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WO2015059792A1 - Climatiseur - Google Patents

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Publication number
WO2015059792A1
WO2015059792A1 PCT/JP2013/078779 JP2013078779W WO2015059792A1 WO 2015059792 A1 WO2015059792 A1 WO 2015059792A1 JP 2013078779 W JP2013078779 W JP 2013078779W WO 2015059792 A1 WO2015059792 A1 WO 2015059792A1
Authority
WO
WIPO (PCT)
Prior art keywords
refrigerant
heat exchanger
source side
heat source
opening
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/JP2013/078779
Other languages
English (en)
Japanese (ja)
Inventor
傑 鳩村
山下　浩司
若本　慎一
直史 竹中
渡辺　和也
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Mitsubishi Electric Corp
Original Assignee
Mitsubishi Electric Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Mitsubishi Electric Corp filed Critical Mitsubishi Electric Corp
Priority to PCT/JP2013/078779 priority Critical patent/WO2015059792A1/fr
Priority to JP2015543648A priority patent/JP5992112B2/ja
Priority to EP13895977.0A priority patent/EP3062031B1/fr
Publication of WO2015059792A1 publication Critical patent/WO2015059792A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/30—Control or safety arrangements for purposes related to the operation of the system, e.g. for safety or monitoring
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/30—Control or safety arrangements for purposes related to the operation of the system, e.g. for safety or monitoring
    • F24F11/41—Defrosting; Preventing freezing
    • F24F11/42—Defrosting; Preventing freezing of outdoor units
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F13/00—Details common to, or for air-conditioning, air-humidification, ventilation or use of air currents for screening
    • F24F13/30—Arrangement or mounting of heat-exchangers
    • 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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
    • F25B41/24—Arrangement of shut-off valves for disconnecting a part of the refrigerant cycle, e.g. an outdoor part
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • 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
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/30—Control or safety arrangements for purposes related to the operation of the system, e.g. for safety or monitoring
    • F24F11/41—Defrosting; Preventing freezing
    • 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
    • F25B2313/005—Outdoor unit expansion valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/025—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple outdoor units
    • F25B2313/0251—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple outdoor units being defrosted alternately
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/031—Sensor arrangements
    • F25B2313/0314—Temperature sensors near the indoor heat exchanger
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/031—Sensor arrangements
    • F25B2313/0315—Temperature sensors near the outdoor heat exchanger
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/02—Compressor control
    • F25B2600/026—Compressor control by controlling unloaders
    • F25B2600/0261—Compressor control by controlling unloaders external to the compressor

Definitions

  • the present invention relates to an air conditioner.
  • an outdoor unit that is a heat source unit arranged outside a building is connected to an indoor unit (indoor unit) arranged inside the building by pipe connection.
  • the refrigerant circuit is configured to circulate the refrigerant.
  • heating or cooling of the air-conditioning target space is performed by heating and cooling the air using the heat radiation and heat absorption of the refrigerant.
  • the heat exchanger installed in the outdoor unit serves as an evaporator, and heat in the air is exchanged between the low-temperature refrigerant and the air, so that the moisture in the air becomes the fins of the heat exchanger. And it condenses on the heat transfer tube and forms frost on the heat exchanger.
  • the heat exchanger is frosted, the air path of the heat exchanger is blocked, and the heat transfer area of the heat exchanger that exchanges heat with air is reduced, which causes a problem of insufficient heating capacity.
  • the heating operation is stopped, the refrigerant flow is switched by the refrigerant flow switching device, and the heat exchanger installed in the outdoor unit is used as a condenser to perform the defrosting operation. .
  • the heat exchanger installed in the outdoor unit is used as a condenser to perform the defrosting operation.
  • the indoor heating operation is also stopped while the defrosting operation is being performed, the indoor temperature is lowered and the comfort of the indoor environment is impaired.
  • a plurality of heat exchangers are provided in the outdoor unit, and the discharge gas of the compressor is configured to be able to flow into each heat exchanger.
  • a bypass pipe is provided so that each of the plurality of heat exchangers can be bypassed via the on-off valve, and the plurality of heat exchangers are divided into an evaporator and a condenser for use in defrosting. Operation and heating operation can be performed simultaneously (see, for example, Patent Documents 1 to 3).
  • Medium pressure defrost is a defrost target condenser in which the pressure of the internal refrigerant is lower than the discharge pressure of the compressor and higher than the suction pressure (pressure that is slightly higher than 0 ° C. in terms of saturation temperature). This means defrost operation that is executed in the state.
  • the refrigerant amount of the entire refrigeration cycle decreases, the refrigerant amount supplied to the evaporator decreases, the indoor heating capacity decreases, and the comfort of the indoor environment is impaired. Will end up.
  • the latent heat of the two-phase part of the refrigerant cannot be used until the refrigerant is stored in the condenser, sufficient defrosting capacity cannot be obtained, and the defrosting time becomes longer, thereby reducing the indoor heating capacity. The comfort of the indoor environment will be impaired.
  • the present invention has been made against the background of the above problems.
  • the indoor heating capacity is reduced and the defrosting capacity is reduced.
  • An object of the present invention is to provide an air-conditioning apparatus that can suppress a decrease in the temperature.
  • the air conditioner according to the present invention is an air conditioner (100, 200) capable of simultaneously performing a heating operation and a defrosting operation, and includes a compressor (10), a load side heat exchanger (21), and a load side throttle.
  • a main circuit that forms at least a heating circuit by connecting a device (22), a plurality of heat source side heat exchangers (12) connected in parallel to each other, and an accumulator (13) by refrigerant piping; and the compressor ( 10), a first gas bypass pipe (5) branched from the discharge side of the plurality of heat source side heat exchangers (12) and allowing the refrigerant to flow into the heat source side heat exchanger (12) to be defrosted, Branched from the discharge side of the compressor (10) and provided in a second gas bypass pipe (7) for allowing the refrigerant to flow into the accumulator (13) and the first gas bypass pipe (5), the first gas Flow through bypass pipe (5)
  • the air conditioner according to the present invention operates the load-side heat exchanger as a condenser and operates a part of the heat-source-side heat exchanger as an evaporator to perform a heating operation, while the rest of the heat-source-side heat exchanger is operated.
  • the defrosting operation is performed by operating a part of the condenser as a condenser, the refrigerant remaining in the accumulator can be supplied to the evaporator and the condenser. Therefore, according to the air conditioning apparatus which concerns on this invention, the fall of the refrigerant
  • FIG. 1 shows the heating capability ratio at the time of defrost with respect to the saturation temperature in the heat source side heat exchanger which is a defrost object heat exchanger of the air conditioning apparatus which concerns on Embodiment 1 of this invention. It is a flowchart which shows the control action at the time of operating the 2nd opening / closing apparatus at the time of the defrost operation mode of the air conditioning apparatus which concerns on Embodiment 1 of this invention. Saturation temperature change in which the pressure in the load-side heat exchanger is converted when the flow rate of the high-temperature and high-pressure gas refrigerant flowing into the accumulator during the defrost mode of the air-conditioning apparatus according to Embodiment 1 of the present invention is changed.
  • FIG. 1 shows the heating capability ratio at the time of defrost with respect to the saturation temperature in the heat source side heat exchanger which is a defrost object heat exchanger of the air conditioning apparatus which concerns on Embodiment 1 of this invention.
  • FIG. 1 is a schematic circuit configuration diagram showing an example of a circuit configuration of an air-conditioning apparatus 100 according to Embodiment 1 of the present invention. Based on FIG. 1, the detailed structure of the air conditioning apparatus 100 is demonstrated.
  • the air conditioner 100 circulates refrigerant and performs air conditioning using a refrigeration cycle.
  • the air-conditioning apparatus 100 has a cooling only operation mode in which all the indoor units 2 to be operated are cooled, a heating only operation mode in which all the indoor units 2 to be heated are heated, or the indoor unit 2 is continuing the heating operation.
  • a defrosting operation mode for defrosting the heat exchanger (heat source side heat exchanger 12a, heat source side heat exchanger 12b) in the outdoor unit 1 can be selected.
  • the air conditioning apparatus 100 includes an outdoor unit 1 and an indoor unit 2, and is configured by connecting the outdoor unit 1 and the indoor unit 2 with a refrigerant main pipe 4.
  • the heat source side heat exchanger 12a and the heat source side heat exchanger 12b may be collectively referred to as the heat source side heat exchanger 12.
  • the outdoor unit 1 includes a compressor 10, a refrigerant flow switching device 11, such as a four-way valve, a heat source side heat exchanger 12a, a heat source side heat exchanger 12b, an accumulator 13, a first opening / closing device 30a, a first opening / closing device 30b, A second opening / closing device 35, a third opening / closing device 31a, a third opening / closing device 31b, a flow rate adjusting device 32a, and a flow rate adjusting device 32b are mounted.
