EP2863153B1 - Klimaanlage - Google Patents

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Publication number
EP2863153B1
EP2863153B1 EP12886561.5A EP12886561A EP2863153B1 EP 2863153 B1 EP2863153 B1 EP 2863153B1 EP 12886561 A EP12886561 A EP 12886561A EP 2863153 B1 EP2863153 B1 EP 2863153B1
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EP
European Patent Office
Prior art keywords
indoor
heat
outdoor
refrigerant
air
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.)
Active
Application number
EP12886561.5A
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English (en)
French (fr)
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EP2863153A4 (de
EP2863153A1 (de
Inventor
Masahiro Honda
Yoshihiro Matsumoto
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.)
Daikin Europe NV
Daikin Industries Ltd
Original Assignee
Daikin Europe NV
Daikin Industries Ltd
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Publication of EP2863153A1 publication Critical patent/EP2863153A1/de
Publication of EP2863153A4 publication Critical patent/EP2863153A4/de
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B13/00—Compression machines, plants or systems, with reversible cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B47/00—Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass
    • F25B47/02—Defrosting cycles
    • F25B47/022—Defrosting cycles hot gas defrosting
    • F25B47/025—Defrosting cycles hot gas defrosting by reversing the cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—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
    • F25B2600/2513—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
    • 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 relates to an air conditioning apparatus, and particularly to an air conditioning apparatus comprising a refrigerant circuit having a heat storage heat exchanger for performing heat exchange between a refrigerant and a heat storage medium, it being possible for a heat storage operation for storing heat in the heat storage medium to be performed by causing the heat storage heat exchanger to function as a heat radiator of the refrigerant, and an air-warming operation and a heat-storage-utilizing operation for radiating heat from the heat storage medium to be performed simultaneously by causing the heat storage heat exchanger to function as an evaporator of the refrigerant during a defrosting operation.
  • air conditioning apparatuses that comprise a refrigerant circuit having a compressor, an outdoor heat exchanger, an indoor heat exchanger, and a heat storage heat exchanger for performing heat exchange between a refrigerant and a heat storage medium, in which a heat storage operation is performed, and a heat-storage-utilizing operation and an air-warming operation can be performed simultaneously during a defrosting operation, as shown in Patent Literature 1 (Japanese Laid-open Patent Application No. 2005-337657 ).
  • the heat storage operation is an operation for storing heat in a heat storage medium by causing the heat storage heat exchanger to function as a heat radiator of the refrigerant.
  • the defrosting operation is an operation for defrosting the outdoor heat exchanger by causing the outdoor heat exchanger to function as a heat radiator of the refrigerant.
  • the heat-storage-utilizing operation is an operation for radiating heat from the heat storage medium by causing the heat storage heat exchanger to function as an evaporator of the refrigerant.
  • the air-warming operation is an operation for causing the indoor heat exchanger to function as a heat radiator of the refrigerant.
  • JP H3-28672 A discloses an air conditioning apparatus comprising a refrigerant circuit having a compressor, an outdoor heat exchanger, indoor heat exchangers, and a heat storage heat exchanger for performing heat exchange between a refrigerant and a heat storage medium, the air conditioning apparatus being capable of performing a heat storage operation for storing heat in the heat storage medium by causing the heat storage heat exchanger to function as a heat radiator of the refrigerant, and, during a defrosting operation for defrosting the outdoor heat exchanger by causing the outdoor heat exchanger to function as a heat radiator of the refrigerant, simultaneously performing a heat-storage-utilizing operation for radiating heat from the heat storage medium by causing the heat storage heat exchanger to function as an evaporator of the refrigerant and an air-warming operation for causing the indoor heat exchangers to function as heat radiators of the refrigerant; wherein the refrigerant circuit also has indoor expansion valves for varying the flow rate of the refrigerant flowing through the indoor heat exchange
  • the conventional air conditioning apparatus described above has an indoor unit provided with an indoor heat exchanger and an indoor expansion valve for varying the flow rate of refrigerant flowing through the indoor heat exchanger, and an outdoor unit provided with an outdoor heat exchanger and an outdoor expansion valve for varying the flow rate of refrigerant flowing through the outdoor heat exchanger.
  • the opening degree of the indoor expansion valve is controlled on the basis of the degree of subcooling of the refrigerant in the outlet of the indoor heat exchanger (degree of subcooling control by the indoor expansion valve), and the air-warming capability of the indoor heat exchanger is thereby ensured.
  • the opening degree of the indoor expansion valve in this degree of subcooling control is decided by an indoor-side control part provided to the indoor unit.
  • the indoor-side control part preferably controls the opening degree of the indoor expansion valve and ensures the air-warming capability of the indoor heat exchanger, similar to during normal air-warming operation, when there is excess in the defrosting capability of the outdoor heat exchanger.
  • the opening degree of the indoor expansion valve must be different from the opening degree during the normal air-warming operation in order to limit the air-warming capability of the indoor heat exchanger.
  • the opening degree of the indoor expansion valve is too great relative to the opening degree of the outdoor expansion valve, the limit on the air-warming capability of the indoor heat exchanger becomes insufficient, the defrosting capability of the outdoor heat exchanger becomes insufficient, and the defrosting operation therefore ends while the outdoor heat exchanger is not yet fully defrosted.
  • An object of the present invention is to provide an air conditioning apparatus that comprises a refrigerant circuit having a heat storage heat exchanger for performing heat exchange between a refrigerant and a heat storage medium, that can perform a heat storage operation, and that can perform a heat-storage-utilizing operation and an air-warming operation simultaneously during a defrosting operation, wherein the opening degrees of the indoor expansion valve and the outdoor expansion valve can be appropriately decided when the air-warming operation is performed simultaneously during the defrosting operation accompanying the heat-storage-utilizing operation.
  • An air conditioning apparatus comprises a refrigerant circuit having a compressor, an outdoor heat exchanger, indoor heat exchangers, and a heat storage heat exchanger for performing heat exchange between a refrigerant and a heat storage medium, the air conditioning apparatus being configured to perform a heat storage operation, and simultaneously performing a heat-storage-utilizing operation and an air-warming operation during a defrosting operation.
  • the heat storage operation is an operation for storing heat in the heat storage medium by causing the heat storage heat exchanger to function as a heat radiator of the refrigerant.
  • the defrosting operation is an operation for defrosting the outdoor heat exchanger by causing the outdoor heat exchanger to function as a heat radiator of the refrigerant.
  • the heat-storage-utilizing operation is an operation for radiating heat from the heat storage medium by causing the heat storage heat exchanger to function as an evaporator of the refrigerant.
  • the air-warming operation is an operation for causing the indoor heat exchangers to function as heat radiators of the refrigerant.
  • the refrigerant circuit also has indoor expansion valves for varying the flow rate of the refrigerant flowing through the indoor heat exchangers, and an outdoor expansion valve for varying the flow rate of the refrigerant flowing through the outdoor heat exchanger.
  • the indoor heat exchangers and the indoor expansion valves herein are provided to indoor units, and the outdoor heat exchanger and the outdoor expansion valve are provided to an outdoor unit.
  • the indoor units have indoor-side control parts for deciding the opening degrees of the indoor expansion valves when only the air-warming operation is performed
  • the outdoor unit has an outdoor-side control part for deciding the opening degree of the outdoor expansion valve when only the air-warming operation is performed and deciding the opening degrees of the indoor expansion valves and the opening degree of the outdoor expansion valve when the air-warming operation is performed during the defrosting operation accompanying the heat-storage-utilizing operation.
  • the air conditioning apparatus is the air conditioning apparatus, wherein when the air-warming operation is performed during the defrosting operation accompanying the heat-storage-utilizing operation, the opening degrees of the indoor expansion valves are decided on the basis of the correlation between the condensation temperature of the refrigerant in the refrigerant circuit and the indoor temperatures of the spaces being air-conditioned by the indoor units, until a first defrosting time elapses from the start of the defrosting operation.
  • the indoor-side control parts decide the opening degrees of the indoor expansion valves and the outdoor-side control part decides the opening degree of the outdoor expansion valve, but when the air-warming operation is performed during the defrosting operation accompanying the heat-storage-utilizing operation, the outdoor-side control part decides not only the opening degree of the outdoor expansion valve but also the opening degrees of the indoor expansion valves.
