WO2013077136A1 - Climatiseur - Google Patents

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Publication number
WO2013077136A1
WO2013077136A1 PCT/JP2012/077465 JP2012077465W WO2013077136A1 WO 2013077136 A1 WO2013077136 A1 WO 2013077136A1 JP 2012077465 W JP2012077465 W JP 2012077465W WO 2013077136 A1 WO2013077136 A1 WO 2013077136A1
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WO
WIPO (PCT)
Prior art keywords
heat exchanger
refrigerant
stage
heating
outside air
Prior art date
Application number
PCT/JP2012/077465
Other languages
English (en)
Japanese (ja)
Inventor
淳哉 南
Original Assignee
ダイキン工業株式会社
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
Priority claimed from JP2011256494A external-priority patent/JP2013108729A/ja
Priority claimed from JP2011256495A external-priority patent/JP5170299B1/ja
Application filed by ダイキン工業株式会社 filed Critical ダイキン工業株式会社
Publication of WO2013077136A1 publication Critical patent/WO2013077136A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B13/00—Compression machines, plants or systems, with reversible cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • 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
    • 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
    • F25B2313/006—Compression machines, plants or systems with reversible cycle not otherwise provided for two pipes connecting the outdoor side to the indoor side with 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
    • F25B2313/023—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
    • 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
    • F25B2313/0315—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
    • 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
    • F25B2700/2106—Temperatures of fresh outdoor air

Definitions

  • the present invention relates to an air conditioner, and more particularly to an air conditioner that performs a heating operation and a reverse cycle defrosting operation.
  • an air conditioner that performs heating operation and reverse cycle defrosting operation.
  • frost formation occurs in the outdoor heat exchanger that functions as a refrigerant evaporator.
  • the frost generated in the outdoor heat exchanger in the heating operation is melted by performing the reverse cycle defrosting operation, and is discharged as drain water through the bottom plate of the outdoor unit disposed below the outdoor heat exchanger.
  • the refrigerant is circulated in the order of the compressor, the outdoor heat exchanger, and the indoor heat exchanger, so that the outdoor heat exchanger is heated by the refrigerant compressed in the compressor.
  • Driving is the order of the compressor, the outdoor heat exchanger, and the indoor heat exchanger, so that the outdoor heat exchanger is heated by the refrigerant compressed in the compressor.
  • the bottom plate of the outdoor unit functions as a drain pan.
  • the drain water generated during the reverse cycle defrosting operation may freeze on the lower side of the outdoor heat exchanger. Such freezing of drain water may cause excessive ice growth (ice-up phenomenon) on the lower side of the outdoor heat exchanger.
  • Patent Document 1 Japanese Patent Laid-Open No. 2009-127939
  • an auxiliary heat exchanger is provided on the lower side of the outdoor heat exchanger, and compressed in the compressor during the reverse cycle defrosting operation.
  • There is an air conditioner configured to heat an auxiliary heat exchanger with a part of a refrigerant.
  • the said conventional air conditioning apparatus freezing of drain water at the time of a defrost operation can be prevented.
  • the drain water melted by performing the defrosting operation exists on the lower side of the outdoor heat exchanger, and the drain water continues to be discharged. Thereafter, when the heating operation is resumed, there is a possibility that the drain water is frozen before the drain water is discharged under a condition where the outside air temperature is low.
  • freezing of drain water at the time of the heating operation after a defrost operation cannot be prevented, and there exists a possibility that an ice-up phenomenon may generate
  • the subject of this invention is suppressing the generation
  • An air conditioner performs a heating operation by circulating a refrigerant in the order of a compression mechanism, an indoor heat exchanger, and an outdoor heat exchanger, and the compression mechanism, the outdoor heat exchanger, and the indoor heat exchange. It is an air conditioner that performs a defrosting operation by circulating refrigerant in the order of the units.
  • a freezing prevention heat exchanger capable of heating the lower side of the outdoor heat exchanger with a part of the refrigerant compressed in the compression mechanism is provided, and the heating operation after the defrosting operation is performed.
  • freeze prevention control at the time of resuming heating is performed in which a part of the refrigerant compressed in the compression mechanism is passed through the freeze prevention heat exchanger.
  • this air conditioner during the heating operation after the defrosting operation, a part of the refrigerant compressed in the compression mechanism is caused to flow through the antifreezing heat exchanger, so that the outdoor heat is removed after the defrosting operation under a condition where the outside air temperature is low.
  • the drain water present on the lower side of the exchanger can be discharged without freezing. For this reason, in this air conditioner, it is possible to suppress the occurrence of the ice-up phenomenon during the heating operation after the defrosting operation.
  • the air conditioner according to the second aspect performs the freeze prevention control at the time of resuming heating when the outside air temperature is equal to or lower than a predetermined outside air temperature.
  • this air conditioner after the defrosting operation, only when the outside air temperature at which the drain water existing on the lower side of the outdoor heat exchanger is likely to freeze is low, anti-freezing control at the time of resuming heating is performed, and the outside air temperature is high. In this case, it is possible to avoid the freeze prevention control when resuming heating. Thereby, in this air conditioning apparatus, the fall of the heating capability in the heating operation after a defrost operation can further be suppressed.
  • An air conditioner according to a third aspect is the air conditioner according to the first or second aspect, wherein the compression mechanism includes a low-stage compressor and a high-stage compressor, and the compression mechanism, Two-stage heating operation is performed in which the refrigerant is circulated in the order of the heat exchanger and the outdoor heat exchanger, and the defrosting operation is performed by circulating the refrigerant in the order of the compression mechanism, the outdoor heat exchanger, and the indoor heat exchanger. is there.
  • the anti-freezing heat exchanger can heat the lower side of the outdoor heat exchanger with a part of the refrigerant compressed in the low-stage compressor, and the anti-freezing control when resuming heating is performed after the defrosting operation.
  • the refrigerant compressed in the low-stage compressor is caused to flow to the heat exchanger for preventing freezing.
  • the refrigerant is circulated in the order of the low-stage compressor, the indoor heat exchanger, and the outdoor heat exchanger without starting the high-stage compressor while performing anti-freezing control when resuming heating.
  • Single stage heating operation is performed when stage heating is resumed.
  • the high pressure of the refrigeration cycle is reduced under a condition where the outside air temperature is low. Accordingly, the pressure of the refrigerant compressed in the low stage compressor (intermediate pressure of the refrigeration cycle) is also reduced. For this reason, since the pressure of the refrigerant flowing into the antifreezing heat exchanger decreases and the pressure difference secured in the refrigerant flow path for supplying the refrigerant to the antifreezing heat exchanger is reduced, the antifreezing heat exchanger The flow rate of the refrigerant flowing through becomes smaller.
  • the pressure of the refrigerant compressed in the low-stage compressor is increased compared with the case where the low-stage compressor and the high-stage compressor are started up, and the anti-freezing heat exchanger Since the pressure difference secured in the refrigerant flow path for supplying the refrigerant to the refrigerant increases, the flow rate of the refrigerant flowing through the freezing prevention heat exchanger increases. If it does so, the drain water which exists in the lower part side of an outdoor heat exchanger will fully be heated.
  • the single-stage heating operation when resuming the two-stage heating may reduce the heating capacity, but here, the single-stage heating operation is performed only at the initial stage of the second-stage heating operation after the defrosting operation. Moreover, the fall of the heating capability in the heating operation after a defrost operation can also be suppressed.
  • An air conditioner according to a fourth aspect is the air conditioner according to the third aspect, wherein the single-stage heating operation when resuming the two-stage heating is performed when the outside air temperature is equal to or lower than a predetermined outside air temperature, or the low pressure of the refrigeration cycle. And when the pressure difference between the high pressure and the high pressure is less than a predetermined height difference. As described above, it is desirable not to perform the single-stage heating operation as much as possible, because the single-stage heating operation is temporarily reduced even in the initial stage of the resumption of the two-stage heating operation after the defrosting operation. .
  • a refrigerant flow path for supplying refrigerant to a condition where the outside air temperature at which the drain water existing on the lower side of the outdoor heat exchanger is frozen after the defrosting operation may freeze or to the antifreezing heat exchanger
  • the single-stage heating operation at the time of restarting the two-stage heating is performed only under the condition that the pressure difference of the refrigeration cycle in which it is difficult to ensure the pressure difference ensured in the above-mentioned is reduced.
  • An air conditioner according to a fifth aspect is the air conditioner according to the third or fourth aspect, wherein the outside air temperature is higher than a predetermined outside air temperature, or the pressure difference between the low pressure and the high pressure of the refrigeration cycle.
  • the difference is greater than or equal to the predetermined height difference, the anti-freezing control at the time of resuming heating is performed at the beginning of the resumption of the two-stage heating operation after the defrosting operation, and the single-stage heating operation at the time of resuming the two-stage heating is not performed.
  • the flow rate of the refrigerant flowing through the antifreezing heat exchanger is determined by the pressure difference secured in the refrigerant flow path for supplying the refrigerant to the antifreezing heat exchanger, as the outside air temperature increases or the pressure of the refrigeration cycle As the difference increases, it increases. For this reason, if the freeze prevention control at the restart of heating and the single-stage heating operation at the restart of the two-stage heating are performed regardless of the conditions of the outside air temperature or the pressure difference of the refrigeration cycle, the refrigerant flowing through the antifreeze heat exchanger The flow rate is larger under conditions where the outside air temperature is high and conditions under which the pressure difference in the refrigeration cycle is larger than conditions under which the outside air temperature is low and the pressure difference in the refrigeration cycle is small.
  • flowing a part of the refrigerant compressed in the low-stage compressor to the anti-freezing heat exchanger means that the flow rate of the refrigerant sent to the indoor heat exchanger is reduced. This will reduce the heating capacity. For this reason, it is preferable to make small the fluctuation
  • the anti-freezing control at the time of resuming heating is performed at the initial stage of resuming the two-stage heating operation after the defrosting operation.
  • the single-stage heating operation is not performed when the second-stage heating is resumed.
  • the two-stage heating operation is performed without performing the single-stage heating operation from the initial stage of the two-stage heating operation after the defrosting operation. Therefore, the pressure of the refrigerant compressed in the low stage side compressor is lowered.
  • An air conditioner according to a sixth aspect is the air conditioner according to any of the first to fifth aspects, wherein the anti-freezing control at the time of resuming heating is performed until a predetermined time elapses after the defrosting operation.
  • the freeze prevention control at the time of resuming heating is managed by time, the time necessary for discharging the drain water present on the lower side of the outdoor heat exchanger after the defrosting operation is taken into consideration. be able to.
  • the freeze prevention control at the time of resuming heating is managed by time, the time necessary for discharging the drain water present on the lower side of the outdoor heat exchanger after the defrosting operation is taken into consideration. be able to.
  • the freeze prevention control at the time of resuming heating is managed by time, the time necessary for discharging the drain water present on the lower side of the outdoor heat exchanger after the defrosting operation is taken into consideration. be able to.
  • An air conditioner according to a seventh aspect is the air conditioner according to the sixth aspect, wherein the air conditioner is predetermined as the outside air temperature decreases, the outside air humidity increases, or the operating time of the defrosting operation increases. Increase time.
  • the amount of drain water present on the lower side of the outdoor heat exchanger after the defrosting operation varies depending on the outside air temperature, the outside air humidity, or the operating time of the defrosting operation. Specifically, the amount of drain water increases as the outside air temperature decreases, the outside air humidity increases, or the operating time of the defrosting operation increases. For this reason, it is preferable to change also about the predetermined time of anti-freezing control at the time of heating resumption by outside temperature, outside humidity, or operating time of defrosting operation.
  • the predetermined time is extended as the outside air temperature decreases, the outside air humidity increases, or the operating time of the defrosting operation increases. For this reason, in this air conditioning apparatus, it is possible to consider the amount of drain water that varies depending on the outside air temperature, the outside air humidity, or the operating time of the defrosting operation. Thereby, in this air conditioner, the freezing prevention control at the time of resuming heating and the single-stage heating operation at the time of resuming two-stage heating can be appropriately performed in consideration of changes in the amount of drain water due to conditions such as the outside air temperature.
  • An air conditioner according to an eighth aspect is the air conditioner according to any of the first to seventh aspects, further comprising a flow rate adjusting valve for varying a flow rate of the refrigerant flowing through the antifreezing heat exchanger. As the outside air temperature decreases, the outside air humidity increases, or the operating time of the defrosting operation increases, the opening degree of the flow control valve is increased.
  • the amount of drain water present on the lower side of the outdoor heat exchanger after the defrosting operation varies depending on the outside air temperature, the outside air humidity, or the operating time of the defrosting operation. Specifically, the amount of drain water increases as the outside air temperature decreases, the outside air humidity increases, or the operating time of the defrosting operation increases. For this reason, it is preferable to change the flow rate of the refrigerant flowing through the antifreezing heat exchanger in the antifreezing control when resuming heating depending on the outside air temperature, the outside air humidity, or the operating time of the defrosting operation. Therefore, in this air conditioner, as described above, the opening degree of the flow control valve is increased as the outside air temperature decreases, the outside air humidity increases, or the operating time of the defrosting operation increases. The flow rate of the refrigerant is increased. For this reason, in this air conditioning apparatus, it is possible to consider the amount of drain water that varies depending on the outside air temperature, the outside air humidity, or the operating time of the defrosting operation.
  • this air conditioner it is possible to appropriately perform freezing prevention control when resuming heating and single-stage heating operation when resuming two-stage heating in consideration of changes in the amount of drain water due to conditions such as outside air temperature.
  • FIG. 1 is a schematic configuration diagram of an air conditioner 1 according to the first embodiment of the present invention.
  • the air conditioning apparatus 1 is an apparatus used for air conditioning in a room such as a building by performing a vapor compression refrigeration cycle.
  • the air conditioner 1 mainly includes a single outdoor unit 2, a plurality (in this case, two) of indoor units 5 and 6, and a liquid refrigerant communication pipe that connects the outdoor unit 2 and the indoor units 5 and 6. 7 and a gas refrigerant communication pipe 8.
  • the vapor compression refrigerant circuit 10 of the air conditioner 1 is configured by connecting the outdoor unit 2, the indoor units 5 and 6, the liquid refrigerant communication pipe 7 and the gas refrigerant communication pipe 8. .
  • the number of indoor units 5 and 6 is not limited to two, and may be one or three or more.
  • the indoor units 5 and 6 are installed by being embedded or suspended in a ceiling of a room such as a building, or by wall hanging on a wall surface of the room.