  • these element devices are connected by a refrigerant pipe 3, a first gas bypass pipe 5, and a second gas bypass pipe 7.
  • the refrigerant pipe 3 connects the compressor 10, the refrigerant flow switching device 11, the heat source side heat exchanger 12a, the heat source side heat exchanger 12b, the flow rate adjusting device 32a, the flow rate adjusting device 32b, and the accumulator 13.
  • the heat source side heat exchanger 12a and the heat source side heat exchanger 12b are connected to each other in parallel by the refrigerant pipe 3.
  • the first gas bypass pipe 5 is connected to the refrigerant pipe 3 between the discharge part of the compressor 10 and the refrigerant flow switching device 11.
  • the first gas bypass pipe 5 is branched into two branches, one end of which is connected to the refrigerant pipe 3 between the heat source side heat exchanger 12a and the third switchgear 31a, and the other end is connected to the heat source side. It connects to the refrigerant
  • a first opening / closing device 30a is provided in the first gas bypass pipe 5 connected to the heat source side heat exchanger 12a.
  • a first opening / closing device 30b is provided in the first gas bypass pipe 5 connected to the heat source side heat exchanger 12b.
  • One end of the second gas bypass pipe 7 is connected to the refrigerant pipe 3 between the discharge part of the compressor 10 and the refrigerant flow switching device 11.
  • the other end of the second gas bypass pipe 7 is connected to the refrigerant pipe 3 between the refrigerant flow switching device 11 and the accumulator 13.
  • a second opening / closing device 35 is provided in the second gas bypass pipe 7.
  • the third opening / closing device 31 a that blocks the refrigerant flowing into the heat source side heat exchanger 12 a is installed in the refrigerant pipe 3 between the heat source side heat exchanger 12 a and the refrigerant flow switching device 11.
  • the third opening / closing device 31b for blocking the refrigerant flowing into the heat source side heat exchanger 12b is installed in the refrigerant pipe 3 between the heat source side heat exchanger 12b and the refrigerant flow switching device 11.
  • the heat source side heat exchanger 12a and the heat source side heat exchanger 12b include a plurality of plate-like fins (fins 51 shown in FIG. 2) and heat transfer tubes (see FIG. 2) inserted so as to be orthogonal to the fins. And a fin tube type heat exchanger having a heat pipe 52).
  • FIG. 2 is a schematic diagram illustrating an example of the configuration of the heat source side heat exchanger 12 of the air conditioner 100.
  • the heat source side heat exchanger 12 is divided into a plurality of heat exchangers.
  • the heat source side heat exchanger 12a and the heat source side heat exchanger 12b have two rows of fins 51 that are adjacent to each other in the row direction (the left-right direction in which each fin faces the same direction).
  • the heat source side heat exchanger 12a and the heat source side heat exchanger 12b are each configured in two stages in the step direction of the heat transfer tubes 52 (up and down directions in which the fins face the same direction).
  • the heat source side heat exchanger 12a and the heat source side heat exchanger 12b are configured by dividing the heat source side heat exchanger 12 in the casing of the outdoor unit 1, so that the fins 51 face the same direction. Are arranged vertically.
  • the heat source side heat exchanger 12a is disposed on the upper side
  • the heat source side heat exchanger 12b is disposed on the lower side
  • the fins 51 in the respective step directions are integrally formed (shared).
  • the refrigerant flow path of the heat source side heat exchanger 12a may be branched by a distributor 12a-1 and a header 12a-2.
  • the refrigerant flow path of the heat source side heat exchanger 12b may be branched by a distributor 12b-1 and a header 12b-2.
  • FIG. 2 In the configuration shown in FIG. 2, two rows of fins adjacent to each other in the row direction (left and right directions in which the respective fins face the same direction) have been described. A configuration may be used, and the path pattern may be different from that shown in FIG. Further, as the heat source side heat exchanger 12, a plurality of units such as three or more in the step direction (vertical direction in which each fin faces the same direction) is located, and the fins in each step direction are integrally formed (shared).
  • the number of stages is not limited to the number of stages shown in FIG. 2, and a larger number or a smaller number may be provided.
  • a plurality of the heat transfer tubes 52 are provided in the step direction perpendicular to the air passage direction and the row direction that is the air passage direction.
  • the fins 51 are arranged at intervals so that air passes in the air passage direction.
  • the heat source side heat exchanger 12 may be divided into left and right parts. However, when the heat source side heat exchanger 12 is divided into left and right parts, the refrigerant inlets to the heat source side heat exchanger 12a and the heat source side heat exchanger 12b are respectively connected to the outdoor unit 1. Because it becomes the left and right ends of the pipe, the pipe connection becomes complicated. For this reason, it is desirable to divide up and down as shown in FIG.
  • the fins 51 may not be divided as shown in FIG. 2, or may be divided. Moreover, the division
  • the outdoor air is conveyed to the heat source side heat exchanger 12a and the heat source side heat exchanger 12b by a blower (not shown) such as a fan, for example.
  • the blower may be installed in each of the heat source side heat exchanger 12a and the heat source side heat exchanger 12b, but may share one unit.
  • the flow rate adjusting device 32a can change the opening degree, and is provided in the refrigerant pipe 3 on the load side expansion device 22 side of the heat source side heat exchanger 12a.
  • the flow rate adjusting device 32b can change the opening degree, and is provided in the refrigerant pipe 3 on the load side expansion device 22 side of the heat source side heat exchanger 12b.
  • the compressor 10 sucks the refrigerant and compresses the refrigerant to a high temperature / high pressure state.
  • the compressor 10 is configured by, for example, an inverter compressor capable of capacity control.
  • the refrigerant flow switching device 11 switches the refrigerant flow in the heating only operation mode and the refrigerant flow in the cooling only operation mode.
  • Both the heat source side heat exchanger 12a and the heat source side heat exchanger 12b function as an evaporator during the heating only operation mode and function as a condenser during the cooling only operation mode. Further, during the defrosting operation, one of the heat source side heat exchanger 12a and the heat source side heat exchanger 12b functions as an evaporator and the other functions as a condenser.
  • the accumulator 13 is provided on the suction side of the compressor 10 and stores excess refrigerant due to a difference in operation state between the heating only operation mode and the cooling only operation mode, and excess refrigerant with respect to a transient change in operation. .
  • the first switchgear 30a causes a high-temperature refrigerant to flow from the first gas bypass pipe 5 into the heat source side heat exchanger 12a. It is.
  • the first opening / closing device 30b allows a high-temperature refrigerant to flow into the heat source side heat exchanger 12b from the first gas bypass pipe 5. It is.
  • the first opening / closing device 30a and the first opening / closing device 30b may be configured to be capable of opening and closing the refrigerant flow path, such as a two-way valve, an electromagnetic valve, and an electronic expansion valve.
  • the first opening / closing device 30a and the first opening / closing device 30b may be collectively referred to as the first opening / closing device 30.
  • the third opening / closing device 31a is a low-temperature two-phase flow that flows into the outdoor unit 1 from the indoor unit 2 through the refrigerant main pipe 4. The flow path of the refrigerant is blocked so that the refrigerant does not flow into the heat source side heat exchanger 12a.
  • the third opening / closing device 31b is a low-temperature two-phase flow that flows into the outdoor unit 1 from the indoor unit 2 through the refrigerant main pipe 4. The refrigerant flow path is blocked so that the refrigerant does not flow into the heat source side heat exchanger 12b.
  • the third opening / closing device 31a and the third opening / closing device 31b may be configured to be capable of opening and closing the refrigerant flow path, such as a two-way valve, an electromagnetic valve, and an electronic expansion valve.
  • the third opening / closing device 31a and the third opening / closing device 31b may be collectively referred to as the third opening / closing device 31.
  • the flow rate adjusting device 32a and the flow rate adjusting device 32b are throttle devices that can change the opening degree (opening area) in order to adjust the pressure in the heat source side heat exchanger 12 serving as a condenser.
  • the flow rate adjusting device 32a and the flow rate adjusting device 32b may be configured by, for example, an electronic expansion valve that is driven by a stepping motor, or a device that can change the opening area by arranging a plurality of small electromagnetic valves in parallel.
  • the flow rate adjusting device 32a and the flow rate adjusting device 32b may be collectively referred to as the flow rate adjusting device 32.
  • the second opening / closing device 35 allows a part of the high-temperature / high-pressure gas refrigerant discharged from the compressor 10 to flow into the accumulator 13 during the defrosting operation mode.
  • the second opening / closing device 35 may be constituted by a device capable of opening and closing the refrigerant flow path, such as a two-way valve, a solenoid valve, or an electronic expansion valve.
  • the outdoor unit 1 is provided with a first pressure sensor 41 and a second pressure sensor 42 as pressure detection means.
  • the first pressure sensor 41 is provided in the refrigerant pipe 3 between the compressor 10 and the refrigerant flow switching device 11.