  • the outdoor-side control part can decide the opening degree of the outdoor expansion valve and the opening degrees of the indoor expansion valves all together, taking into account a balance between the defrosting capability of the outdoor heat exchanger and the air-warming capabilities of the indoor heat exchangers.
  • the opening degrees of the indoor expansion valves and the outdoor expansion valve can thereby be appropriately decided herein when the air-warming operation is performed during the defrosting operation accompanying the heat-storage-utilizing operation.
  • the opening degrees of the indoor expansion valves must be decided while the air-warming capabilities of the indoor heat exchangers are reliably ensured.
  • the outdoor-side control part decides the opening degrees of the indoor expansion valves, it is difficult to take into account the effects of pressure loss and the like in the refrigerant in the refrigerant pipes connecting the outdoor unit and the indoor units.
  • the opening degrees of the indoor expansion valves are decided herein on the basis of the correlation between the condensation temperature of the refrigerant in the refrigerant circuit and the indoor temperatures of the spaces being air-conditioned by the indoor units until the first defrosting time elapses from the start of the defrosting operation, as described above. For example, when the condensation temperature is lower than a threshold temperature obtained from the indoor temperatures, the outdoor-side control part determines that the air-warming capabilities of the indoor heat exchangers are not being ensured, and increases the opening degrees of the indoor expansion valves so that the air-warming capabilities of the indoor heat exchangers are ensured.
  • such a decision about the opening degree for the indoor expansion valves is performed until the first defrosting time elapses from the start of the defrosting operation, and in the initial period of the defrosting operation, the defrosting operation is performed with priority given to ensuring the air-warming capabilities of the indoor heat exchangers.
  • the outdoor-side control part thereby appropriately decides the opening degrees of the indoor expansion valves on the basis of the correlation between the condensation temperature and the indoor temperatures, whereby the defrosting operation can be performed with priority given to ensuring the air-warming capabilities of the indoor heat exchangers.
  • An air conditioning apparatus according to a second aspect is defined by the appended claim 2.
  • An air conditioning apparatus is the air conditioning apparatus according to the first or second aspect, wherein after the first defrosting time has elapsed from the start of the defrosting operation, the opening degrees of the indoor expansion valves and the outdoor expansion valve are altered so that the air-warming capabilities of the indoor heat exchangers decrease and the defrosting capability of the outdoor heat exchanger increases.
  • the defrosting capability of the outdoor heat exchanger must be increased in order to reliably end defrosting of the outdoor heat exchanger.
  • the opening degrees of the indoor expansion valves and the outdoor expansion valve are herein altered so that the air-warming capabilities of the indoor heat exchangers decrease and the defrosting capability of the outdoor heat exchanger increases, as described above.
  • the outdoor-side control part reduces the opening degrees of the indoor expansion valves and increases the opening degree of the outdoor expansion valve to reduce the air-warming capabilities of the indoor heat exchangers and increase the defrosting capability of the outdoor heat exchanger, whereby operation of the air conditioning apparatus transitions from prioritizing air-warming to prioritizing defrosting.
  • the outdoor-side control part thereby appropriately decides the opening degrees of the indoor expansion valves and the outdoor expansion valve, whereby operation can be made to transition from prioritizing air-warming to prioritizing defrosting, and the defrosting of the outdoor heat exchanger can be reliably ended.
  • An air conditioning apparatus is the air conditioning apparatus according to any one of the first to third aspects, wherein the first defrosting time is decided on the basis of the outdoor temperature of the external space where the outdoor unit is disposed.
  • the first defrosting time which is the time during which an operation prioritizing air-warming is performed, is also preferably decided on the basis of the outdoor temperature.
  • the first defrosting time herein is decided on the basis of the outdoor temperature as described above. For example, the lower the outdoor temperature, the shorter the time must be for an operation prioritizing air-warming and the longer the time must be for an operation prioritizing defrosting, and the first defrosting time is therefore decided so as to be shorter as the outdoor temperature decreases.
  • the first defrosting time during which an operation prioritizing air-warming is performed is thereby herein decided on the basis of the outdoor temperature, whereby a longer operation prioritizing defrosting can be performed, and defrosting of the outdoor heat exchanger can be reliably ended.
  • An air conditioning apparatus is the air conditioning apparatus according to any one of the first through fourth aspects, wherein during the defrosting operation, the air conditioning apparatus determines whether or not the opening degrees of the indoor expansion valves are too large on the basis of the degree of superheating of the refrigerant discharged from the compressor.
  • the refrigerant in the outlets of the indoor heat exchangers readily reaches a gas-liquid two-phase state when the opening degrees of the indoor expansion valves become too large.
  • Refrigerant in a gas state then readily fills the refrigerant pipes connecting the outlet sides (liquid sides) of the indoor heat exchangers and the inlet side (liquid side) of the heat storage heat exchanger functioning as an evaporator of the refrigerant.
  • the outdoor-side control part herein is designed to determine, on the basis of the degree of superheating of the refrigerant discharged from the compressor, that liquid backflow is occurring due to the opening degrees of the indoor expansion valves being too large. For example, when the degree of superheating of the refrigerant discharged from the compressor is lower than a threshold degree of superheating, the outdoor-side control part determines that liquid backflow is occurring. The opening degrees of the indoor expansion valves are then reduced as necessary.
  • FIG. 1 is a schematic overview of an air conditioning apparatus 1 according to an embodiment of the present invention.
  • the air conditioning apparatus 1 is an apparatus used to air-condition the interior of a room in a building or the like by performing a vapor-compression refrigeration cycle operation.
  • the air conditioning apparatus 1 is configured by connecting primarily an outdoor unit 2 and a plurality (two in this case) of indoor units 4a, 4b.
  • the outdoor unit 2 and the plurality of indoor units 4a, 4b herein are connected via a liquid refrigerant communication pipe 6 and a gas refrigerant communication pipe 7.
  • a vapor-compression refrigerant circuit 10 of the air conditioning apparatus 1 is configured by connecting the outdoor unit 2 and the plurality of indoor units 4a, 4b via the refrigerant communication pipes 6, 7.
  • the indoor units 4a, 4b are installed in a room.
  • the configuration of the indoor units 4a, 4b will be described. Because the indoor unit 4b has a configuration identical to that of the indoor unit 4a, only the configuration of the indoor unit 4a is described herein, and the configuration of the indoor unit 4b, for which the components are not described, uses the letter "b" in place of the letter "a” indicating the components of the indoor unit 4a.
  • the indoor unit 4a has primarily an indoor-side refrigerant circuit 10a constituting part of the refrigerant circuit 10 (the indoor unit 4b has an indoor-side refrigerant circuit 10b).
  • the indoor-side refrigerant circuit 10a has primarily an indoor expansion valve 41a and an indoor heat exchanger 42a.
  • the indoor expansion valve 41a is a valve for depressurizing the refrigerant flowing through the indoor-side refrigerant circuit 10a and varying the flow rate of the refrigerant flowing through the indoor heat exchanger 42a.
  • 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, e.g., 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 proximity to the indoor heat exchanger 42a. Heat exchange between the refrigerant and indoor air is performed in the indoor heat exchanger 42a by the blowing of indoor air to the indoor heat exchanger 42a by the indoor fan 43a.
  • the indoor fan 43a is designed to be rotatably driven by an indoor fan motor 44a.
  • the indoor heat exchanger 42a is thereby designed to function as a heat radiator of the refrigerant and/or an evaporator of the refrigerant.
  • a liquid-side temperature sensor 45a for detecting the temperature Trla of refrigerant in a liquid state or a gas-liquid two-phase state is provided to the liquid side of the indoor heat exchanger 42a.
  • a gas-side temperature sensor 46a for detecting the temperature Trga of refrigerant in a gas state is provided to the gas side of the indoor heat exchanger 42a.
  • An indoor temperature sensor 47a for detecting the temperature of indoor air (i.e. the indoor temperature Tra) in the space to be air-conditioned by the indoor unit 4a is provided in the indoor air intake port side of the indoor unit 4a.
  • the indoor unit 4a also has an indoor-side control part 48a for controlling the actions of the components constituting the indoor unit 4a.
  • the indoor-side control part 48a which has components such as a microcomputer and/or a memory provided in order to perform controls for the indoor unit 4a, is designed to be capable of exchanging control signals and the like with a remote controller 49a for operating the indoor unit 4a individually, and exchanging control signals and the like with the outdoor unit 2.