  • the indoor units 5 and 6 are connected to the outdoor unit 2 via the liquid refrigerant communication pipe 7 and the gas refrigerant communication pipe 8 and constitute a part of the refrigerant circuit 10.
  • the configuration of the indoor units 5 and 6 will be described.
  • the indoor unit 5 and the indoor unit 6 have the same configuration, only the configuration of the indoor unit 5 will be described here.
  • the reference numerals in the 60s are attached instead of the reference numerals, and description of each part is omitted.
  • the indoor unit 5 mainly has an indoor expansion valve 51 and an indoor heat exchanger 52.
  • the indoor expansion valve 51 is a device that adjusts the pressure and flow rate of the refrigerant flowing through the indoor unit 5.
  • the indoor expansion valve 51 has one end connected to the liquid side of the indoor heat exchanger 52 and the other end connected to the liquid refrigerant communication tube 7.
  • an electric expansion valve is used as the indoor expansion valve 51.
  • the indoor heat exchanger 52 is a heat exchanger that functions as a refrigerant evaporator during cooling operation to cool indoor air and functions as a refrigerant condenser during heating operation to heat indoor air.
  • the indoor heat exchanger 52 has a liquid side connected to the indoor expansion valve 51 and a gas side connected to the gas refrigerant communication tube 8.
  • the indoor heat exchanger 52 is a cross-fin type fin-and-tube heat exchanger composed of heat transfer tubes and a large number of fins.
  • the type of the indoor heat exchanger 52 is not limited to the cross fin type fin-and-tube type heat exchanger, and other types such as a laminated heat exchanger using corrugated fins or flat tubes, for example. It may be a type of heat exchanger.
  • the indoor unit 5 has an indoor fan 53 for supplying indoor air as supply air after sucking indoor air into the indoor unit 5 and exchanging heat with the refrigerant in the indoor heat exchanger 52.
  • the indoor fan 53 a centrifugal fan or a multiblade fan driven by an indoor fan motor 53a is used.
  • the indoor unit 5 includes an indoor side control unit 54 that controls the operation of each unit constituting the indoor unit 5.
  • the indoor side control part 54 has a microcomputer, memory, etc. for controlling the indoor unit 5, and between the remote controllers (not shown) for operating the indoor unit 5 separately. Control signals and the like can be exchanged, and control signals and the like can be exchanged with the outdoor unit 2 via the transmission line 9a.
  • the outdoor unit 2 is installed outside a building or the like.
  • the outdoor unit 2 is connected to the indoor units 5 and 6 via the liquid refrigerant communication pipe 7 and the gas refrigerant communication pipe 8 and constitutes a part of the refrigerant circuit 10.
  • the outdoor unit 2 mainly includes a compressor 21 as a compression mechanism, a switching mechanism 22, an outdoor heat exchanger 23, an outdoor expansion valve 24, and a freezing prevention heat exchanger 25.
  • the compressor 21 is a device that compresses the low-pressure refrigerant in the refrigeration cycle until the pressure becomes high.
  • the compressor 21 has a hermetic structure in which a rotary type or scroll type positive displacement compression element (not shown) is rotationally driven by a compressor motor 21a.
  • the compressor 21 has a first gas refrigerant pipe 26a connected to the suction side and a second gas refrigerant pipe 26b connected to the discharge side.
  • the first gas refrigerant pipe 26 a is a refrigerant pipe that connects the suction side of the compressor 21 and the first port 22 a of the switching mechanism 22.
  • the second gas refrigerant pipe 26 b is a refrigerant pipe that connects the discharge side of the compressor 21 and the second port 22 b of the switching mechanism 22.
  • the one compressor 21 comprises the compression mechanism here, you may comprise a compression mechanism by connecting the several compressor 21 in parallel.
  • the switching mechanism 22 is a mechanism for switching the direction of refrigerant flow in the refrigerant circuit 10.
  • the switching mechanism 22 causes the outdoor heat exchanger 23 to function as a condenser for the refrigerant compressed in the compressor 21 during the cooling operation and the defrosting operation, and causes the indoor heat exchangers 52 and 62 to function as the outdoor heat exchanger 23. Is switched to function as an evaporator for the refrigerant condensed in step. That is, the switching mechanism 22 switches between the second port 22b and the third port 22c and the first port 22a and the fourth port 22d during the cooling operation and the defrosting operation.
  • the discharge side (here, the second gas refrigerant pipe 26b) of the compressor 21 and the gas side (here, the third gas refrigerant pipe 26c) of the outdoor heat exchanger 23 are connected (switching in FIG. 1). (See solid line for mechanism 22).
  • the suction side (here, the first gas refrigerant pipe 26a) of the compressor 21 and the gas refrigerant communication pipe 8 side (here, the fourth gas refrigerant pipe 26d) are connected (of the switching mechanism 22 of FIG. 1). (See solid line).
  • the switching mechanism 22 causes the outdoor heat exchanger 23 to function as an evaporator of the refrigerant condensed in the indoor heat exchangers 42 and 52 during the heating operation, and compresses the indoor heat exchangers 52 and 62 in the compressor 21. Switch to function as a condenser for the refrigerant. That is, during the heating operation, the switching mechanism 22 switches the second port 22b and the fourth port 22d to communicate and the first port 22a and the third port 22c to communicate. Thereby, the discharge side (here, the second gas refrigerant pipe 26b) of the compressor 21 and the gas refrigerant communication pipe 8 side (here, the fourth gas refrigerant pipe 26d) are connected (the switching mechanism 22 in FIG. 1). See the dashed line).
  • the suction side (here, the first gas refrigerant pipe 26a) of the compressor 21 and the gas side (here, the third gas refrigerant pipe 26c) of the outdoor heat exchanger 23 are connected (the switching mechanism in FIG. 1). (See dashed line 22).
  • the third gas refrigerant pipe 26 c is a refrigerant pipe that connects the third port 22 c of the switching mechanism 22 and the gas side of the outdoor heat exchanger 23.
  • the fourth gas refrigerant pipe 26d is a refrigerant pipe that connects the fourth port 22d of the switching mechanism 22 and the gas refrigerant communication pipe 8 side.
  • the switching mechanism 22 is a four-way switching valve.
  • the configuration of the switching mechanism 22 is not limited to the four-way switching valve, and may be, for example, a configuration in which a plurality of electromagnetic valves or the like are connected so as to perform the above switching function.
  • the outdoor heat exchanger 23 is a heat exchanger that functions as a refrigerant condenser during cooling operation and defrosting operation, and functions as a refrigerant evaporator during heating operation.
  • the outdoor heat exchanger 23 has a liquid side connected to the liquid refrigerant pipe 26e and a gas side connected to the third gas refrigerant pipe 26c.
  • the liquid refrigerant pipe 26e is a refrigerant pipe that connects the liquid side of the outdoor heat exchanger 23 and the liquid refrigerant communication pipe 7 side.
  • the outdoor heat exchanger 23 is a cross-fin type fin-and-tube heat exchanger composed of heat transfer tubes and a large number of fins.
  • the type of the outdoor heat exchanger 23 is not limited to a cross fin type fin-and-tube type heat exchanger, and other types such as a laminated heat exchanger using corrugated fins or flat tubes, for example. It may be a type of heat exchanger.
  • the outdoor expansion valve 24 is a device that adjusts the pressure, flow rate, and the like of the refrigerant flowing through the outdoor unit 2.
  • the outdoor expansion valve 24 is provided in the liquid refrigerant pipe 26e.
  • an electric expansion valve is used as the outdoor expansion valve 24.
  • the antifreezing heat exchanger 25 is a heat exchanger that heats the lower side of the outdoor heat exchanger 23 with a part of the refrigerant compressed in the compressor 21 as a compression mechanism.
  • the antifreezing heat exchanger 25 is provided in the hot gas bypass pipe 27.
  • the anti-freezing heat exchanger 25 is a cross-fin type fin-and-tube heat exchanger composed of heat transfer tubes and a large number of fins, and as shown in FIG. 2, an outdoor heat exchanger. 23 is integrated with the lower part.
  • the outdoor heat exchanger 23 and the antifreezing heat exchanger 25 are configured as an integral fin-and-tube heat exchanger, and the heat transfer tubes and fins on the upper side are the outdoor heat exchanger 23.
  • FIG. 2 is a schematic view showing the lower side of the outdoor heat exchanger 23 including the freeze-preventing heat exchanger 25 and the bottom plate 2 a of the outdoor unit 2.
  • the type of the anti-freezing heat exchanger 25 is not limited to the cross-fin type fin-and-tube type heat exchanger, for example, a laminated heat exchanger using corrugated fins or flat tubes, etc. Other types of heat exchangers may be used.
  • the hot gas bypass pipe 27 is a refrigerant pipe that branches a part of the refrigerant compressed in the compressor 21.
  • One end side of the hot gas bypass pipe 27 is connected so as to branch from a middle portion of the second gas refrigerant pipe 26c, and the other end side is connected to the liquid side of the outdoor heat exchanger 23 of the liquid refrigerant pipe 26e and the outdoor expansion valve 24. It is connected to join the part between.
  • a hot gas decompression mechanism 27a, a hot gas opening / closing mechanism 27b, and a hot gas check mechanism 27c are provided at a portion of the hot gas bypass pipe 27 on the outlet side of the heat exchanger 25 for preventing freezing.
  • the hot gas decompression mechanism 27a is a device that decompresses the refrigerant.
  • a capillary tube is used as the hot gas decompression mechanism 27a.
  • the hot gas opening / closing mechanism 27b is opened when a part of the refrigerant compressed in the compressor 21 is branched into the hot gas bypass pipe 27, and a part of the refrigerant compressed in the compressor 21 is branched into the hot gas bypass pipe 27. It is a device that can be closed if not.
  • an electromagnetic valve is used as the hot gas opening / closing mechanism 27b.
  • the hot gas check mechanism 27c is a mechanism that allows the flow of the refrigerant from the outlet side of the antifreezing heat exchanger 25 to the liquid refrigerant tube 26e side and blocks the flow in the reverse direction.
  • a check valve is used as the hot gas check mechanism 27c.
  • the outdoor unit 2 has an outdoor fan 28 for sucking outdoor air into the outdoor unit 2, exchanging heat with the refrigerant in the outdoor heat exchanger 23, and then discharging the air outside the outdoor unit 2.
  • an outdoor fan 28 an axial fan or the like driven by an outdoor fan motor 28a is used.
  • the anti-freezing heat exchanger 25 is integrated with the lower part of the outdoor heat exchanger 23. Therefore, the outdoor fan 28 is not only the outdoor heat exchanger 23 but also the anti-freezing heat. Outdoor air is also supplied to the exchanger 25.
  • the outdoor unit 2 is provided with various sensors.
  • the outdoor unit 2 is mainly provided with a suction pressure sensor 29a, a discharge pressure sensor 29b, an outdoor heat exchange temperature sensor 29c, and an outdoor temperature sensor 29d.
  • the suction pressure sensor 29a is a pressure sensor that detects the suction pressure Ps of the compressor 21 corresponding to a low pressure in the refrigeration cycle.
  • the discharge pressure sensor 29b is a pressure sensor that detects the discharge pressure Pd of the compressor 21 corresponding to the high pressure in the refrigeration cycle.
  • the outdoor heat exchange temperature sensor 29 c is a temperature sensor that detects the temperature Tb of the refrigerant flowing through the outdoor heat exchanger 23.
  • the outside air temperature sensor 29d is a temperature sensor that detects the outside air temperature Ta in the outdoor unit 2.
  • the outdoor unit 2 also has an outdoor control unit 30 that controls the operation of each part constituting the outdoor unit 2.
  • the outdoor side control part 30 has a microcomputer, memory, etc. for controlling the outdoor unit 2, and connects the transmission line 9a between the indoor side control parts 54 and 64 of the indoor units 5 and 6. It is possible to exchange control signals and the like. That is, the control part 9 which performs operation control of the whole air conditioning apparatus 1 is comprised by the indoor side control parts 54 and 64, the outdoor side control part 30, and the transmission line 9a which connects between control parts 30,54,64. Yes. As shown in FIG.
  • FIG. 3 is a control block diagram of the air conditioner 1.
  • Refrigerant communication pipes 7 and 8 are refrigerant pipes constructed on site when the air conditioner 1 is installed at a place such as a building, and installation conditions such as a combination of the installation place and an outdoor unit and an indoor unit, etc. Those having various lengths and tube diameters are used.
  • the refrigerant circuit 10 of the air conditioner 1 is configured by connecting the outdoor unit 2, the indoor units 5 and 6, and the refrigerant communication tubes 7 and 8.
  • the air conditioner 1 is operated by the control unit 9 including the indoor side control units 54 and 64 and the outdoor side control unit 30, such as a cooling operation, a heating operation, and a defrosting operation described below. Can be done.
  • the air conditioner 1 can mainly perform a cooling operation, a heating operation, and a defrosting operation.
  • the cooling operation is an operation in which the refrigerant is circulated mainly in the order of the compressor 21, the outdoor heat exchanger 23, and the indoor heat exchangers 52 and 62 as a compression mechanism in order to cool the indoor air.
  • the heating operation is an operation in which the refrigerant is circulated mainly in the order of the compressor 21 as the compression mechanism, the indoor heat exchangers 52 and 62, and the outdoor heat exchanger 23 in order to heat the indoor air.
  • the defrosting operation is mainly performed in the order of the compressor 21 as the compression mechanism, the outdoor heat exchanger 23, and the indoor heat exchangers 52 and 62. It is an operation to circulate. That is, the defrosting operation is a so-called reverse cycle defrosting operation in which the refrigerant flow direction is reversed from that of the heating operation.
  • operation of the air conditioning apparatus 1 is demonstrated.
  • FIG. 4 is a schematic configuration diagram illustrating the flow of the refrigerant during the cooling operation of the air-conditioning apparatus 1.
  • the switching mechanism 22 is switched to the state shown by the solid line in FIG. 4, that is, the communication between the second port 22b and the third port 22c and the communication between the first port 22a and the fourth port 22d.
  • the outdoor heat exchanger 23 functions as a condenser for the refrigerant compressed in the compressor 21, and the indoor heat exchangers 52 and 62 are evaporated in the outdoor heat exchanger 23.
  • a refrigeration cycle is made to function as a vessel.
  • low-pressure gas refrigerant in the refrigeration cycle is sucked into the compressor 21 and compressed to become high-pressure gas refrigerant.
  • This high-pressure gas refrigerant is sent to the outdoor heat exchanger 23 through the switching mechanism 22, exchanges heat with the outdoor air supplied by the outdoor fan 28, and condenses to become a high-pressure liquid refrigerant.