  • the first pressure sensor 41 detects the pressure of the high-temperature and high-pressure refrigerant discharged from the compressor 10.
  • the second pressure sensor 42 is provided in the refrigerant pipe 3 between the refrigerant flow switching device 11 and the accumulator 13.
  • the second pressure sensor 42 detects the pressure of the low-pressure refrigerant sucked into the compressor 10.
  • the outdoor unit 1 is provided with a first temperature sensor 43, a second temperature sensor 45, a third temperature sensor 48a, and a third temperature sensor 48b as temperature detection means.
  • the first temperature sensor 43, the second temperature sensor 45, the third temperature sensor 48a, and the third temperature sensor 48b may be configured by a thermistor, for example.
  • the first temperature sensor 43 is provided in the refrigerant pipe 3 between the compressor 10 and the refrigerant flow switching device 11.
  • the first temperature sensor 43 measures the temperature of the refrigerant discharged from the compressor 10.
  • the 2nd temperature sensor 45 is provided in the air suction part of either the heat source side heat exchanger 12a or the heat source side heat exchanger 12b.
  • the second temperature sensor 45 measures the air temperature around the outdoor unit 1.
  • the third temperature sensor 48 a is provided in the refrigerant pipe 3 between the heat source side heat exchanger 12 a and the refrigerant flow switching device 11.
  • the third temperature sensor 48a measures the temperature of the refrigerant flowing into the heat source side heat exchanger 12a operating as an evaporator or the refrigerant flowing out of the heat source side heat exchanger 12a operating as a condenser.
  • the third temperature sensor 48 b is provided in the refrigerant pipe 3 between the heat source side heat exchanger 12 b and the refrigerant flow switching device 11.
  • the third temperature sensor 48b measures the temperature of the refrigerant flowing into the heat source side heat exchanger 12b operating as an evaporator or the refrigerant flowing out of the heat source side heat exchanger 12b operating as a condenser.
  • a control device 50 is installed in the outdoor unit 1.
  • the pressure information detected by the first pressure sensor 41 and the second pressure sensor 42 and the temperature information detected by the first temperature sensor 43, the second temperature sensor 45, the third temperature sensor 48a, and the third temperature sensor 48b are: Is input to the control device 50.
  • the load-side heat exchanger 21 is connected to the outdoor unit 1 through the refrigerant main pipe 4, and the refrigerant flows in or out.
  • the load-side heat exchanger 21 performs heat exchange between air and a refrigerant supplied from a blower (not shown) such as a fan, for example.
  • the load-side heat exchanger 21 generates heating air or cooling air to be supplied to the indoor space.
  • the heat exchange medium that exchanges heat with the refrigerant in the load-side heat exchanger 21 is not limited to air, and water, brine, or the like may be used as the heat exchange medium.
  • the load-side throttle device 22 has a function as a pressure reducing valve and an expansion valve, and decompresses and expands the refrigerant.
  • the load side expansion device 22 is provided on the upstream side of the load side heat exchanger 21 in the refrigerant flow during the cooling only operation mode.
  • the load-side throttle device 22 is configured with an opening degree that can be variably controlled.
  • the load-side throttle device 22 may be configured with, for example, an electronic expansion valve.
  • the indoor unit 2 is provided with a fourth temperature sensor 46, a fifth temperature sensor 47, and a sixth temperature sensor 44 as temperature detection means.
  • the 4th temperature sensor 46, the 5th temperature sensor 47, and the 6th temperature sensor 44 are good to comprise a thermistor etc., for example.
  • the fourth temperature sensor 46 is provided in the refrigerant pipe 3 between the load side expansion device 22 and the load side heat exchanger 21.
  • the fourth temperature sensor 46 detects the temperature of the refrigerant flowing into the load side heat exchanger 21 or the refrigerant flowing out of the load side heat exchanger 21.
  • the fifth temperature sensor 47 is provided in the refrigerant pipe 3 between the load side heat exchanger 21 and the refrigerant flow switching device 11 of the outdoor unit 1.
  • the fifth temperature sensor 47 detects the temperature of the refrigerant flowing into the load side heat exchanger 21 or the refrigerant flowing out of the load side heat exchanger 21.
  • the sixth temperature sensor 44 is provided in the air suction portion of the load side heat exchanger 21. The sixth temperature sensor 44 detects the ambient air temperature in the room.
  • Temperature information detected by the fourth temperature sensor 46, the fifth temperature sensor 47, and the sixth temperature sensor 44 is input to the control device 50 installed in the outdoor unit 1.
  • the air conditioner 100 includes the compressor 10, the refrigerant flow switching device 11, the load side heat exchanger 21, the load side expansion device 22, and the heat source side heat exchanger 12a connected in parallel to each other.
  • the heat source side heat exchanger 12b is sequentially connected by piping to form a main circuit in which the refrigerant circulates.
  • a bypass circuit that branches a part of the refrigerant discharged from the compressor 10 and flows into one of the heat source side heat exchangers 12 to be defrosted among the heat source side heat exchanger 12a and the heat source side heat exchanger 12b.
  • FIG. 1 a case where one indoor unit 2 is connected to one outdoor unit 1 through the refrigerant main pipe 4 is shown as an example.
  • the present invention is not limited to this configuration.
  • a plurality of indoor units 2 may be provided, and the plurality of indoor units 2 may be connected to one outdoor unit 1 in parallel.
  • Two or more outdoor units may be connected in parallel.
  • a refrigerant circuit configuration that enables each indoor unit to perform cooling and heating simultaneous selection of cooling and heating is possible. It may be adopted.
  • the air conditioner 100 has a control device 50 composed of a microcomputer.
  • the control device 50 switches the driving frequency of the compressor 10, the rotational speed of the blower (including ON / OFF), the switching of the refrigerant flow switching device 11, based on detection information from various detection means and instructions from the remote controller, Controlling the opening / closing of the opening / closing device 30a, the first opening / closing device 30b, the opening / closing of the third opening / closing device 31, the opening of the load-side throttle device 22, and the like, execute each operation mode to be described later.
  • control device 50 may be provided for each unit or may be provided in the indoor unit 2.
  • control devices 50 may be connected to each other by a wired or wireless connection so that information can be exchanged.
  • each operation mode executed by the air conditioner 100 will be described. Below, each operation mode is demonstrated with the flow of a refrigerant
  • FIG. 3 is a refrigerant circuit diagram illustrating a refrigerant flow when the air-conditioning apparatus 100 is in the cooling only operation mode. Based on FIG. 3, the cooling only operation mode which the air conditioning apparatus 100 performs is demonstrated. In FIG. 3, the cooling only operation mode will be described by taking as an example a case where a cooling load is generated in the load-side heat exchanger 21. In FIG. 3, the flow direction of the refrigerant is indicated by solid arrows.
  • the refrigerant flow switching device 11 is switched to the state shown by the solid line in FIG.
  • the first opening / closing device 30a, the first opening / closing device 30b, and the second opening / closing device 35 are each switched to a closed state and block the refrigerant.
  • the third opening / closing device 31a, the third opening / closing device 31b, the flow rate adjusting device 32a, and the flow rate adjusting device 32b are each switched to the open state and allow the refrigerant to pass therethrough.
  • the low-temperature and low-pressure refrigerant When the compressor 10 is driven, the low-temperature and low-pressure refrigerant is compressed and discharged as a high-temperature and high-pressure gas refrigerant.
  • the high-temperature and high-pressure gas refrigerant discharged from the compressor 10 flows into the heat source side heat exchanger 12a and the heat source side heat exchanger 12b via the refrigerant flow switching device 11.
  • the high-temperature and high-pressure gas refrigerant that has flowed into the heat-source-side heat exchanger 12a and the heat-source-side heat exchanger 12b is radiated to the outdoor air in each of the heat-source-side heat exchanger 12a and the heat-source-side heat exchanger 12b, and is a high-pressure liquid refrigerant. It becomes.
  • the high-pressure liquid refrigerant that has flowed out of the heat source side heat exchanger 12a and the heat source side heat exchanger 12b merges through the flow rate adjustment device 32a and the flow rate adjustment device 32b, respectively, and flows out of the outdoor unit 1.
  • the high-pressure liquid refrigerant that has flowed out of the outdoor unit 1 flows into the indoor unit 2 through the refrigerant main pipe 4 and is expanded by the load-side expansion device 22 to become a low-temperature / low-pressure two-phase refrigerant.
  • the two-phase refrigerant flows into the load-side heat exchanger 21 that operates as an evaporator and absorbs heat from the room air, thereby cooling the room air and becoming a low-temperature and low-pressure gas refrigerant.
  • the gas refrigerant that has flowed out of the load-side heat exchanger 21 flows into the outdoor unit 1 again through the refrigerant main pipe 4.
  • the refrigerant flowing into the outdoor unit 1 passes through the refrigerant flow switching device 11 and the accumulator 13 and is sucked into the compressor 10 again.