  • the remote controller 49a is a device for the user to perform various settings and/or operations/stop commands pertaining to air conditioning operation.
  • the outdoor unit 2 is installed outside of the room.
  • the outdoor unit 2 which is connected to the indoor units 4a, 4b via the refrigerant communication pipes 6, 7, constitutes part of the refrigerant circuit 10.
  • the outdoor unit 2 has primarily an outdoor-side refrigerant circuit 10c constituting part of the refrigerant circuit 10.
  • the outdoor-side refrigerant circuit 10c has primarily 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 expansion valve 29.
  • the compressor 21 is a hermetic compressor accommodating a compression element (not shown) inside a casing and a compressor motor 20 for rotatably driving the compression element.
  • the compressor motor 20 is supplied with electric power via an inverter apparatus (not shown), and the operating capacity can be varied by changing the frequency (i.e. the rotational speed) of the inverter apparatus.
  • the first switching mechanism 22 is a four-way switching valve for switching the direction of refrigerant flow.
  • the first switching mechanism 22 performs a switch connecting the discharge side of the compressor 21 and the gas side of the outdoor heat exchanger 23, and connecting the gas side of the heat storage heat exchanger 28 and the intake side of the compressor 21 (outdoor heat-radiating switched state; refer to the solid lines of the first switching mechanism 22 in FIG. 1 ).
  • the heat storage heat exchanger 28 can be made to function as an evaporator of the refrigerant.
  • the first switching mechanism 22 When the outdoor heat exchanger 23 is made to function as an evaporator of the refrigerant, the first switching mechanism 22 performs a switch connecting the intake side of the compressor 21 and the gas side of the outdoor heat exchanger 23, and connecting the gas side of the heat storage heat exchanger 28 and the discharge side of the compressor 21 (outdoor evaporating switched state; refer to the dashed lines of the first switching mechanism 22 in FIG. 1 ).
  • the heat storage heat exchanger 28 can be made to function as a heat radiator of the refrigerant.
  • the first switching mechanism 22 may be configured by combining a three-way valve, an electromagnetic valve, and/or the like to fulfill the same function.
  • the outdoor heat exchanger 23 is composed of, e.g., 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 proximity to the outdoor heat exchanger 23. Heat exchange between the refrigerant and outdoor air is performed in the outdoor heat exchanger 23 by the blowing of outdoor air to the outdoor heat exchanger 23 by the outdoor fan 25.
  • the outdoor fan 25 is designed to be rotatably driven by an outdoor fan motor 26.
  • the outdoor heat exchanger 23 is thereby designed to function as a heat radiator of the refrigerant and/or an evaporator of the refrigerant.
  • the outdoor expansion valve 24 is a valve for depressurizing the refrigerant flowing through the outdoor heat exchanger 23 within the outdoor-side refrigerant circuit 10c and varying the flow rate of the refrigerant flowing through the outdoor heat exchanger 23.
  • 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 a switch connecting the intake side of the compressor 21 and the gas refrigerant communication pipe 7 (indoor evaporating switched state; refer to the solid lines of the second switching mechanism 27 in FIG. 1 ).
  • the second switching mechanism 27 performs a switch connecting the discharge side of the compressor 21 and the gas refrigerant communication pipe 7 (indoor heat-radiating switched state; refer to the dashed lines of the second switching mechanism 27 in FIG. 1 ).
  • One of the four ports of the second switching mechanism 27 (the port near the right of the image in FIG. 1 ) is substantially an unused port, due to being connected to the port connected to the intake side of the compressor 21 (the port near the top of the image in FIG. 1 ) via a capillary tube 271.
  • the second switching mechanism 27 may be configured by combining a three-way valve, an electromagnetic valve, and/or the like to fulfill the same function.
  • the heat storage heat exchanger 28 which is a heat exchanger for performing heat exchange between the refrigerant and the heat storage medium, is made to function as a heat radiator of the refrigerant to cause heat to be stored in the heat storage medium, and is made to function as an evaporator of the refrigerant to cause heat to be radiated (heat storage to be utilized) from the heat storage medium.
  • the heat storage heat exchanger 28 has primarily a heat storage tank 281 in which the heat storage medium is retained, and a heat transfer tube group 282 disposed so as to be submerged in the heat storage medium.
  • the heat storage tank 281 herein is a box shaped as a substantial rectangular parallelepiped as shown in FIG. 2 , the heat storage medium being retained in the interior.
  • a substance that stores heat by changing phases is used herein as the heat storage medium.
  • a medium such as polyethylene glycol, sodium sulfate hydrate, paraffin, or the like, having a phase change temperature of about 30°C to 40°C, is used so that the heat storage medium changes phases (melts) and stores heat when the heat storage heat exchanger 28 is used as a heat radiator of the refrigerant, and changes phases (congeals) to allow the heat storage to be utilized when the heat storage heat exchanger 28 is used as an evaporator of the refrigerant.
  • 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 pipe 283 and a flow diverter 284 provided to the refrigerant exit and entrance, as shown in FIG. 2 .
  • the plurality of heat transfer tubes 285 all have shapes that vertically turn back, and the ends of the plurality of heat transfer tubes 285 are connected to the header tube 283 and the flow diverter 284, thereby constituting the heat transfer tube group 282.
  • the gas side of the heat storage heat exchanger 28 i.e. 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 (i.e.
  • FIG. 2 herein is a schematic overview of the heat storage heat exchanger 28.
  • the heat storage expansion valve 29 is a valve for depressurizing the refrigerant flowing through the heat storage heat exchanger 28 within the outdoor-side refrigerant circuit 10c and varying the flow rate of the refrigerant flowing through the heat storage heat exchanger 28.
  • 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 an intake pressure sensor 31 for detecting the intake pressure Ps of the compressor 21, a discharge pressure sensor 32 for detecting the discharge pressure Pd of the compressor 21, an intake temperature sensor 33 for detecting the intake temperature Ts of the compressor 21, and a discharge temperature sensor 34 for detecting the discharge temperature Td of the compressor 21.
  • the outdoor heat exchanger 23 is provided with an outdoor heat exchange temperature sensor 35 for detecting the temperature Tol1 of refrigerant in a gas-liquid two-phase state.
  • the liquid side of the outdoor heat exchanger 23 is provided with a liquid-side temperature sensor 36 for detecting the temperature Tol2 of refrigerant in a liquid state or a gas-liquid two-phase state.
  • the outdoor air intake port side of the outdoor unit 2 is provided with an outdoor temperature sensor 37 for detecting the temperature of outdoor air (i.e. the outdoor temperature Ta) in the external space where the outdoor unit 2 (i.e. the outdoor heat exchanger 23 and/or the heat storage heat exchanger 28) is located.
  • the outdoor unit 2 also has an outdoor-side control part 38 for controlling the actions of the components constituting the outdoor unit 2.
  • the outdoor-side control part 38 which has components such as a microcomputer and/or a memory provided in order to perform controls for the outdoor unit 2 and/or an inverter device for controlling the compressor motor 20, is designed to be capable of exchanging control signals and the like with the indoor-side control parts 48a, 48b of the indoor units 4a, 4b.
  • the refrigerant communication pipes 6, 7 are refrigerant pipes constructed on site when the air conditioning apparatus 1 is installed; these pipes have various lengths and diameters, depending on the conditions in which the outdoor unit 2 and the indoor units 4a, 4b are installed.
  • the remote controllers 49a, 49b for individually operating the indoor units 4a, 4b, the indoor-side control parts 48a, 48b of the indoor units 4a, 4b, and the outdoor-side control part 38 of the outdoor unit 2 constitute a control part 8 for performing operation controls for the entire air conditioning apparatus 1, as shown in FIG. 1 .
  • the control part 8 is connected so as to be capable of receiving detection signals from various sensors such as 31 to 37, 45a, 45b, 46a, 46b, 47a, and 47b, as shown in FIG. 3 .
  • the control part 8 is configured so as to be capable of performing air conditioning operations (an air-cooling operation and an air-warming operation) by controlling various devices and valves 20, 22, 24, 26, 41a, 41b, 44a, and 44b on the basis of these detection signals and the like.
  • FIG. 3 is a control block diagram of the air conditioning apparatus 1.