  • the high-pressure liquid refrigerant is sent to the indoor expansion valves 51 and 61 through the outdoor expansion valve 24 and the liquid refrigerant communication pipe 7, and is reduced in pressure to become a low-pressure refrigerant.
  • the low-pressure refrigerant is sent to the indoor heat exchangers 52 and 62, exchanges heat with the indoor air supplied by the indoor fans 53 and 63, and evaporates to become a low-pressure gas refrigerant.
  • the low-pressure gas refrigerant is again sucked into the compressor 21 through the gas refrigerant communication pipe 8 and the switching mechanism 22.
  • the hot gas opening / closing mechanism 27b is opened. For this reason, a part of the high-pressure refrigerant that is compressed in the compressor 21 and flows through the second gas refrigerant pipe 26 b is branched to the hot gas bypass pipe 27.
  • the high-pressure refrigerant branched into the hot gas bypass pipe 27 is sent to the antifreezing heat exchanger 25 to heat the lower side of the outdoor heat exchanger 23. That is, the antifreezing heat exchanger 25 functions as a refrigerant condenser, similarly to the outdoor heat exchanger 23.
  • the antifreezing heat exchanger 25 a part of the high-pressure gas refrigerant compressed in the compressor 21 is sent to the antifreezing heat exchanger 25 through the hot gas bypass pipe 27 and exchanges heat with the outdoor air supplied by the outdoor fan 28. It goes and condenses to become a high-pressure liquid refrigerant.
  • the high-pressure liquid refrigerant is sent to the liquid refrigerant pipe 26e through the hot gas decompression mechanism 27a, the hot gas opening / closing mechanism 27b, and the hot gas check mechanism 27c, and merges with the high-pressure liquid refrigerant from the outdoor heat exchanger 23.
  • the antifreezing heat exchanger 25 functions as a refrigerant condenser during the cooling operation.
  • cooling of the refrigerant sent to the indoor heat exchangers 52 and 62 is promoted during the cooling operation, compared to a case where only the outdoor heat exchanger 23 functions as a refrigerant condenser, The cooling capacity is improved.
  • FIG. 5 is a schematic configuration diagram illustrating the flow of the refrigerant during the heating operation of the air-conditioning apparatus 1.
  • the switching mechanism 22 is switched to the state indicated by the broken line in FIG. 5, that is, the second port 22b and the fourth port 22d are communicated and the first port 22a and the third port 22c are communicated.
  • the outdoor heat exchanger 23 functions as an evaporator of the refrigerant condensed in the indoor heat exchangers 42 and 52, and the indoor heat exchangers 52 and 62 are compressed in the compressor 21.
  • a refrigeration cycle is made to function as a condenser.
  • low-pressure gas refrigerant in the refrigeration cycle is sucked into the compressor 21 and compressed to become high-pressure gas refrigerant.
  • the high-pressure gas refrigerant is sent to the indoor heat exchangers 52 and 62 through the switching mechanism 22 and the gas refrigerant communication pipe 8, exchanges heat with the indoor air supplied by the indoor fans 53 and 63, and is condensed to high pressure. It becomes a liquid refrigerant.
  • the high-pressure liquid refrigerant is sent to the outdoor expansion valve 24 through the indoor expansion valves 51 and 61 and the liquid refrigerant communication pipe 7, and is decompressed to become a low-pressure refrigerant.
  • the low-pressure refrigerant is sent to the outdoor heat exchanger 23, exchanges heat with outdoor air supplied by the outdoor fan 28, and evaporates to become a low-pressure gas refrigerant.
  • the low-pressure gas refrigerant is again sucked into the compressor 21 through the switching mechanism 22.
  • the hot gas opening / closing mechanism 27b is closed except when performing anti-freezing control when resuming heating, which will be described later.
  • the high-pressure refrigerant that is compressed in the compressor 21 and flows through the second gas refrigerant pipe 26b is not branched to the hot gas bypass pipe 27 except when the anti-freezing control at the time of resuming heating described later is performed. That is, during the heating operation, the refrigerant does not flow through the anti-freezing heat exchanger 25, except when performing anti-freezing control when resuming heating, which will be described later.
  • the air conditioner 1 all the high-pressure gas refrigerant compressed in the compressor 21 is heated in the indoor heat exchangers 52 and 62 except for the case where the antifreezing control at the time of resuming heating described later is performed during the heating operation. To be sent to.
  • the flow rate of the refrigerant sent to the indoor heat exchangers 52 and 62 is larger than that in the case where the refrigerant is passed through the antifreezing heat exchanger 25 during the heating operation, and the heating capacity is increased. The decline of the is suppressed.
  • FIG. 4 is a schematic configuration diagram illustrating the flow of the refrigerant during the defrosting operation of the air conditioner 1.
  • the defrosting operation is a reverse cycle defrosting operation in which the refrigerant flow direction is reversed from the heating operation. Therefore, during the defrosting operation, the switching mechanism 22 is in the state indicated by the solid line in FIG. 4, that is, the second port 22b and the third port 22c are communicated, and the first port 22a and the fourth port 22d are connected. Change the communication.
  • the outdoor heat exchanger 23 functions as a condenser for the refrigerant compressed in the compressor 21, and the indoor heat exchangers 52 and 62 are operated in the outdoor heat, as in the above cooling operation.
  • a refrigeration cycle that functions as an evaporator for the refrigerant condensed in the exchanger 23 is performed.
  • the defrosting operation is performed when the controller 9 determines that frost formation has occurred in the outdoor heat exchanger 23 during the heating operation. This determination is performed based on the temperature Tb of the refrigerant flowing through the outdoor heat exchanger 23 detected by the outdoor heat exchanger temperature sensor 29c and the accumulated time of the heating operation. For example, when it is detected that the temperature Tb of the refrigerant detected by the outdoor heat exchanger temperature sensor 29c has decreased to a predetermined temperature or less that can be regarded as frost formation in the outdoor heat exchanger 23, or heating If the accumulated time of operation has passed a predetermined time that can be regarded as frost formation in the outdoor heat exchanger 23, it is determined that frost formation has occurred in the outdoor heat exchanger 23.
  • the refrigerant circuit 10 When the temperature and time conditions are not reached, it is determined that frost formation has not occurred in the outdoor heat exchanger 23.
  • the refrigerant circulates in the same flow direction as in the cooling operation. Then, the high-pressure refrigerant that is compressed by the compressor 21 and flows through the second gas refrigerant pipe 26 b is sent to the outdoor heat exchanger 23 through the switching mechanism 22 to heat the outdoor heat exchanger 23. Thereby, the frost generated in the outdoor heat exchanger 23 in the heating operation is melted to become drain water, and passes through the anti-freezing heat exchanger 25 integrated with the outdoor heat exchanger 23 to the lower side of the outdoor heat exchanger 23. It collects on the bottom plate 2a of the outdoor unit 2 as a drain pan arranged. The drain water accumulated on the bottom plate 2a is discharged out of the outdoor unit 2 through a discharge port 2b formed on the bottom plate 2a.
  • the defrosting operation ends when the control unit 9 determines that the defrosting of the outdoor heat exchanger 23 has been completed.
  • This determination is performed based on the temperature Tb of the refrigerant flowing through the outdoor heat exchanger 23 detected by the outdoor heat exchanger temperature sensor 29c and the operating time of the defrosting operation. For example, when it is detected that the temperature Tb of the refrigerant detected by the outdoor heat exchange temperature sensor 29c is equal to or higher than a temperature at which frost can be regarded as melted, or the operation time of the defrosting operation is a predetermined time When the time has elapsed, it is determined that the defrosting of the outdoor heat exchanger 23 has been completed.
  • the defrosting of the outdoor heat exchanger 23 is completed. It is determined that it is not.
  • the hot gas opening / closing mechanism 27b is opened as in the cooling operation. For this reason, a part of the high-pressure refrigerant that is compressed in the compressor 21 and flows through the second gas refrigerant pipe 26 b is branched to the hot gas bypass pipe 27.
  • the high-pressure refrigerant branched into the hot gas bypass pipe 27 is sent to the antifreezing heat exchanger 25 to heat the lower side of the outdoor heat exchanger 23. That is, the anti-freezing heat exchanger 25 functions as a heater for drain water melted by performing the defrosting operation.
  • the drain water from the outdoor heat exchanger 23 is heated on the lower side of the outdoor heat exchanger 23 and then collected on the bottom plate 2a of the outdoor unit 2 as a drain pan. Discharged outside.
  • the antifreezing heat exchanger 25 heats the drain water generated in the outdoor heat exchanger 23 on the lower side of the outdoor heat exchanger 23. Yes.
  • the drain water from the outdoor heat exchanger 23 can be prevented from freezing on the lower side of the outdoor heat exchanger 23 during the defrosting operation, and the drain water is outside the outdoor unit 2. Therefore, the occurrence of an ice-up phenomenon during the defrosting operation is suppressed.
  • FIG. 6 is a flowchart of the freeze prevention control at the time of resuming the heating of the air-conditioning apparatus 1.
  • FIG. 7 is a schematic configuration diagram illustrating the flow of the refrigerant during the freeze prevention control at the resumption of heating of the air-conditioning apparatus 1.
  • the control part 9 determines whether it is heating operation after defrost operation in step S1. If it is determined in step S1 that the heating operation is performed after the defrosting operation, the process proceeds to step S2 in which it is determined whether or not an outside air temperature condition that requires anti-freezing control when resuming heating is satisfied.
  • step S2 the controller 9 determines whether or not the outside air temperature Ta detected by the outside air temperature sensor 29d is equal to or lower than a predetermined outside air temperature Tas.
  • step S2 when the outside air temperature Ta is equal to or lower than the predetermined outside air temperature Tas, that is, when the outside air temperature condition is satisfied, the process proceeds to steps S3 to S5 for executing the freeze prevention control at the time of resuming heating.
  • the outside air temperature Ta is higher than the predetermined outside air temperature Tas, that is, when the outside air temperature condition is not satisfied, the heating operation is resumed without performing the freeze prevention control at the time of resuming the heating in steps S3 to S5.
  • the predetermined outside air temperature Tas is set in view of whether or not the drain water present on the lower side of the outdoor heat exchanger 23 may be frozen after the defrosting operation, and is, for example, the melting point of water. It is set to 0 ° C.
  • the predetermined outside air temperature Tas is stored in advance in a memory or the like of the control unit 9 and can be changed by a switch (not shown) or a remote controller (not shown) provided in the control unit 9. It is like that.
  • control part 9 starts freezing prevention control at the time of the heating restart which flows the one part refrigerant
  • the antifreezing heat exchanger 25 functions as a heater for drain water existing on the lower side of the outdoor heat exchanger 23 after the defrosting operation.
  • the outlet of the hot gas bypass pipe 27 is connected to a portion of the liquid refrigerant pipe 26e through which the low-pressure refrigerant flows downstream of the outdoor expansion valve 24, the flow rate of the refrigerant flowing through the hot gas bypass pipe 27 is high. It is easy to be secured.
  • the refrigerant that has heated the drain water in the antifreezing heat exchanger 25 condenses in the antifreezing heat exchanger 25, but then merges with the refrigerant flowing through the liquid refrigerant pipe 26e and functions as a refrigerant evaporator.
  • the refrigerant condensed in the antifreezing heat exchanger 25 remains in a liquid state and is not sucked into the compressor 21.
  • the drain water present on the lower side of the outdoor heat exchanger 23 is heated in the antifreezing heat exchanger 25 and then the bottom plate 2a of the outdoor unit 2 as a drain pan. It accumulates on the top and is discharged out of the outdoor unit 2.
  • the anti-freezing heat exchanger 25 heats the drain water present on the lower side of the outdoor heat exchanger 23 during the heating operation after the defrosting operation.
  • the drain water existing on the lower side of the outdoor heat exchanger 23 can be discharged without freezing after the defrosting operation. Occurrence of ice-up phenomenon during heating operation after operation is suppressed.
  • control part 9 determines whether predetermined time ts passed after the defrost operation in step S4, and when predetermined time ts passed, it transfers to the process of step S5.
  • the predetermined time ts is set to about several minutes in consideration of the time required to discharge the drain water present on the lower side of the outdoor heat exchanger 23 after the defrosting operation.
  • the predetermined time ts is stored in advance in a memory or the like of the control unit 9 and can be changed by a switch (not shown) or a remote controller (not shown) provided in the control unit 9. It has become.
  • the same refrigeration cycle as that in the heating operation is performed, and the hot gas opening / closing mechanism 27b is closed.
  • a predetermined time ts for discharging the drain water existing on the lower side of the outdoor heat exchanger 23 after the defrosting operation without freezing that is, after the defrosting operation. Only when the heating operation is restarted, the freeze prevention control is performed when heating is restarted.
  • flowing a part of the refrigerant compressed in the compressor 21 to the anti-freezing heat exchanger 25 means that the flow rate of the refrigerant sent to the indoor heat exchangers 52 and 62 is reduced.
  • the air conditioner 1 of the present embodiment has the following features. ⁇ A> In the air conditioner 1, in the heating operation after the defrosting operation, by flowing a part of the refrigerant compressed in the compressor 21 as the compression mechanism to the heat exchanger 25 for preventing freezing, the outside air temperature Ta is low. The drain water present on the lower side of the outdoor heat exchanger 23 after the defrosting operation can be discharged without freezing. For this reason, in the air conditioning apparatus 1, generation
  • flowing a part of the refrigerant compressed in the compressor 21 to the anti-freezing heat exchanger 25 means that the flow rate of the refrigerant sent to the indoor heat exchangers 52 and 62 is reduced. This will reduce the heating capacity. Therefore, in the air conditioner 1, as described above, a part of the refrigerant compressed in the compressor 21 is transferred to the antifreezing heat exchanger 25 only in the initial stage of restarting the heating operation in the heating operation after the defrosting operation. It is made to flow (that is, freeze prevention control when resuming heating). For this reason, in the air conditioning apparatus 1, the fall of the heating capability in the heating operation after a defrost operation can be suppressed.
  • the anti-freezing control when resuming heating is performed when the outside air temperature Ta is equal to or lower than a predetermined outside air temperature Tas. For this reason, in the air conditioner 1, only when the outdoor air temperature Ta at which the drain water present on the lower side of the outdoor heat exchanger 23 may freeze after the defrosting operation is low (here, 0 ° C. or lower). When the heating is resumed, the freeze prevention control is performed. Under the condition where the outside air temperature Ta is high (in this case, higher than 0 ° C.), the freeze prevention control when the heating is resumed can be omitted. Thereby, in the air conditioning apparatus 1, the fall of the heating capability in the heating operation after a defrost operation can further be suppressed.
