WO2014061133A1 - Climatiseur - Google Patents

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Publication number
WO2014061133A1
WO2014061133A1 PCT/JP2012/076940 JP2012076940W WO2014061133A1 WO 2014061133 A1 WO2014061133 A1 WO 2014061133A1 JP 2012076940 W JP2012076940 W JP 2012076940W WO 2014061133 A1 WO2014061133 A1 WO 2014061133A1
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WO
WIPO (PCT)
Prior art keywords
heat
heat exchanger
outdoor
defrosting
indoor
Prior art date
Application number
PCT/JP2012/076940
Other languages
English (en)
Japanese (ja)
Inventor
雅裕 本田
圭弘 松本
Original Assignee
ダイキン工業株式会社
ダイキン ヨーロッパ エヌ．ヴイ．
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 ダイキン工業株式会社, ダイキン ヨーロッパ エヌ．ヴイ． filed Critical ダイキン工業株式会社
Priority to ES12886542.5T priority Critical patent/ES2683363T3/es
Priority to JP2014541877A priority patent/JP5955400B2/ja
Priority to CN201280076455.0A priority patent/CN104736951B/zh
Priority to EP12886542.5A priority patent/EP2860474B1/fr
Priority to PCT/JP2012/076940 priority patent/WO2014061133A1/fr
Publication of WO2014061133A1 publication Critical patent/WO2014061133A1/fr

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B47/00—Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass
    • F25B47/02—Defrosting cycles
    • F25B47/022—Defrosting cycles hot gas defrosting
    • F25B47/025—Defrosting cycles hot gas defrosting by reversing the cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B47/00—Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass
    • F25B47/02—Defrosting cycles
    • 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
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/021—Indoor unit or outdoor unit with auxiliary heat exchanger not forming part of the indoor or outdoor unit
    • 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
    • F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
    • F25B2313/02742—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using two four-way 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
    • F25B2313/031—Sensor arrangements
    • F25B2313/0314—Temperature sensors near the indoor heat exchanger
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/031—Sensor arrangements
    • F25B2313/0315—Temperature sensors near the outdoor heat exchanger
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/24—Storage receiver heat
    • 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
    • F25B2600/25—Control of valves
    • F25B2600/2507—Flow-diverting 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
    • 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
    • F25B2700/2104—Temperatures of an indoor room or compartment
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2106—Temperatures of fresh outdoor air
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2115—Temperatures of a compressor or the drive means therefor
    • F25B2700/21151—Temperatures of a compressor or the drive means therefor at the suction side of the compressor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2115—Temperatures of a compressor or the drive means therefor
    • F25B2700/21152—Temperatures of a compressor or the drive means therefor at the discharge side of the compressor

Definitions

  • the present invention includes an air conditioner, and in particular, a refrigerant circuit having a heat storage heat exchanger that performs heat exchange between the refrigerant and the heat storage material, and allows the heat storage heat exchanger to function as a refrigerant radiator. It is possible to perform a heat storage operation that stores heat to the heat storage material, and simultaneously perform a heat storage operation and a heating operation that release heat from the heat storage material by causing the heat storage heat exchanger to function as a refrigerant evaporator during defrosting operation.
  • the present invention relates to an air conditioner.
  • Patent Document 1 Japanese Patent Application Laid-Open No. 2005-337657
  • heat storage heat that performs heat exchange between a compressor, an outdoor heat exchanger, an indoor heat exchanger, a refrigerant, and a heat storage material.
  • an air conditioner that includes a refrigerant circuit having an exchanger, performs a heat storage operation, and can simultaneously perform a heat storage use operation and a heating operation during a defrosting operation.
  • the heat storage operation is an operation for storing heat to the heat storage material by causing the heat storage heat exchanger to function as a refrigerant radiator.
  • the defrosting operation is an operation for defrosting the outdoor heat exchanger by causing the outdoor heat exchanger to function as a refrigerant radiator.
  • the heat storage use operation is an operation in which heat is released from the heat storage material by causing the heat storage heat exchanger to function as a refrigerant evaporator.
  • the heating operation is an operation in which the indoor heat exchanger functions as a refrigerant radiator.
  • the defrosting capacity of the outdoor heat exchanger required during the defrosting operation with the heat storage operation is the weather conditions (outdoor temperature, humidity, degree of snowfall) of the area where the air conditioner is installed, etc. It depends on. For the difference in defrosting capacity due to such regional weather conditions, we assume the weather conditions that require the most defrosting capacity during defrosting operation with heat storage operation such as in cold regions. It is conceivable to determine the specifications of the heat storage heat exchanger including the capacity of the heat storage material. However, in such a method of determining the specifications of the heat storage heat exchanger, a large-capacity heat storage material is required, which greatly affects the size, weight, and cost of the heat storage heat exchanger. In addition, when installing the air conditioner in a cold region, the specifications of the air conditioner including the heat storage heat exchanger are appropriate, but when installing in a warm region, the air conditioner including the heat storage heat exchanger The specifications will be excessive.
  • An object of the present invention includes a refrigerant circuit having a heat storage heat exchanger that performs heat exchange between a refrigerant and a heat storage material, performs heat storage operation, and simultaneously performs heat storage use operation and heating operation during defrosting operation.
  • the heat storage heat exchanger having a specific capacity of the heat storage material can be used in a wide range of areas.
  • An air conditioner includes a refrigerant circuit having a compressor, an outdoor heat exchanger, an indoor heat exchanger, and a heat storage heat exchanger that performs heat exchange between the refrigerant and the heat storage material. Therefore, it is possible to perform the heat storage operation and simultaneously perform the heat storage use operation and the heating operation during the defrosting operation.
  • the heat storage operation is an operation for storing heat to the heat storage material by causing the heat storage heat exchanger to function as a refrigerant radiator.
  • the defrosting operation is an operation for defrosting the outdoor heat exchanger by causing the outdoor heat exchanger to function as a refrigerant radiator.
  • the heat storage use operation is an operation in which heat is released from the heat storage material by causing the heat storage heat exchanger to function as a refrigerant evaporator.
  • the heating operation is an operation in which the indoor heat exchanger functions as a refrigerant radiator.
  • the defrosting ability of the outdoor heat exchanger is set to the outdoor temperature of the external space where the outdoor heat exchanger is arranged and / or the previous defrosting. It changes based on the outdoor heat exchanger outlet temperature which is the temperature of the refrigerant at the outlet of the outdoor heat exchanger at the end of the operation or the time required for the previous defrosting operation.
  • the defrosting capacity of the outdoor heat exchanger that needs to be changed according to the weather conditions in the area where the air conditioner is installed, the outdoor temperature and / or the previous time
  • the outdoor heat exchange outlet temperature at the end of the defrosting operation or the time required for the previous defrosting operation is changed.
  • the defrosting capability of the outdoor heat exchanger can be made appropriate according to the weather conditions in the area where the air conditioner is installed.
  • the defrosting capacity of the outdoor heat exchanger is made appropriate according to the weather conditions of the area where the air conditioner is installed, and the heat storage heat exchanger having a specific capacity of the heat storage material can be used in a wide range of areas. Can respond.
  • the air conditioner according to the second aspect is the air conditioner according to the first aspect, wherein the outdoor temperature and / or the outdoor heat exchange outlet at the end of the previous defrost operation in the defrost operation with the heat storage use operation.
  • the heating capacity of the indoor heat exchanger is reduced while simultaneously performing the heating operation. To do.
  • the heating operation When the heating operation is simultaneously performed in the defrosting operation with the heat storage use operation, a part of the defrosting capability of the outdoor heat exchanger is used as the heating capability of the indoor heat exchanger. At this time, there is a possibility that the defrosting capacity of the outdoor heat exchanger will be insufficient if the heating capacity of the indoor heat exchanger is maintained even though it is necessary to increase the defrosting capacity of the outdoor heat exchanger. . Therefore, here, as described above, in the case where the heating operation is simultaneously performed in the defrosting operation with the heat storage use operation, when a change to increase the defrosting capacity of the outdoor heat exchanger is required, the indoor heat exchange is performed. The heater's heating capacity is made small. Thereby, here, in the defrosting operation with the heat storage utilization operation, the defrosting capability of the outdoor heat exchanger can be ensured while continuing the heating operation as much as possible.
  • the air conditioning apparatus when the heating operation is simultaneously performed in the defrosting operation with the heat storage use operation, the outdoor temperature and / or the previous defrosting operation are performed.
  • the interval time between the defrosting operations is changed based on the outdoor heat exchange outlet temperature at the end of the time or the time required for the previous defrosting operation.