  • the air conditioning apparatus 1 has the refrigerant circuit 10 configured by connecting a plurality (two in this case) of indoor units 4a, 4b to the outdoor unit 2.
  • operation controls such as the following are performed by the control part 8.
  • FIGS. 4 to 7 are used to describe the basic actions of the air-cooling operation, the air-warming operation, the heat storage operation, and a defrosting operation of the air conditioning apparatus 1.
  • FIG. 4 is a drawing showing the flow of refrigerant through the refrigerant circuit in the air-cooling operation.
  • FIG. 5 is a drawing showing the flow of refrigerant through the refrigerant circuit in the air-warming operation.
  • FIG 6 is a drawing showing the flow of refrigerant through the refrigerant circuit in the heat storage operation (the heat storage operation during the air-warming operation).
  • FIG. 7 is a drawing showing the flow of refrigerant through the refrigerant circuit in the defrosting operation (the defrosting operation accompanying the heat-storage-utilizing operation).
  • the first switching mechanism 22 is switched to the outdoor heat-radiating switched state (the state shown by the solid lines of the first switching mechanism 22 in FIG. 4 )
  • the second switching mechanism 27 is switched to the indoor evaporating switched state (the state shown by the solid lines of the second switching mechanism 27 in FIG. 4 )
  • the heat storage expansion valve 29 is closed (i.e. the heat storage heat exchanger 28 is not used), and the compressor 21, the outdoor fan 25, and the indoor fans 43a, 43b start up.
  • the low-pressure gas refrigerant in the refrigerant circuit 10 is then drawn into the compressor 21 and compressed to high-pressure gas refrigerant.
  • This high-pressure gas refrigerant is sent through the first switching mechanism 22 to the outdoor heat exchanger 23.
  • the high-pressure gas refrigerant sent to the outdoor heat exchanger 23 is condensed to high-pressure liquid refrigerant by being cooled by heat exchange with outdoor air supplied by the outdoor fan 25 in the outdoor heat exchanger 23 functioning as a heat radiator of the refrigerant.
  • This high-pressure liquid refrigerant is sent through the outdoor expansion valve 24 and the liquid refrigerant communication pipe 6, from the outdoor unit 2 to the indoor units 4a, 4b.
  • the high-pressure liquid refrigerant sent to the indoor units 4a, 4b is depressurized by the indoor expansion valves 41a, 41b to low-pressure gas-liquid two-phase refrigerant.
  • This low-pressure gas-liquid two-phase refrigerant is sent to the indoor heat exchangers 42a, 42b.
  • the low-pressure gas-liquid two-phase refrigerant sent to the indoor heat exchangers 42a, 42b is evaporated to low-pressure gas refrigerant by being heated by heat exchange with indoor air supplied by the indoor fans 43a, 43b in the indoor heat exchangers 42a, 42b functioning as evaporators of the refrigerant.
  • This low-pressure gas refrigerant is sent through the gas refrigerant communication pipe 7, from the indoor units 4a, 4b to the outdoor unit 2.
  • the low-pressure gas refrigerant sent to the outdoor unit 2 is drawn through the second switching mechanism 27 back into the compressor 21.
  • the first switching mechanism 22 is switched to the outdoor evaporating switched state (the state shown by the dashed lines of the first switching mechanism 22 in FIG. 5 )
  • the second switching mechanism 27 is switched to the indoor heat-radiating switched state (the state shown by the dashed lines of the second switching mechanism 27 in FIG. 5 )
  • the heat storage expansion valve 29 is closed (i.e. the heat storage heat exchanger 28 is not used), and the compressor 21, the outdoor fan 25, and the indoor fans 43a, 43b start up.
  • the low-pressure gas refrigerant in the refrigerant circuit 10 is then drawn into the compressor 21 and compressed to high-pressure gas refrigerant.
  • This high-pressure gas refrigerant is sent through the second switching mechanism 27 and the gas refrigerant communication pipe 7, from the outdoor unit 2 to the indoor units 4a, 4b.
  • the high-pressure gas refrigerant sent to the indoor units 4a, 4b is sent to the indoor heat exchangers 42a, 42b.
  • the high-pressure gas refrigerant sent to the indoor heat exchangers 42a, 42b is condensed to high-pressure liquid refrigerant by being cooled by heat exchange with indoor air supplied by the indoor fans 43a, 43b in the indoor heat exchangers 42a, 42b functioning as heat radiators of the refrigerant.
  • This high-pressure liquid refrigerant is depressurized by the indoor expansion valves 41a, 41b.
  • the refrigerant depressurized by the indoor expansion valves 41a, 41b is sent through the gas refrigerant communication pipe 7, from the indoor units 4a, 4b to the outdoor unit 2.
  • the refrigerant sent to the outdoor unit 2 is sent to the outdoor expansion valve 24 and is depressurized by the outdoor expansion valve 24 to low-pressure gas-liquid two-phase refrigerant.
  • This 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 evaporated to low-pressure gas refrigerant by being heated by heat exchange with outdoor air supplied by the outdoor fan 25 in the outdoor heat exchanger 23 functioning as an evaporator of the refrigerant.
  • This low-pressure gas refrigerant is drawn through the first switching mechanism 22 back into the compressor 21.
  • the heat storage operation is performed, in which heat is stored in the heat storage medium by causing the heat storage heat exchanger 28 to function as a heat radiator of the refrigerant.
  • the heat storage operation (the heat storage operation during the air-warming operation) is performed wherein heat is stored in the heat storage medium by causing the heat storage heat exchanger 28 to function as a heat radiator of the refrigerant.
  • the heat storage operation during the air-warming operation is performed by opening the heat storage expansion valve 29 when the switching mechanisms 22, 27 have been switched to the same switched state as the air-warming operation (see FIG. 6 ).
  • the low-pressure gas refrigerant in the refrigerant circuit 10 is then drawn into the compressor 21 and compressed to high-pressure gas refrigerant.
  • Some of this high-pressure gas refrigerant is sent through the second switching mechanism 27 and the gas refrigerant communication pipe 7, from the outdoor unit 2 to the indoor units 4a, 4b, similar to the air-warming operation.
  • This high-pressure gas refrigerant sent to the indoor units 4a, 4b is condensed to high-pressure liquid refrigerant by being cooled by heat exchange with indoor air supplied by the indoor fans 43a, 43b in the indoor heat exchangers 42a, 42b functioning as heat radiators of the refrigerant.
  • This high-pressure liquid refrigerant is depressurized by the indoor expansion valves 41a, 41b.
  • the refrigerant depressurized by the indoor expansion valves 41a, 41b is sent through the gas refrigerant communication pipe 7, from the indoor units 4a, 4b to the outdoor unit 2.
  • the rest of the high-pressure gas refrigerant discharged from the compressor 21 is sent through the first switching mechanism 22 to the heat storage heat exchanger 28.
  • the high-pressure gas refrigerant sent to the heat storage heat exchanger 28 is condensed to high-pressure liquid refrigerant by being cooled by heat exchange with the heat storage medium in the heat storage heat exchanger 28 functioning as a heat radiator of the refrigerant.
  • This high-pressure liquid refrigerant is depressurized by the heat storage expansion valve 29.
  • the heat storage medium of the heat storage heat exchanger 28 herein changes phases (melts) and stores heat due to being heated by heat exchange with the refrigerant.
  • the refrigerant depressurized by the heat storage expansion valve 29 converges with the refrigerant sent from the indoor units 4a, 4b to the outdoor unit 2, and the converged refrigerant is sent to the outdoor expansion valve 24 and depressurized by the outdoor expansion valve 24 to low-pressure gas-liquid two-phase refrigerant.
  • This 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 evaporated to low-pressure gas refrigerant by being heated by heat exchange with outdoor air supplied by the outdoor fan 25 in the outdoor heat exchanger 23 functioning as an evaporator of the refrigerant.
  • the heat storage heat exchanger 28 is designed to function as a heat radiator of the refrigerant in parallel with the indoor heat exchangers 42a, 42b.
  • the refrigerant circuit 10 is configured to be capable of sending high-pressure gas refrigerant discharged from the compressor 21 in parallel to the indoor heat exchangers 42a, 42b and the heat storage heat exchanger 28 in the heat storage operation during the air-warming operation.
  • the defrosting operation is performed for defrosting the outdoor heat exchanger by causing the outdoor heat exchanger 23 to function as a heat radiator of the refrigerant.