  • the anti-freezing control when resuming heating is performed until a predetermined time ts has elapsed after the defrosting operation. That is, in the air conditioner 1, since the antifreezing control at the time of resuming heating is managed by time, the time required for discharging the drain water present on the lower side of the outdoor heat exchanger 23 after the defrosting operation. Can be considered.
  • the air conditioning apparatus 1 it is possible to appropriately perform the freeze prevention control at the time of resuming the heating in consideration of the time necessary for discharging the drain water.
  • the predetermined time ts of the freeze prevention control when resuming heating can be changed by a switch (not shown), a remote controller (not shown), etc., but automatically according to the operating conditions. It is not intended to be changed.
  • the amount of drain water present on the lower side of the outdoor heat exchanger 23 after the defrosting operation varies depending on the outside air temperature Ta, the outside air humidity, or the operation time of the defrosting operation.
  • the amount of drain water increases as the outside air humidity increases or the operating time of the defrosting operation increases. For this reason, it is preferable to change also about predetermined time ts of anti-freezing control at the time of heating resumption by outside temperature Ta, outside air humidity, or operating time of defrosting operation.
  • the predetermined time ts is set to increase as the outside air temperature Ta decreases, the outside air humidity increases, or the operating time of the defrosting operation increases. (See step S3 in FIG. 8). For this reason, in the air conditioning apparatus 1 of this modification, the amount of drain water that varies depending on the outside air temperature Ta can be taken into account.
  • the predetermined time ts of the freeze prevention control at the time of resuming heating can be changed by the outside air humidity, it is necessary to provide a humidity sensor in the outdoor unit 2 although not shown here.
  • the freeze prevention control at the time of heating resumption can be appropriately performed in consideration of the change in the amount of drain water due to conditions such as the outside air temperature Ta.
  • the hot gas opening / closing mechanism 27b provided in the hot gas bypass pipe 27 is an electromagnetic valve, and therefore, in the freeze prevention control at the time of resuming heating, heat exchange for freeze prevention is performed.
  • the flow rate of the refrigerant flowing through the vessel 25 cannot be varied.
  • the amount of drain water present on the lower side of the outdoor heat exchanger 23 after the defrosting operation varies depending on the outside air temperature Ta, the outside air humidity, or the operation time of the defrosting operation. Specifically, the amount of drain water increases as the outside air temperature Ta decreases, the outside air humidity increases, or the operating time of the defrosting operation increases. For this reason, it is preferable to change also the flow volume of the refrigerant
  • the hot gas bypass pipe 27 is provided with a hot gas flow rate adjustment valve 27d for changing the flow rate of the refrigerant flowing through the antifreezing heat exchanger 25 (see FIG. 9).
  • the opening degree of the hot gas flow rate control valve 27d in the freeze prevention control at the time of resuming heating is set to be increased. (See step S3 in FIG. 10). For this reason, in the air conditioning apparatus 1 of the present modification, the amount of drain water that changes depending on the outside air temperature Ta, the outside air humidity, or the operating time of the defrosting operation can be taken into consideration.
  • FIG. 11 is a schematic configuration diagram of an air conditioner 1 according to the second embodiment of the present invention.
  • the air conditioning apparatus 1 is an apparatus used for air conditioning in a room such as a building by performing a vapor compression refrigeration cycle.
  • the air conditioner 1 mainly includes one outdoor unit 2, one intermediate unit 4, a plurality (two in this case) of indoor units 5 and 6, an outdoor unit 2, a functional unit 4, and an indoor unit.
  • a liquid refrigerant communication pipe 7 and a gas refrigerant communication pipe 8 for connecting the units 5 and 6 are provided. That is, the vapor compression refrigerant circuit 10 of the air conditioner 1 is connected to the outdoor unit 2, the functional unit 4, the indoor units 5 and 6, the liquid refrigerant communication pipe 7 and the gas refrigerant communication pipe 8. It is constituted by. Note that the number of indoor units 5 and 6 is not limited to two, and may be one or three or more.
  • the indoor units 5 and 6 are installed by being embedded or suspended in a ceiling of a room such as a building, or by wall hanging on a wall surface of the room.
  • the indoor units 5 and 6 are connected to the functional unit 4 via a first liquid refrigerant communication tube 7a which is a part of the liquid refrigerant communication tube 7 and a second gas refrigerant communication tube 8a which is a part of the gas refrigerant communication tube 8. And constitutes a part of the refrigerant circuit 10.
  • a first liquid refrigerant communication tube 7a which is a part of the liquid refrigerant communication tube 7
  • a second gas refrigerant communication tube 8a which is a part of the gas refrigerant communication tube 8.
  • the indoor unit 5 mainly has an indoor expansion valve 51 and an indoor heat exchanger 52.
  • the indoor expansion valve 51 is a device that adjusts the pressure and flow rate of the refrigerant flowing through the indoor unit 5.
  • the indoor expansion valve 51 has one end connected to the liquid side of the indoor heat exchanger 52 and the other end connected to the first liquid refrigerant communication pipe 7a.
  • an electric expansion valve is used as the indoor expansion valve 51.
  • the indoor heat exchanger 52 is a heat exchanger that functions as a refrigerant evaporator during cooling operation to cool indoor air and functions as a refrigerant condenser during heating operation to heat indoor air.
  • the indoor heat exchanger 52 has a liquid side connected to the indoor expansion valve 51 and a gas side connected to the first gas refrigerant communication pipe 8a.
  • the indoor heat exchanger 52 is a cross-fin type fin-and-tube heat exchanger composed of heat transfer tubes and a large number of fins.
  • the type of the indoor heat exchanger 52 is not limited to the cross fin type fin-and-tube type heat exchanger, and other types such as a laminated heat exchanger using corrugated fins or flat tubes, for example. It may be a type of heat exchanger.
  • the indoor unit 5 has an indoor fan 53 for supplying indoor air as supply air after sucking indoor air into the indoor unit 5 and exchanging heat with the refrigerant in the indoor heat exchanger 52.
  • the indoor fan 53 a centrifugal fan or a multiblade fan driven by an indoor fan motor 53a is used.
  • the indoor unit 5 includes an indoor side control unit 54 that controls the operation of each unit constituting the indoor unit 5.
  • the indoor side control part 54 has a microcomputer, memory, etc. for controlling the indoor unit 5, and between the remote controllers (not shown) for operating the indoor unit 5 separately. Control signals and the like can be exchanged, and control signals and the like can be exchanged with the outdoor unit 2 and the functional unit 4 via the transmission line 9a.
  • the outdoor unit 2 is installed outside a building or the like.
  • the outdoor unit 2 is connected to the functional unit 4 via a second liquid refrigerant communication tube 7b which is a part of the liquid refrigerant communication tube 7 and a second gas refrigerant communication tube 8b which is a part of the gas refrigerant communication tube 8. And constitutes a part of the refrigerant circuit 10.
  • the outdoor unit 2 mainly includes a low-stage compressor 21, which constitutes the compression mechanism 20, together with a high-stage compressor 32 (described later) of the functional unit 4, switching mechanisms 22, 31, an outdoor heat exchanger 23, an outdoor unit It has an expansion valve 24 and a heat exchanger 25 for preventing freezing.
  • the low stage compressor 21 is a device that compresses the refrigerant.
  • the low-stage compressor 21 has a hermetic structure in which a rotary compression element or a scroll-type displacement compression element (not shown) is rotationally driven by a low-stage compressor motor 21a.
  • the low-stage compressor 21 has a first gas refrigerant pipe 26a connected to the suction side and a second gas refrigerant pipe 26b connected to the discharge side.
  • the first gas refrigerant pipe 26 a is a refrigerant pipe that connects the suction side of the low-stage compressor 21 and the first port 22 a of the first switching mechanism 22.
  • the second gas refrigerant pipe 26 b is a refrigerant pipe that connects the discharge side of the low-stage compressor 21 and the second port 22 b of the first switching mechanism 22.
  • one low-stage compressor 21 constitutes the compression mechanism 20 together with the high-stage compressor 32, but a plurality of low-stage compressors 21 connected in parallel and a high stage
  • the compression mechanism 20 may be configured with the side compressor 32.
  • the switching mechanisms 22 and 31 are mechanisms for switching the direction of refrigerant flow in the refrigerant circuit 10.
  • the switching mechanisms 22 and 31 cause the outdoor heat exchanger 23 to function as a condenser of the refrigerant compressed in the low-stage compressor 21 during the cooling operation and the defrosting operation, and the indoor heat exchangers 52 and 62 Switching is performed so as to function as an evaporator of the refrigerant condensed in the outdoor heat exchanger 23.
  • the first switching mechanism 22 switches between the second port 22b and the third port 22c and the first port 22a and the fourth port 22d during the cooling operation and the defrosting operation. .
  • the second switching mechanism 31 switches between the second port 31b and the third port 31c and the first port 31a and the fourth port 31d during the cooling operation and the defrosting operation. .
  • the discharge side of the low-stage compressor 21 here, the second gas refrigerant pipe 26b
  • the gas side of the outdoor heat exchanger 23 here, the third gas refrigerant pipe 26c
  • the suction side of the low-stage compressor 21 (here, the first gas refrigerant pipe 26a) and the second gas refrigerant communication pipe 8b side (here, the fifth gas refrigerant pipe 26f and the sixth gas refrigerant pipe 26g) are connected (see the solid line of the second switching mechanism 31 in FIG. 11).
  • the switching mechanisms 22 and 31 cause the outdoor heat exchanger 23 to function as an evaporator of the refrigerant condensed in the indoor heat exchangers 42 and 52 during the heating operation, and the indoor heat exchangers 52 and 62 are set on the lower stage side. Switching to function as a condenser for the refrigerant compressed in the compressor 21 is performed.
  • the first switching mechanism 22 switches the second port 22b and the fourth port 22d to communicate with each other and the first port 22a and the third port 22c to communicate with each other.
  • the second switching mechanism 31 performs switching so that the second port 31b and the fourth port 31d communicate with each other and the first port 31a and the third port 31c communicate with each other.
  • the discharge side here, the second gas refrigerant pipe 26b
  • the gas refrigerant communication pipe 8 side here, the fourth gas refrigerant pipe 26d and the fifth gas refrigerant pipe 26f
  • the suction side (here, the first gas refrigerant pipe 26a) of the low-stage compressor 21 and the gas side (here, the third gas refrigerant pipe 26c) of the outdoor heat exchanger 23 are connected (FIG. 11).
  • the third gas refrigerant pipe 26 c is a refrigerant pipe that connects the third port 22 c of the first switching mechanism 22 and the gas side of the outdoor heat exchanger 23.
  • the fourth gas refrigerant pipe 26 d is a refrigerant pipe that connects a middle portion of the second gas refrigerant pipe 26 b and the fourth port 31 d of the second switching mechanism 31.
  • the fifth gas refrigerant pipe 26f is a refrigerant pipe that connects the second port 31b of the second switching mechanism 31 and the second gas refrigerant communication pipe 8b side.
  • the first switching mechanism 22 is a four-way switching valve.
  • the 4th port 22d of the 1st switching mechanism 22 is connected to the 1st gas refrigerant pipe 26a through the 7th gas refrigerant pipe 26h consisting of a capillary tube with very large channel resistance. For this reason, almost no refrigerant flows through the seventh gas refrigerant pipe 26h, so that the first switching mechanism 22 functions as a three-way valve having the first to third ports 22a to 22c. ing.
  • the first port 31a of the second switching mechanism 31 is connected to the sixth gas refrigerant pipe 26g through an eighth gas refrigerant pipe 26i made of a capillary tube having a very large flow path resistance. For this reason, almost no refrigerant flows through the eighth gas refrigerant pipe 26a, so that the second switching mechanism 31 functions as a three-way valve having the second to fourth ports 31b to 31d. ing.
  • the configuration of the switching mechanisms 22 and 31 is not limited to that using two four-way switching valves.
  • the switching mechanisms 22 and 31 may be configured by one four-way switching valve or a plurality of electromagnetic A configuration in which valves and the like are connected so as to perform the switching function described above may be used.
  • the outdoor heat exchanger 23 is a heat exchanger that functions as a refrigerant condenser during cooling operation and defrosting operation, and functions as a refrigerant evaporator during heating operation.
  • the outdoor heat exchanger 23 has a liquid side connected to the first liquid refrigerant pipe 26e and a gas side connected to the third gas refrigerant pipe 26c.
  • the first liquid refrigerant pipe 26e is a refrigerant pipe that connects the liquid side of the outdoor heat exchanger 23 and the second liquid refrigerant communication pipe 7b side.
  • the outdoor heat exchanger 23 is a cross-fin type fin-and-tube heat exchanger composed of heat transfer tubes and a large number of fins.
  • the type of the outdoor heat exchanger 23 is not limited to the cross fin type fin-and-tube type heat exchanger. It may be a type of heat exchanger.
  • the outdoor expansion valve 24 is a device that adjusts the pressure and flow rate of the refrigerant flowing through the outdoor unit 2.
  • the outdoor expansion valve 24 is provided in the first liquid refrigerant pipe 26e.
  • an electric expansion valve is used as the outdoor expansion valve 24.
  • the antifreezing heat exchanger 25 is a heat exchanger that heats the lower side of the outdoor heat exchanger 23 with a part of the refrigerant compressed in the low-stage compressor 21 constituting the compression mechanism 20.
  • the antifreezing heat exchanger 25 is provided in the hot gas bypass pipe 27.
  • the anti-freezing heat exchanger 25 is a cross-fin type fin-and-tube heat exchanger composed of heat transfer tubes and a large number of fins, and as shown in FIG. 2, an outdoor heat exchanger. 23 is integrated with the lower part.
  • the outdoor heat exchanger 23 and the antifreezing heat exchanger 25 are configured as an integral fin-and-tube heat exchanger, and the heat transfer tubes and fins on the upper side are the outdoor heat exchanger 23.
  • FIG. 2 is a schematic view showing the lower side of the outdoor heat exchanger 23 including the freeze-preventing heat exchanger 25 and the bottom plate 2 a of the outdoor unit 2.
  • the type of the anti-freezing heat exchanger 25 is not limited to the cross-fin type fin-and-tube type heat exchanger, for example, a laminated heat exchanger using corrugated fins or flat tubes, etc. Other types of heat exchangers may be used.
