EP2801770A1 - Kühlvorrichtung - Google Patents

Kühlvorrichtung Download PDF

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Publication number
EP2801770A1
EP2801770A1 EP12859176.5A EP12859176A EP2801770A1 EP 2801770 A1 EP2801770 A1 EP 2801770A1 EP 12859176 A EP12859176 A EP 12859176A EP 2801770 A1 EP2801770 A1 EP 2801770A1
Authority
EP
European Patent Office
Prior art keywords
refrigerant
heat exchanger
expansion mechanism
outdoor heat
compressor
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.)
Granted
Application number
EP12859176.5A
Other languages
English (en)
French (fr)
Other versions
EP2801770B1 (de
EP2801770A4 (de
Inventor
Takayuki Setoguchi
Keisuke Tanimoto
Noriyuki Okuda
Takamune Okui
Junichi Shimoda
Tsuyoshi Yamada
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 Industries Ltd
Original Assignee
Daikin Industries Ltd
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Filing date
Publication date
Application filed by Daikin Industries Ltd filed Critical Daikin Industries Ltd
Publication of EP2801770A1 publication Critical patent/EP2801770A1/de
Publication of EP2801770A4 publication Critical patent/EP2801770A4/de
Application granted granted Critical
Publication of EP2801770B1 publication Critical patent/EP2801770B1/de
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B13/00—Compression machines, plants or systems, with reversible cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B29/00—Combined heating and refrigeration systems, e.g. operating alternately or simultaneously
    • F25B29/003—Combined heating and refrigeration systems, e.g. operating alternately or simultaneously of the compression type system
    • 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
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/005—Compression machines, plants or systems with non-reversible cycle of the single unit type
    • 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
    • F25B39/00—Evaporators; Condensers
    • 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
    • F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
    • F25B2313/02741—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using one four-way valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/031—Sensor arrangements
    • F25B2313/0314—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
    • 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
    • F25B2400/12—Inflammable refrigerants
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/13—Economisers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • 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
    • F25B2400/23—Separators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/39—Dispositions with two or more expansion means arranged in series, i.e. multi-stage expansion, on a refrigerant line leading to the same evaporator

Definitions

  • the present invention relates to a refrigeration apparatus, and particularly relates to a refrigeration apparatus capable of performing a cooling operation and a heating operation.
  • refrigerant that cannot be accommodated by the indoor heat exchanger during the air-warming operation is temporarily stored in a refrigerant storage tank or the like connected to an intake side of a compressor.
  • An object of the present invention is to provide a refrigeration apparatus capable of performing a cooling operation and a heating operation, wherein the excess refrigerant produced during the cooling operation can be accommodated when the capacity of the outdoor heat exchanger is equal to or less than the capacity of the indoor heat exchanger.
  • a refrigeration apparatus is a refrigeration apparatus in which a refrigerant flows sequentially through a compressor, an outdoor heat exchanger, expansion mechanisms, and an indoor heat exchanger during a cooling operation, and the refrigerant flows sequentially through the compressor, the indoor heat exchanger, the expansion mechanisms, and the outdoor heat exchanger during a heating operation.
  • the indoor heat exchanger is a cross-fin type heat exchanger and the outdoor heat exchanger is a stacked heat exchanger.
  • the expansion mechanisms include an upstream-side expansion mechanism for depressurizing the refrigerant and a downstream-side expansion mechanism for depressurizing the refrigerant that has been depressurized in the upstream-side expansion mechanism, and a refrigerant storage tank for storing the refrigerant depressurized by the upstream-side expansion mechanism is provided between the upstream-side expansion mechanism and the downstream-side expansion mechanism.
  • a capacity of a stacked heat exchanger is less than a capacity of a cross-fin type heat exchanger having similar heat exchange performance.
  • the capacity of this stacked outdoor heat exchanger will then not only be less than the capacity of a cross-fin type outdoor heat exchanger, but will also be less than the capacity of the cross-fin type indoor heat exchanger connected thereto.
  • the refrigerant storage tank for storing the refrigerant depressurized by the upstream-side expansion mechanism is provided between the upstream-side expansion mechanism and the downstream-side expansion mechanism, and the excess refrigerant that could not be accommodated in the outdoor heat exchanger during the cooling operation is thereby accommodated in the refrigerant storage tank positioned in the vicinity of the downstream side of the outdoor heat exchanger.