  • the control device 50 loads the throttle device on the load side so that the superheat (superheat degree) obtained as the difference between the temperature detected by the fourth temperature sensor 46 and the temperature detected by the fifth temperature sensor 47 is constant. 22 is controlled.
  • FIG. 4 is a refrigerant circuit diagram illustrating a refrigerant flow when the air-conditioning apparatus 100 is in the heating only operation mode. Based on FIG. 4, the heating only operation mode which the air conditioning apparatus 100 performs is demonstrated. In FIG. 4, the heating only operation mode will be described by taking as an example a case where a thermal load is generated in the load-side heat exchanger 21. In FIG. 4, the flow direction of the refrigerant is indicated by solid line arrows.
  • the refrigerant flow switching device 11 is switched to the state shown by the solid line in FIG.
  • the first opening / closing device 30a, the first opening / closing device 30b, and the second opening / closing device 35 are each switched to a closed state and block the refrigerant.
  • the third opening / closing device 31a, the third opening / closing device 31b, the flow rate adjusting device 32a, and the flow rate adjusting device 32b are each switched to the open state and allow the refrigerant to pass therethrough.
  • the compressor 10 When the compressor 10 is driven, the low-temperature and low-pressure refrigerant is compressed and discharged as a high-temperature and high-pressure gas refrigerant.
  • the high-temperature and high-pressure gas refrigerant discharged from the compressor 10 flows out of the outdoor unit 1 through the refrigerant flow switching device 11.
  • the high-temperature and high-pressure gas refrigerant that has flowed out of the outdoor unit 1 flows into the indoor unit 2 through the refrigerant main pipe 4, and dissipates heat to the indoor air in the load-side heat exchanger 21, thereby heating the indoor air. It becomes a liquid refrigerant.
  • the liquid refrigerant that has flowed out of the load-side heat exchanger 21 is expanded by the load-side expansion device 22, becomes a low-temperature / medium-pressure two-phase refrigerant or liquid refrigerant, and flows into the outdoor unit 1 again through the refrigerant main pipe 4.
  • the low-temperature / medium-pressure two-phase refrigerant or liquid refrigerant flowing into the outdoor unit 1 flows into the heat source side heat exchanger 12a and the heat source side heat exchanger 12b via the flow rate adjustment device 32a and the flow rate adjustment device 32b, respectively.
  • the refrigerant that has flowed into the heat source side heat exchanger 12a and the heat source side heat exchanger 12b absorbs heat from the outdoor air and becomes a low-temperature / low-pressure gas refrigerant, and the compressor 10 passes through the refrigerant flow switching device 11 and the accumulator 13. Inhaled again.
  • the control device 50 has a constant subcool (degree of subcooling) obtained as a difference between a value obtained by converting the pressure detected by the first pressure sensor 41 into a saturation temperature and a temperature detected by the fourth temperature sensor 46. Thus, the opening degree of the load side expansion device 22 is controlled.
  • the detection results of the third temperature sensor 48a and the third temperature sensor 48b provided on the respective outlet sides of the heat source side heat exchanger 12a and the heat source side heat exchanger 12b are equal to or less than a predetermined value.
  • the control device 50 performs the heating only operation mode, and when the detection results of the third temperature sensor 48a and the third temperature sensor 48b are below a predetermined value (for example, about ⁇ 10 ° C. or less), the heat source side heat exchanger 12a, it is determined that a predetermined amount of frost has been generated on the fins of the heat source side heat exchanger 12b, and the defrosting operation mode is performed.
  • frost formation determination for example, when the saturation temperature converted from the suction pressure of the compressor 10 is significantly lower than the preset outside air temperature, or the temperature difference between the outside air temperature and the evaporation temperature is It may be carried out by a method such as when a predetermined time has passed after a predetermined value or more.
  • the heat source side heat exchanger 12b located on the lower side is defrosted, and then the heat source side heat exchanger 12a located on the upper side is defrosted.
  • the heat source side heat exchanger 12a and the heat source side heat exchanger 12b the heat source side heat exchanger 12 that is not to be defrosted is operated as an evaporator, and the load side heat exchanger 21 of the indoor unit 2 is operated as a condenser. Let the heating operation continue.
  • FIG. 5 is a refrigerant circuit diagram illustrating the flow of the refrigerant when the defrosting of the heat source side heat exchanger 12b is performed in the defrosting operation mode of the air-conditioning apparatus 100.
  • the flow direction of the refrigerant is indicated by solid line arrows.
  • the refrigerant flow switching device 11 In the defrosting operation mode, the refrigerant flow switching device 11 is maintained in the state shown by the solid line in FIG.
  • the states of the first opening / closing device 30, the second opening / closing device 35, the third opening / closing device 31, and the flow rate adjusting device 32 when the heat source side heat exchanger 12b is to be defrosted are as follows. Street. Both are controlled by the control device 50.
  • the first opening / closing device 30b is switched to the open state and allows the refrigerant to pass therethrough.
  • the third opening / closing device 31b is switched to the closed state and blocks the refrigerant.
  • the first opening / closing device 30a is maintained in a closed state and blocks the refrigerant.
  • the third opening / closing device 31a is maintained in the open state and allows the refrigerant to pass therethrough.
  • the flow rate adjusting device 32a is set to a fully open state and allows the refrigerant to pass therethrough.
  • the flow rate adjusting device 32b has a preset pressure at which the saturation pressure of the two-phase refrigerant calculated from the detection result of the third temperature sensor 48b is greater than 0 ° C. in terms of saturation temperature (for example, about 0.8 MPa for R410A refrigerant).
  • the opening is controlled so that is constant.
  • the second opening / closing device 35 or the compressor 10 detected by the second pressure sensor 42 is used.
  • a first predetermined value for example, about 0.3 MPa or less with R410A refrigerant
  • the amount of refrigerant circulating in the main circuit may be regarded as insufficient.
  • FIG. 6 is a diagram showing a change in enthalpy difference that can be used for defrosting due to a saturation temperature change in the heat source side heat exchanger 12 that is a defrost target heat exchanger of the air conditioner 100.
  • the horizontal axis indicates the saturation temperature in the heat source side heat exchanger 12 that is the defrost target heat exchanger
  • the left side of the vertical axis indicates the average refrigerant density (kg / kg) in the heat source side heat exchanger 12 that is the defrost target heat exchanger.
  • the continuous line of FIG. 6 has shown the required average refrigerant
  • the enthalpy difference which can be used for the defrosting by the saturation temperature change in the vessel 12 is shown.
  • the enthalpy difference that can be used for defrosting increases in the vicinity of about 1 ° C. where the saturation temperature in the heat source side heat exchanger 12 that is the defrost target heat exchanger is greater than 0 ° C. It becomes clear that the latent heat of the part can be used more effectively, and the required average refrigerant density in the heat source side heat exchanger 12 at that time is about 600 (kg / m 3 ) or more.
  • the load side heat used as a condenser for heating operation moves into the heat source side heat exchanger 12. Therefore, the amount of refrigerant in the load-side heat exchanger 21 decreases, so that the pressure (high pressure) in the load-side heat exchanger 21 decreases, and the low pressure also decreases due to the decrease in the amount of gas refrigerant in the entire cycle.
  • the load-side heat exchanger 21 is used as a condenser, it is necessary to supply indoor air at a temperature that does not give the user unpleasant feeling due to cold air.
  • a predetermined temperature difference (for example, 10 ° C. or more) is required between the room temperature and the saturation temperature at the pressure in the load-side heat exchanger 21.
  • a predetermined temperature difference for example, 10 ° C. or more
  • JIS-B8616 which is a standard for performance tests of packaged air conditioners
  • the pressure in the load-side heat exchanger 21 The saturation temperature is required to be 30 ° C. or higher. Therefore, in the defrosting operation mode, the pressure on the low-pressure side in the situation where the saturation temperature in the pressure in the load-side heat exchanger 21 can be secured at 30 ° C. or more is about the first predetermined value of about 0.3 MPa. It becomes.
  • the low pressure side pressure is in an operating state below about 0.3 MPa. Therefore, in order to store the refrigerant in the heat source side heat exchanger 12 while suppressing a decrease in the pressure on the low pressure side, it is necessary to supply a refrigerant that is not used in the heating operation and the defrosting operation.
  • the low-temperature and low-pressure refrigerant is compressed and discharged as a high-temperature and high-pressure gas refrigerant.
  • a part of the high-temperature and high-pressure gas refrigerant discharged from the compressor 10 flows through the first gas bypass pipe 5 and is depressurized by the first switchgear 30b so as to become higher than 0 ° C. in terms of saturation temperature, and the medium pressure -It becomes a high-temperature gas refrigerant and flows into the heat source side heat exchanger 12b.