  • the heat-storage-utilizing operation is performed for radiating heat from the heat storage medium by causing the heat storage heat exchanger 28 to function as an evaporator of the refrigerant.
  • the heat-storage-utilizing operation (the heat-storage-utilizing operation during the defrosting operation, and the defrosting operation accompanying the heat-storage-utilizing operation) is performed wherein the outdoor heat exchanger 23 is made to function as a heat radiator of the refrigerant and the heat storage heat exchanger 28 is made to function as an evaporator of the refrigerant.
  • the air-warming operation is also performed simultaneously herein by causing the indoor heat exchangers 42a, 42b to function as heat radiators of the refrigerant.
  • the heat-storage-utilizing operation and the air-warming operation are performed simultaneously during the defrosting operation (or the air-warming operation is performed simultaneously during the defrosting operation accompanying the heat-storage-utilizing operation).
  • This heat-storage-utilizing operation during the defrosting operation is performed by opening the heat storage expansion valve 29 when the first switching mechanism 22 has been switched to the outdoor heat-radiating switched state and the second switching mechanism 27 has been switched to the indoor heat-radiating switched state (see FIG. 7 ).
  • the outdoor fan 25 is stopped.
  • the low-pressure gas refrigerant in the refrigerant circuit 10 is then drawn into the compressor 21 and compressed to high-pressure gas refrigerant.
  • Some of this high-pressure gas refrigerant is sent through the second switching mechanism 27 and the gas refrigerant communication pipe 7, from the outdoor unit 2 to the indoor units 4a, 4b, similar to the air-warming operation.
  • the high-pressure gas refrigerant sent to the indoor units 4a, 4b is condensed to high-pressure liquid refrigerant by being cooled by heat exchange with indoor air supplied by the indoor fans 43a, 43b in the indoor heat exchangers 42a, 42b functioning as heat radiators of the refrigerant.
  • This high-pressure liquid refrigerant is depressurized by the indoor expansion valves 41a, 41b.
  • the refrigerant depressurized by the indoor expansion valves 41a, 41b is sent through the gas refrigerant communication pipe 7, from the indoor units 4a, 4b to the outdoor unit 2.
  • the rest of the high-pressure gas refrigerant discharged from the compressor 21 is sent through the first switching mechanism 22 to the outdoor heat exchanger 23.
  • the high-pressure gas refrigerant sent to the outdoor heat exchanger 23 is cooled by heat exchange with the frost and/or ice adhering to the outdoor heat exchanger 23, in the outdoor heat exchanger 23 functioning as a heat radiator of the refrigerant.
  • This high-pressure refrigerant is depressurized by the outdoor expansion valve 24.
  • the frost and/or ice adhering to the outdoor heat exchanger 23 herein is melted by being heated by heat exchange with the refrigerant, and the outdoor heat exchanger 23 is defrosted.
  • the high-pressure refrigerant depressurized by the outdoor expansion valve 24 converges with the refrigerant sent from the indoor units 4a, 4b to the outdoor unit 2, and this converged refrigerant is sent to the heat storage expansion valve 29 and depressurized by the heat storage expansion valve 29 to low-pressure gas-liquid two-phase refrigerant.
  • 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 is evaporated to low-pressure gas refrigerant by being heated by heat exchange with the heat storage medium in the heat storage heat exchanger 28 functioning as an evaporator of the refrigerant.
  • This low-pressure gas refrigerant is drawn through the first switching mechanism 22 back into the compressor 21.
  • the heat storage medium of the heat storage heat exchanger 28 herein changes phases (congeals) due to being cooled by heat exchange with the refrigerant, and the heat storage medium is utilized for heat storage.
  • the indoor heat exchangers 42a, 42b are designed to function as heat radiators of the refrigerant in parallel with the outdoor heat exchanger 23.
  • the refrigerant circuit 10 is configured so as to be capable of sending the high-pressure gas refrigerant discharged from the compressor 21 in parallel to the outdoor heat exchanger 23 and the indoor heat exchangers 42a, 42b, when the air-warming operation is performed simultaneously during the defrosting operation accompanying the heat-storage-utilizing operation (or the heat-storage-utilizing operation during the defrosting operation).
  • the control part 8 determines and controls the opening degrees of the indoor expansion valves 41a, 41b so that the degrees of superheating SHra, SHrb of the refrigerant in the outlets of the indoor heat exchangers 42a, 42b reach target degrees of superheating SHras, SHrbs (this control is referred to below as "degree of superheating control by the indoor expansion valves").
  • the degrees of superheating SHra, SHrb herein are calculated from the intake pressure Ps detected by the intake pressure sensor 31, and the temperatures Trga, Trgb of refrigerant on the gas sides of the indoor heat exchangers 42a, 42b detected by the gas-side temperature sensors 46a, 46b.
  • the intake pressure Ps is converted to the refrigerant saturation temperature to obtain the evaporation temperature Te which is a state quantity equivalent to the evaporation pressure Pe in the refrigerant circuit 10 (i.e., the evaporation pressure Pe and the evaporation temperature Te are different terms but refer essentially to the same state quantity).
  • the term "evaporation pressure Pe” means a pressure representing the low-pressure refrigerant flowing from the outlets of the indoor expansion valves 41a, 41b, through the indoor heat exchangers 42a, 42b, to the intake side of the compressor 21 during the air-cooling operation.
  • the degrees of superheating SHra, SHrb are then obtained by subtracting the evaporation temperature Te from the temperatures Trga, Trgb of refrigerant on the gas sides of the indoor heat exchangers 42a, 42b.
  • the controls of the different devices of the indoor units 4a, 4b, including the indoor expansion valves 41a, 41b, are performed by the indoor-side control parts 48a, 48b of the control part 8.
  • the controls of the different devices of the outdoor unit 2, including the outdoor expansion valve 24, are performed by the outdoor-side control part 38 of the control part 8.
  • the control part 8 determines and controls the opening degrees of the indoor expansion valves 41a, 41b so that the degrees of subcooling SCra, SCrb of the refrigerant in the outlets of the indoor heat exchangers 42a, 42b reach target degrees of subcooling SCras, SCrbs (this control is referred to below as "degree of subcooling control by the indoor expansion valves").
  • the degrees of subcooling SCra, SCrb herein are calculated from the discharge pressure Pd detected by the discharge pressure sensor 32, and the temperatures Trla, Trlb of refrigerant on the liquid sides of the indoor heat exchangers 42a, 42b detected by the liquid-side temperature sensors 45a, 45b.
  • the discharge pressure Pd is converted to the refrigerant saturation temperature to obtain the condensation temperature Tc which is a state quantity equivalent to the condensation pressure Pc in the refrigerant circuit 10 (i.e., the condensation pressure Pc and the condensation temperature Tc are different terms but mean essentially the same state quantity).
  • the term "condensation pressure Pc” means a pressure representing the high-pressure refrigerant flowing from the discharge side of the compressor 21, through the indoor heat exchangers 42a, 42b, to the indoor expansion valves 41a, 41b during the air-warming operation.
  • the degrees of subcooling SCra, SCrb are then obtained by subtracting the temperatures Trla, Trlb of refrigerant in the liquid sides of the indoor heat exchangers 42a, 42b from the condensation temperature Tc.
  • the controls of the different devices of the indoor units 4a, 4b, including the indoor expansion valves 41a, 41b, are performed by the indoor-side control parts 48a, 48b of the control part 8.
  • the controls of the different devices of the outdoor unit 2, including the outdoor expansion valve 24, are performed by the outdoor-side control part 38 of the control part 8.
  • the control part 8 ends the heat storage operation and transitions to the air-warming operation when heat storage in the heat storage medium of the heat storage heat exchanger 28 has ended.
  • a transition is made to the defrosting operation.
  • the interval time ⁇ tbet means the interval time between the defrosting operations. Basically, during the interval time ⁇ tbet, the heat storage operation during the air-warming operation and the air-warming operation following the end of the heat storage operation are performed, and the defrosting operation is performed with each elapse of the interval time ⁇ tbet.
  • the air conditioning apparatus 1 is designed so that operation can switch between air-cooling and air-warming.
  • Heat can be stored in the heat storage medium while the air-warming operation is continued by performing the heat storage operation during the air-warming operation, and the heat storage of the heat storage medium can be utilized to perform the defrosting operation by performing the heat-storage-utilizing operation during the defrosting operation.