  • a refrigeration apparatus is a refrigeration apparatus in which a refrigerant flows sequentially through a compressor, an outdoor heat exchanger, expansion mechanisms, and an indoor heat exchanger during a cooling operation, and refrigerant flows sequentially through the compressor, the indoor heat exchanger, the expansion mechanisms, and the outdoor heat exchanger during a heating operation.
  • a capacity of the outdoor heat exchanger is 100% or less of a capacity of the indoor heat exchanger.
  • the expansion mechanisms include an upstream-side expansion mechanism for depressurizing the refrigerant and a downstream-side expansion mechanism for depressurizing the refrigerant that has been depressurized in the upstream-side expansion mechanism, and a refrigerant storage tank for storing the refrigerant depressurized by the upstream-side expansion mechanism is provided between the upstream-side expansion mechanism and the downstream-side expansion mechanism.
  • the refrigerant storage tank for storing the refrigerant depressurized by the upstream-side expansion mechanism is provided between the upstream-side expansion mechanism and the downstream-side expansion mechanism, and the excess refrigerant that could not be accommodated in the outdoor heat exchanger during the cooling operation is thereby accommodated in the refrigerant storage tank positioned in the vicinity of the downstream side of the outdoor heat exchanger.
  • a refrigeration apparatus is the refrigeration apparatus according to the first or second aspect, wherein the refrigerant is R32.
  • R32 When R32 is used as the refrigerant in the refrigeration apparatus, a refrigerator oil sealed with the refrigerant in order to lubricate the compressor tends to have extremely low solubility in low-temperature conditions. Therefore, at a low pressure in the refrigeration cycle, the solubility of the refrigerator oil greatly decreases due to the decrease in a refrigerant temperature.
  • R32 is used as the refrigerant in a conventional refrigeration apparatus having the refrigerant storage tank on the intake side of the compressor, for example, the refrigerant and the refrigerator oil separate into two layers in the refrigerant storage tank which has a low pressure in the refrigeration cycle, and the refrigerator oil has difficulty returning to the compressor.
  • the refrigerator oil returns more readily to the compressor, in comparison to cases in which the refrigerant storage tank is provided to the intake side of the compressor.
  • a refrigeration apparatus is the refrigeration apparatus according to any of the first through third aspects, wherein the outdoor heat exchanger is a stacked heat exchanger having a plurality of flat tubes arrayed so as to be superposed set apart by gaps, and fins sandwiched between the adjacent flat tubes.
  • the refrigerant quantity in the refrigeration apparatus is reduced because the capacity of the outdoor heat exchanger is equal to or less than the capacity of the indoor heat exchanger.
  • the excess refrigerant is produced during the cooling operation in this refrigeration apparatus, but because this excess refrigerant can be accommodated in the refrigerant storage tank, hindrances to the refrigerant control can be prevented.
  • a refrigeration apparatus is the refrigeration apparatus according to any of the first through third aspects, wherein the outdoor heat exchanger is a stacked heat exchanger having a plurality of flat tubes arrayed so as to be superposed set apart by gaps, and fins having notches formed therein where the flat tubes are inserted.
  • the refrigerant quantity in the refrigeration apparatus is reduced because the capacity of the outdoor heat exchanger is equal to or less than the capacity of the indoor heat exchanger.
  • the excess refrigerant is produced during the cooling operation in this refrigeration apparatus, but because this excess refrigerant can be accommodated in the refrigerant storage tank, hindrances to the refrigerant control can be prevented.
  • a refrigeration apparatus is the refrigeration apparatus according to any of the first through third aspects, wherein the outdoor heat exchanger is a stacked heat exchanger having flat tubes molded into serpentine shapes, and fins inserted between mutually adjacent surfaces of the flat tubes.
  • the refrigerant quantity in the refrigeration apparatus is reduced because the capacity of the outdoor heat exchanger is equal to or less than the capacity of the indoor heat exchanger.
  • the excess refrigerant is produced during the cooling operation in this refrigeration apparatus, but because this excess refrigerant can be accommodated in the refrigerant storage tank, hindrances to the refrigerant control can be prevented.
  • a refrigeration apparatus is the refrigeration apparatus according to the second aspect, wherein the refrigerant is R32.