  • the medium-pressure / high-temperature gas refrigerant flowing into the heat source side heat exchanger 12b is a two-phase refrigerant having a low intermediate pressure while melting frost adhering to the heat source side heat exchanger 12b, or an intermediate pressure liquid refrigerant. And passes through the flow rate adjusting device 32b.
  • the refrigerant that has passed through the flow rate adjusting device 32b joins the two-phase refrigerant or liquid refrigerant having a low intermediate pressure and low temperature that has flowed into the outdoor unit 1 from the indoor unit 2 and upstream of the flow rate adjusting device 32a.
  • the liquid refrigerant that has flowed out of the load-side heat exchanger 21 is expanded by the load-side expansion device 22, becomes a low-temperature / medium-pressure two-phase refrigerant or liquid refrigerant, and flows into the outdoor unit 1 again through the refrigerant main pipe 4.
  • the low-temperature / medium-pressure two-phase refrigerant or liquid refrigerant that has flowed into the outdoor unit 1 merges with the refrigerant from the flow rate adjusting device 32b upstream of the flow rate adjusting device 32a, and flows into the heat source side heat exchanger 12a.
  • the refrigerant flowing into the heat source side heat exchanger 12a absorbs heat from the outdoor air and becomes a low-temperature and low-pressure gas refrigerant.
  • the gas refrigerant that has flowed out of the heat source side heat exchanger 12a is again sucked into the compressor 10 via the refrigerant flow switching device 11 and the accumulator 13.
  • the control device 50 has a preset pressure at which the saturation pressure of the two-phase refrigerant calculated from the detection result of the third temperature sensor 48b is greater than 0 ° C. in terms of the saturation temperature (for example, about 0.8 MPa for the R410A refrigerant).
  • the opening degree of the flow rate adjusting device 32b is controlled so as to be constant. That is, the control device 50 has a saturation pressure of the two-phase refrigerant calculated from the detection result of the third temperature sensor 48b greater than a pressure (for example, about 0.8 MPa for the R410A refrigerant) that is greater than 0 ° C. in terms of saturation temperature. In this manner, the opening degree of the flow rate adjusting device 32b is controlled.
  • Completion of defrosting of the heat source side heat exchanger 12b is determined, for example, that the frost has melted when a predetermined time elapses or when the temperature of the third temperature sensor 48b becomes a predetermined value or higher (for example, 5 ° C.). do it. It is assumed that the predetermined time is set to be equal to or longer than the time required until all of the frost is melted, assuming that the entire heat source side heat exchanger 12b has been frosted without any gap and injecting a part of the high-temperature / high-pressure refrigerant. Good.
  • the high-temperature / high-pressure gas refrigerant branched from the discharge side of the compressor 10 flows through the second gas bypass pipe 7, and the second
  • the low-temperature and low-pressure gas refrigerant that has flowed out of the heat source side heat exchanger 12 a is joined via the switchgear 35 and flows into the accumulator 13.
  • the refrigerant that has flowed into the accumulator 13 evaporates the liquid refrigerant that remains in the accumulator 13. Therefore, the amount of the gas refrigerant flowing out from the accumulator 13 can be increased, and the density of the low-pressure gas refrigerant can be increased. Therefore, the pressure of the low-pressure gas refrigerant increases, and the pressure of the low-pressure gas refrigerant can be maintained in a state higher than the first predetermined value (for example, about 0.3 MPa for the R410A refrigerant).
  • the pressure of the low-pressure gas refrigerant is equal to or lower than a first predetermined value (for example, about 0.3 MPa or less for the R410A refrigerant)
  • a first predetermined value for example, about 0.3 MPa or less for the R410A refrigerant
  • the density of the low-pressure gas refrigerant is reduced and the amount of refrigerant discharged from the compressor 10 is reduced.
  • the air conditioner 100 by using the second gas bypass pipe 7, the amount of the gas refrigerant flowing out from the accumulator 13 can be increased and the pressure of the low-pressure gas refrigerant can be increased. Therefore, the fall of the refrigerant
  • the outdoor air temperature detected by the second temperature sensor 45 is equal to or lower than a second predetermined value (for example, 0 ° C. or lower)
  • the outdoor air temperature decreases and the influence of frost formation
  • coolant pressure in the heat source side heat exchanger 12a currently used as an evaporator falls. Therefore, the refrigerant temperature in the heat source side heat exchanger 12a reaches about ⁇ 27 ° C.
  • saturated pressure is about 0.3 MPa
  • the pressure of the low-pressure gas refrigerant in the suction portion of the compressor 10 is There is a possibility of reaching a predetermined value of 1 (for example, about 0.3 MPa with R410A refrigerant). Therefore, even when the outdoor air temperature is equal to or lower than the second predetermined value (for example, 0 ° C. or lower), the controller 50 maintains the second opening / closing device 35 in the open state, thereby discharging the compressor 10 from the compressor 10. Since the fall of the refrigerant
  • the compressor 10 sucks the gas refrigerant having a higher density than before the second opening / closing device 35 is opened. Therefore, the circulation amount of the refrigerant discharged from the compressor 10 can be increased.
  • the alphabet a in the description of the defrosting operation of the heat source side heat exchanger 12b is used. It becomes the operation
  • the saturation temperature of the refrigerant in the heat source side heat exchanger 12 serving as a condenser is set to a medium pressure (for example, higher than 0 ° C., which is higher than the frost temperature).
  • R410A refrigerant is about 0.8 MPa or more).
  • the air conditioning apparatus 100 can defrost the heat source side heat exchanger 12a and the heat source side heat exchanger 12b while continuing the heating operation. Moreover, the defrost of the heat source side heat exchanger 12b located in the lower side of the housing
  • FIG. 7 shows a change in the heating capacity with respect to the saturation temperature in the heat source side heat exchanger 12 which is a defrost target heat exchanger.
  • FIG. 8 is a flowchart showing a control operation when operating the second opening / closing device 35 when the air-conditioning apparatus 100 is in the defrosting operation mode.
  • operation movement of the control apparatus 50 at the time of operating the 2nd opening / closing apparatus 35 at the time of a defrost operation mode is demonstrated.
  • CT1 When the detection result of the third temperature sensor 48a and the third temperature sensor 48b is equal to or lower than a predetermined value (for example, about ⁇ 10 ° C. or lower) in the heating operation mode, the control device 50 performs heat source side heat exchanger 12a and heat source side heat exchange. It determines with the predetermined amount of frost having generate
  • a predetermined value for example, about ⁇ 10 ° C. or lower
  • CT2 The control device 50 determines whether or not the outdoor air temperature detected by the second temperature sensor 45 is equal to or higher than a predetermined value (for example, 0 ° C.). This predetermined value corresponds to the second predetermined value. If the value detected by the second temperature sensor 45 is greater than or equal to the predetermined value, the process proceeds to CT3. If the value detected by the second temperature sensor 45 is not equal to or greater than the predetermined value, the process proceeds to CT4.
  • a predetermined value for example, 0 ° C.
  • CT3 The control device 50 determines whether or not the pressure substantially equal to the refrigerant pressure in the suction portion of the compressor 10 detected by the second pressure sensor 42 is equal to or higher than a predetermined value (for example, 0.3 MPa or higher for the R410A refrigerant). To do. This predetermined value corresponds to the first predetermined value. If the value detected by the second pressure sensor 42 is greater than or equal to the predetermined value, the process proceeds to CT5. If the value detected by the second pressure sensor 42 is not equal to or greater than the predetermined value, the process proceeds to CT4.
  • a predetermined value for example, 0.3 MPa or higher for the R410A refrigerant
  • CT4 The control device 50 opens the second opening / closing device 35, branches the high-temperature / high-pressure gas refrigerant discharged from the compressor 10, and passes through the second gas bypass pipe 7 and the second opening / closing device 35 to accumulate the accumulator 13. To flow into. As a result, the liquid refrigerant staying in the accumulator 13 is evaporated, the amount of the gas refrigerant flowing out of the accumulator 13 is increased, and the pressure of the low-pressure gas refrigerant can be increased.
  • the control device 50 proceeds to CT6 after opening the second opening / closing device 35.
  • CT5 The control device 50 closes the second opening / closing device 35, branches from the discharge side of the compressor 10, and flows into the accumulator 13 via the second gas bypass pipe 7 and the second opening / closing device 35. Block the refrigerant flow path. After closing the second opening / closing device 35, the control device 50 proceeds to CT6.
  • CT6 The control device 50 determines whether or not the defrosting operation mode has ended. If the defrosting operation mode has not ended, the process proceeds to CT2. When the defrosting operation mode is completed, the process proceeds to CT7.
  • CT7 When the defrosting operation mode is completed, the control device 50 closes the second opening / closing device 35, branches off from the discharge side of the compressor 10, and passes through the second gas bypass pipe 7 and the second opening / closing device 35. Thus, the flow path of the high-temperature and high-pressure gas refrigerant flowing into the accumulator 13 is blocked. The control device 50 shifts to the heating only operation mode after closing the second opening / closing device 35.