  • the hot gas bypass pipe 27 is a refrigerant pipe that branches a part of the refrigerant compressed in the low-stage compressor 21.
  • One end side of the hot gas bypass pipe 27 is connected so as to branch from a middle portion of the second gas refrigerant pipe 26c, and the other end side is connected to the liquid side of the outdoor heat exchanger 23 of the first liquid refrigerant pipe 26e and the outdoor expansion valve. 24 is connected so as to join the portion between the two.
  • a hot gas decompression mechanism 27a, a hot gas opening / closing mechanism 27b, and a hot gas check mechanism 27c are provided at a portion of the hot gas bypass pipe 27 on the outlet side of the heat exchanger 25 for preventing freezing.
  • the hot gas decompression mechanism 27a is a device that decompresses the refrigerant.
  • a capillary tube is used as the hot gas decompression mechanism 27a.
  • the hot gas opening / closing mechanism 27b is opened when a part of the refrigerant compressed in the low stage compressor 21 is branched into the hot gas bypass pipe 27, and is compressed in the low stage compressor 21 by the hot gas bypass pipe 27.
  • This is a device that can be closed when a part of the refrigerant is not branched.
  • an electromagnetic valve is used as the hot gas opening / closing mechanism 27b.
  • the hot gas check mechanism 27c is a mechanism that allows the refrigerant to flow from the outlet side of the antifreezing heat exchanger 25 to the first liquid refrigerant pipe 26e and blocks the flow in the reverse direction.
  • a check valve is used as the hot gas check mechanism 27c.
  • a functional unit is connected between the outdoor unit 2 and the indoor units 5 and 6 to thereby perform a two-stage compression refrigeration cycle. To be able to do.
  • An outdoor heat exchanger 23 in which frost formation occurs is provided in the outdoor unit 2.
  • the freeze prevention heat exchanger 25 is provided in the outdoor unit 2, and the refrigerant compressed in the low-stage compressor 21 provided in the outdoor unit 2 is used as a heating source for the freeze prevention heat exchanger 25.
  • the hot gas bypass pipe 27 that uses the section is provided. As a result, the hot gas bypass pipe 27 is configured to be accommodated in the outdoor unit 2 so as not to be configured to straddle between the outdoor unit 2 and the functional unit 4.
  • the outdoor unit 2 has an outdoor fan 28 for sucking outdoor air into the outdoor unit 2, exchanging heat with the refrigerant in the outdoor heat exchanger 23, and then discharging it to the outside of the outdoor unit 2.
  • an outdoor fan 28 an axial fan or the like driven by an outdoor fan motor 28a is used.
  • the anti-freezing heat exchanger 25 is integrated with the lower part of the outdoor heat exchanger 23. Therefore, the outdoor fan 28 is not only the outdoor heat exchanger 23 but also the anti-freezing heat. Outdoor air is also supplied to the exchanger 25.
  • the outdoor unit 2 is provided with various sensors.
  • the outdoor unit 2 is mainly provided with an intake pressure sensor 29a, a discharge pressure sensor 29b, an outdoor heat exchange temperature sensor 29c, and an outdoor temperature sensor 29d.
  • the suction pressure sensor 29 a is a pressure sensor that detects the suction pressure Ps of the low-stage compressor 21.
  • the discharge pressure sensor 29b is a pressure sensor that detects the discharge pressure Pd1 of the low-stage compressor 21.
  • the outdoor heat exchange temperature sensor 29 c is a temperature sensor that detects the temperature Tb of the refrigerant flowing through the outdoor heat exchanger 23.
  • the outside air temperature sensor 29d is a temperature sensor that detects the outside air temperature Ta in the outdoor unit 2.
  • the outdoor unit 2 also has an outdoor control unit 30 that controls the operation of each part constituting the outdoor unit 2.
  • the outdoor control unit 30 includes a microcomputer and a memory for controlling the outdoor unit 2, and is connected to the indoor control units 54 and 64 of the indoor units 5 and 6 and the functional unit 4. Control signals and the like can be exchanged via the transmission line 9a.
  • the functional unit 4 is a unit that allows a two-stage compression refrigeration cycle to be performed by being connected between the outdoor unit 2 and the indoor units 5 and 6 in order to increase the heating capacity in a condition where the outside air temperature is low. It is installed outside the building.
  • the functional unit 4 is connected to the indoor units 5 and 6 via the first liquid refrigerant communication pipe 7a and the first gas refrigerant communication pipe 8a, and the second liquid refrigerant communication pipe 7b and the second gas refrigerant communication pipe. It is connected to the outdoor unit 2 via 8b and constitutes a part of the refrigerant circuit 10.
  • the functional unit 4 mainly includes a high-stage compressor 32 that constitutes the compression mechanism 20 together with the low-stage compressor 21 of the outdoor unit 2, a gas-liquid separator 33, a ninth gas refrigerant pipe 34a, and a second liquid. And a refrigerant pipe 34b.
  • the ninth gas refrigerant tube 34a is a refrigerant tube that connects the first gas refrigerant communication tube 8a and the second gas refrigerant communication tube 8b.
  • a first gas refrigerant opening / closing mechanism 35 is provided in the ninth gas refrigerant pipe 34a.
  • an electromagnetic valve is used as the first gas refrigerant opening / closing mechanism 35.
  • the second liquid refrigerant pipe 34b is a refrigerant pipe that connects the first liquid refrigerant communication pipe 7a and the second liquid refrigerant communication pipe 7b.
  • the second liquid refrigerant pipe 34b has a third liquid refrigerant pipe 34c and a fourth liquid refrigerant pipe 34d connected in parallel to the third liquid refrigerant pipe 34c.
  • the third liquid refrigerant pipe 34c is a refrigerant pipe for flowing a refrigerant from the second liquid refrigerant communication pipe 7b toward the first liquid refrigerant communication pipe 7a.
  • a first liquid refrigerant check mechanism 36 is provided in the third liquid refrigerant pipe 34c.
  • the first liquid refrigerant check mechanism 36 is a mechanism that allows the flow of refrigerant from the second liquid refrigerant communication pipe 7b side to the first liquid refrigerant communication pipe 7a side and blocks the flow in the reverse direction.
  • a check valve is used as the first liquid refrigerant check mechanism 36.
  • the fourth liquid refrigerant pipe 34d is a refrigerant pipe for flowing the refrigerant from the first liquid refrigerant communication pipe 7a toward the second liquid refrigerant communication pipe 7b.
  • the fourth liquid refrigerant pipe 34d is provided with a first liquid refrigerant opening / closing mechanism 37 and a second liquid refrigerant check mechanism 38.
  • an electromagnetic valve is used as the first liquid refrigerant opening / closing mechanism 37.
  • the second liquid refrigerant check mechanism 38 is a mechanism that allows the flow of refrigerant from the first liquid refrigerant communication pipe 7a side to the second liquid refrigerant communication pipe 7b side and blocks the flow in the reverse direction.
  • a check valve is used as the second liquid refrigerant check mechanism 38.
  • the high stage compressor 32 is a device that compresses the refrigerant.
  • the high stage compressor 32 has a hermetic structure in which a rotary type or scroll type positive displacement compression element (not shown) is rotationally driven by a high stage compressor motor 32a.
  • the high stage compressor 32 has a tenth gas refrigerant pipe 34e connected to the suction side and an eleventh gas refrigerant pipe 34f connected to the discharge side.
  • the tenth gas refrigerant pipe 34e connects the suction side of the high-stage compressor 32 and the portion of the ninth gas refrigerant pipe 34a closer to the second gas refrigerant communication pipe 8b than the first gas refrigerant opening / closing mechanism 35. It is.
  • a high stage suction expansion valve 39 is provided in the tenth gas refrigerant pipe 34e.
  • the high-stage suction expansion valve 39 is opened when the refrigerant compressed in the low-stage compressor 21 is sucked into the high-stage compressor 32 and further compressed, and the refrigerant compressed in the low-stage compressor 21 is high.
  • This is a device that can be closed when the stage-side compressor 32 is not inhaled.
  • an electric expansion valve is used as the high stage intake expansion valve 39.
  • the eleventh gas refrigerant pipe 34f connects the discharge side of the high-stage compressor 32 and the portion of the ninth gas refrigerant pipe 34a closer to the first gas refrigerant communication pipe 8a than the first gas refrigerant open / close mechanism 35. It is.
  • the gas-liquid separator 33 is a device that introduces the refrigerant flowing through the second liquid refrigerant pipe 34b and separates it into a gas refrigerant and a liquid refrigerant.
  • a vertical cylindrical container is used as the gas-liquid separator 33.
  • a fifth liquid refrigerant pipe 34g, a sixth liquid refrigerant pipe 34h, and a twelfth gas refrigerant pipe 34i are connected to the gas-liquid separator 33.
  • the fifth liquid refrigerant pipe 34g includes a portion of the fourth liquid refrigerant pipe 34d closer to the first liquid refrigerant communication pipe 7a than the first liquid refrigerant open / close mechanism 37 and the second liquid refrigerant check mechanism 38 and the gas-liquid separator 33.
  • the fifth liquid refrigerant pipe 34g is provided with a second liquid refrigerant opening / closing mechanism 40 and a third liquid refrigerant check mechanism 41.
  • an electromagnetic valve is used as the second liquid refrigerant opening / closing mechanism 40.
  • the third liquid refrigerant check mechanism 41 is a mechanism that allows the flow of refrigerant from the second liquid refrigerant pipe 34b side to the refrigerant inlet side of the gas-liquid separator 33 and blocks the flow in the reverse direction.
  • a check valve is used as the third liquid refrigerant check mechanism 41.
  • the sixth liquid refrigerant pipe 34h includes a portion of the fourth liquid refrigerant pipe 34d closer to the second liquid refrigerant communication pipe 7b than the first liquid refrigerant open / close mechanism 37 and the second liquid refrigerant check mechanism 38 and the gas-liquid separator 33. It is a refrigerant pipe connecting between the liquid refrigerant outlet formed in the lower part.
  • a fourth liquid refrigerant check mechanism 42 is provided in the sixth liquid refrigerant pipe 34h.
  • the fourth liquid refrigerant check mechanism 42 is a mechanism that allows the flow of refrigerant from the liquid refrigerant outlet side of the gas-liquid separator 33 to the second liquid refrigerant pipe 34b side and blocks the flow in the reverse direction.
  • a check valve is used as the fourth liquid refrigerant check mechanism 42.
  • the twelfth gas refrigerant pipe 34i is between a portion of the tenth gas refrigerant pipe 34e closer to the higher stage compressor 32 than the higher stage suction expansion valve 39 and a gas refrigerant outlet formed at the upper part of the gas-liquid separator 33. It is a refrigerant pipe which connects.
  • the functional unit 4 is provided with various sensors. Specifically, the functional unit 4 is mainly provided with a discharge pressure sensor 43.
  • the discharge pressure sensor 43 is a pressure sensor that detects the discharge pressure Pd2 of the high-stage compressor 32.
  • the functional unit 4 includes a function side control unit 44 that controls the operation of each unit constituting the functional unit 4.
  • the function-side control unit 44 includes a microcomputer, a memory, and the like for controlling the function unit 4, and controls the indoor-side control units 54 and 64 of the indoor units 5 and 6 and the outdoor-side control of the outdoor unit 2. Control signals and the like can be exchanged with the unit 30 via the transmission line 9a.
  • the operation control of the entire air conditioner 1 is performed by the indoor side control units 54 and 64, the outdoor side control unit 30, the function side control unit 44, and the transmission line 9a connecting the control units 30, 44, 54 and 64.
  • the control part 9 to perform is comprised.
  • FIG. 12 is a control block diagram of the air conditioner 1.
  • Refrigerant communication pipes 7 and 8 are refrigerant pipes constructed on site when the air conditioner 1 is installed at a place such as a building, and installation conditions such as a combination of the installation place and an outdoor unit and an indoor unit, etc. Those having various lengths and tube diameters are used.
  • the refrigerant circuit 10 of the air conditioner 1 is configured by connecting the outdoor unit 2, the functional unit 4, the indoor units 5 and 6, and the refrigerant communication tubes 7 and 8.
  • the air conditioner 1 is controlled by the control unit 9 including the indoor side control units 54 and 64, the function side control unit 44, and the outdoor side control unit 30, and the cooling operation, heating operation, and removal described below.
  • Various operations such as frost operation can be performed.
  • the air conditioner 1 can mainly perform a cooling operation, a heating operation, and a defrosting operation.
  • the cooling operation is an operation in which the refrigerant is circulated mainly in the order of the compression mechanism 20, the outdoor heat exchanger 23, and the indoor heat exchangers 52 and 62 in order to cool the indoor air.
  • the cooling operation is a single-stage compression refrigeration cycle in which only the low-stage compressor 21 of the compression mechanism 20 is operated.
  • the heating operation is an operation in which the refrigerant is circulated mainly in the order of the compression mechanism 20, the indoor heat exchangers 52 and 62, and the outdoor heat exchanger 23 in order to heat the indoor air.
  • the heating operation includes a single-stage heating operation under a condition where the outside air temperature is high and a two-stage heating operation under a condition where the outside air temperature is low.
  • the single-stage heating operation performs a single-stage compression refrigeration cycle in which only the low-stage compressor 21 of the compression mechanism 20 is operated.
  • the two-stage heating operation performs a two-stage compression refrigeration cycle that operates both the low-stage compressor 21 and the high-stage compressor 32 in the compression mechanism 20.
  • the defrosting operation is an operation in which the compression mechanism 20, the outdoor heat exchanger 23, and the indoor heat exchangers 52 and 62 are circulated in order in order to melt the frost generated in the outdoor heat exchanger 23 by the heating operation. is there.
  • the defrosting operation is a so-called reverse cycle defrosting operation in which the flow direction of the refrigerant is reversed from that of the heating operation.
  • the defrosting operation includes a single-stage defrosting operation under a condition where the outside air temperature is high and a two-stage defrosting operation under a condition where the outside air temperature is low.
  • the single-stage defrosting operation performs a single-stage compression refrigeration cycle in which only the low-stage compressor 21 of the compression mechanism 20 is operated.
  • the two-stage defrosting operation performs a two-stage compression refrigeration cycle that operates both the low-stage compressor 21 and the high-stage compressor 32 in the compression mechanism 20.
  • operation of the air conditioning apparatus 1 is demonstrated.
  • FIG. 13 is a schematic configuration diagram illustrating a refrigerant flow during the cooling operation of the air-conditioning apparatus 1.