  • R32 When R32 is used as the refrigerant in the refrigeration apparatus, a refrigerator oil sealed with the refrigerant in order to lubricate the compressor tends to have extremely low solubility in low-temperature conditions. Therefore, at a low pressure in the refrigeration cycle, the solubility of the refrigerator oil greatly decreases due to the decrease in a refrigerant temperature.
  • R32 is used as the refrigerant in a conventional refrigeration apparatus having the refrigerant storage tank on the intake side of the compressor, for example, the refrigerant and the refrigerator oil separate into two layers in the refrigerant storage tank which has a low pressure in the refrigeration cycle, and the refrigerator oil has difficulty returning to the compressor.
  • the refrigerator oil returns more readily to the compressor, in comparison to cases in which the refrigerant storage tank is provided to the intake side of the compressor.
  • a refrigeration apparatus is the refrigeration apparatus according to the second or seventh aspect, wherein the outdoor heat exchanger and the indoor heat exchanger are cross-fin type heat exchangers, and a diameter of heat transfer tubes in the outdoor heat exchanger is designed to be less than a diameter of heat transfer tubes in the indoor heat exchanger.
  • the refrigerant quantity in the refrigeration apparatus is reduced because the capacity of the outdoor heat exchanger is equal to or less than the capacity of the indoor heat exchanger.
  • the excess refrigerant is produced during the cooling operation in this refrigeration apparatus, but because this excess refrigerant can be accommodated in the refrigerant storage tank, hindrances to the refrigerant control can be prevented.
  • a refrigeration apparatus is the refrigeration apparatus according to any of the first through eighth aspects, further provided with a bypass tube for leading a gas component of the refrigerant accumulated in the refrigerant storage tank to the compressor or to a refrigerant tube on an intake side of the compressor.
  • the refrigerant depressurized in the upstream-side expansion mechanism is separated into a liquid component and the gas component in the refrigerant storage tank, and the gas component heads toward the bypass tube.
  • the gas component which does not contribute to evaporation, thereby ceases to flow into the outdoor heat exchanger functioning as an evaporator of the refrigerant during the heating operation in this refrigeration apparatus, it is therefore possible to proportionately reduce the flow rate of the refrigerant flowing through the outdoor heat exchanger functioning as an evaporator of the refrigerant, and a depressurization loss in the refrigeration cycle can be reduced.
  • a refrigeration apparatus is the refrigeration apparatus according to the ninth aspect, wherein the bypass tube has a flow rate adjustment mechanism.
  • the refrigerant that has passed through the flow rate adjustment mechanism converges with the refrigerant which has evaporated in the outdoor heat exchanger, and then heads to the compressor or the intake tube of the compressor.
  • the flow rate adjustment mechanism is an electric expansion valve
  • the state of the refrigerant just before being drawn into the compressor can be adjusted more optimally by controlling the valve opening degree.
  • the refrigerant circulation flow rate i.e. the flow rate of the refrigerant flowing through the indoor heat exchanger can be controlled according to the refrigeration load on the indoor heat exchanger side.
  • a refrigeration apparatus is the refrigeration apparatus according to any of the first through tenth aspects, wherein the refrigerant storage tank is a gas-liquid separator.
  • the refrigerant storage tank composed of the gas-liquid separator has both a function of accumulating a liquid component and a function of separating the liquid component and a gas component.
  • FIG. 1 is a schematic configuration diagram of an air-conditioning apparatus 1 as a refrigeration apparatus according to an embodiment of the present invention.
  • the air-conditioning apparatus 1 is a refrigeration apparatus capable of performing an air-cooling operation as a cooling operation and an air-warming operation as a heating operation by performing a vapor-compression refrigeration cycle.
  • the air-conditioning apparatus 1 is configured primarily from the connection between an outdoor unit 2 and an indoor unit 4.
  • the outdoor unit 2 and the indoor unit 4 are connected via a liquid refrigerant communication tube 5 and a gas refrigerant communication tube 6.
  • a vapor-compression refrigerant circuit 10 of the air-conditioning apparatus 1 is configured from the connection between the outdoor unit 2 and the indoor unit 4 via the refrigerant communication tubes 5, 6.
  • the indoor unit 4 which is installed inside a room, constitutes part of the refrigerant circuit 10.
  • the indoor unit 4 primarily has an indoor heat exchanger 41.