  • the interval time between the defrosting operations is set. To change. For example, when the outdoor temperature is low, the outdoor heat exchange outlet temperature at the end of the previous defrost operation is low, or the time required for the previous defrost operation is long, the interval time between defrost operations Change to shorten. Thereby, here, the frequency of a defrost operation can be changed as needed, and the defrost operation accompanied by heat storage utilization operation can be performed favorably.
  • the air conditioner according to the fourth aspect is the air conditioner according to the second or third aspect, wherein the outdoor temperature and / or the outdoor at the end of the previous defrost operation is performed in the defrost operation with the heat storage use operation. If a change to further increase the defrosting capacity of the outdoor heat exchanger based on the heat exchange outlet temperature or the time required for the previous defrosting operation is required, stop supplying the refrigerant to the indoor heat exchanger, Defrost the outdoor heat exchanger. When performing the heating operation simultaneously in the defrosting operation using the heat storage use operation, the outdoor temperature is so low that the defrosting capability of the outdoor heat exchanger cannot be covered only by reducing the heating capability of the indoor heat exchanger.
  • the outdoor heat exchange outlet temperature at the end of the previous defrosting operation may be low, or the time required for the previous defrosting operation may be increased. Therefore, here, as described above, in the defrosting operation with the heat storage use operation, when a change to further increase the defrosting capacity of the outdoor heat exchanger is required, supply of the refrigerant to the indoor heat exchanger The outdoor heat exchanger is defrosted.
  • An air conditioner according to a fifth aspect is the air conditioner according to the fourth aspect, wherein the outdoor temperature and / or the outdoor heat exchange outlet at the end of the previous defrost operation in the defrost operation with the heat storage use operation If a change to further increase the defrosting capacity of the outdoor heat exchanger based on the temperature or the time required for the previous defrosting operation is required, the refrigerant pipe connecting the indoor heat exchanger and the compressor The pipe heat recovery operation for recovering the heat held by the engine and / or the indoor heat exchanger heat recovery operation for recovering the heat obtained by the refrigerant by causing the indoor heat exchanger to function as an evaporator of the refrigerant.
  • the outdoor temperature is so low that the supply of refrigerant to the indoor heat exchanger in the defrosting operation with the heat storage operation (ie, the heating operation is stopped) cannot sufficiently meet the defrosting capacity of the outdoor heat exchanger.
  • the outdoor heat exchange outlet temperature at the end of the previous defrosting operation may be low, or the time required for the previous defrosting operation may be increased.
  • the defrosting capability of the outdoor heat exchanger can be reduced even if it is not possible to cover the defrosting capability of the outdoor heat exchanger simply by stopping the heating operation in the defrosting operation with the heat storage use operation. Can be secured.
  • An air conditioner according to a sixth aspect is the air conditioner according to the fifth aspect, further comprising an indoor fan that supplies air to the indoor heat exchanger, and for the indoor heat exchanger heat recovery operation, There are a first indoor heat exchanger heat recovery operation in which the indoor fan is not operated and a second indoor heat exchanger heat recovery operation in which the indoor fan is operated.
  • the indoor heat exchanger heat recovery operation the first indoor heat exchanger heat recovery operation for recovering heat from the indoor heat exchanger while suppressing the influence on the air-conditioned space without operating the indoor fan, and the indoor fan
  • a second indoor heat exchanger heat recovery operation that can recover more heat than the first indoor heat exchanger heat recovery operation, although the effect on the air-conditioned space is increased by performing this operation.
  • the second indoor heat exchanger heat recovery operation can be performed.
  • An air conditioner according to a seventh aspect is the air conditioner according to the fifth or sixth aspect, wherein the connecting pipe heat recovery operation and / or the indoor heat exchanger heat recovery operation is performed in the defrosting operation involving the heat storage use operation. When performing, the defrosting operation is performed every time the heat storage operation is completed.
  • the defrosting operation When performing the heat recovery operation simultaneously in the defrosting operation with the heat storage use operation, the defrosting operation is frequently performed, and in the heat storage operation performed before the defrosting operation, the heat storage to the heat storage material is performed. It is preferable that it is sufficiently performed. Therefore, here, as described above, when the heat recovery operation is simultaneously performed in the defrosting operation with the heat storage utilization operation, the defrosting operation is performed every time the heat storage operation is completed. For this reason, while heat storage to the heat storage material in the heat storage operation before the defrost operation is performed reliably, the interval time between the defrost operations can be shortened by omitting the heating operation after the heat storage operation.
  • An air conditioner according to an eighth aspect is the air conditioner according to any one of the fifth to seventh aspects, wherein the connection pipe heat recovery operation and / or the heat of the indoor heat exchanger is performed in the defrosting operation involving the heat storage use operation.
  • Heat recovery operation setting means for setting whether to permit or prohibit the recovery operation is provided.
  • the heat recovery operation setting means can set whether the heat recovery operation is simultaneously performed or prohibited in the defrosting operation with the heat storage utilization operation. For example, in a cold region, a setting for performing a heat recovery operation in a defrosting operation with a heat storage use operation may be performed, and in a warm region, a setting for not performing a heat recovery operation in a defrosting operation with a heat storage use operation may be performed. it can. Thereby, it can be set here whether heat recovery operation is performed according to the weather conditions etc. of the area where an air harmony device is installed.
  • An air conditioner according to a ninth aspect is the air conditioner according to the eighth aspect, wherein the heat recovery operation setting means is in the defrosting operation involving the heat storage use operation, in the connecting pipe heat recovery operation, and in the first indoor heat exchange.
  • An oven heat recovery operation and a second indoor heat exchanger heat recovery operation can be set respectively.
  • the heat recovery operation setting means can set which of the three heat recovery operations is performed when the heat recovery operation is simultaneously performed in the defrosting operation with the heat storage use operation. . Thereby, here, it can be set up about which heat recovery operation is performed according to the weather conditions etc. of the area where an air harmony device is installed.
  • FIG. 1 is a schematic configuration diagram of an air conditioner 1 according to an embodiment of the present invention.
  • the air conditioning apparatus 1 is an apparatus used for air conditioning indoors such as buildings by performing a vapor compression refrigeration cycle operation.
  • the air conditioner 1 is mainly configured by connecting an outdoor unit 2 and a plurality (here, two) of indoor units 4a and 4b.
  • the outdoor unit 2 and the plurality of indoor units 4 a and 4 b are connected via a liquid refrigerant communication tube 6 and a gas refrigerant communication tube 7.
  • the vapor compression refrigerant circuit 10 of the air conditioner 1 is configured by connecting the outdoor unit 2 and the plurality of indoor units 4 a and 4 b via the refrigerant communication pipes 6 and 7.
  • the indoor units 4a and 4b are installed indoors.
  • the indoor units 4 a and 4 b are connected to the outdoor unit 2 via the refrigerant communication pipes 6 and 7 and constitute a part of the refrigerant circuit 10.
  • the configuration of the indoor units 4a and 4b will be described. Since the indoor unit 4b has the same configuration as the indoor unit 4a, only the configuration of the indoor unit 4a will be described here, and the configuration of the indoor unit 4b is indicated by the suffix a indicating each part of the indoor unit 4a. Instead, a subscript “b” is attached and description of each part is omitted.
  • the indoor unit 4a mainly has an indoor refrigerant circuit 10a (in the indoor unit 4b, the indoor refrigerant circuit 10b) that constitutes a part of the refrigerant circuit 10.
  • the indoor refrigerant circuit 10a mainly has an indoor expansion valve 41a and an indoor heat exchanger 42a.
  • the indoor expansion valve 41a is a valve that varies the flow rate of the refrigerant flowing through the indoor heat exchanger 42a by reducing the pressure of the refrigerant flowing through the indoor refrigerant circuit 10a.
  • the indoor expansion valve 41a is an electric expansion valve connected to the liquid side of the indoor heat exchanger 42a.
  • the indoor heat exchanger 42a is composed of, for example, a cross fin type fin-and-tube heat exchanger.
  • An indoor fan 43a for sending indoor air to the indoor heat exchanger 42a is provided in the vicinity of the indoor heat exchanger 42a. By blowing indoor air to the indoor heat exchanger 42a by the indoor fan 43a, the indoor heat exchanger 42a performs heat exchange between the refrigerant and the indoor air.
  • the indoor fan 43a is rotationally driven by an indoor fan motor 44a. Thereby, the indoor heat exchanger 42a functions as a refrigerant radiator or a refrigerant evaporator.
  • various sensors are provided in the indoor unit 4a.
  • a liquid side temperature sensor 45a that detects the temperature Trla of the refrigerant in the liquid state or the gas-liquid two-phase state is provided.
  • a gas side temperature sensor 46a for detecting the temperature Trga of the refrigerant in the gas state is provided.