  • the switching mechanisms 22 and 31 are in the state indicated by the solid lines in FIG. 13, that is, the first switching mechanism 22 is connected to the second port 22b and the third port 22c, and the first port 22a Switching for connecting the fourth port 22d is performed.
  • switching is performed for connecting the second port 31b and the third port 31c, and for connecting the first port 31a and the fourth port 31d. I do.
  • the first gas refrigerant opening / closing mechanism 35 is opened, and the first liquid refrigerant opening / closing mechanism 37, the high-stage suction expansion valve 39, and the second liquid refrigerant opening / closing mechanism 40 are closed.
  • the outdoor heat exchanger 23 is made to function as a condenser of the refrigerant
  • a single-stage compression refrigeration cycle is performed which functions as a refrigerant evaporator.
  • the low-pressure gas refrigerant in the refrigeration cycle is sucked into the low-stage compressor 21 and compressed to become a high-pressure gas refrigerant.
  • This high-pressure gas refrigerant is sent to the outdoor heat exchanger 23 through the first switching mechanism 22, exchanges heat with outdoor air supplied by the outdoor fan 28, and condenses to become a high-pressure liquid refrigerant.
  • the high-pressure liquid refrigerant is sent to the indoor expansion valves 51 and 61 through the outdoor expansion valve 24, the second liquid refrigerant communication pipe 7b, the first liquid refrigerant check mechanism 36, and the first liquid refrigerant communication pipe 7a, and decompressed. It becomes a low-pressure refrigerant.
  • the low-pressure refrigerant is sent to the indoor heat exchangers 52 and 62, exchanges heat with the indoor air supplied by the indoor fans 53 and 63, and evaporates to become a low-pressure gas refrigerant.
  • the low-pressure gas refrigerant is sucked into the low-stage compressor 21 again through the first gas refrigerant communication pipe 8a, the first gas refrigerant open / close mechanism 35, the second gas refrigerant communication pipe 8b, and the second switching mechanism 31. .
  • the hot gas opening / closing mechanism 27b is opened. For this reason, a part of the high-pressure refrigerant that is compressed in the low-stage compressor 21 and flows through the second gas refrigerant pipe 26 b is branched to the hot gas bypass pipe 27.
  • the high-pressure refrigerant branched into the hot gas bypass pipe 27 is sent to the antifreezing heat exchanger 25 to heat the lower side of the outdoor heat exchanger 23. That is, the antifreezing heat exchanger 25 functions as a refrigerant condenser, similarly to the outdoor heat exchanger 23.
  • the anti-freezing heat exchanger 25 a part of the high-pressure gas refrigerant compressed in the low-stage compressor 21 is sent to the anti-freezing heat exchanger 25 through the hot gas bypass pipe 27 and the outdoor air supplied by the outdoor fan 28 and Heat exchange is performed to condense into a high-pressure liquid refrigerant.
  • the high-pressure liquid refrigerant is sent to the liquid refrigerant pipe 26e through the hot gas decompression mechanism 27a, the hot gas opening / closing mechanism 27b, and the hot gas check mechanism 27c, and merges with the high-pressure liquid refrigerant from the outdoor heat exchanger 23.
  • the antifreezing heat exchanger 25 functions as a refrigerant condenser during the cooling operation.
  • cooling of the refrigerant sent to the indoor heat exchangers 52 and 62 is promoted during the cooling operation, compared to a case where only the outdoor heat exchanger 23 functions as a refrigerant condenser, The cooling capacity is improved.
  • FIG. 14 is a schematic configuration diagram showing a refrigerant flow during the single-stage heating operation of the air-conditioning apparatus 1.
  • the single-stage heating operation is a heating operation performed under a condition where the outside air temperature is high, that is, a condition in which the heating capacity is easily secured.
  • the single-stage heating operation is performed when the outside air temperature Ta detected by the outside air temperature sensor 29d is equal to or higher than a predetermined first outside air temperature Tas1 (for example, 5 ° C.).
  • a predetermined first outside air temperature Tas1 for example, 5 ° C.
  • the first switching mechanism 22 is connected to the second port 22b and the fourth port 22d, and the first port
  • the second switching mechanism 31 communicates the second port 31b and the fourth port 31d and communicates the first port 31a and the third port 31c with each other. Change the mode. Further, the first gas refrigerant opening / closing mechanism 35 and the first liquid refrigerant opening / closing mechanism 37 are opened, and the high-stage suction expansion valve 39 and the second liquid refrigerant opening / closing mechanism 40 are closed.
  • the outdoor heat exchanger 23 functions as an evaporator for the refrigerant condensed in the indoor heat exchangers 42 and 52, and the indoor heat exchangers 52 and 62 are compressed in the low-stage compressor 21.
  • a single-stage compression refrigeration cycle is performed that functions as a condenser for the refrigerated refrigerant.
  • the low-pressure gas refrigerant in the refrigeration cycle is sucked into the low-stage compressor 21 and compressed to become a high-pressure gas refrigerant.
  • the high-pressure gas refrigerant passes through the first switching mechanism 22, the second switching mechanism 31, the second gas refrigerant communication pipe 8b, the first gas refrigerant opening / closing mechanism 35, and the first gas refrigerant communication pipe 8a, and the indoor heat exchangers 52 and 62.
  • the heat is exchanged with the indoor air supplied by the indoor fans 53 and 63 to condense into a high-pressure liquid refrigerant.
  • the high-pressure liquid refrigerant is expanded outdoors through the indoor expansion valves 51 and 61, the first liquid refrigerant communication pipe 7a, the first liquid refrigerant open / close mechanism 37, the second liquid refrigerant check mechanism 38, and the second liquid refrigerant communication pipe 7b.
  • the low-pressure refrigerant that is sent to the valve 24 and decompressed to become a low-pressure refrigerant is sent to the outdoor heat exchanger 23 to evaporate by exchanging heat with the outdoor air supplied by the outdoor fan 28. It becomes a low-pressure gas refrigerant. This low-pressure gas refrigerant is again sucked into the low-stage compressor 21 through the first switching mechanism 22.
  • the hot gas opening / closing mechanism 27b is closed. For this reason, the high-pressure refrigerant that is compressed in the low-stage compressor 21 and flows through the second gas refrigerant pipe 26 b is not branched to the hot gas bypass pipe 27. That is, during the single-stage heating operation, the refrigerant does not flow through the anti-freezing heat exchanger 25. Thus, in the air conditioner 1, all the high-pressure gas refrigerant compressed in the low-stage compressor 21 is sent to the indoor heat exchangers 52 and 62 during the single-stage heating operation.
  • FIG. 15 is a schematic configuration diagram illustrating a refrigerant flow during the two-stage heating operation of the air-conditioning apparatus 1.
  • the two-stage heating operation is a heating operation performed under a condition where the outside air temperature is low, that is, a condition where it is difficult to ensure the heating capacity.
  • the two-stage heating operation is performed when the outside air temperature Ta detected by the outside air temperature sensor 29d is lower than a predetermined first outside air temperature Tas1 (for example, 5 ° C.).
  • the switching mechanisms 22 and 31 are in the state indicated by the broken line in FIG. 15, that is, for the first switching mechanism 22, the second port 22b and the fourth port 22d are communicated, and the first port The second switching mechanism 31 communicates the second port 31b and the fourth port 31d and communicates the first port 31a and the third port 31c with each other. Change the mode.
  • the high-stage intake expansion valve 39 and the second liquid refrigerant opening / closing mechanism 40 are opened, and the first gas refrigerant opening / closing mechanism 35 and the first liquid refrigerant opening / closing mechanism 37 are closed.
  • the outdoor heat exchanger 23 is caused to function as an evaporator for the refrigerant condensed in the indoor heat exchangers 42 and 52, and the indoor heat exchangers 52 and 62 are A two-stage compression refrigeration cycle that functions as a condenser for the refrigerant compressed in the stage-side compressor 32 is performed.
  • the low-pressure gas refrigerant in the refrigeration cycle is sucked into the low-stage compressor 21 and compressed to become an intermediate-pressure gas refrigerant.
  • This intermediate-pressure gas refrigerant is sucked into the high-stage compressor 32 through the first switching mechanism 22, the second switching mechanism 31, the second gas refrigerant communication pipe 8b, and the high-stage suction expansion valve 39, and is compressed and pressurized.
  • This high-pressure gas refrigerant is sent to the indoor heat exchangers 52 and 62 through the first gas refrigerant communication pipe 8a, and is condensed by exchanging heat with the indoor air supplied by the indoor fans 53 and 63. Becomes a refrigerant.
  • This high-pressure liquid refrigerant is sent to the gas-liquid separator 33 through the indoor expansion valves 51 and 61, the first liquid refrigerant communication pipe 7a, the second liquid refrigerant open / close mechanism 40, and the third liquid refrigerant check mechanism 41, It is separated into a refrigerant and a liquid refrigerant.
  • the gas refrigerant separated in the gas-liquid separator 33 is sucked into the high stage compressor 32. Further, the liquid refrigerant separated in the gas-liquid separator 33 is sent to the outdoor expansion valve 24 through the fourth liquid refrigerant check mechanism 42 and the second liquid refrigerant communication pipe 7b, and is depressurized to be a low-pressure refrigerant. Become.
  • the low-pressure refrigerant is sent to the outdoor heat exchanger 23, exchanges heat with outdoor air supplied by the outdoor fan 28, and evaporates to become a low-pressure gas refrigerant.
  • This low-pressure gas refrigerant is again sucked into the low-stage compressor 21 through the first switching mechanism 22.
  • the hot gas opening / closing mechanism 27b is closed except when performing anti-freezing control when resuming heating, which will be described later.
  • the intermediate-pressure refrigerant that is compressed in the low-stage compressor 21 and flows through the second gas refrigerant pipe 26b is branched to the hot gas bypass pipe 27, except when performing anti-freezing control at the time of resuming heating described later.
  • the refrigerant does not flow through the anti-freezing heat exchanger 25 except when performing anti-freezing control when resuming heating described later.
  • the air conditioning apparatus 1 during the two-stage heating operation, all of the intermediate-pressure gas refrigerant compressed in the low-stage compressor 21 is high except for the case where anti-freezing control at the time of heating restart described later is performed. It is compressed in the stage side compressor 32 to become a high-pressure gas refrigerant, and is sent to the indoor heat exchangers 52 and 62. As described above, in the air conditioner 1, the flow rate of the refrigerant sent to the indoor heat exchangers 52 and 62 is increased in the two-stage heating operation as compared with the case where the refrigerant is passed through the freeze prevention heat exchanger 25. The decrease in heating capacity is suppressed.
  • FIG. 13 is a schematic configuration diagram illustrating the flow of the refrigerant during the single-stage defrosting operation of the air-conditioning apparatus 1.
  • the single-stage defrosting operation is a defrosting operation performed under a condition in which the outside air temperature is high, like the heating operation.
  • the single-stage defrosting operation is performed when the outside air temperature Ta detected by the outside air temperature sensor 29d is equal to or higher than a predetermined first outside air temperature Tas1.
  • the single-stage defrosting operation is a reverse cycle defrosting operation in which the refrigerant flow direction is reversed from the single-stage heating operation. Therefore, during the single-stage defrosting operation, the switching mechanisms 22 and 31 are in the state indicated by the solid line in FIG. 13, that is, the first switching mechanism 22 is connected to the second port 22b and the third port 22c, and The first port 22a and the fourth port 22d are switched to communicate with each other, the second switching mechanism 31 is connected to the second port 31b and the third port 31c, and the first port 31a and the fourth port are communicated. Switching to communicate with 31d is performed.
  • the first gas refrigerant opening / closing mechanism 35 is opened, and the first liquid refrigerant opening / closing mechanism 37, the high-stage suction expansion valve 39, and the second liquid refrigerant opening / closing mechanism 40 are closed.
  • the outdoor heat exchanger 23 is made to function as a condenser of the refrigerant
  • a single-stage compression refrigeration cycle is performed which functions as a refrigerant evaporator.
  • the single-stage defrosting operation is performed when the control unit 9 determines that frost formation has occurred in the outdoor heat exchanger 23 during the heating operation. This determination is performed based on the temperature Tb of the refrigerant flowing through the outdoor heat exchanger 23 detected by the outdoor heat exchanger temperature sensor 29c and the accumulated time of the heating operation. For example, when it is detected that the temperature Tb of the refrigerant detected by the outdoor heat exchanger temperature sensor 29c has decreased to a predetermined temperature or less that can be regarded as frost formation in the outdoor heat exchanger 23, or heating If the accumulated time of operation has passed a predetermined time that can be regarded as frost formation in the outdoor heat exchanger 23, it is determined that frost formation has occurred in the outdoor heat exchanger 23.
  • the refrigerant circuit 10 When the temperature condition or time condition is not reached, it is determined that frost formation has not occurred in the outdoor heat exchanger 23.
  • the refrigerant circulates in the same flow direction as in the cooling operation. Then, the high-pressure refrigerant that is compressed by the low-stage compressor 21 and flows through the second gas refrigerant pipe 26 b is sent to the outdoor heat exchanger 23 through the switching mechanism 22 to heat the outdoor heat exchanger 23. Thereby, the frost generated in the outdoor heat exchanger 23 in the heating operation is melted to become drain water, and passes through the anti-freezing heat exchanger 25 integrated with the outdoor heat exchanger 23 to the lower side of the outdoor heat exchanger 23. It collects on the bottom plate 2a of the outdoor unit 2 as a drain pan arranged. The drain water accumulated on the bottom plate 2a is discharged out of the outdoor unit 2 through a discharge port 2b formed on the bottom plate 2a.
  • the single-stage defrosting operation ends when the control unit 9 determines that the defrosting of the outdoor heat exchanger 23 has been completed. This determination is made based on the temperature Tb of the refrigerant flowing through the outdoor heat exchanger 23 detected by the outdoor heat exchanger temperature sensor 29c and the operation time of the single-stage defrosting operation.
  • the hot gas opening / closing mechanism 27b is opened as in the above cooling operation.
  • the anti-freezing heat exchanger 25 functions as a heater for drain water melted by performing a single-stage defrosting operation.
  • the drain water from the outdoor heat exchanger 23 is heated on the lower side of the outdoor heat exchanger 23 and then collected on the bottom plate 2a of the outdoor unit 2 as a drain pan.
  • the freeze prevention heat exchanger 25 heats the drain water generated in the outdoor heat exchanger 23 on the lower side of the outdoor heat exchanger 23. It has become. Thereby, in the air conditioning apparatus 1, the drain water from the outdoor heat exchanger 23 is quickly discharged
  • FIG. 16 is a schematic configuration diagram illustrating the flow of the refrigerant during the two-stage defrosting operation of the air-conditioning apparatus 1.