  • the indoor heat exchanger 41 is a heat exchanger that functions as an evaporator of refrigerant to cool indoor air during the air-cooling operation, and functions as a heat radiator of refrigerant during the air-warming operation to heat indoor air.
  • a liquid side of the indoor heat exchanger 41 is connected to the liquid refrigerant communication tube 5, and a gas side of the indoor heat exchanger 41 is connected to the gas refrigerant communication tube 6.
  • the indoor heat exchanger 41 which is a cross-fin type heat exchanger, has primarily heat transfer fins 411 and heat transfer tubes 412, as shown in FIG. 2.
  • FIG. 2 is a front view of the indoor heat exchanger 41.
  • the heat transfer fins 411 are thin aluminum flat plates, and pluralities of through-holes are formed in the heat transfer fins 411.
  • the heat transfer tubes 412 have straight tubes 412a inserted through the through-holes of the heat transfer fins 411, and U-shaped tubes 412b, 412c linking the ends of adjacent straight tubes 412a together.
  • the straight tubes 412a are firmly adhered to the heat transfer fins 411 by undergoing an expanding process after being inserted through the through-holes of the heat transfer fins 411.
  • the straight tubes 412a and the first U-shaped tubes 412b are formed integrally, and the second U-shaped tubes 412c are linked to the ends of the straight tubes 412a by welding, soldering, or the like, after being inserted through the through-holes of the heat transfer fins 411 and undergoing the expanding process.
  • the indoor unit 4 also has an indoor fan 42 for drawing indoor air into the indoor unit 4 and supplying the air back into the room as supplied air after the air has exchanged heat with the refrigerant in the indoor heat exchanger 41.
  • the indoor fan 42 is a centrifugal fan, a multi-blade fan, or the like driven by an indoor fan motor 43.
  • the indoor unit 4 has an indoor-side control part 44 for controlling the actions of the components constituting the indoor unit 4.
  • the indoor-side control part 44 which has a microcomputer, a memory, and the like for performing control on the indoor unit 4, is designed to be capable of exchanging control signals and the like with a remote controller (not shown), and also of exchanging control signals and the like with the outdoor unit 2 via a transmission line 8a.
  • the outdoor unit 2 which is installed outside of the room, constitutes part of the refrigerant circuit 10.
  • the outdoor unit 2 has primarily a compressor 21, a switching mechanism 22, an outdoor heat exchanger 23, a first expansion mechanism 24, a refrigerant storage tank 25, a second expansion mechanism 26, a liquid-side shutoff valve 27, and a gas-side shutoff valve 28.
  • the compressor 21 is a device for compressing low-pressure refrigerant in the refrigeration cycle to a high pressure.
  • the compressor 21 has a sealed structure in which a rotary, scroll, or other type of displacement compression element (not shown) is rotatably driven by a compressor motor 21 a controlled by an inverter.
  • An intake tube 31 is connected to the intake side of the compressor 21, and a discharge tube 32 is connected to the discharge side.
  • the intake tube 31 is a refrigerant tube connecting the intake side of the compressor 21 and a first port 22a of the switching mechanism 22.
  • An accumulator 29 is provided to the intake tube 31.
  • the discharge tube 32 is a refrigerant tube connecting the discharge side of the compressor 21 and a second port 22b of the switching mechanism 22.
  • the switching mechanism 22 is a mechanism for switching the direction of refrigerant flow in the refrigerant circuit 10.
  • the switching mechanism 22 performs a switch that causes the outdoor heat exchanger 23 to function as a heat radiator of refrigerant compressed in the compressor 21, and causes the indoor heat exchanger 41 to function as an evaporator of refrigerant that has radiated heat in the outdoor heat exchanger 23.
  • the switching mechanism 22 performs a switch that interconnects the second port 22b and a third port 22c, and interconnects the first port 22a and a fourth port 22d.
  • the discharge side of the compressor 21 (the discharge tube 32 herein) and the gas side of the outdoor heat exchanger 23 (a first gas refrigerant tube 33 herein) are thereby connected (refer to the solid lines of the switching mechanism 22 in FIG. 1 ).
  • the intake side of the compressor 21 (the intake tube 31 herein) and the gas refrigerant communication tube 6 side (a second gas refrigerant tube 34 herein) are connected (refer to the solid lines of the switching mechanism 22 in FIG. 1 ).