  • an indoor temperature sensor 47a for detecting the temperature of indoor air in the air-conditioned space targeted by the indoor unit 4a (that is, the indoor temperature Tra) is provided.
  • the indoor unit 4a has the indoor side control part 48a which controls operation
  • the indoor side control part 48a has a microcomputer, memory, etc. provided in order to control the indoor unit 4a, and controls between the remote controllers 49a for operating the indoor unit 4a separately. Signals and the like can be exchanged, and control signals and the like can be exchanged with the outdoor unit 2.
  • the remote controller 49a is a device that allows the user to make various settings related to the air conditioning operation and to run / stop commands.
  • the outdoor unit 2 is installed outdoors.
  • the outdoor unit 2 is connected to the indoor units 4 a and 4 b via the refrigerant communication pipes 6 and 7 and constitutes a part of the refrigerant circuit 10.
  • the outdoor unit 2 mainly has an outdoor refrigerant circuit 10 c that constitutes a part of the refrigerant circuit 10.
  • the outdoor refrigerant circuit 10c mainly includes a compressor 21, a first switching mechanism 22, an outdoor heat exchanger 23, an outdoor expansion valve 24, a second switching mechanism 27, a heat storage heat exchanger 28, and a heat storage. And an expansion valve 29.
  • the compressor 21 is a hermetic compressor in which a compression element (not shown) and a compressor motor 20 that rotationally drives the compression element are accommodated in a casing.
  • the compressor motor 20 is supplied with electric power via an inverter device (not shown), and the operating capacity can be varied by changing the frequency (that is, the rotation speed) of the inverter device. ing.
  • the first switching mechanism 22 is a four-way switching valve for switching the direction of refrigerant flow.
  • the first switching mechanism 22 connects the discharge side of the compressor 21 and the gas side of the outdoor heat exchanger 23 when the outdoor heat exchanger 23 functions as a refrigerant radiator, Switching to connect the gas side and the suction side of the compressor 21 is performed (outdoor heat radiation switching state, see the solid line of the first switching mechanism 22 in FIG. 1).
  • the heat storage heat exchanger 28 can function as a refrigerant evaporator.
  • the first switching mechanism 22 connects the suction side of the compressor 21 and the gas side of the outdoor heat exchanger 23 when the outdoor heat exchanger 23 functions as a refrigerant evaporator, and also stores the heat storage heat exchanger. Switching to connect the gas side 28 and the discharge side of the compressor 21 is performed (outdoor evaporation switching state, see broken line of the first switching mechanism 22 in FIG. 1).
  • the heat storage heat exchanger 28 can function as a refrigerant radiator.
  • the first switching mechanism 22 may be configured to perform the same function by combining a three-way valve, an electromagnetic valve, or the like instead of the four-way switching valve.
  • the outdoor heat exchanger 23 includes, for example, a cross fin type fin-and-tube heat exchanger.
  • An outdoor fan 25 for sending outdoor air to the outdoor heat exchanger 23 is provided in the vicinity of the outdoor heat exchanger 23. By blowing outdoor air to the outdoor heat exchanger 23 by the outdoor fan 25, the outdoor heat exchanger 23 performs heat exchange between the refrigerant and the outdoor air.
  • the outdoor fan 25 is rotationally driven by an outdoor fan motor 26. Accordingly, the outdoor heat exchanger 23 functions as a refrigerant radiator or a refrigerant evaporator.
  • the outdoor expansion valve 24 is a valve that varies the flow rate of the refrigerant flowing through the outdoor heat exchanger 23 by reducing the pressure of the refrigerant flowing through the outdoor heat exchanger 23 in the outdoor refrigerant circuit 10c.
  • the outdoor expansion valve 24 is an electric expansion valve connected to the liquid side of the outdoor heat exchanger 23.
  • the second switching mechanism 27 is a four-way switching valve for switching the direction of refrigerant flow.
  • the second switching mechanism 27 performs switching to connect the suction side of the compressor 21 and the gas refrigerant communication pipe 7 when the indoor heat exchangers 42a and 42b function as a refrigerant evaporator (indoor evaporation switching state). (Refer to the solid line of the second switching mechanism 27 in FIG. 1). Further, the second switching mechanism 27 performs switching to connect the discharge side of the compressor 21 and the gas refrigerant communication pipe 7 when the indoor heat exchangers 42a and 42b function as a refrigerant radiator (indoor heat radiation). Switching state, see broken line of second switching mechanism 27 in FIG. 1).
  • one of the four ports of the second switching mechanism 27 is a port (in FIG. 1) that is always connected to the suction side of the compressor 21 via the capillary tube 271. By being connected to a port on the upper side of the drawing, the port is substantially unused.
  • the second switching mechanism 27 may be configured to perform the same function by combining a three-way valve, an electromagnetic valve, or the like instead of the four-way switching valve.
  • the heat storage heat exchanger 28 is a heat exchanger that exchanges heat between the refrigerant and the heat storage material, and stores heat in the heat storage material by functioning as a heat radiator of the refrigerant, and functions as an evaporator of the refrigerant. It is used when radiating heat (using heat storage) from the heat storage material.
  • the heat storage heat exchanger 28 mainly includes a heat storage tank 281 in which a heat storage material is stored, and a heat transfer tube group 282 arranged so as to be immersed in the heat storage material.
  • the heat storage tank 281 is a substantially rectangular parallelepiped box, and a heat storage material is stored therein.
  • the heat storage material here, a substance that stores heat by phase change is used.
  • the heat storage heat exchanger 28 when used as a refrigerant radiator, phase change (melting) is performed to store heat, and when the heat storage heat exchanger 28 is used as a refrigerant evaporator, phase change (solidification) is performed.
  • polyethylene glycol, sodium sulfate hydrate, paraffin or the like having a phase change temperature of about 30 ° C. to 40 ° C. is used so as to be used for heat storage.
  • the heat transfer tube group 282 has a structure in which a plurality of heat transfer tubes 285 are branched and connected via a header tube 283 and a flow divider 284 provided at the refrigerant inlet / outlet.
  • each of the plurality of heat transfer tubes 285 has a shape folded in the vertical direction, and both ends of the plurality of heat transfer tubes 285 are connected to the header tube 283 and the flow divider 284 to thereby heat transfer tubes.
  • a group 282 is formed.
  • the gas side of the heat storage heat exchanger 28 (that is, one end of the heat transfer tube group 282) is connected to the first switching mechanism 22, and the liquid side of the heat storage heat exchanger 28 (that is, other than the heat transfer tube group 282).
  • the end of the refrigerant circuit 10 (here, the outdoor refrigerant circuit 10c) is connected to a portion between the outdoor expansion valve 24 and the liquid refrigerant communication pipe 6 via a heat storage expansion valve 29.
  • FIG. 2 is a schematic configuration diagram of the heat storage heat exchanger 28.
  • the heat storage expansion valve 29 is a valve that varies the flow rate of the refrigerant flowing through the heat storage heat exchanger 28 by reducing the pressure of the refrigerant flowing through the heat storage heat exchanger 28 in the outdoor refrigerant circuit 10c.
  • the heat storage expansion valve 29 is an electric expansion valve connected to the liquid side of the heat storage heat exchanger 28.
  • the outdoor unit 2 is provided with various sensors.
  • the outdoor unit 2 includes a suction pressure sensor 31 that detects the suction pressure Ps of the compressor 21, a discharge pressure sensor 32 that detects the discharge pressure Pd of the compressor 21, and a suction temperature that detects the suction temperature Ts of the compressor 21.
  • a sensor 33 and a discharge temperature sensor 34 for detecting the discharge temperature Td of the compressor 21 are provided.
  • the outdoor heat exchanger 23 is provided with an outdoor heat exchange temperature sensor 35 that detects the temperature Tol1 of the refrigerant in the gas-liquid two-phase state.
  • a liquid side temperature sensor 36 for detecting the temperature Tol2 of the refrigerant in the liquid state or the gas-liquid two-phase state is provided on the liquid side of the outdoor heat exchanger 23 .
  • the outdoor air temperature of the outdoor unit 2 (that is, the outdoor heat exchanger 23 or the heat storage heat exchanger 28) (that is, the outdoor temperature Ta) is placed on the outdoor air inlet side of the outdoor unit 2.
  • An outdoor temperature sensor 37 for detection is provided.
  • the outdoor unit 2 also has an outdoor control unit 38 that controls the operation of each part constituting the outdoor unit 2.
  • the outdoor side control unit 38 includes a microcomputer provided to control the outdoor unit 2, an inverter device that controls the memory and the compressor motor 25, and the like, and is provided on the indoor side of the indoor units 4 a and 4 b. Control signals and the like can be exchanged with the control units 48a and 48b.