  • the two-stage defrosting operation is a defrosting operation performed under a condition where the outside air temperature is low.
  • the two-stage defrosting operation is performed when the outside air temperature Ta detected by the outside air temperature sensor 29d is lower than the predetermined first outside air temperature Tas1.
  • the two-stage defrosting operation is a reverse cycle defrosting operation in which the refrigerant flow direction is reversed from the two-stage heating operation.
  • the switching mechanisms 22 and 31 are in the state indicated by the solid line in FIG. 16, that is, the first switching mechanism 22 is connected to the second port 22b and the third port 22c, and The first port 22a and the fourth port 22d are switched to communicate with each other, the second switching mechanism 31 is connected to the second port 31b and the third port 31c, and the first port 31a and the fourth port are communicated. Switching to communicate with 31d is performed. Further, the first gas refrigerant opening / closing mechanism 35 and the second liquid refrigerant opening / closing mechanism 40 are opened, and the first liquid refrigerant opening / closing mechanism 37 and the high stage suction expansion valve 39 are closed.
  • the outdoor heat exchanger 23 is caused to function as a condenser for the refrigerant compressed in the high-stage compressor 32 and the low-stage compressor 21, and the indoor heat exchangers 52 and 62 are operated outdoors.
  • a two-stage compression refrigeration cycle that functions as an evaporator for the refrigerant condensed in the heat exchanger 23 is performed.
  • the two-stage defrosting operation is performed when the controller 9 determines that frost formation has occurred in the outdoor heat exchanger 23 during the heating operation. Since the content of this determination is the same as the content of the determination in the single stage defrosting operation, the description is omitted here.
  • the gas refrigerant is sucked into the low stage compressor 21 and compressed to become a high-pressure gas refrigerant. This high-pressure gas refrigerant is sent to the outdoor heat exchanger 23 through the first switching mechanism 22 to heat the outdoor heat exchanger 23.
  • the frost generated in the outdoor heat exchanger 23 in the heating operation is melted to become drain water, and passes through the anti-freezing heat exchanger 25 integrated with the outdoor heat exchanger 23 to the lower side of the outdoor heat exchanger 23. It collects on the bottom plate 2a of the outdoor unit 2 as a drain pan arranged. The drain water accumulated on the bottom plate 2a is discharged out of the outdoor unit 2 through a discharge port 2b formed on the bottom plate 2a. The high-pressure refrigerant that has melted frost in the outdoor heat exchanger 24 is sent to the outdoor expansion valve 24 to be depressurized.
  • a part of the decompressed refrigerant is sent to the indoor expansion valves 51 and 61 through the second liquid refrigerant communication pipe 7b, the first liquid refrigerant check mechanism 36 and the first liquid refrigerant communication pipe 7a, and the rest
  • the second liquid refrigerant communication pipe 7b, the first liquid refrigerant check mechanism 36, the second liquid refrigerant open / close mechanism 40, and the third liquid refrigerant check mechanism 41 are sent to the gas-liquid separator 33.
  • the low-pressure refrigerant sent to the indoor expansion valves 51 and 61 is sent to the ninth gas refrigerant pipe 34a through the indoor expansion valves 51 and 61, the indoor heat exchangers 52 and 62, and the first gas refrigerant communication pipe 8a.
  • the low-pressure refrigerant sent to the gas-liquid separator 33 is sucked into the high-stage compressor 32 and compressed, sent to the ninth gas refrigerant pipe 34a, and sent to the indoor expansion valves 51 and 61 and the indoor It merges with the refrigerant sent to the ninth gas refrigerant pipe 34a through the heat exchangers 52 and 62.
  • the refrigerant merged in the ninth gas refrigerant pipe 34 a is again sucked into the low-stage compressor 21 through the first gas refrigerant opening / closing mechanism 35, the second gas refrigerant communication pipe 8 b and the second switching mechanism 31.
  • the two-stage defrosting operation ends when the control unit 9 determines that the defrosting of the outdoor heat exchanger 23 is completed, as in the single-stage defrosting operation. Since the content of this determination is the same as the content of the determination in the single stage defrosting operation, the description is omitted here.
  • the hot gas opening / closing mechanism 27b is opened in the same manner as in the single-stage defrosting operation. For this reason, a part of the high-pressure refrigerant that is compressed in the low-stage compressor 21 and flows through the second gas refrigerant pipe 26 b is branched to the hot gas bypass pipe 27.
  • the high-pressure refrigerant branched into the hot gas bypass pipe 27 is sent to the antifreezing heat exchanger 25 to heat the lower side of the outdoor heat exchanger 23. That is, the anti-freezing heat exchanger 25 functions as a heater for drain water melted by performing the two-stage defrosting operation.
  • the drain water from the outdoor heat exchanger 23 is heated on the lower side of the outdoor heat exchanger 23 and then collected on the bottom plate 2a of the outdoor unit 2 as a drain pan. It is discharged out of the unit 2.
  • the antifreezing heat exchanger 25 heats the drain water generated in the outdoor heat exchanger 23 on the lower side of the outdoor heat exchanger 23.
  • drain water is quickly discharged out of the outdoor unit 2 during the two-stage defrosting operation.
  • the two-stage defrosting operation is performed under conditions where the outside air temperature is lower than the outside air temperature condition where the single-stage defrosting operation is performed (that is, when the outside air temperature Ta is lower than the predetermined first outside air temperature Tas1).
  • the drain water from the outdoor heat exchanger 23 can be prevented from freezing on the lower side of the outdoor heat exchanger 23, and the occurrence of the ice-up phenomenon during the two-stage defrosting operation is suppressed.
  • FIG. 17 is a flowchart of the freeze prevention control at the resumption of heating of the air-conditioning apparatus 1.
  • FIG. 18 is a schematic configuration diagram illustrating the refrigerant flow during the freeze prevention control at the time of resuming heating of the air-conditioning apparatus 1.
  • control part 9 determines whether it is the two-stage heating operation after a defrost operation in step S1.
  • step S1 when it is determined that the two-stage heating operation is performed after the defrosting operation, the process proceeds to the process of step S2 for determining whether or not an outside air temperature condition that requires anti-freezing control when resuming heating is satisfied. .
  • control part 9 determines whether the external temperature Ta detected by the external temperature sensor 29d is below predetermined 2nd external temperature Tas2 in step S2.
  • step S2 when the outside air temperature Ta is equal to or lower than the predetermined second outside air temperature Tas2, that is, when the outside air temperature condition is satisfied, the process proceeds to the processing of steps S3 to S5 for executing the anti-freezing control when resuming heating.
  • the outside air temperature Ta is higher than the predetermined second outside air temperature Tas2, that is, when the outside air temperature condition is not satisfied, the two-stage heating operation is performed without performing the freeze prevention control at the time of resuming the heating in steps S3 to S5. Resume.
  • the predetermined second outside air temperature Tas2 is set in view of whether or not the drain water present on the lower side of the outdoor heat exchanger 23 may be frozen after the defrosting operation. Is set to 0 ° C.
  • the predetermined second outside air temperature Tas2 is lower than the first outside air temperature Tas1, which is a temperature at which switching between the single-stage heating operation and the two-stage heating operation is performed.
  • the predetermined second outside air temperature Tas2 is stored in advance in a memory or the like of the control unit 9, and is changed by a switch (not shown) or a remote controller (not shown) provided in the control unit 9. Can be done.
  • control part 9 starts antifreezing control at the time of resumption of heating which flows a part of refrigerant
  • the high-pressure refrigerant branched into the hot gas bypass pipe 27 is sent to the antifreezing heat exchanger 25 to heat the lower side of the outdoor heat exchanger 23. That is, the antifreezing heat exchanger 25 functions as a heater for drain water existing on the lower side of the outdoor heat exchanger 23 after the defrosting operation.
  • the outlet of the hot gas bypass pipe 27 is connected to a portion of the liquid refrigerant pipe 26e through which the low-pressure refrigerant flows downstream of the outdoor expansion valve 24, the flow rate of the refrigerant flowing through the hot gas bypass pipe 27 is high. It is easy to be secured.
  • the refrigerant that has heated the drain water in the antifreezing heat exchanger 25 condenses in the antifreezing heat exchanger 25, but then merges with the refrigerant flowing through the liquid refrigerant pipe 26e and functions as a refrigerant evaporator. Therefore, the refrigerant condensed in the freezing prevention heat exchanger 25 remains in a liquid state and is not sucked into the low-stage compressor 21. As a result, during the two-stage heating operation after the defrosting operation, the drain water present on the lower side of the outdoor heat exchanger 23 is heated in the freezing prevention heat exchanger 25 and then the outdoor unit 2 as a drain pan. It accumulates on the bottom plate 2 a and is discharged out of the outdoor unit 2.
  • the anti-freezing heat exchanger 25 heats the drain water present on the lower side of the outdoor heat exchanger 23 during the two-stage heating operation after the defrosting operation. Yes.
  • the drain water present on the lower side of the outdoor heat exchanger 23 can be discharged without freezing after the defrosting operation. Occurrence of the ice-up phenomenon during the two-stage heating operation after the defrosting operation is suppressed.
  • control part 9 determines whether predetermined time ts passed after the defrost operation in step S4, and when predetermined time ts passed, it transfers to the process of step S5.
  • the predetermined time ts is set to about several minutes in consideration of the time required to discharge the drain water present on the lower side of the outdoor heat exchanger 23 after the defrosting operation.
  • the predetermined time ts is stored in advance in a memory or the like of the control unit 9 and can be changed by a switch (not shown) or a remote controller (not shown) provided in the control unit 9. It has become.
  • the same refrigeration cycle as in the above-described two-stage heating operation is performed, and the hot gas opening / closing mechanism 27b is closed.
  • the predetermined time ts for discharging the drain water existing on the lower side of the outdoor heat exchanger 23 after the defrosting operation without freezing that is, the defrosting operation. Only when the subsequent two-stage heating operation is restarted, the anti-freezing control at the time of restarting heating is performed.
  • the air conditioner 1 can suppress the occurrence of the ice-up phenomenon during the two-stage heating operation after the defrosting operation while suppressing the decrease in the heating capacity in the heating operation after the defrosting operation. It has become.
  • (3) Features of the air conditioner The air conditioner 1 that performs the two-stage compression refrigeration cycle as in the present embodiment also has the same features as the air conditioner 1 of the first embodiment. ⁇ A> That is, in the air conditioner 1, during the two-stage heating operation after the defrosting operation, a part of the refrigerant compressed in the compression mechanism 20 (here, the low-stage compressor 21) is transferred to the antifreezing heat exchanger 25.
  • the drain water present on the lower side of the outdoor heat exchanger 23 is frozen after the defrosting operation in a condition where the outside air temperature Ta is low (here, the outside air temperature Ta is equal to or less than the second outside air temperature Tas2). Can be discharged without any problems. For this reason, in the air conditioning apparatus 1, generation
  • the fall of the heating capability in the heating operation after a defrost operation can be suppressed.
  • production of the ice-up phenomenon at the time of the two-stage heating operation after a defrost operation can be suppressed, suppressing the fall of the heating capability in the heating operation after a defrost operation.
  • the anti-freezing control when resuming heating is performed when the outside air temperature Ta is equal to or lower than a predetermined second outside air temperature Tas2. For this reason, in the air conditioner 1, only when the outdoor air temperature Ta at which the drain water present on the lower side of the outdoor heat exchanger 23 may freeze after the defrosting operation is low (here, 0 ° C. or lower). When the heating is resumed, the freeze prevention control is performed. Under the condition where the outside air temperature Ta is high (in this case, higher than 0 ° C.), the freeze prevention control when the heating is resumed can be omitted. Thereby, in the air conditioning apparatus 1, the fall of the heating capability in the heating operation after a defrost operation can further be suppressed.
  • the anti-freezing control when resuming heating is performed until a predetermined time ts has elapsed after the defrosting operation. That is, in the air conditioner 1, since the antifreezing control at the time of resuming heating is managed by time, the time required for discharging the drain water present on the lower side of the outdoor heat exchanger 23 after the defrosting operation. Can be considered.
  • the air conditioning apparatus 1 it is possible to appropriately perform the freeze prevention control at the time of resuming the heating in consideration of the time required for discharging the drain water.
  • the outside air humidity increases as the outside air temperature Ta decreases, as in the modified example 1 (see FIG. 8) of the air conditioner 1 of the first embodiment.
  • the predetermined time ts may be set longer.
  • the heat exchanger 25 for antifreezing is added to the hot gas bypass pipe 27 similarly to the modification 2 (refer FIG.9 and FIG.10) of the air conditioning apparatus 1 of 1st Embodiment.
  • the hot gas flow rate control valve 27d for changing the flow rate of the refrigerant flowing through the refrigerant is provided, and heating is resumed as the outside air temperature Ta is lowered, the outside air humidity is increased, or the operating time of the defrosting operation is increased. You may set so that the opening degree of the hot gas flow control valve 27d in a time freezing prevention control may be enlarged.
  • the operation of the air conditioner 1 according to the present embodiment is that a single stage heating operation (described later) is performed at the time of restarting the second stage heating at the initial stage of restart of the two stage heating operation after the defrosting operation. Except for this, the operation is the same as that of the air conditioner 1 according to the second embodiment (FIGS. 13 to 18 and related descriptions). For this reason, about the operation
  • the description of each operation of the air conditioner 1 according to the second embodiment is substituted, and the description is omitted here.
  • the high pressure of the refrigeration cycle (here, the high stage) under the condition that the outside air temperature Ta is low. Since the discharge pressure Pd2 of the side compressor 32 is decreased, the pressure of the refrigerant compressed in the low stage compressor 21 in response to the decrease in the high pressure (here, the discharge pressure Pd1 of the low stage compressor 21; Therefore, the pressure of the refrigerant flowing into the antifreezing heat exchanger 25 is reduced, and the refrigerant flow path for supplying the refrigerant to the antifreezing heat exchanger 25 (that is, hot gas).
  • FIG. 19 is a flowchart of the single-stage heating operation when the air-conditioning apparatus 1 resumes the two-stage heating.
  • FIG. 20 is a schematic configuration diagram illustrating a refrigerant flow when the air-conditioning apparatus 1 performs the anti-freezing control when resuming heating and the single-stage heating operation when resuming two-stage heating.
  • FIG. 21 is a table showing the operation of the hot gas switching mechanism 27b in various heating operations of the air conditioner 1.