  • the switching mechanism 22 performs a switch that causes the outdoor heat exchanger 23 to function as an evaporator of refrigerant that has radiated heat in the indoor heat exchanger 41, and causes the indoor heat exchanger 41 to function as a heat radiator of refrigerant that has been compressed in the compressor 21. Specifically, during the air-warming operation, the switching mechanism 22 performs a switch that interconnects the second port 22b and the fourth port 22d, and interconnects the first port 22a and the third port 22c.
  • the discharge side of the compressor 21 (the discharge tube 32 herein) and the gas refrigerant communication tube 6 side (the second gas refrigerant tube 34 herein) are thereby connected (refer to the dashed lines of the switching mechanism 22 in FIG. 1 ).
  • the intake side of the compressor 21 (the intake tube 31 herein) and the gas side of the outdoor heat exchanger 23 (the first gas refrigerant tube 33 herein) are connected (refer to the dashed lines of the switching mechanism 22 in FIG. 1 ).
  • the first gas refrigerant tube 33 is a refrigerant tube connecting the third port 22c of the switching mechanism 22 and the gas side of the outdoor heat exchanger 23.
  • the second gas refrigerant tube 34 is a refrigerant tube connecting the fourth port 22d of the switching mechanism 22 and the gas refrigerant communication tube 6 side.
  • the switching mechanism 22 herein is a four-way switching valve.
  • the outdoor heat exchanger 23 is a heat exchanger that functions as a heat radiator of refrigerant that uses outdoor air as a cooling source during the air-cooling operation, and functions as an evaporator of refrigerant that uses outdoor air as a heating source during the air-warming operation.
  • the liquid side of the outdoor heat exchanger 23 is connected to a liquid refrigerant tube 35, and the gas side is connected to the first gas refrigerant tube 33.
  • the liquid refrigerant tube 35 is a refrigerant tube connecting the liquid side of the outdoor heat exchanger 23 and the liquid refrigerant communication tube 5 side.
  • the outdoor heat exchanger 23 which is a stacked heat exchanger, has primarily flat tubes 231, corrugated fins 232, and headers 233a, 233b, as shown in FIG. 3.
  • FIG. 3 is an external perspective view of the outdoor heat exchanger 23.
  • the flat tubes 231 which are molded from aluminum or an aluminum alloy, have flat surface parts 231a that serve as heat transfer surfaces and a plurality of internal flow channels (not shown) through which refrigerant flows.
  • the flat tubes 231 are arrayed in multiple levels so as to be superposed set apart by gaps (air passage spaces) with the flat surface parts 231a being made to face up and down.
  • the corrugated fins 232 are fins made of aluminum or an aluminum alloy, bent into a corrugated formation.
  • the corrugated fins 232 are disposed in air passage spaces enclosed between vertically adjacent flat tubes 231, and the troughs and peaks thereof are in contact with the flat surface parts 231 a of the flat tubes 231.
  • the troughs, peaks, and flat surface parts 231a are bonded by soldering or the like.
  • the headers 233a, 233b are linked to the ends of the flat tubes 231 arrayed in multiple levels in the vertical direction.
  • the headers 233a, 233b have the function of supporting the flat tubes 231, the function of leading refrigerant into the internal flow channels of the flat tubes 231, and the function of collecting refrigerant coming out of the internal flow channels.
  • refrigerant flowing in through a first inlet/outlet 234 of the first header 233a is distributed mostly equally to the internal flow channels of the topmost flat tube 231, and the refrigerant flows toward the second header 233b.
  • the refrigerant is distributed mostly equally to the internal flow channels of the second highest flat tube 231, and the refrigerant flows toward the first header 233a.
  • the refrigerant in the flat tubes 231 of odd-numbered levels flows toward the second header 233b, and the refrigerant in the flat tubes 231 of even-numbered levels flows toward the first header 233a.
  • the refrigerant in the bottommost and even-numbered level flat tubes 231 flows toward the first header 233a, collects in the first header 233a, and flows out through a second inlet/outlet 235 of the first header 233a.
  • refrigerant flows in through the second inlet/outlet 235 of the first header 233a, and after flowing through the flat tubes 231 and the headers 233a, 233b in the opposite direction of when the outdoor heat exchanger functions as a heat radiator of refrigerant, the refrigerant flows out through the first inlet/outlet 234 of the first header 233a.