  • the refrigerant communication pipes 6 and 7 are refrigerant pipes that are constructed on the site when the air conditioner 1 is installed, and have various lengths and pipe diameters depending on the installation conditions of the outdoor unit 2 and the indoor units 4a and 4b. Are used.
  • FIG. 3 is a control block diagram of the air conditioner 1.
  • the air conditioner 1 includes the refrigerant circuit 10 configured by connecting a plurality (two in this case) of the indoor units 4 a and 4 b to the outdoor unit 2.
  • the following operation control is performed by the control unit 8.
  • FIG. 4 is a diagram illustrating the flow of the refrigerant in the refrigerant circuit in the cooling operation.
  • FIG. 5 is a diagram illustrating a refrigerant flow in the refrigerant circuit in the heating operation.
  • FIG. 6 is a diagram illustrating the flow of the refrigerant in the refrigerant circuit in the heat storage operation (heat storage operation during the heating operation).
  • FIG. 7 is a diagram illustrating the flow of the refrigerant in the refrigerant circuit in the defrosting operation (defrosting operation with heat storage use operation).
  • the high-pressure gas refrigerant is sent to the outdoor heat exchanger 23 via the first switching mechanism 22.
  • the high-pressure gas refrigerant sent to the outdoor heat exchanger 23 is condensed by being cooled by exchanging heat with outdoor air supplied by the outdoor fan 25 in the outdoor heat exchanger 23 functioning as a refrigerant radiator.
  • a high-pressure liquid refrigerant is obtained.
  • the high-pressure liquid refrigerant is sent from the outdoor unit 2 to the indoor units 4a and 4b via the outdoor expansion valve 24 and the liquid refrigerant communication pipe 6.
  • the high-pressure liquid refrigerant sent to the indoor units 4a and 4b is depressurized by the indoor expansion valves 41a and 41b, and becomes a low-pressure gas-liquid two-phase refrigerant.
  • This low-pressure gas-liquid two-phase refrigerant is sent to the indoor heat exchangers 42a and 42b.
  • the low-pressure gas-liquid two-phase refrigerant sent to the indoor heat exchangers 42a and 42b is combined with the indoor air supplied by the indoor fans 43a and 43b in the indoor heat exchangers 42a and 42b that function as refrigerant evaporators. By evaporating by heating through heat exchange, it becomes a low-pressure gas refrigerant.
  • the low-pressure gas refrigerant is sent from the indoor units 4 a and 4 b to the outdoor unit 2 via the gas refrigerant communication pipe 7.
  • the low-pressure gas refrigerant sent to the outdoor unit 2 is again sucked into the compressor 21 via the second switching mechanism 27.
  • the low-pressure gas refrigerant in the refrigerant circuit 10 is sucked into the compressor 21 and compressed to become a high-pressure gas refrigerant.
  • the high-pressure gas refrigerant is sent from the outdoor unit 2 to the indoor units 4a and 4b via the second switching mechanism 27 and the gas refrigerant communication pipe 7.
  • the high-pressure gas refrigerant sent to the indoor units 4a and 4b is sent to the indoor heat exchangers 42a and 42b.
  • the high-pressure gas refrigerant sent to the indoor heat exchangers 42a and 42b exchanges heat with the indoor air supplied by the indoor fans 43a and 43b in the indoor heat exchangers 42a and 42b functioning as a refrigerant radiator.
  • the high-pressure liquid refrigerant is depressurized by the indoor expansion valves 41a and 41b.
  • the refrigerant decompressed by the indoor expansion valves 41 a and 41 b is sent from the indoor units 4 a and 4 b to the outdoor unit 2 via the gas refrigerant communication pipe 7.
  • the refrigerant sent to the outdoor unit 2 is sent to the outdoor expansion valve 24, where it is depressurized by the outdoor expansion valve 24 to become a low-pressure gas-liquid two-phase refrigerant.
  • the low-pressure gas-liquid two-phase refrigerant is sent to the outdoor heat exchanger 23.
  • the low-pressure gas-liquid two-phase refrigerant sent to the outdoor heat exchanger 23 is heated by exchanging heat with outdoor air supplied by the outdoor fan 25 in the outdoor heat exchanger 23 functioning as an evaporator of the refrigerant. As a result, it evaporates and becomes a low-pressure gas refrigerant.
  • the low-pressure gas refrigerant is sucked into the compressor 21 again via the first switching mechanism 22.
  • Heat storage operation (heat storage operation during heating operation)> During the heating operation, a heat storage operation for storing heat in the heat storage material is performed by causing the heat storage heat exchanger 28 to function as a refrigerant radiator. That is, during the heating operation in which the outdoor heat exchanger 23 functions as a refrigerant evaporator and the indoor heat exchangers 42a and 42b function as a refrigerant radiator, the heat storage heat exchanger 28 functions as a refrigerant radiator. Thus, a heat storage operation (heat storage operation during heating operation) for storing heat in the heat storage material is performed. The heat storage operation during the heating operation is performed by opening the heat storage expansion valve 29 after switching the switching mechanisms 22 and 27 to the same switching state as the heating operation (see FIG. 6).
  • the low-pressure gas refrigerant in the refrigerant circuit 10 is sucked into the compressor 21 and compressed to become a high-pressure gas refrigerant.
  • a part of the high-pressure gas refrigerant is sent from the outdoor unit 2 to the indoor units 4a and 4b via the second switching mechanism 27 and the gas refrigerant communication pipe 7 as in the heating operation.
  • the high-pressure gas refrigerant sent to the indoor units 4a and 4b is cooled by exchanging heat with the indoor air supplied by the indoor fans 43a and 43b in the indoor heat exchangers 42a and 42b that function as a refrigerant radiator. As a result, it is condensed and becomes a high-pressure liquid refrigerant.
  • the high-pressure liquid refrigerant is depressurized by the indoor expansion valves 41a and 41b.
  • the refrigerant decompressed by the indoor expansion valves 41 a and 41 b is sent from the indoor units 4 a and 4 b to the outdoor unit 2 via the gas refrigerant communication pipe 7. Further, the remainder of the high-pressure gas refrigerant discharged from the compressor 21 is sent to the heat storage heat exchanger 28 via the first switching mechanism 22.
  • the high-pressure gas refrigerant sent to the heat storage heat exchanger 28 is condensed by being cooled by exchanging heat with the heat storage material in the heat storage heat exchanger 28 functioning as a radiator of the refrigerant. It becomes.
  • This high-pressure liquid refrigerant is depressurized by the heat storage expansion valve 29.
  • the heat storage material of the heat storage heat exchanger 28 is heated by heat exchange with the refrigerant to change phase (melt) and store heat.
  • the refrigerant decompressed by the heat storage expansion valve 29 merges with the refrigerant sent from the indoor units 4a and 4b to the outdoor unit 2, and is sent to the outdoor expansion valve 24.
  • the refrigerant is decompressed by the outdoor expansion valve 24, It becomes a liquid two-phase refrigerant.
  • the low-pressure gas-liquid two-phase refrigerant is sent to the outdoor heat exchanger 23.
  • the low-pressure gas-liquid two-phase refrigerant sent to the outdoor heat exchanger 23 is heated by exchanging heat with outdoor air supplied by the outdoor fan 25 in the outdoor heat exchanger 23 functioning as an evaporator of the refrigerant. As a result, it evaporates and becomes a low-pressure gas refrigerant.
  • the heat storage heat exchanger 28 functions as a refrigerant radiator parallel to the indoor heat exchangers 42a and 42b. That is, the refrigerant circuit 10 is configured to be able to send the high-pressure gas refrigerant discharged from the compressor 21 to the indoor heat exchangers 42a and 42b and the heat storage heat exchanger 28 in parallel in the heat storage operation during the heating operation. Has been.
  • a defrosting operation for defrosting the outdoor heat exchanger is performed by causing the outdoor heat exchanger 23 to function as a refrigerant radiator.
  • a heat storage use operation is performed in which the heat storage heat exchanger 28 functions as a refrigerant evaporator to release heat from the heat storage material. That is, the heat storage use operation (excluding the heat storage use operation and the heat storage use operation during the defrosting operation) in which the outdoor heat exchanger 23 functions as a refrigerant radiator and the heat storage heat exchanger 28 functions as a refrigerant evaporator. Frost operation) is performed.
  • the indoor heat exchangers 42a and 42b function as refrigerant radiators so that the heating operation is also performed at the same time. That is, here, the heat storage use operation and the heating operation are simultaneously performed during the defrosting operation (or the heating operation is simultaneously performed in the defrost operation accompanied by the heat storage use operation).