  • the indoor-side control parts 48a, 48b preferably perform opening degree control on the indoor expansion valves 41a, 41b (degree of subcooling control by the indoor expansion valves 41a, 41b herein), ensuring the air-warming capabilities of the indoor heat exchangers 42a, 42b, similar to during the normal air-warming operation (i.e. during an air-warming operation that does not accompany a heat-storage-utilizing operation and/or a defrosting operation).
  • the opening degree control of the indoor expansion valves 41a, 41b must be different from the control during the normal air-warming operation in order to limit the air-warming capabilities of the indoor heat exchangers 42a, 42b.
  • the limit on the air-warming capabilities of the indoor heat exchangers 42a, 42b becomes insufficient and the defrosting capability of the outdoor heat exchanger 23 becomes insufficient; therefore, the defrosting operation ends while the outdoor heat exchanger 23 is not yet fully defrosted.
  • the indoor-side control parts 48a, 48b decide the opening degrees of the indoor expansion valves 41a, 41b and the outdoor-side control part 38 decides the opening degree of the outdoor expansion valve 24, but when the air-warming operation is performed during the defrosting operation accompanying the heat-storage-utilizing operation, the outdoor-side control part 38 decides not only the opening degree of the outdoor expansion valve 24 but also the opening degrees of the indoor expansion valves 41 a, 41b.
  • the outdoor-side control part 38 can decide the opening degree of the outdoor expansion valve 24 and the opening degrees of the indoor expansion valves 41a, 41b all together, taking into account a balance between the defrosting capability of the outdoor heat exchanger 23 and the air-warming capabilities of the indoor heat exchangers 42a, 42b.
  • the opening degrees of the indoor expansion valves 41a, 41b and the outdoor expansion valve 24 can thereby be appropriately decided herein when first the air-warming operation is performed during the defrosting operation accompanying the heat-storage-utilizing operation.
  • the opening degrees of the indoor expansion valves 41a, 41b must be decided while the air-warming capabilities of the indoor heat exchangers 42a, 42b are reliably ensured.
  • the outdoor-side control part 38 decides the opening degrees of the indoor expansion valves 41a, 41b, it is difficult to take into account the effects of pressure loss and the like in the refrigerant in the refrigerant pipes connecting the outdoor unit 2 and the indoor units 4a, 4b (mainly the liquid refrigerant communication pipe 6 and the gas refrigerant communication pipe 7 herein).
  • the defrosting capability of the outdoor heat exchanger 23 must also be increased in order to reliably end the defrosting of the outdoor heat exchanger 23.
  • the opening degrees of the indoor expansion valves 41a, 41b are decided on the basis of the correlation between the condensation temperature Tc of the refrigerant in the refrigerant circuit 10 and the indoor temperatures Tra, Trb (collectively referred to as Tr) of the spaces to be air-conditioned by the indoor units 4a, 4b.
  • the opening degrees of the indoor expansion valves 41a, 41b and the outdoor expansion valve 24 are altered so that the air-warming capabilities of the indoor heat exchangers 42a, 42b decrease and the defrosting capability of the outdoor heat exchanger 23 increases.
  • the opening degrees of the indoor expansion valves 41a, 41b and the outdoor expansion valve 24 are decided by the outdoor-side control part 38 in accordance with steps ST1 to ST5 shown in the flowchart of FIG. 8 .
  • step ST1 when the heat storage operation during the air-warming operation ends, the air-warming operation following the end of the heat storage operation ends, and the defrosting operation (the defrosting operation accompanying the heat-storage-utilizing operation) is started, in step ST1, the opening degrees of the indoor expansion valves 41a, 41b are set to an initial opening degree MVrd1 for the defrosting operation, and the opening degree of the outdoor expansion valve 24 is set to an initial opening degree MVod1 for the defrosting operation.
  • the opening degrees of the indoor expansion valves 41a, 41b and the opening degree of the outdoor expansion valve 24 are decided herein by the outdoor-side control part 38 as described above.
  • the air-warming/defrosting prioritizing start condition herein is a condition for determining whether or not the current state allows for an operation prioritizing air-warming and/or an operation prioritizing defrosting to be performed by altering the opening degrees of the indoor expansion valves 41a, 41b and the opening degree of the outdoor expansion valve 24.
  • the air-warming/defrosting prioritizing start condition is satisfied herein in cases in which the time is within a second defrosting time tah from the start of the defrosting operation, a predetermined time tdef1 has elapsed from the start of the defrosting operation, and the condensation temperature Tc is less than a predetermined threshold temperature Trdef obtained from the indoor temperature Tr (e.g., a value obtained by adding a predetermined temperature to the indoor temperature Tr).
  • the second defrosting time tah herein is the time taken to perform an operation prioritizing air-warming and/or an operation prioritizing defrosting from the start of the defrosting operation.
  • the time tdef1 is a standby time from the start of the defrosting operation until a transition is made to an operation prioritizing air-warming and/or an operation prioritizing defrosting, and is an extremely short time compared to the second defrosting time tah.
  • step ST4 when the defrosting operation has transitioned from step ST2 to step ST3 satisfies an air-warming prioritizing condition, the sequence transitions to the process of step ST4, and control is performed for deciding the opening degrees of the indoor expansion valves 41a, 41b and the opening degree of the outdoor expansion valve 24 so that an operation prioritizing air-warming is performed.
  • the air-warming prioritizing condition is a condition for determining whether or not the current state is not ensuring the air-warming capabilities of the indoor heat exchangers 42a, 42b.
  • the air-warming prioritizing condition is concluded to be satisfied herein in cases in which the time is within the first defrosting time taj (a time shorter than the second defrosting time tah) from the start of the defrosting operation the start of the defrosting operation, a predetermined time tdef2 has elapsed from the start of the defrosting operation the transition to step ST3, and the condensation temperature Tc is less than a threshold temperature Trdef (the same as the threshold temperature Trdef in the air-warming/defrosting prioritizing start condition described above) obtained from the indoor temperature Tr.
  • the time tdef2 herein is a standby time for maintaining the opening degree holding state of step ST3.
  • the sequence transitions to the process of step ST4 the opening degrees of the indoor expansion valves 41a, 41b are increased (by an opening degree ⁇ MVrd2 herein), the opening degree of the outdoor expansion valve 24 is reduced (by an opening degree ⁇ MVod2 herein), and the sequence returns to the process of step ST3.
  • the outdoor-side control part 38 herein determines whether or not the air-warming prioritizing condition (including the determination according to the threshold temperature Trdef) is satisfied and/or decides the opening degrees of the indoor expansion valves 41a, 41b and the opening degree of the outdoor expansion valve 24.
  • the opening degrees of the indoor expansion valves 41a, 41b are appropriately decided herein on the basis of the correlation between the condensation temperature Tc and the indoor temperature Tr.
  • step ST4 By repeating this process of step ST3, the air-warming prioritizing condition determination, and step ST4, it is possible to perform the defrosting operation while prioritizing that the air-warming capabilities of the indoor heat exchangers 42a, 42b are ensured with increased opening degrees of the indoor expansion valves 41a, 41b and a reduced opening degree of the outdoor expansion valve 24, until the elapse of the first defrosting time taj from the start of the defrosting operation the start of the defrosting operation (i.e. in the initial period of the defrosting operation) as shown in FIG. 9 .
  • the defrosting prioritizing condition is a condition for determining whether or not the current state is not ensuring the defrosting capability of the outdoor heat exchanger 23.
  • the defrosting prioritizing condition is satisfied in cases in which the first defrosting time taj has elapsed from the start of the defrosting operation the start of the defrosting operation, a predetermined time tdef3 has elapsed from the start of the defrosting operation the transition to step ST3, and an outdoor heat exchange outlet temperature Tol2, which is the temperature of the refrigerant in the outlet of the outdoor heat exchanger 23, is less than a predetermined defrosting operation intermediate temperature Tdefm (a temperature equal to or less than a defrosting operation ending temperature Tdefe for determining whether or not the defrosting operation has ended).
  • the time tdef3 herein is a standby time for maintaining the opening degree holding state of step ST3.