  • the pressure substantially equal to the refrigerant pressure in the suction portion of the compressor 10 detected by the second pressure sensor 42 is set to about 0.3 MPa with the R410A refrigerant, but this is not limitative. Is not to be done. That is, a temperature difference of a predetermined value or more (for example, 10 ° C. or more) between the room temperature and the saturation temperature at the pressure in the load-side heat exchanger 21 so as not to give the user an unpleasant feeling due to cold air depending on the operating state. Can be ensured, the first predetermined value may be set smaller than 0.3 MPa.
  • the second pressure sensor 42 is not limited to the pressure sensor, and is provided with a temperature sensor such as a thermistor.
  • the control device 50 calculates the saturation pressure based on the detected value of the temperature sensor, and uses the saturation pressure. You may make it do.
  • the 2nd opening / closing device 35 has shown the example opened according to the detection result of the refrigerant
  • coolant can be supplied to the heat source side heat exchanger 12 used as a defrost object faster, and defrost time can be shortened.
  • the second pressure sensor 42 when the pressure approximately equal to the refrigerant pressure in the suction portion of the compressor 10 detected by the second pressure sensor 42 is equal to or higher than a first predetermined value (for example, 0.3 MPa or higher for the R410A refrigerant), the second Although the opening / closing device 35 is shown as being closed, the present invention is not limited to this.
  • the increase in the pressure of the refrigerant in the suction portion of the compressor 10 in the defrosting operation mode may be predicted in advance by a test or the like, and may be closed after a predetermined time has elapsed.
  • the time for keeping the second opening / closing device 35 open may be different depending on the outside air temperature.
  • the temperature difference between the outside air and the refrigerant in the heat source side heat exchanger 12 is obtained when the heat source side heat exchanger 12 used as an evaporator obtains a heat exchange amount equal to or higher than that in the low outside air during high outside air.
  • the pressure of the refrigerant in the heat source side heat exchanger 12 increases, and the pressure of the refrigerant in the suction portion of the compressor 10 also increases.
  • the circulation amount of the refrigerant in the refrigerant circuit is large, and the second opening / closing device 35 is opened, and the refrigerant remaining in the accumulator 13 is sufficiently defrosted and heated even if the amount of refrigerant supplied into the refrigerant circuit is small. You can drive. Therefore, when the outside air is high, the time for opening the second opening / closing device 35 can be set short.
  • the pressure of the refrigerant in the heat source side heat exchanger 12 decreases, and the pressure of the refrigerant in the suction portion of the compressor 10 also decreases. Therefore, the circulation amount of the refrigerant in the refrigerant circuit is small, and a large amount of the refrigerant staying in the accumulator 13 is required to be supplied into the refrigerant circuit, and the time for opening the second opening / closing device 35 is set long. There is a need. That is, by setting the time for opening the second opening / closing device 35 according to the change in the outside air temperature, the high-temperature and high-pressure gas refrigerant branched from the discharge side of the compressor 10 is wasted, particularly when the outside air is high. Bypassing can be prevented and a decrease in heating capacity can be suppressed.
  • FIG. 9 shows a change in saturation temperature in terms of the pressure in the load-side heat exchanger 21 when the flow rate of the high-temperature and high-pressure gas refrigerant flowing into the accumulator 13 during the defrost mode of the air conditioner 100 is changed.
  • FIG. 9 when the outdoor air temperature is about 0 ° C. and the indoor air temperature is about 20 ° C., the load-side heat exchange when the flow rate of the high-temperature and high-pressure gas refrigerant flowing into the accumulator 13 in the defrosting operation mode is changed.
  • the saturation temperature change which converted the pressure in the vessel 21 is shown. Further, in FIG.
  • gas refrigerant flow ratio A value obtained by dividing all the high-temperature and high-pressure gas refrigerants (hereinafter referred to as gas refrigerant flow ratio), and the vertical axis represents the saturation temperature obtained by converting the pressure in the load-side heat exchanger 21.
  • the size of the second opening / closing device 35 may be a valve having a size that satisfies the gas refrigerant flow rate ratio of less than 0.65.
  • FIG. 10 is a schematic circuit configuration diagram illustrating another example of the circuit configuration of the air-conditioning apparatus 100.
  • the other end of the second gas bypass pipe 7 may be connected to the accumulator 13.
  • the high-temperature / high-pressure gas refrigerant discharged from the compressor 10 is branched and directly flows into the accumulator 13 via the second gas bypass pipe 7 and the second opening / closing device 35. It becomes possible.
  • the high-temperature and high-pressure gas refrigerant branched from the discharge side of the compressor 10 evaporates.
  • the heat energy is reduced by dissipating heat to the low-temperature, low-pressure gas or two-phase refrigerant that has flowed from the heat source side heat exchanger 12 that is a heat exchanger.
  • heat is exchanged only with the liquid surface located above the liquid refrigerant staying in the accumulator 13.
  • heat exchange can be performed efficiently between the gas refrigerant that has flowed into the accumulator 13 and the liquid refrigerant that has accumulated in the accumulator 13. Therefore, the refrigerant staying in the accumulator 13 is defrosted faster than the case where the high-temperature / high-pressure gas refrigerant branched from the discharge side of the compressor 10 is caused to flow into the piping of the inflow portion of the accumulator 13. It becomes possible to supply to a certain heat source side heat exchanger 12, and defrosting can be performed more quickly. Therefore, the indoor heating capacity can be further prevented from being lowered, and the room can be kept comfortable.
  • FIG. FIG. 11 is a schematic circuit configuration diagram showing an example of a circuit configuration of the air-conditioning apparatus 200 according to Embodiment 2 of the present invention. Based on FIG. 11, the detailed structure of the air conditioning apparatus 200 is demonstrated. In the second embodiment, differences from the first embodiment will be mainly described, and the same parts as those in the first embodiment will be denoted by the same reference numerals and description thereof will be omitted. Moreover, in FIG. 11, the flow direction of the refrigerant
  • a fourth opening / closing device 33 a that newly blocks the refrigerant flow path of the heat source side heat exchanger 12 a to the pipe on the load side expansion device 22 side of the heat source side heat exchanger 12 a.
  • a fourth opening / closing device 33b that blocks the refrigerant flow path of the heat source side heat exchanger 12b is installed in the piping on the load side expansion device 22 side of the heat source side heat exchanger 12b.
  • the refrigerant bypass pipe 6 is installed. One end of the refrigerant bypass pipe 6 is connected to the refrigerant pipe 3 between each of the heat source side heat exchanger 12a and the heat source side heat exchanger 12b and each of the third switchgear 31a and the third switchgear 31b. . The other end of the refrigerant bypass pipe 6 is connected to a flow path between each of the fourth opening / closing device 33 a and the fourth opening / closing device 33 b and the load side expansion device 22.
  • the refrigerant bypass pipe 6 allows the refrigerant in the heat source side heat exchanger 12 serving as a condenser to flow into the refrigerant pipe 3 in the defrosting operation mode.
  • the fifth switching device 34a and the fifth switching device 34b for switching the refrigerant flow path of the refrigerant bypass pipe 6 are connected between the heat source side heat exchanger 12 and the third switching device 31 each corresponding to one end.
  • the refrigerant bypass pipe 6 is installed.
  • the flow rate adjusting device 32b (or the flow rate), which is a throttle device whose opening degree (opening area) is changed to adjust the pressure of the refrigerant in the heat source side heat exchanger 12 to the other end side of the refrigerant bypass pipe 6.
  • One of the adjusting devices 32a) is installed.
  • the fourth opening / closing device 33a is a low-temperature two-phase flow that flows into the outdoor unit 1 from the indoor unit 2 through the refrigerant main pipe 4 when the heat source side heat exchanger 12a operates as a condenser during the defrosting operation mode. The flow path of the refrigerant is blocked so that the refrigerant does not flow into the heat source side heat exchanger 12a.
  • the fourth switchgear 33b is a low-temperature two-phase flow that flows from the indoor unit 2 into the outdoor unit 1 through the refrigerant main pipe 4 when the heat source side heat exchanger 12b operates as a condenser during the defrosting operation mode. The refrigerant flow path is blocked so that the refrigerant does not flow into the heat source side heat exchanger 12b.
  • the fourth opening / closing device 33a and the fourth opening / closing device 33b may be configured to be capable of opening / closing a refrigerant flow path, such as a two-way valve, an electromagnetic valve, or an electronic expansion valve.
  • a refrigerant flow path such as a two-way valve, an electromagnetic valve, or an electronic expansion valve.
  • the fourth switchgear 33a and the fourth switchgear 33b may be collectively referred to as the fourth switchgear 33.