  • the heat storage use operation (or the defrost operation accompanied by the heat storage use operation) switches the first switching mechanism 22 to the outdoor heat radiation switching state and switches the second switching mechanism 27 to the indoor heat radiation switching state.
  • the heat storage expansion valve 29 is opened (see FIG. 7). Further, during the defrosting operation, the outdoor fan 25 is stopped.
  • the low-pressure gas refrigerant in the refrigerant circuit 10 is sucked into the compressor 21 and compressed to become a high-pressure gas refrigerant.
  • a part of the high-pressure gas refrigerant is sent from the outdoor unit 2 to the indoor units 4a and 4b via the second switching mechanism 27 and the gas refrigerant communication pipe 7 as in the heating operation.
  • the high-pressure gas refrigerant sent to the indoor units 4a and 4b is cooled by exchanging heat with the indoor air supplied by the indoor fans 43a and 43b in the indoor heat exchangers 42a and 42b that function as a refrigerant radiator. As a result, it is condensed and becomes a high-pressure liquid refrigerant.
  • the high-pressure liquid refrigerant is depressurized by the indoor expansion valves 41a and 41b.
  • the refrigerant decompressed by the indoor expansion valves 41 a and 41 b is sent from the indoor units 4 a and 4 b to the outdoor unit 2 via the gas refrigerant communication pipe 7. Further, the remaining high-pressure gas refrigerant discharged from the compressor 21 is sent to the outdoor heat exchanger 23 via the first switching mechanism 22.
  • the high-pressure gas refrigerant sent to the outdoor heat exchanger 23 is cooled by exchanging heat with frost and ice adhering to the outdoor heat exchanger 23 in the outdoor heat exchanger 23 functioning as a refrigerant radiator.
  • the This high-pressure refrigerant is decompressed by the outdoor expansion valve 24.
  • the frost and ice adhering to the outdoor heat exchanger 23 are melted by being heated by heat exchange with the refrigerant, and the outdoor heat exchanger 23 is defrosted.
  • the high-pressure refrigerant decompressed by the outdoor expansion valve 24 merges with the refrigerant sent from the indoor units 4a and 4b to the outdoor unit 2, is sent to the heat storage expansion valve 29, is decompressed by the heat storage expansion valve 29, and is low-pressure.
  • This is a refrigerant in a gas-liquid two-phase state.
  • This low-pressure gas-liquid two-phase refrigerant is sent to the heat storage heat exchanger 28.
  • the low-pressure gas-liquid two-phase refrigerant sent to the heat storage heat exchanger 28 evaporates by heat exchange with the heat storage material in the heat storage heat exchanger 28 that functions as a refrigerant evaporator. It becomes a low-pressure gas refrigerant.
  • the low-pressure gas refrigerant is sucked into the compressor 21 again via the first switching mechanism 22.
  • the heat storage material of the heat storage heat exchanger 28 is phase-changed (solidified) by being cooled by heat exchange with the refrigerant and used for heat storage.
  • the indoor heat exchangers 42a and 42b are connected to the outdoor heat exchanger 23 and It is designed to function as a parallel refrigerant radiator.
  • the refrigerant circuit 10 supplies the high-pressure gas refrigerant discharged from the compressor 21. It is configured to be able to send to the outdoor heat exchanger 23 and the indoor heat exchangers 42a and 42b in parallel.
  • the control unit 8 opens the indoor expansion valves 41a and 41b so that the superheat degrees SHra and SHrb of the refrigerant at the outlets of the indoor heat exchangers 42a and 42b become the target superheat degrees SHras and SHrbs.
  • this control is referred to as “superheat degree control by an indoor expansion valve”.
  • the superheat degrees SHra and SHrb are the suction pressure Ps detected by the suction pressure sensor 31 and the refrigerant temperatures Trga and Trgb on the gas side of the indoor heat exchanger 42a detected by the gas side temperature sensors 46a and 46b.
  • the suction pressure Ps is converted into the refrigerant saturation temperature, and the evaporation temperature Te (that is, the evaporation pressure Pe and the evaporation temperature Te, which is equivalent to the evaporation pressure Pe in the refrigerant circuit 10), Although the wording itself is different, it means substantially the same state quantity).
  • the evaporation pressure Pe is a low-pressure refrigerant that flows from the outlets of the indoor expansion valves 41a and 41b to the suction side of the compressor 21 via the indoor heat exchangers 42a and 42b during the cooling operation. Is a representative pressure.
  • superheat degree SHra and SHrb are obtained by subtracting the evaporation temperature Te from the temperature Trga and Trgb of the gas side refrigerant
  • control of each device of the indoor units 4a and 4b including the indoor expansion valves 41a and 41b is performed by the indoor side control units 48a and 48b of the control unit 8.
  • Control of each device of the outdoor unit 2 including the outdoor expansion valve 24 is performed by the outdoor control unit 38 of the control unit 8.
  • the control unit 8 controls the indoor expansion valves 41a and 41b so that the refrigerant subcooling degrees SCra and SCrb at the outlets of the indoor heat exchangers 42a and 42b become the target subcooling degrees SCras and SCrbs.
  • this control is referred to as “supercooling degree control by an indoor expansion valve”.
  • the degree of supercooling SCra, SCrb is the discharge pressure Pd detected by the discharge pressure sensor 32, and the temperature Tla of the refrigerant on the liquid side of the indoor heat exchanger 42a detected by the liquid side temperature sensors 45a, 45b, Calculated from Trlb.
  • the discharge pressure Pd is converted into the saturation temperature of the refrigerant, and the condensing temperature Tc (that is, the condensing pressure Pc and the condensing temperature Tc) is a state quantity equivalent to the condensing pressure Pc in the refrigerant circuit 10.
  • the condensation pressure Pc represents a high-pressure refrigerant that flows between the discharge side of the compressor 21 and the indoor expansion valves 41a and 41b via the indoor heat exchangers 42a and 42b during the heating operation. Means the pressure to do.
  • the subcooling degrees SCra and SCrb are obtained by subtracting the liquid-side refrigerant temperatures Trla and Trlb of the indoor heat exchangers 42a and 42b from the condensation temperature Tc.
  • control of each apparatus of the indoor units 4a and 4b including the indoor expansion valves 41a and 41b is performed by the indoor side control units 48a and 48b of the control unit 8.
  • Control of each device of the outdoor unit 2 including the outdoor expansion valve 24 is performed by the outdoor control unit 38 of the control unit 8.
  • the control unit 8 ends the heat storage operation and shifts to the heating operation.
  • the interval time ⁇ tbet means an interval time between defrosting operations. Basically, during the interval time ⁇ tbet, the heat storage operation during the heating operation and the heating operation after the end of the heat storage operation are performed, and the defrosting operation is performed every time the interval time ⁇ tbet elapses. .
  • the air conditioner 1 can be switched between the cooling operation and the heating operation. And by performing the heat storage operation during the heating operation, the heat storage material is stored while continuing the heating operation, and by performing the heat storage use operation during the defrosting operation, the defrost operation is performed using the heat storage of the heat storage material. Can be done.
  • the necessary defrosting capacity of the outdoor heat exchanger 23 depends on the weather conditions (outdoor temperature, It depends on the humidity and the degree of snowfall.
  • the weather conditions that require the most defrosting capacity during defrosting operation with heat storage operation such as in cold regions. It is conceivable to determine the specifications of the heat storage heat exchanger including the capacity of the heat storage material. However, such a method for determining the specifications of the heat storage heat exchanger 28 requires a large-capacity heat storage material, which increases the size, weight, and cost of the heat storage heat exchanger 28.
  • the specifications of the air conditioner 1 including the heat storage heat exchanger 28 are appropriate.
  • the heat storage heat exchanger 28 is installed.
  • the specification of the air conditioning apparatus 1 to include will become excessive.
  • the air conditioners 1 having a plurality of specifications including the heat storage heat exchangers 28 are prepared for each region, it will be possible to deal with a wide range of regions, but the productivity will be reduced by increasing the number of items. Disadvantages such as cost increases.
  • the defrosting ability of the outdoor heat exchanger 23 is set to the outdoor temperature Ta of the external space where the outdoor heat exchanger 23 is arranged and / or the previous defrosting.
  • the temperature is changed based on the outdoor heat exchange outlet temperature Tol2, which is the refrigerant temperature at the outlet of the outdoor heat exchanger 23 at the end of the operation.
  • Tol2 the refrigerant temperature at the outlet of the outdoor heat exchanger 23 at the end of the operation.
  • the heating capacity of the indoor heat exchangers 42a and 42b is increased while performing the heating operation. I try to make it smaller.
