Air Conditioning Control Device (AREA)

Abstract

Le circuit de fluide frigorigène de ce climatiseur comprend un compresseur (2), un échangeur de chaleur extérieur (5), une soupape de détente (23), et un échangeur de chaleur intérieur (21), et fait circuler un fluide frigorigène à travers celui-ci. Le dispositif de commande (10) du circuit de fluide frigorigène calcule un indice à utiliser pour déterminer la détérioration du compresseur (2) sur la base d'une quantité d'état de fonctionnement montrant l'état de fonctionnement du circuit de fluide frigorigène. Le dispositif de commande (10) détecte la détérioration de force du compresseur (2) lorsque la différence entre la valeur initiale et la valeur actuelle de l'indice dans une période de temps stable pendant laquelle l'état de fonctionnement du circuit de fluide frigorigène est stable dépasse une valeur de seuil. Le dispositif de commande (10) commande le circuit de fluide frigorigène de telle sorte que le fluide frigorigène liquide ne peut pas être aspiré dans le compresseur (2).
PCT/JP2016/080649 2016-10-17 2016-10-17 Climatiseur WO2018073855A1 (fr)

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JPWO2021095237A1 (fr) * 2019-11-15 2021-05-20
CN112984881A (zh) * 2021-03-05 2021-06-18 四川长虹空调有限公司 制冷系统压缩机的回液判断方法及系统
JPWO2021186670A1 (fr) * 2020-03-19 2021-09-23
WO2022064989A1 (fr) * 2020-09-25 2022-03-31 住友重機械工業株式会社 Congélateur à ultra-basse température, et procédé de surveillance de congélateur à ultra-basse température
CN114543185A (zh) * 2022-02-16 2022-05-27 青岛海信日立空调系统有限公司 一种空调系统
CN115135880A (zh) * 2020-02-26 2022-09-30 三菱电机株式会社 电力转换装置
WO2023112831A1 (fr) * 2021-12-17 2023-06-22 ダイキン工業株式会社 Dispositif de ventilation et procédé de ventilation

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WO2021000634A1 (fr) * 2019-07-02 2021-01-07 青岛海尔空调电子有限公司 Climatiseur et procédé associé de commande de retour d'huile
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CN115135880B (zh) * 2020-02-26 2024-05-14 三菱电机株式会社 电力转换装置
CN115135880A (zh) * 2020-02-26 2022-09-30 三菱电机株式会社 电力转换装置
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WO2022064989A1 (fr) * 2020-09-25 2022-03-31 住友重機械工業株式会社 Congélateur à ultra-basse température, et procédé de surveillance de congélateur à ultra-basse température
CN112984881A (zh) * 2021-03-05 2021-06-18 四川长虹空调有限公司 制冷系统压缩机的回液判断方法及系统
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WO2023112831A1 (fr) * 2021-12-17 2023-06-22 ダイキン工業株式会社 Dispositif de ventilation et procédé de ventilation
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CN114543185B (zh) * 2022-02-16 2023-09-26 青岛海信日立空调系统有限公司 一种空调系统
CN114543185A (zh) * 2022-02-16 2022-05-27 青岛海信日立空调系统有限公司 一种空调系统

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