  • the control part 9 determines whether the freeze prevention control at the time of heating resumption started in step S11. If it is determined in this step S1 that the freeze prevention control at the time of resuming heating has started, the process proceeds to the process of step S12 for determining whether or not the outside air temperature condition that requires the single-stage heating operation at the time of resuming the two-stage heating is satisfied. To do.
  • step S12 the controller 9 determines whether or not the outside air temperature Ta detected by the outside air temperature sensor 29d is equal to or lower than a predetermined third outside air temperature Tas3.
  • the outside air temperature Ta is higher than the predetermined third outside air temperature Tas3, that is, when the outside air temperature condition is not satisfied, the single-stage heating operation at the time of resuming the two-stage heating in steps S13 to S15 is not performed.
  • the predetermined third outside air temperature Tas3 is a refrigeration cycle in the two-stage heating operation in addition to whether drain water present on the lower side of the outdoor heat exchanger 23 may be frozen after the defrosting operation. Is set from the viewpoint of whether or not the pressure difference in the hot gas bypass pipe 27 that supplies the refrigerant to the freeze-preventing heat exchanger 25 can be ensured, for example, set to ⁇ 10 ° C. Has been.
  • the predetermined third outside air temperature Tas3 is a temperature lower than the second outside air temperature Tas2, which is a threshold temperature for determining whether or not to perform anti-freezing control when resuming heating.
  • the predetermined third outside air temperature Tas3 is stored in advance in a memory or the like of the control unit 9, and is changed by a switch (not shown) or a remote controller (not shown) provided in the control unit 9. Can be done.
  • the switching condition of other operation control may be set under the condition of the outside air temperature Ta, and the condition for determining the necessity of the single stage heating operation when resuming the two-stage heating is also the condition of the outside air temperature Ta. (That is, the third outside air temperature Tas3 or less) is adopted, but from the viewpoint of securing a pressure difference in the hot gas bypass pipe 27, the pressure difference between the low pressure and the high pressure in the refrigeration cycle is equal to or less than a predetermined height difference. You may adopt the condition of whether or not.
  • the pressure difference between the low pressure and the high pressure of the refrigeration cycle in the immediately preceding two-stage heating operation is obtained from the discharge pressure sensors 29b and 43 and compared with a predetermined height difference, thereby restarting the two-stage heating. Whether or not the single-stage heating operation is necessary can be determined.
  • step S13 the control unit 9 performs anti-freezing control at the time of resuming heating in which a part of the refrigerant compressed by the low-stage compressor 21 is passed to the anti-freezing heat exchanger 25, and at the time of resuming two-stage heating.
  • Start single-stage heating operation That is, in the refrigerant circuit 10, the hot gas opening / closing mechanism 27b is opened and the same refrigeration cycle as in the single-stage heating operation is performed. For this reason, compared with the case where the low stage side compressor 21 and the high stage side compressor 32 are started (that is, the case where the two-stage heating operation is performed), the pressure of the refrigerant compressed in the low stage side compressor 21 increases.
  • the single-stage heating operation at the time of restarting the two-stage heating may reduce the heating capacity, but here, the single-stage heating operation is performed only at the initial stage of the restart of the two-stage heating operation after the defrosting operation. Moreover, the fall of the heating capability in the heating operation after a defrost operation can also be suppressed.
  • the air conditioning apparatus 1 the flow volume of the refrigerant
  • control part 9 determines whether freezing prevention control at the time of heating resumption was complete
  • the completion of the freeze prevention control at the time of resuming heating is the same as the elapse of the predetermined time ts after the defrosting operation.
  • the same refrigeration cycle as in the above-described two-stage heating operation is performed, and the hot gas opening / closing mechanism 27b is closed.
  • the predetermined time ts for discharging the drain water existing on the lower side of the outdoor heat exchanger 23 after the defrosting operation without freezing that is, the defrosting operation. Only when the subsequent two-stage heating operation is restarted, the anti-freezing control when restarting the heating and the single-stage heating operation when restarting the two-stage heating are performed.
  • the air conditioner 1 of the present embodiment has the following features. ⁇ A> In the air conditioner 1, during the two-stage heating operation after the defrosting operation, a part of the refrigerant compressed in the low-stage compressor 21 is caused to flow to the anti-freezing heat exchanger 25, thereby the outdoor heat after the defrosting operation.
  • the drain water present on the lower side of the exchanger 23 can be discharged without freezing. For this reason, in the air conditioning apparatus 1, generation
  • the high pressure of the refrigeration cycle is reduced under a condition where the outside air temperature Ta is low.
  • the pressure of the refrigerant compressed in the low stage compressor 21 (intermediate pressure in the refrigeration cycle) also decreases.
  • the pressure of the refrigerant flowing into the antifreezing heat exchanger 25 decreases, and the pressure difference secured in the refrigerant flow path (hot gas bypass pipe 27) that supplies the refrigerant to the antifreezing heat exchanger 25 is small. Therefore, the flow rate of the refrigerant flowing through the antifreezing heat exchanger 25 is reduced.
  • the low-stage compressor 21 the indoor heat exchange are performed without starting the high-stage compressor 32 only at the initial stage of restart of the two-stage heating operation after the defrosting operation.
  • the single stage heating operation at the time of restarting the two-stage heating in which the refrigerant is circulated in the order of the units 52 and 62 and the outdoor heat exchanger 23 is performed.
  • the air conditioner 1 compared with the case where the low stage side compressor 21 and the high stage side compressor 32 are started, the pressure of the refrigerant
  • the single-stage heating operation when resuming the two-stage heating may reduce the heating capacity, but here, the single-stage heating operation is performed only at the initial stage of the second-stage heating operation after the defrosting operation. Moreover, the fall of the heating capability in the heating operation after a defrost operation can also be suppressed.
  • the air conditioning apparatus 1 the flow rate of the refrigerant
  • the refrigerant is supplied to the freezing prevention heat exchanger 25 under conditions where the outside air temperature Ta at which the drain water present on the lower side of the outdoor heat exchanger 23 is frozen after the defrosting operation may be frozen is low.
  • the single-stage heating operation at the time of resuming the two-stage heating is performed only under the condition that the pressure difference of the refrigeration cycle in which it is difficult to ensure the pressure difference secured in the hot gas bypass pipe 27 is small.
  • the single-stage heating operation at the time of restarting the two-stage heating is performed when the outside air temperature Ta is equal to or lower than a predetermined third outside air temperature Tas3, or the pressure difference between the low pressure and the high pressure in the refrigeration cycle is equal to or lower than a predetermined height difference.
  • the fall of the heating capability in the heating operation after a defrost operation can further be suppressed.
  • the flow rate of the refrigerant flowing through the anti-freezing heat exchanger 25 is determined by the pressure difference secured in the hot gas bypass pipe 27 that supplies the refrigerant to the anti-freezing heat exchanger 25, or as the outside air temperature Ta increases, or As the pressure difference in the refrigeration cycle increases, it increases. For this reason, if the freezing prevention control at the time of resuming heating and the single-stage heating operation at the time of resuming the two-stage heating are performed regardless of the conditions of the outside air temperature Ta or the pressure difference of the refrigeration cycle, the antifreezing heat exchanger 25 is installed.
  • the flow rate of the flowing refrigerant is larger under conditions where the outside air temperature Ta is high and conditions under which the refrigeration cycle pressure difference is large than conditions under which the outside air temperature Ta is low and conditions under which the refrigeration cycle pressure difference is small.
  • the flow resistance of the hot gas bypass pipe 27 that supplies the refrigerant to the antifreezing heat exchanger 25 is determined under a condition where the outside air temperature Ta is low or a pressure difference of the refrigeration cycle is small, the outside air temperature Under the condition where Ta is high or the pressure difference in the refrigeration cycle is large, the flow rate of the refrigerant flowing through the antifreezing heat exchanger 25 becomes larger than necessary.
  • flowing a part of the refrigerant compressed in the low-stage compressor 21 to the anti-freezing heat exchanger 25 is sent to the indoor heat exchangers 52 and 62.
  • the flow rate of the refrigerant to be reduced is reduced, and the heating capacity is reduced.
  • the anti-freezing control at the restart of heating is performed at the initial stage of the restart of the two-stage heating operation after the defrosting operation. Single-stage heating operation is not performed when heating is resumed.
  • the two-stage heating after the defrosting operation when the outside air temperature Ta is higher than a predetermined third outside air temperature Tas3, or when the pressure difference between the low pressure and the high pressure in the refrigeration cycle is equal to or higher than a predetermined height difference, the two-stage heating after the defrosting operation At the initial stage of resuming operation, freeze prevention control is performed when heating is resumed, and single-stage heating operation is not performed when two-stage heating is resumed. For this reason, under the condition where the outside air temperature Ta is high or the pressure difference of the refrigeration cycle is large, the two-stage heating operation is performed without performing the single-stage heating operation from the beginning of the restart of the two-stage heating operation after the defrosting operation. Therefore, the pressure of the refrigerant compressed in the low stage compressor 21 becomes low.
  • the fall of the heating capability by freezing prevention control at the time of heating resumption can be suppressed on the conditions with the high outdoor temperature Ta, or the conditions with a large pressure difference of a refrigerating cycle.
  • the predetermined time ts of the anti-freezing control when resuming heating can be changed by a switch (not shown), a remote controller (not shown), etc. It is not automatically changed according to conditions.
  • the amount of drain water present on the lower side of the outdoor heat exchanger 23 after the defrosting operation varies depending on the outside air temperature Ta, the outside air humidity, or the operation time of the defrosting operation.
  • the amount of drain water increases as the outside air humidity increases or the operating time of the defrosting operation increases. For this reason, it is preferable to change also about predetermined time ts of anti-freezing control at the time of heating resumption by outside temperature Ta, outside air humidity, or operating time of defrosting operation.
  • the predetermined time ts is set to increase as the outside air temperature Ta decreases, the outside air humidity increases, or the operating time of the defrosting operation increases. (See step S3 in FIG. 22). For this reason, in the air conditioning apparatus 1 of this modification, the amount of drain water that varies depending on the outside air temperature Ta can be taken into consideration.
  • the freezing prevention control at the time of resuming heating and the single-stage heating operation at the time of resuming two-stage heating are appropriately performed in consideration of changes in the amount of drain water due to conditions such as the outside air temperature Ta. It can be carried out.
  • the present invention is applied to an air conditioner that can be switched between cooling and heating by switching between cooling operation, heating operation, and reverse cycle defrosting operation, but is not limited thereto, for example,
  • the present invention may be applied to a heating-only air conditioner that performs switching between heating operation and reverse cycle defrosting operation but does not perform cooling operation.
  • the configuration of the functional unit is not limited to those of the second and third embodiments and the modifications thereof, and includes a high-stage compressor, and is provided between the outdoor unit and the indoor unit. What is necessary is just the structure which enables it to perform a two-stage compression refrigeration cycle by being connected.
  • the present invention is widely applicable to an air conditioner that performs heating operation and reverse cycle defrosting operation.
  • Air Conditioner 20 Compression Mechanism 21 Compressor, Low Stage Compressor (Compression Mechanism) 23 Outdoor heat exchanger 25 Freezing prevention heat exchanger 32 High-stage compressor 52, 62 Indoor heat exchanger 27d Hot gas flow control valve (flow control valve)

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

Abstract

L'invention porte sur un climatiseur. Un échangeur de chaleur destiné à éviter le gel (25), qui est apte à chauffer le côté inférieur de l'échangeur de chaleur extérieur (23) en utilisant une partie d'un fluide frigorigène comprimé dans un mécanisme de compression (21), est agencé sur un climatiseur (1). Initialement, lorsqu'une opération de chauffage a repris après une opération de dégivrage, la commande de prévention du gel à la reprise du chauffage est exécutée de telle sorte qu'une partie du fluide frigorigène comprimé dans le mécanisme de compression (21) pénètre dans l'échangeur de chaleur pour éviter le gel (25).
PCT/JP2012/077465 2011-11-24 2012-10-24 Climatiseur WO2013077136A1 (fr)

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JP2011256494A JP2013108729A (ja) 2011-11-24 2011-11-24 空気調和装置
JP2011-256494 2011-11-24
JP2011256495A JP5170299B1 (ja) 2011-11-24 2011-11-24 空気調和装置
JP2011-256495 2011-11-24

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104748464A (zh) * 2013-12-25 2015-07-01 珠海格力电器股份有限公司 空调系统的多联机化霜方法及装置和空调器

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Publication number Priority date Publication date Assignee Title
JPS63178762U (fr) * 1987-05-12 1988-11-18
JPH0213765A (ja) * 1988-06-30 1990-01-18 Toshiba Corp 冷凍サイクル装置
JPH06241623A (ja) * 1993-02-22 1994-09-02 Mitsubishi Electric Corp 冷却装置
JPH09243211A (ja) * 1996-03-12 1997-09-19 Fujitsu General Ltd 空気調和機の制御方法
JP2007263391A (ja) * 2006-03-27 2007-10-11 Sanyo Electric Co Ltd 冷凍サイクル装置
JP2008138921A (ja) * 2006-11-30 2008-06-19 Mitsubishi Electric Corp 空気調和装置
JP2009127939A (ja) * 2007-11-22 2009-06-11 Mitsubishi Heavy Ind Ltd ヒートポンプ式空気調和機
JP2010156490A (ja) * 2008-12-26 2010-07-15 Daikin Ind Ltd 空気調和装置

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS63178762U (fr) * 1987-05-12 1988-11-18
JPH0213765A (ja) * 1988-06-30 1990-01-18 Toshiba Corp 冷凍サイクル装置
JPH06241623A (ja) * 1993-02-22 1994-09-02 Mitsubishi Electric Corp 冷却装置
JPH09243211A (ja) * 1996-03-12 1997-09-19 Fujitsu General Ltd 空気調和機の制御方法
JP2007263391A (ja) * 2006-03-27 2007-10-11 Sanyo Electric Co Ltd 冷凍サイクル装置
JP2008138921A (ja) * 2006-11-30 2008-06-19 Mitsubishi Electric Corp 空気調和装置
JP2009127939A (ja) * 2007-11-22 2009-06-11 Mitsubishi Heavy Ind Ltd ヒートポンプ式空気調和機
JP2010156490A (ja) * 2008-12-26 2010-07-15 Daikin Ind Ltd 空気調和装置

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104748464A (zh) * 2013-12-25 2015-07-01 珠海格力电器股份有限公司 空调系统的多联机化霜方法及装置和空调器

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