  • the table of the defrosting operation pattern for changing the defrosting capability of the outdoor heat exchanger 23 shown in FIG. 8 and the defrosting capability of the outdoor heat exchanger 23 of FIG. 9 are changed.
  • the defrosting capacity of the outdoor heat exchanger 23 is changed according to steps ST1 to ST3 shown in the flowchart of the defrosting operation pattern for the above.
  • the pattern 1 transition condition is a condition for determining whether or not the pattern 1 defrosting operation can be performed based on the outdoor temperature Ta representing the situation at the start of the defrosting operation.
  • a threshold temperature obtained based on the predetermined first outdoor temperature Tadef1 for example, a value obtained by adding the predetermined temperature ⁇ Tadef to the first outdoor temperature Tadef1
  • the indoor heat exchange is performed.
  • the pattern 1 return condition is based on the outdoor temperature Ta representing the situation at the start of the defrosting operation and the outdoor heat exchange outlet temperature Tol2 representing the situation at the end of the previous defrosting operation. This is a condition for determining whether or not it is possible to return from the defrosting operation to the pattern 1 defrosting operation.
  • the outdoor heat exchange outlet temperature Tol2 at the end of the previous three defrosting operations is the predetermined first defrosting operation determination temperature Tdef1 (here, the defrosting operation means the end of the defrosting operation).
  • the indoor heat exchangers 42a and 42b are equal to or higher than the end temperature Tdefe.
  • a predetermined second outdoor temperature Tadef2 here, a temperature lower than the first outdoor temperature Tadef1
  • the indoor heat exchangers 42a and 42b are equal to or higher than the end temperature Tdefe.
  • High-pressure gas refrigerant is supplied to the indoor heat exchangers 42a and 42b that function as refrigerant radiators by opening the expansion valves 41a and 41b by a predetermined degree of opening, and the indoor fans 43a and 43b are operated at the minimum rotational speed. Is done by.
  • the outdoor control unit 38 is configured such that the outdoor unit 38 includes the devices (compressor 21, switching mechanisms 22 and 27, outdoor expansion valve 24, outdoor fan 25, and heat storage expansion valve 29). ) As well as the control contents of the devices (indoor expansion valves 41a and 41b and indoor fans 43a and 43b) constituting the indoor units 4a and 4b.
  • the previous defrosting operation is the pattern 1 defrosting operation
  • the defrosting operation is performed while ensuring the heating capacity of the indoor heat exchangers 42a and 42b
  • the defrosting of the outdoor heat exchanger 23 is insufficient. May occur. Therefore, when the previous defrosting operation is the pattern 1 defrosting operation, it is determined whether or not the pattern 2 transition condition is satisfied. And when satisfy
  • the pattern 2 transition condition is based on the outdoor temperature Ta representing the situation at the start of the defrosting operation and the outdoor heat exchange outlet temperature Tol2 representing the situation at the end of the previous defrosting operation.
  • the outdoor heat exchange outlet temperature Tol2 at the end of the previous defrosting operation is a predetermined first defrosting operation determination temperature Tdef1 (here, the defrosting operation end temperature Tdefe that means the end of the defrosting operation) If the outdoor temperature Ta is lower than or equal to the predetermined first outdoor temperature Tadef1, or if the outdoor temperature Ta is lower than or equal to the predetermined second outdoor temperature Tadef2, the indoor heat exchangers 42a and 42b If the defrosting operation is performed while ensuring the heating capacity of the outdoor heat exchanger 23, it is assumed that the defrosting of the outdoor heat exchanger 23 may be insufficient, and the pattern 2 transition condition is satisfied.
  • Tdef1 the defrosting operation end temperature Tdefe that means the end of the defrosting operation
  • the defrosting operation of pattern 2 performs defrosting of the outdoor heat exchanger 23 while reducing the heating capacity of the indoor heat exchangers 42a and 42b, as shown in FIG.
  • the expansion valves 41a and 41b are slightly opened (for example, an opening of 15% or less when fully opened) to supply high-pressure gas refrigerant to the indoor heat exchangers 42a and 42b that function as a refrigerant radiator, and an indoor fan It is performed by operating 43a and 43b at the minimum rotation speed.
  • the outdoor side control unit 38 is connected to the devices (compressor 21, switching mechanisms 22 and 27, outdoor expansion valve 24, outdoor fan 25, and heat storage expansion valve 29) constituting the outdoor unit 2. )
  • the devices indoor expansion valves 41a and 41b and indoor fans 43a and 43b constituting the indoor units 4a and 4b.
  • the previous defrosting operation was the pattern 2 defrosting operation
  • the outdoor expansion valves 41a and 41b were slightly opened to reduce the heating capacity of the indoor heat exchangers 42a and 42b. Insufficient defrosting of the heat exchanger 23 may not be resolved. Therefore, when the previous defrosting operation is the pattern 2 defrosting operation, it is determined whether or not the pattern 3 transition condition is satisfied.
  • the defrosting operation of pattern 3 in step ST3 is performed.
  • whether the pattern 3 transition condition should be shifted from the pattern 2 defrosting operation to the pattern 3 defrosting operation based on the outdoor heat exchange outlet temperature Tol2 representing the situation at the end of the previous defrosting operation. It is a condition for judging.
  • the outdoor heat exchange outlet temperature Tol2 at the end of the previous defrosting operation is a predetermined second defrosting operation determination temperature Tdef2 (here, the defrosting operation end temperature Tdefe that means the end of the defrosting operation) If the temperature is lower than the same, if the defrosting operation is performed only by reducing the heating capacity of the indoor heat exchangers 42a and 42b, the defrosting of the outdoor heat exchanger 23 may be insufficient. The condition shall be met. Moreover, the defrosting operation of the pattern 3 stops the supply of the heating capacity to the indoor heat exchangers 42a and 42b and performs the defrosting of the outdoor heat exchanger 23 as shown in FIG. The indoor expansion valves 41a and 41b are fully closed and the indoor fans 43a and 43b are stopped.
  • the previous defrosting operation is the pattern 3 defrosting operation
  • the outdoor heat exchanger 23 is defrosted and the outdoor heat exchanger 23 is defrosted and the outdoor heat exchanger 23 is defrosted. Insufficient defrosting of the exchanger 23 may be resolved. Therefore, when the previous defrosting operation is the pattern 3 defrosting operation, it is determined whether or not the pattern 2 return condition is satisfied.
  • the pattern 2 return condition is satisfied, the pattern 2 defrosting operation in step ST2 is performed.
  • whether the pattern 2 return condition can return from the defrosting operation of the pattern 3 to the defrosting operation of the pattern 2 based on the outdoor heat exchange outlet temperature Tol2 representing the situation at the end of the previous defrosting operation. It is a condition for judging.
  • the outdoor heat exchange outlet temperature Tol2 at the end of the previous three defrosting operations is the predetermined second defrosting operation determination temperature Tdef2 (here, the defrosting operation means the end of the defrosting operation). If it is equal to or higher than the end temperature Tdef), the defrosting of the outdoor heat exchanger 23 is insufficient even if the outdoor heat exchanger 23 is defrosted while supplying the heating capacity to the indoor heat exchangers 42a and 42b. Assuming that there is no possibility of occurrence of pattern 2, it is assumed that the pattern 2 return condition is satisfied.
  • the outdoor side control unit 38 is connected to the devices (compressor 21, switching mechanisms 22, 27, outdoor expansion valve 24, outdoor fan 25, heat storage expansion valve 29) constituting the outdoor unit 2. ) As well as the control contents of the devices (indoor expansion valves 41a and 41b and indoor fans 43a and 43b) constituting the indoor units 4a and 4b.
  • the defrosting capability of the outdoor heat exchanger 23 that needs to be changed according to the weather conditions in the area where the air conditioner 1 is installed is defined as the outdoor temperature.
  • the temperature is changed based on Ta and / or the outdoor heat exchange outlet temperature Tol2 at the end of the previous defrosting operation.
  • the defrosting ability of the outdoor heat exchanger 23 can be made appropriate according to the weather conditions of the area where the air conditioner 1 is installed. Thereby, it can respond to a wide area by the heat storage heat exchanger 28 which has the heat storage material of a specific capacity
  • the outdoor side control unit 38 includes the devices (compressor 21, switching mechanisms 22, 27, Not only the control contents of the outdoor expansion valve 24, the outdoor fan 25, and the heat storage expansion valve 29) but also the control contents of the devices (the indoor expansion valves 41a and 41b and the indoor fans 43a and 43b) constituting the indoor units 4a and 4b are determined. This is different from the case where only the cooling operation or the heating operation is performed. For this reason, the outdoor side control part 38 comes to be able to collectively control now the apparatus control of the air conditioning apparatus 1 whole in the defrost operation accompanied by heat storage utilization operation, and control of each apparatus is performed appropriately.