  • step ST5 When the defrosting prioritizing condition is satisfied during the process of step ST3, the sequence transitions to the process of step ST5, the opening degrees of the indoor expansion valves 41a, 41b are reduced (by an opening degree ⁇ MVrd3 herein), the opening degree of the outdoor expansion valve 24 is increased (by an opening degree ⁇ MVod3 herein), and the sequence returns to the process of step ST3. Determining whether or not the defrosting prioritizing condition is satisfied and/or deciding the opening degrees of the indoor expansion valves 41a, 41b and the opening degree of the outdoor expansion valve 24 herein is done by the outdoor-side control part 38, as described above.
  • the opening degrees of the indoor expansion valves 41a, 41b are appropriately decided herein on the basis of the outdoor heat exchange outlet temperature Tol2.
  • step ST5 By repeating this process of step ST3, the defrosting prioritizing condition determination, and step ST5, it is possible to make a transition from an operation prioritizing air-warming to an operation prioritizing defrosting by reducing the opening degrees of the indoor expansion valves 41a, 41b and increasing the opening degree of the outdoor expansion valve 24 to reduce the air-warming capabilities of the indoor heat exchangers 42a, 42b and increase the defrosting capability of the outdoor heat exchanger 23, after the first defrosting time taj has elapsed from the start of the defrosting operation the start of the defrosting operation as shown in FIG. 9 .
  • the defrosting operation (including an operation prioritizing air-warming and/or an operation prioritizing defrosting), having transitioned from step ST2 to step ST3, returns to the process of step ST1, the opening degrees of the indoor expansion valves 41a, 41b are returned to the initial opening degree MVrd1 for the defrosting operation, and the opening degree of the outdoor expansion valve 24 is returned to the initial opening degree MVod1 for the defrosting operation.
  • the opening degrees of the indoor expansion valves 41a, 41b decrease more rapidly and the opening degree of the outdoor expansion valve 24 increases more rapidly than when the opening degrees of the indoor expansion valves 41a, 41b and the opening degree of the outdoor expansion valve 24 are altered by the process of steps ST4 and ST5, an operation prioritizing defrosting is therefore promoted even further until the defrosting operation is ended either by the outdoor heat exchange outlet temperature Tol2 being equal to or greater than a predetermined defrosting operation ending temperature Tdefe or by a predetermined defrosting operation ending time tdefe elapsing, and defrosting of the outdoor heat exchanger 23 can be reliably ended.
  • the time required for defrosting is affected by heat radiation loss from the heat storage medium and/or the devices constituting the refrigerant circuit 10, and this time therefore tends to be longer as the outdoor temperature Ta is lower. Therefore, the first defrosting time taj, which is the time during which an operation prioritizing air-warming is performed, is also preferably decided on the basis of the outdoor temperature Ta.
  • the first defrosting time taj is designed herein to be decided on the basis of the outdoor temperature Ta.
  • the second defrosting time tah is decided as a function of the outdoor temperature Ta, such as the function shown in the following formula 1.
  • tah Ta + tah 0
  • the value tah herein is a standard value of the second defrosting time tah. According to formula 1, the second defrosting time tah is shorter as the outdoor temperature Ta is lower.
  • the first defrosting time taj is then decided using the second defrosting time tah decided by formula 1, and the following formula 2.
  • taj tah ⁇ tah 1
  • the value tah1 herein is equivalent to the time for performing an operation prioritizing defrosting by means of steps ST3 and ST5 described above.
  • the first defrosting time taj is shorter as the outdoor temperature Ta is lower.
  • the defrosting operation thereby has a shorter time for an operation prioritizing air-warming by means of steps ST3 and ST4 described above.
  • the first defrosting time taj for performing an operation prioritizing air-warming is thereby decided herein on the basis of the outdoor temperature Ta, whereby a longer operation prioritizing defrosting is performed, and the defrosting of the outdoor heat exchanger 23 can be reliably ended.
  • the first defrosting time taj and the second defrosting time tah are both herein decided on the basis of the outdoor temperature Ta, but it is also possible for the first defrosting time taj alone to be decided on the basis of the outdoor temperature Ta.
  • the air-warming operation is performed during the defrosting operation accompanying the heat-storage-utilizing operation.
  • the refrigerant in the outlets of the indoor heat exchangers 42a, 42b readily reaches the gas-liquid two-phase state.
  • Refrigerant in a gas state then readily fills the refrigerant pipes (such as the liquid refrigerant communication pipe 6 herein) connecting the outlet sides (liquid sides) of the indoor heat exchangers 42a, 42b and the inlet side (liquid side) of the heat storage heat exchanger 28 functioning as an evaporator of the refrigerant.
  • the outdoor-side control part 38 herein is designed to determine, on the basis of the degree of superheating SHd of the refrigerant discharged from the compressor 21, that liquid backflow is occurring due to the opening degrees of the indoor expansion valves 41a, 41b being too large.
  • the degree of superheating SHd of the refrigerant discharged from the compressor 21 is calculated herein from the discharge pressure Pd detected by the discharge pressure sensor 32 and the discharge temperature Td detected by the discharge temperature sensor 34. More specifically, the discharge pressure Pd is first converted to a refrigerant saturation temperature to obtain the condensation temperature Tc. The degree of superheating SHd is then found by subtracting the condensation temperature Tc from the discharge temperature Td.
  • the outdoor-side control part 38 determines that liquid backflow is occurring when the degree of superheating SHd is lower than a threshold degree of superheating during the above-described defrosting operation control, as shown in FIG. 10 .
  • the opening degrees of the indoor expansion valves 41a, 41b are reduced as necessary.
  • a further condition that the degree of superheating SHd be equal to or greater than a first threshold degree of superheating SHd1 is added as the condition for transitioning from step ST1 to step ST2.
  • step ST1 when a predetermined time tdef4 (a standby time from the start of the defrosting operation until the transition to the next process) has elapsed from the start of the defrosting operation and the degree of superheating SHd is less than a predetermined third threshold degree of superheating SHd3, it is determined that liquid backflow is occurring in the compressor 21 and the sequence transitions to the process of step ST6.
  • the third threshold degree of superheating SHd3 herein is set to a value lower than the first threshold degree of superheating SHd1.
  • step ST6 the opening degrees of the indoor expansion valves 41a, 41b are set to a liquid-backflow-eliminating opening degree MVrd4 (an opening degree less than the initial opening degree MVrd1), and the opening degree of the outdoor expansion valve 24 is set to a liquid-backflow-eliminating opening degree MVod4 (herein the same opening degree as the initial opening degree MVod1).
  • MVrd4 an opening degree less than the initial opening degree MVrd1
  • MVod4 a liquid-backflow-eliminating opening degree MVod4
  • step ST1 the sequence returns again to the process of step ST1, or in other words to a state in which the opening degrees of the indoor expansion valves 41a, 41b have been set to the initial opening degree MVrd1 and the opening degree of the outdoor expansion valve 24 has been set to the initial opening degree MVod1.
  • steps ST2 to ST5 it is determined that liquid backflow is occurring in the compressor 21 when the degree of superheating SHd is less than a predetermined second threshold degree of superheating SHd2, the process of steps ST2 to ST5 is terminated even if the second defrosting time tah has not elapsed from the start of the defrosting operation, and the sequence returns to the process of step ST1, or in other words to a state in which the opening degrees of the indoor expansion valves 41a, 41b have been set to the initial opening degree MVrd1 and the opening degree of the outdoor expansion valve 24 has been set to the initial opening degree MVod1.
  • the liquid backflow in the compressor 21 is thereby eliminated.
  • the present invention can be widely applied to air conditioning apparatuses comprising a refrigerant circuit having a heat storage heat exchanger for performing heat exchange between a refrigerant and a heat storage medium, wherein a heat storage operation for storing heat in the heat storage medium can be performed by causing the heat storage heat exchanger to function as a heat radiator of the refrigerant, and an air-warming operation and a heat-storage-utilizing operation for radiating heat from the heat storage medium can be performed simultaneously by causing the heat storage heat exchanger to function as an evaporator of the refrigerant during a defrosting operation.