  • the fifth opening / closing device 34a removes the refrigerant flowing out of the heat source side heat exchanger 12a from the flow rate adjusting device 32b (or the flow rate adjusting device). It is made to flow into the refrigerant pipe 3 via 32a).
  • the fifth opening / closing device 34b removes the refrigerant flowing out of the heat source side heat exchanger 12a from the flow rate adjustment device 32b (or the flow rate adjustment device). It is made to flow into the refrigerant pipe 3 via 32a).
  • the fifth opening / closing device 34a and the fifth opening / closing device 34b may be configured to be capable of opening and closing a refrigerant flow path, such as a two-way valve, an electromagnetic valve, and an electronic expansion valve.
  • a refrigerant flow path such as a two-way valve, an electromagnetic valve, and an electronic expansion valve.
  • the fifth opening / closing device 34a and the fifth opening / closing device 34b may be collectively referred to as the fifth opening / closing device 34.
  • the other end of the first gas bypass pipe 5 branched into two branches is connected to the refrigerant pipe 3 between the heat source side heat exchanger 12a and the fourth switchgear 33a, and the other is connected to the heat source side heat exchanger. It connects to the refrigerant
  • the 3rd temperature sensor 48a is provided in the refrigerant
  • the 3rd temperature sensor 48b is the heat source side heat exchanger 12b and 3rd. It is provided in the refrigerant pipe 3 between the switchgear 31b.
  • the third temperature sensor 48a measures the temperature of the refrigerant flowing out from the heat source side heat exchanger 12a operating as an evaporator or the refrigerant flowing out from the heat source side heat exchanger 12a operating as a condenser.
  • the third temperature sensor 48b measures the temperature of the refrigerant flowing in from the heat source side heat exchanger 12b operating as an evaporator or the refrigerant flowing out of the heat source side heat exchanger 12b operating as a condenser.
  • the fourth opening / closing device 33a and the fourth opening / closing device 33b are open, and the fifth opening / closing device 34a and the fifth opening / closing device 34b are closed. Since the other operations of the switchgear and the flow of the refrigerant are the same as those of the air conditioner 100 according to Embodiment 1, the description thereof is omitted.
  • the refrigerant flow switching device 11 In the defrosting operation mode, the refrigerant flow switching device 11 is maintained in the state indicated by the solid line in FIG. Further, in the defrosting operation mode, the first opening / closing device 30, the second opening / closing device 35, the third opening / closing device 31, the fourth opening / closing device 33, and the fifth opening / closing device when the heat source side heat exchanger 12b is to be defrosted. 34 and the state of the flow rate adjusting device 32 are as follows. Both are controlled by the control device 50.
  • the first opening / closing device 30b is switched to the open state and allows the refrigerant to pass therethrough.
  • the third opening / closing device 31b is switched to the closed state and blocks the refrigerant.
  • the fourth opening / closing device 33b is switched to the closed state and blocks the refrigerant.
  • the fifth opening / closing device 34b is switched to the open state and allows the refrigerant to pass therethrough.
  • the first opening / closing device 30a is maintained in a closed state and blocks the refrigerant.
  • the third opening / closing device 31a is maintained in the open state and allows the refrigerant to pass therethrough.
  • the fourth opening / closing device 33a is switched to the open state and allows the refrigerant to pass therethrough.
  • the fifth opening / closing device 34a is switched to the closed state and blocks the refrigerant.
  • the flow rate adjusting device 32b (or the flow rate adjusting device 32a) is configured such that the saturation pressure of the two-phase refrigerant calculated from the detection result of the third temperature sensor 48b, which is the “defrosting refrigerant amount decrease detecting means”, is 0 ° C. in terms of saturation temperature.
  • the opening degree is controlled such that a preset pressure (for example, about 0.8 MPa for the R410A refrigerant) that becomes larger is constant.
  • the second opening / closing device 35 or the compressor 10 detected by the second pressure sensor 42 is used.
  • a first predetermined value for example, about 0.3 MPa or less with R410A refrigerant
  • the open state is maintained and the refrigerant passes.
  • the low-temperature and low-pressure refrigerant is compressed and discharged as a high-temperature and high-pressure gas refrigerant.
  • a part of the high-temperature and high-pressure gas refrigerant discharged from the compressor 10 flows through the first gas bypass pipe 5 and is depressurized by the first switchgear 30b so as to become higher than 0 ° C. in terms of saturation temperature, and the medium pressure -It becomes a high-temperature gas refrigerant and flows into the heat source side heat exchanger 12b.
  • the medium-pressure and high-temperature gas refrigerant that has flowed into the heat source side heat exchanger 12b becomes a two-phase refrigerant having a low intermediate pressure or a medium pressure refrigerant while melting frost adhering to the heat source side heat exchanger 12b. And passes through the fifth opening / closing device 34b.
  • the refrigerant that has passed through the fifth opening / closing device 34b is depressurized by the flow rate adjusting device 32b (or the flow rate adjusting device 32a) and flows into the outdoor unit 1 from the indoor unit 2 into the outdoor unit 1 or a low-drying two-phase refrigerant having a low intermediate pressure or low temperature, or The liquid refrigerant merges on the upstream side of the fourth opening / closing device 33a.
  • the high-temperature and high-pressure gas refrigerant discharged from the compressor 10 flows out of the outdoor unit 1 through the refrigerant flow switching device 11.
  • the high-temperature and high-pressure gas refrigerant that has flowed out of the outdoor unit 1 flows into the indoor unit 2 through the refrigerant main pipe 4, and dissipates heat to the indoor air in the load-side heat exchanger 21, thereby heating the indoor air. It becomes a liquid refrigerant.
  • the liquid refrigerant that has flowed out of the load-side heat exchanger 21 is expanded by the load-side expansion device 22, becomes a low-temperature / medium-pressure two-phase refrigerant or liquid refrigerant, and flows into the outdoor unit 1 again through the refrigerant main pipe 4.
  • the low-temperature / medium-pressure two-phase refrigerant or liquid refrigerant flowing into the outdoor unit 1 merges with the refrigerant from the flow rate adjusting device 32b (or the flow rate adjusting device 32a) upstream of the fourth opening / closing device 33a to perform heat source side heat exchange.
  • the refrigerant flowing into the heat source side heat exchanger 12a absorbs heat from the outdoor air and becomes a low-temperature and low-pressure gas refrigerant.
  • the gas refrigerant that has flowed out of the heat source side heat exchanger 12a is again sucked into the compressor 10 via the third opening / closing device 31a, the refrigerant flow switching device 11, and the accumulator 13.
  • the control device 50 has a preset pressure at which the saturation pressure of the two-phase refrigerant calculated from the detection result of the third temperature sensor 48b is greater than 0 ° C. in terms of the saturation temperature (for example, about 0.8 MPa for the R410A refrigerant).
  • the opening degree of the flow rate adjusting device 32b (or the flow rate adjusting device 32a) is controlled so as to be constant. That is, the controller 50 adjusts the flow rate adjusting device 32b (or the flow rate adjusting device 32a) so that the saturation pressure of the two-phase refrigerant calculated from the detection result of the third temperature sensor 48b is greater than 0 ° C. in terms of saturation temperature. ) Is controlled.
  • Completion of defrosting of the heat source side heat exchanger 12b is determined, for example, that the frost has melted when a predetermined time elapses or when the temperature of the third temperature sensor 48b becomes a predetermined value or higher (for example, 5 ° C.). do it. It is assumed that the predetermined time is set to be equal to or longer than the time required until all of the frost is melted, assuming that the entire heat source side heat exchanger 12b has been frosted without any gap and injecting a part of the high-temperature / high-pressure refrigerant. Good.
  • control device 50 when operating the second opening / closing device 35 is also the same as that of the air conditioner 100 according to the first embodiment, and is therefore omitted.
  • the heat source side heat exchanger 12b when configured by two rows of heat exchangers and used as an evaporator, the heat source side heat exchanger 12b is positioned in the first row on the outdoor air inlet side of the heat source side heat exchanger 12b. Most of the outdoor air is dehumidified by the fins located in the first row, which is the side flowing into the heat source side heat exchanger 12b. That is, the frost formation amount of the fins located in the first row on the side flowing into the heat source side heat exchanger 12b is large, and the frost formation amount of the fins located in the second row is small.
  • the alphabet a in the description of the defrosting operation of the heat source side heat exchanger 12b is used. It becomes the operation
  • the open / close state is reversed, and the refrigerant flows in the heat source side heat exchanger 12a and the heat source side heat exchanger 12b are switched.
  • the saturation temperature of the refrigerant in the heat source side heat exchanger 12 serving as a condenser is set to a medium pressure (for example, higher than 0 ° C., which is higher than the frost temperature).
  • R410A refrigerant is about 0.8 MPa or more).