  • the interval between the defrosting operations is A change is made to shorten the interval time ⁇ tbet.
  • the frequency of a defrost operation can be changed as needed, and the defrost operation accompanied by heat storage utilization operation can be performed favorably.
  • the connecting pipe heat recovery operation and / or the indoor heat exchange heat recovery operation are performed without simultaneously performing the heating operation.
  • the table of the defrosting operation pattern for changing the defrosting capability of the outdoor heat exchanger 23 shown in FIG. 11 and the defrosting capability of the outdoor heat exchanger 23 of FIG. 12 are changed.
  • the defrosting capacity of the outdoor heat exchanger 23 is changed according to steps ST1 to ST6 shown in the flowchart of the defrosting operation pattern for the above.
  • the heating capacity of the indoor heat exchangers 42a and 42b is reduced (heating capacity) as in the patterns 1 to 3 (steps ST1 to ST3) of the above embodiment. (Including stopping the supply) and defrosting operation.
  • the previous defrosting operation was the pattern 3 defrosting operation
  • the supply of the heating capacity to the indoor heat exchangers 42a and 42b was stopped by fully closing the indoor expansion valves 41a and 41b. Insufficient defrosting of the outdoor heat exchanger 23 may not be resolved. Therefore, when the previous defrosting operation is the pattern 3 defrosting operation, it is determined whether or not the pattern 4 transition condition is satisfied. And when satisfy
  • the outdoor heat exchange outlet temperature Tol2 at the end of the previous defrosting operation is equal to a predetermined third defrosting operation determination temperature Tdef3 (here, the defrosting operation end temperature Tdefe that means the end of the defrosting operation) The same), and when the setting for performing the defrosting operation of the pattern 4 is made, the defrosting of the outdoor heat exchanger 23 is insufficient just by stopping the supply of the heating capacity to the indoor heat exchangers 42a and 42b. It is assumed that the pattern 4 transition condition is satisfied.
  • the setting of whether or not to perform the defrosting operation of pattern 4 is the heat provided in the control unit 8 as shown in FIG. This is performed by the collection operation setting means 81.
  • the heat recovery operation setting means 81 is a memory provided in the outdoor side control unit 38 of the control unit 8, and the pattern 4 is obtained by communication from an external device for performing various control settings of the air conditioner 1. It is possible to set whether or not to perform the defrosting operation of 6 to 6.
  • the heat recovery operation setting means 81 is not limited to the one described above. For example, whether or not to perform the defrosting operation of the patterns 4 to 6 such as a dip switch provided in the outdoor control unit 38.
  • the defrosting operation of the pattern 4 is in the state which stopped supply of the heating capability to the indoor heat exchanger 42a, 42b by fully closing indoor expansion valve 41a, 41b.
  • the outdoor heat exchanger performs the connection pipe heat recovery operation for recovering the heat held by the refrigerant pipe (mainly the gas refrigerant communication pipe 7) connecting the indoor heat exchangers 42a and 42b and the compressor 21. 23 defrosting is performed.
  • the second switching mechanism 27 which has been switched to the indoor heat radiation switching state in order to cause the indoor heat exchangers 42a and 42b to function as a refrigerant radiator, functions as the indoor heat exchangers 42a and 42b as a refrigerant evaporator.
  • the refrigerant pipe (mainly the gas refrigerant communication pipe 7) connecting between the indoor heat exchangers 42a and 42b and the compressor 21 is set to a low pressure and accumulated in this refrigerant pipe.
  • the high-temperature gas refrigerant is sucked into the compressor 21 together with the low-pressure refrigerant from the heat storage heat exchanger 28 (see FIG. 14).
  • the outdoor side control unit 38 also includes the devices constituting the outdoor unit 2 (the compressor 21, the switching mechanisms 22, 27, the outdoor expansion valve 24, the outdoor fan 25, the heat storage expansion valve 29). ) As well as the control contents of the devices (indoor expansion valves 41a and 41b and indoor fans 43a and 43b) constituting the indoor units 4a and 4b.
  • the previous defrosting operation is the defrosting operation of pattern 4
  • the defrosting of the outdoor heat exchanger 23 is insufficient by performing the defrosting of the outdoor heat exchanger 23 while performing the connecting pipe heat recovery operation. May be resolved. Therefore, when the previous defrosting operation is the pattern 4 defrosting operation, it is determined whether or not the pattern 3 return condition is satisfied.
  • the pattern 3 return condition is satisfied, the pattern 3 defrosting operation in step ST3 is performed.
  • whether the pattern 3 return condition can be returned from the pattern 4 defrosting operation to the pattern 3 defrosting operation based on the outdoor heat exchange outlet temperature Tol2 representing the situation at the end of the previous defrosting operation. It is a condition for judging.
  • the outdoor heat exchanger 23 defrosting the outdoor heat exchanger 23 just by stopping the supply of the heating capacity to the indoor heat exchangers 42a and 42b. Assuming that there is no possibility of insufficient defrosting of the vessel 23, it is assumed that the pattern 3 return condition is satisfied.
  • the defrosting of the outdoor heat exchanger 23 is insufficient only by performing the defrosting of the outdoor heat exchanger 23 while performing the connecting pipe heat recovery operation. May not be resolved. Therefore, when the previous defrosting operation is the pattern 4 defrosting operation, it is determined whether or not the pattern 5 & 6 transition condition is satisfied. And when satisfy
  • the pattern 5 & 6 transition condition is to shift from the pattern 4 defrosting operation to the patterns 5 and 6 defrosting operation based on the outdoor heat exchange outlet temperature Tol2 representing the situation at the end of the previous defrosting operation.
  • This is a condition for determining whether or not
  • the outdoor heat exchange outlet temperature Tol2 at the end of the previous defrosting operation is a predetermined fourth defrosting operation determination temperature Tdef4 (here, the defrosting operation end temperature Tdefe that means the end of the defrosting operation) If the setting is made to perform the defrosting operation of pattern 5 or pattern 6 that is lower than the same), outdoor heat exchange is performed only by defrosting the outdoor heat exchanger 23 while performing the connecting pipe heat recovery operation.
  • the setting of whether or not to perform the defrosting operation of the patterns 5 and 6 is performed by the heat recovery operation setting means 81 provided in the control unit 8 as described above. Further, as shown in FIGS. 11 and 15, the defrosting operation of the patterns 5 and 6 is performed in the state where the outdoor heat exchanger 23 is defrosted while performing the connecting pipe heat recovery operation, as shown in FIGS. The outdoor heat exchanger 23 is defrosted while performing the heat recovery operation of the indoor heat exchanger that recovers the heat obtained by the refrigerant by causing 42b to function as an evaporator of the refrigerant.
  • the indoor expansion valves 41a and 41b that are fully closed in the communication pipe heat recovery operation are opened, and the indoor heat exchangers 42a and 42b function as a refrigerant evaporator (see FIG. 15).
  • the pattern 5 defrosting operation is set by the heat recovery operation setting means 81
  • the first indoor heat exchanger heat recovery operation is performed in which heat recovery is performed without operating the indoor fans 43a and 43b.
  • the pattern 6 defrosting operation is set, the second indoor heat exchanger heat recovery operation for operating the indoor fans 43a and 43b is performed (see FIG. 11).
  • the outdoor heat exchanger 23 is performing the first indoor heat exchanger heat recovery operation or the second indoor heat exchanger heat recovery operation.
  • the lack of defrosting of the outdoor heat exchanger 23 may be resolved. Therefore, when the previous defrosting operation is the pattern 5 or pattern 6 defrosting operation, it is determined whether or not the pattern 4 return condition is satisfied. If the pattern 4 return condition is satisfied, the defrosting operation of pattern 4 in step ST4 is performed.
  • the return condition of pattern 4 returns from the defrosting operation of pattern 5 or pattern 6 to the defrosting operation of pattern 4 based on the outdoor heat exchange outlet temperature Tol2 representing the situation at the end of the previous defrosting operation.
  • the outdoor side control unit 38 is configured so that the equipment constituting the outdoor unit 2 (the compressor 21, the switching mechanisms 22, 27, the outdoor expansion valve 24, the outdoor fan 25, the thermal storage expansion).
  • the control contents of the devices indoor expansion valves 41a and 41b and indoor fans 43a and 43b constituting the indoor units 4a and 4b are also determined.
  • the defrosting operation involving the heat storage use operation
  • the defrosting capacity of the outdoor heat exchanger 23 cannot be provided.
  • the defrosting operation connection pipe heat recovery operation
  • the defrosting operation is performed prior to the defrosting operation (indoor heat exchanger heat recovery operation) of pattern 5 or pattern 6.