  • Patent Literature 1 Japanese Laid-open Patent Application No. 2005-337657

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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)

Claims (5)

  1. Klimatisierungsvorrichtung (1), die einen Kältemittelkreislauf (10) aufweist, der einen Verdichter (21), einen Außenwärmetauscher (23), Innenwärmetauscher (42a, 42b) und einen Wärmespeicher-Wärmetauscher (28) zum Durchführen eines Wärmetauschs zwischen einem Kältemittel und einem Wärmespeichermedium aufweist, wobei die Klimatisierungsvorrichtung konfiguriert ist, einen Wärmespeicherbetrieb zum Speichern von Wärme im Wärmespeichermedium durchzuführen, indem bewirkt wird, dass der Wärmespeicher-Wärmetauscher als ein Wärmeradiator des Kältemittels dient, und indem während eines Entfrostungsbetriebs zum Entfrosten des Außenwärmetauschers bewirkt wird, dass der Außenwärmetauscher als ein Wärmeradiator des Kältemittels dient, gleichzeitig einen Wärmespeichernutzungsbetrieb zum Abstrahlen von Wärme aus dem Wärmespeichermedium, indem bewirkt wird, dass der Wärmespeicher-Wärmetauscher als ein Verdampfer des Kältemittels dient, und einen Lufterwärmungsbetrieb durchzuführen, um zu bewirken, dass die Innenwärmetauscher als Wärmeradiatoren des Kältemittels deinen; wobei der Kältemittelkreislauf außerdem Innenexpansionsventile (41a, 41b) zum Verändern des Durchflusses des Kältemittels, das durch die Innenwärmetauscher fließt, und ein Außenexpansionsventil (24) zum Verändern des Durchflusses des Kältemittels aufweist, das durch den Außenwärmetauscher fließt;
    die Innenwärmetauscher und die Innenexpansionsventile für Inneneinheiten (4a, 4b) vorgesehen sind; und
    der Außenwärmetauscher und das Außenexpansionsventil für eine Außeneinheit (2) vorgesehen sind;
    dadurch gekennzeichnet, dass
    die Inneneinheiten Innenseiten-Steuerteile (48a, 48b) aufweisen zum Festlegen der Öffnungsgrade der Innenexpansionsventile, wenn nur der Lufterwärmungsbetrieb durchgeführt wird; und
    die Außeneinheit ein Außenseiten-Steuerteil (38) zum Festlegen des Öffnungsgrads des Außenexpansionsventils, wenn nur der Lufterwärmungsbetrieb durchgeführt wird, und zum Festlegen der Öffnungsgrade der Innenexpansionsventile und des Öffnungsgrads des Außenexpansionsventils aufweist, wenn der Lufterwärmungsbetrieb während des Entfrostungsbetriebs durchgeführt wird, der mit dem Wärmespeichernutzungsbetrieb einhergeht;
    wenn der Lufterwärmungsbetrieb während des Entfrostungsbetriebs durchgeführt wird, der mit dem Wärmespeichernutzungsbetrieb einhergeht, die Öffnungsgrade der Innenexpansionsventile (41a, 41b) durch den Außenseiten-Steuerteil (38) auf der Grundlage der Korrelation zwischen der Kondensationstemperatur des Kältemittels im Kältemittelkreislauf (10) und den Innentemperaturen der Räume festgelegt werden, die durch die Inneneinheiten (4a, 4b) klimatisiert werden, bis eine erste Entfrostungszeit (taj) vom Beginn des Entfrostungsbetriebs verstreicht.
  2. Klimatisierungsvorrichtung (1) nach Anspruch 1, wobei
    wenn die Kondensationstemperatur niedriger als eine Schwellentemperatur ist, die aus den Innentemperaturen erhalten wird, das Außenseiten-Steuerteil (38) konfiguriert ist festzustellen, dass die Lufterwärmungsfähigkeiten der Innenwärmetauscher (42a, 42b) nicht sichergestellt sind, und die Öffnungsgrade der Innenexpansionsventile (41a, 41b) zu erhöhen, so dass die Lufterwärmungsfähigkeiten der Innenwärmetauscher (42a, 42b) sichergestellt werden.
  3. Klimatisierungsvorrichtung (1) nach Anspruch 1 oder 2, wobei
    nachdem die erste Entfrostungszeit vom Beginn des Entfrostungsbetriebs verstrichen ist, die Öffnungsgrade der Innenexpansionsventile (41a, 41b) und des Außenexpansionsventils (24) durch den Außenseiten-Steuerteil (38) so geändert werden, dass die Lufterwärmungsfähigkeiten der Innenwärmetauscher (42a, 42b) abnehmen und die Entfrostungsfähigkeit des Außenwärmetauschers (23) zunimmt.
  4. Klimatisierungsvorrichtung (1) nach Anspruch 1, 2 oder 3, wobei
    die erste Entfrostungszeit auf der Grundlage der Außentemperatur des Außenraums festgelegt wird, wo die Außeneinheit (2) angeordnet ist.
  5. Klimatisierungsvorrichtung (1) nach einem der Ansprüche 1 bis 4, wobei
    während des Entfrostungsbetriebs auf der Grundlage des Grads der Überhitzung des Kältemittels, das aus dem Verdichter (21) ausgestoßen wird, festgestellt wird, ob die Öffnungsgrade der Innenexpansionsventile (41a, 41b) zu groß sind.
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JP6248878B2 (ja) * 2014-09-18 2017-12-20 株式会社富士通ゼネラル 空気調和装置
JP6007965B2 (ja) * 2014-12-15 2016-10-19 ダイキン工業株式会社 空気調和装置
US10443901B2 (en) * 2015-04-30 2019-10-15 Daikin Industries, Ltd. Indoor unit of air conditioner
CN104949265B (zh) * 2015-06-03 2018-09-07 广东美的暖通设备有限公司 空调系统及空调系统的能源管理方法
JP6808812B2 (ja) * 2017-03-24 2021-01-06 東芝キヤリア株式会社 空気調和装置
JP2019020081A (ja) * 2017-07-20 2019-02-07 三菱重工サーマルシステムズ株式会社 空気調和装置及びその運転方法
CN108131858B (zh) * 2017-11-08 2019-08-27 珠海格力电器股份有限公司 一种热泵空调系统及其控制方法
CN111615608B (zh) * 2018-02-19 2022-04-05 大金工业株式会社 空调装置
CN114450545B (zh) 2019-09-26 2023-11-10 大金工业株式会社 固态制冷装置
CN113375376A (zh) * 2020-03-10 2021-09-10 开利公司 集成热泵系统及其控制方法
WO2021214931A1 (ja) * 2020-04-23 2021-10-28 日立ジョンソンコントロールズ空調株式会社 空気調和システムおよび制御方法
CN112050498B (zh) * 2020-09-16 2022-02-18 浙江正理生能科技有限公司 一种热泵机组化霜方法
JP7537489B2 (ja) 2022-12-19 2024-08-21 株式会社富士通ゼネラル 空気調和機

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2503659B2 (ja) * 1989-06-23 1996-06-05 ダイキン工業株式会社 蓄熱式空気調和装置
JP2503660B2 (ja) * 1989-06-23 1996-06-05 ダイキン工業株式会社 蓄熱式空気調和装置
JP3277665B2 (ja) * 1993-12-29 2002-04-22 ダイキン工業株式会社 空気調和機
KR101003356B1 (ko) * 2003-10-21 2010-12-23 삼성전자주식회사 공기 조화기 및 그 제어방법
JP4367236B2 (ja) 2004-05-31 2009-11-18 ダイキン工業株式会社 空気調和装置
JP2007010288A (ja) * 2005-07-04 2007-01-18 Jfe Engineering Kk 既設ヒートポンプ式空調装置の冷暖房能力増強方法、蓄熱ユニット装置および該装置を用いたヒートポンプ式空調装置
JP5125124B2 (ja) * 2007-01-31 2013-01-23 ダイキン工業株式会社 冷凍装置
JP4245064B2 (ja) * 2007-05-30 2009-03-25 ダイキン工業株式会社 空気調和装置
JP5634682B2 (ja) * 2009-04-24 2014-12-03 日立アプライアンス株式会社 空気調和機
JP5517131B2 (ja) * 2010-11-29 2014-06-11 日立アプライアンス株式会社 蓄熱式空気調和装置
JP5418622B2 (ja) * 2012-02-20 2014-02-19 ダイキン工業株式会社 冷凍装置

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None *

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JPWO2014061134A1 (ja) 2016-09-05
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WO2014061134A1 (ja) 2014-04-24
EP2863153A1 (de) 2015-04-22

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