  • the air conditioning apparatus 200 can defrost the heat source side heat exchanger 12a and the heat source side heat exchanger 12b while continuing the heating operation. Moreover, the defrost of the heat source side heat exchanger 12b located in the lower side of the housing
  • the high-temperature / high-pressure gas refrigerant branched from the discharge side of the compressor 10 is caused to flow into the piping of the inflow portion of the accumulator 13.
  • the high-temperature / high-pressure gas refrigerant branched from the discharge side of the compressor 10 is supplied to the second gas bypass pipe 7 and the second opening / closing device 35. Therefore, a circuit configuration that flows directly into the accumulator 13 may be adopted. With such a configuration, it is possible to obtain the same effects as those of the air conditioner 100 according to Embodiment 1, efficiently perform defrosting, suppress a decrease in indoor heating capacity, It becomes possible to keep it comfortable.
  • non-flammable refrigerants such as R410A, R407C, and R22, HFO1234yf, HFO1234ze (E), R32, HC, a refrigerant containing R32 and HFO1234yf, a refrigerant exhibiting slight flammability such as a refrigerant using a refrigerant mixture containing at least one of the aforementioned refrigerants, a highly flammable refrigerant such as propane (R290), CO 2 (R744)
  • a refrigerant that operates supercritically on the high-pressure side such as) can be used as the heat-source-side refrigerant.
  • the air conditioner 100 according to the first embodiment and the flow rate adjusting device 32a and the flow rate adjusting device 32b of the air conditioner 200 according to the second embodiment are the throttle devices that can change the opening degree (opening area), Any device that can change the opening area of the road may be used.
  • the expansion device may be an electronic expansion valve that is driven by a stepping motor, or a plurality of small electromagnetic valves arranged in parallel and switched to change the opening area.
  • the air conditioner 100a which concerns on Embodiment 1 and the flow volume adjustment apparatus 32a of the air conditioning apparatus 200 which concerns on Embodiment 2
  • the flow volume adjustment apparatus 32b are set as the apparatus which can change the opening area of a flow path.
  • the flow rate adjusting device 32a may be a device capable of changing the opening area of the flow path
  • the flow rate adjusting device 32b may be configured by arranging a plurality of small solenoid valves in parallel. The same effect as 2 is obtained.
  • opening each opening / closing device means that each opening / closing device is fully open or close to full opening.
  • To close each opening / closing device means to make each opening / closing device fully closed or close to the fully closed position.
  • To open means to open the flow rate adjustment device to the full open or close to full open, and to close the flow rate adjustment device, to fully close or fully close the flow rate adjustment device.
  • the opening degree is close to 0, that is, the state is such that the refrigerant hardly flows.
  • the heat source side heat exchanger 12a and the heat source side heat exchanger 12b of the air conditioner 100 according to the first embodiment and the air conditioner 200 according to the second embodiment are arranged in the step direction (the fins face the same direction).
  • the heat source side heat exchanger 12 may be configured to have a plurality of units such as three or more in the step direction (vertical direction in which each fin faces the same direction).
  • the arrangement of the plurality of heat source side heat exchangers 12 is not limited to the upper and lower sides, and may be arranged in the left and right direction and the front and rear direction.
  • the air-conditioning apparatus 100 according to Embodiment 1 and the air-conditioning apparatus 200 according to Embodiment 2 have been described using the air-conditioning apparatus capable of switching between cooling and heating operations as an example.
  • the present invention can also be applied to an air conditioner having a possible circuit configuration.
  • a heating circuit refers to the refrigerant circuit structure of the air conditioning apparatus 100 and the air conditioning apparatus 200 formed at the time of heating operation mode.

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

Abstract

L'invention concerne un climatiseur (100) qui comprend : une première tuyauterie de dérivation de gaz (5) qui est ramifiée à partir du côté de décharge d'un compresseur (10), et dans laquelle un réfrigérant s'écoule vers un échangeur de chaleur côté source de chaleur (12) qui doit être dégivré, parmi une pluralité d'échangeurs de chaleur côté source de chaleur (12) ; une seconde tuyauterie de dérivation de gaz (7) qui est ramifiée à partir du côté de décharge du compresseur (10), et dans laquelle un réfrigérant s'écoule vers un accumulateur (13) ; une pluralité de premiers dispositifs d'ouverture et de fermeture (30) qui sont situés dans la première tuyauterie de dérivation de gaz (5) et qui permettent ou bloquent le passage de réfrigérant s'écoulant dans la première tuyauterie de dérivation de gaz (5) ; et au moins un second dispositif d'ouverture et de fermeture (35) qui est situé dans la seconde tuyauterie de dérivation de gaz (7) et qui permet ou bloque le passage de réfrigérant s'écoulant dans la seconde tuyauterie de dérivation de gaz (7).
PCT/JP2013/078779 2013-10-24 2013-10-24 Climatiseur Ceased WO2015059792A1 (fr)

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JP2015543648A JP5992112B2 (ja) 2013-10-24 2013-10-24 空気調和装置
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CN106871381A (zh) * 2017-04-01 2017-06-20 青岛海尔空调器有限总公司 空调器不停机除霜运行方法
CN106940071A (zh) * 2017-03-24 2017-07-11 青岛海尔空调器有限总公司 空调装置及其控制方法
CN107023948A (zh) * 2017-04-01 2017-08-08 青岛海尔空调器有限总公司 空调器及其不停机除霜运行方法
CN107023946A (zh) * 2017-04-01 2017-08-08 青岛海尔空调器有限总公司 空调器不停机除霜运行方法
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CN107560217A (zh) * 2017-09-07 2018-01-09 珠海格力电器股份有限公司 热泵系统及其控制方法
CN110579014A (zh) * 2019-09-03 2019-12-17 青岛海信日立空调系统有限公司 一种换热装置及其控制方法、控制装置
CN110736203A (zh) * 2019-09-25 2020-01-31 青岛海尔空调器有限总公司 用于空调除霜的控制方法、控制装置及空调
JPWO2019003291A1 (ja) * 2017-06-27 2020-03-19 三菱電機株式会社 空気調和装置
JP2021021513A (ja) * 2019-07-25 2021-02-18 株式会社富士通ゼネラル 空気調和装置
JPWO2021090414A1 (fr) * 2019-11-06 2021-05-14
WO2021169542A1 (fr) * 2019-10-23 2021-09-02 珠海格力电器股份有限公司 Système de climatisation pouvant effectuer un chauffage en continu
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US20220299247A1 (en) * 2019-11-12 2022-09-22 Mitsubishi Electric Corporation Refrigeration cycle apparatus
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CN116772287A (zh) * 2023-05-16 2023-09-19 海信（广东）空调有限公司 一种空调器及空调器的除霜控制方法
WO2024218939A1 (fr) * 2023-04-20 2024-10-24 三菱電機株式会社 Climatiseur

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CN106918122B (zh) * 2017-04-01 2020-05-29 青岛海尔空调器有限总公司 空调器不停机除霜运行方法
CN107940876A (zh) * 2017-11-03 2018-04-20 广东美的暖通设备有限公司 空调器及空调器的控制方法
EP4006441B1 (fr) * 2019-07-25 2025-09-10 Mitsubishi Electric Corporation Climatiseur
KR102870664B1 (ko) * 2022-10-25 2025-10-13 현대위아 주식회사 어큐뮬레이터 장치 및 이를 이용한 냉매 순환 시스템

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CN106871381A (zh) * 2017-04-01 2017-06-20 青岛海尔空调器有限总公司 空调器不停机除霜运行方法
CN107084561A (zh) * 2017-06-19 2017-08-22 Tcl空调器(中山)有限公司 空调器及其除霜控制方法
JPWO2019003291A1 (ja) * 2017-06-27 2020-03-19 三菱電機株式会社 空気調和装置
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JP7408942B2 (ja) 2019-07-25 2024-01-09 株式会社富士通ゼネラル 空気調和装置
JP2021021513A (ja) * 2019-07-25 2021-02-18 株式会社富士通ゼネラル 空気調和装置
CN110579014A (zh) * 2019-09-03 2019-12-17 青岛海信日立空调系统有限公司 一种换热装置及其控制方法、控制装置
CN110736203A (zh) * 2019-09-25 2020-01-31 青岛海尔空调器有限总公司 用于空调除霜的控制方法、控制装置及空调
WO2021169542A1 (fr) * 2019-10-23 2021-09-02 珠海格力电器股份有限公司 Système de climatisation pouvant effectuer un chauffage en continu
CN114600341A (zh) * 2019-11-06 2022-06-07 三菱电机株式会社 空调装置
US12092356B2 (en) 2019-11-06 2024-09-17 Mitsubishi Electric Corporation Air-conditioning apparatus
WO2021090414A1 (fr) * 2019-11-06 2021-05-14 三菱電機株式会社 Dispositif de climatisation
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CN115235141B (zh) * 2022-07-14 2023-10-31 黄永年 高效化霜的热泵式小型空调
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EP3062031A1 (fr) 2016-08-31

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