  • the frost operation may be omitted.
  • the pattern 3 defrost operation is shifted to the pattern 5 or pattern 6 defrost operation, and when the pattern 4 return condition is satisfied, the pattern 5 or pattern 6 defrost is performed.
  • the indoor heat exchanger heat recovery operation the first indoor heat exchange for recovering heat from the indoor heat exchangers 42a and 42b while suppressing the influence on the air-conditioned space without operating the indoor fans 43a and 43b.
  • the second indoor heat that can recover more heat than the first indoor heat exchanger heat recovery operation although the influence on the air-conditioned space is increased by performing the heat recovery operation and the indoor fans 43a and 43b.
  • the defrosting capability of the outdoor heat exchanger 23 can be ensured by properly using two indoor heat exchanger heat recovery operations with different degrees of heat recovery as required.
  • the heat recovery operation setting means 81 provided in the control unit 8 can set whether or not the heat recovery operation is performed simultaneously or prohibited in the defrosting operation with the heat storage use operation. Yes. For example, in a cold region, a setting for performing a heat recovery operation in a defrosting operation with a heat storage use operation may be performed, and in a warm region, a setting for not performing a heat recovery operation in a defrosting operation with a heat storage use operation may be performed. it can. Thereby, it can be set here whether heat recovery driving
  • the heat recovery operation setting means 81 simultaneously performs the heat recovery operation in the defrosting operation with the heat storage use operation, three heat recovery operations (the communication tube heat recovery operation, the first indoor heat exchanger heat) It is possible to set whether to perform the recovery operation or the second indoor heat exchanger heat recovery operation). Thereby, here, it can be set up about which heat recovery operation is performed according to the weather conditions etc. of the area where the air conditioning apparatus 1 is installed. Further, in the case of performing the heat recovery operation as in patterns 4 to 6 simultaneously in the defrosting operation with the heat storage use operation, the defrosting operation is frequently performed and the heat storage performed before the defrosting operation is performed. In operation, it is preferable that heat storage to the heat storage material is sufficiently performed.
  • the index representing the situation at the end of the previous defrosting operation is not limited to this.
  • the time tdef required for the previous defrosting operation is used. It may be. That is, in the defrosting operation pattern changing process of FIG. 9 or FIG. 12, “the outdoor heat exchange outlet temperature Tol2 at the end of the previous defrosting operation is lower than the defrosting operation determination temperatures Tdef1, Tdef2, Tdef3, and Tdef4”.
  • the condition may be changed to a condition that “the time tdef required for the previous defrosting operation is larger than a predetermined time”.
  • the outdoor heat exchange outlet temperature Tol2 at the end of the previous three defrosting operations is equal to or higher than the defrosting operation determination temperatures Tdef1 and Tdef2
  • “required for the previous three defrosting operations” It is only necessary to change to the condition that all the times tdef are equal to or less than the predetermined time.
  • the defrosting capability of the outdoor heat exchanger 23 that needs to be changed according to the weather conditions in the area where the air conditioner 1 is installed is defined as the outdoor temperature. It is made to change based on Ta and / or time tdef required for the last defrost operation. For this reason, in the defrosting operation accompanied by the heat storage utilization operation, the defrosting ability of the outdoor heat exchanger 23 is determined in the same manner as the above embodiment and the first and second modifications, and the weather conditions in the area where the air conditioner 1 is installed. Depending on the situation, it can be made appropriate.
  • the heat storage heat exchanger 28 which has the heat storage material of a specific capacity
  • the defrosting ability of the outdoor heat exchanger 23 can be ensured while continuing the heating operation as much as possible.
  • the time tdef required for the previous defrosting operation is long, it is preferable to perform the defrosting operation frequently so that the defrosting operation is performed well.
  • the defrosting operation is frequently performed, and in the heat storage operation performed before the defrosting operation, It is preferable that heat storage is sufficiently performed.
  • the interval time ⁇ tbet between the defrosting operations is changed based on the outdoor temperature Ta and / or the time required for the previous defrosting operation.
  • the time required for the previous defrosting operation is long (here, when performing the defrosting operation of pattern 2), as shown in FIGS. 10 and 11, the interval time ⁇ tbet between the defrosting operations is shown. Change to shorten.
  • the heat recovery operation is simultaneously performed in the defrosting operation with the heat storage use operation (here, when the defrosting operation of patterns 3 to 6 is performed), the heat storage is performed in the same manner as in the second modification (see FIG. 11).
  • a defrosting operation is performed every time the operation ends.
  • the frequency of a defrost operation can be changed as needed, and the defrost operation accompanied by heat storage utilization operation can be performed favorably.
  • heat storage to the heat storage material in the heat storage operation before the defrosting operation is reliably performed, and the interval time ⁇ tbet between the defrosting operations can be shortened by omitting the heating operation after the heat storage operation.
  • the present invention includes a refrigerant circuit having a heat storage heat exchanger that performs heat exchange between the refrigerant and the heat storage material, and the heat storage heat exchanger functions as a refrigerant radiator to store heat in the heat storage material.
  • a refrigerant circuit having a heat storage heat exchanger that performs heat exchange between the refrigerant and the heat storage material, and the heat storage heat exchanger functions as a refrigerant radiator to store heat in the heat storage material.

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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 concerne un climatiseur (1) comprenant : un compresseur (21), un échangeur thermique extérieur (23), des échangeurs thermiques intérieurs (42a, 42b), et un circuit de réfrigérant (10) comportant un échangeur thermique à chaleur emmagasinée (28) qui échange la chaleur entre un réfrigérant et un matériau de stockage thermique ; et pouvant effectuer une opération de stockage thermique, et utiliser simultanément la chaleur emmagasinée et effectuer une opération de chauffage pendant une opération de dégivrage. Dans le climatiseur (1), pour une opération de dégivrage accompagnant l'opération d'utilisation de chaleur emmagasinée, la capacité de dégivrage de l'échangeur thermique extérieur (23) est changée sur base de la température extérieure d'un espace externe dans lequel l'échangeur thermique extérieur (23) est installé, et/ou d'une température extérieure de sortie d'échange thermique, qui est la température du réfrigérant à la sortie de l'échangeur thermique extérieur (23) à l'achèvement de l'opération précédente de dégivrage, ou le temps nécessaire pour l'opération de dégivrage précédente.
PCT/JP2012/076940 2012-10-18 2012-10-18 Climatiseur WO2014061133A1 (fr)

Priority Applications (5)

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ES12886542.5T ES2683363T3 (es) 2012-10-18 2012-10-18 Aire acondicionado
JP2014541877A JP5955400B2 (ja) 2012-10-18 2012-10-18 空気調和装置
CN201280076455.0A CN104736951B (zh) 2012-10-18 2012-10-18 空调装置
EP12886542.5A EP2860474B1 (fr) 2012-10-18 2012-10-18 Climatiseur
PCT/JP2012/076940 WO2014061133A1 (fr) 2012-10-18 2012-10-18 Climatiseur

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PCT/JP2012/076940 WO2014061133A1 (fr) 2012-10-18 2012-10-18 Climatiseur

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WO2014061133A1 true WO2014061133A1 (fr) 2014-04-24

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CN (1) CN104736951B (fr)
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WO (1) WO2014061133A1 (fr)

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CN105627530A (zh) * 2014-11-07 2016-06-01 青岛海尔空调电子有限公司 一种变频空调及其控制方法
JP2016102641A (ja) * 2014-11-28 2016-06-02 ダイキン工業株式会社 圧縮機、および、それを用いた空気調和機
JP2020098044A (ja) * 2018-12-17 2020-06-25 富士電機株式会社 ショーケース及びショーケースの除霜制御方法

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EP3492841A1 (fr) * 2014-12-26 2019-06-05 Daikin Industries, Ltd. Climatiseur d'air régénératif

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CN105627530A (zh) * 2014-11-07 2016-06-01 青岛海尔空调电子有限公司 一种变频空调及其控制方法
JP2016102641A (ja) * 2014-11-28 2016-06-02 ダイキン工業株式会社 圧縮機、および、それを用いた空気調和機
WO2016084794A1 (fr) * 2014-11-28 2016-06-02 ダイキン工業株式会社 Compresseur et climatiseur l'utilisant
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CN104736951B (zh) 2017-03-08
EP2860474B1 (fr) 2018-07-04
EP2860474A1 (fr) 2015-04-15
EP2860474A4 (fr) 2015-06-03
CN104736951A (zh) 2015-06-24
JP5955400B2 (ja) 2016-07-20
JPWO2014061133A1 (ja) 2016-09-05

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