  • the refrigerant flowing in the flat tubes 231 radiates heat to the air flow passing through the air passage spaces via the corrugated fins 232.
  • the outdoor heat exchanger 23 functions as an evaporator of refrigerant
  • the refrigerant flowing in the flat tubes 231 absorbs heat from the air flow passing through the air passage spaces via the corrugated fins 232. Due to a stacked heat exchanger such as the one described above being used as the outdoor heat exchanger 23, the capacity of the outdoor heat exchanger 23 is less than the capacity of the indoor heat exchanger 41. This point is described using FIG. 4 , giving a package air-conditioner as an example.
  • FIG. 4 giving a package air-conditioner as an example.
  • the symbol ⁇ represents a normal type (a cross-fin type outdoor heat exchanger) of a package air-conditioner
  • the symbol ⁇ represents a small diameter type of outdoor heat exchanger (a stacked outdoor heat exchanger) of a package air-conditioner
  • the symbol ⁇ represents a normal type (a cross-fin type outdoor heat exchanger) of a room air-conditioner
  • the symbol ⁇ represents a small diameter type of outdoor heat exchanger (a stacked outdoor heat exchanger) of a room air-conditioner.
  • the outdoor heat exchanger capacity/indoor heat exchanger capacity ratio is less than 1.0 when only the outdoor heat exchanger is changed to a stacked heat exchanger having a similar heat exchange performance, in contrast to when the outdoor heat exchanger and the indoor heat exchanger are both cross-fin type heat exchangers.
  • the refrigerant storage tank 25 for accommodating excess refrigerant is preferably used when the outdoor heat exchanger capacity/indoor heat exchanger capacity ratio is 0.3 to 0.9, but stable refrigerant control is made possible by using the refrigerant storage tank 25 also when the outdoor heat exchanger capacity/indoor heat exchanger capacity ratio is 1.0.
  • the first expansion mechanism 24 functions as an upstream-side expansion mechanism for depressurizing the refrigerant that has radiated heat in the outdoor heat exchanger 23 to an intermediate pressure in the refrigeration cycle, and during the air-warming operation, the first expansion mechanism 24 functions as a downstream-side expansion mechanism for depressurizing the refrigerant temporarily stored in the refrigerant storage tank 25 to a low pressure in the refrigeration cycle after the refrigerant has been depressurized in the second expansion mechanism 26 as an upstream-side expansion mechanism.
  • the first expansion mechanism 24 is provided to a portion near the outdoor heat exchanger 23 in the liquid refrigerant tube 35.
  • An electric expansion valve is used herein as the first expansion mechanism 24.
  • the second expansion mechanism 26 functions as a downstream-side expansion mechanism for depressurizing the refrigerant temporarily stored in the refrigerant storage tank 25 to a low pressure in the refrigeration cycle, after the refrigerant has been depressurized in the first expansion mechanism 24 as an upstream-side expansion mechanism.
  • the second expansion mechanism 26 functions as an upstream-side expansion mechanism for depressurizing the refrigerant that has radiated heat in the indoor heat exchanger 41 to an intermediate pressure in the refrigeration cycle.
  • the second expansion mechanism 26 is provided to a portion of the liquid refrigerant tube 35 that is near the liquid-side shutoff valve 27. An electric expansion valve is used herein as the second expansion mechanism 26.
  • the refrigerant storage tank 25, which is provided between the first expansion mechanism 24 and the second expansion mechanism 26, is a container that can collect refrigerant as excess refrigerant, after the refrigerant has been depressurized by the first expansion mechanism 24 or second expansion mechanism 26 functioning as an upstream-side expansion mechanism.
  • the liquid refrigerant quantity that can be accommodated in the indoor heat exchanger 41 is 1100 cc during the air-warming operation in which the indoor heat exchanger 41 functions as a heat radiator of refrigerant
  • the liquid refrigerant quantity that can be accommodated in the outdoor heat exchanger 23 is 800 cc during the air-cooling operation in which the outdoor heat exchanger 23 functions as a heat radiator of refrigerant
  • 300 cc of leftover liquid refrigerant that could not be accommodated in the outdoor heat exchanger 23 during the air-cooling operation is temporarily accommodated in the refrigerant storage tank 25.
  • the gas refrigerant separated in the refrigerant storage tank 25 passes through a bypass tube 30 and flows to the intake tube 31 of the compressor 21.
  • the liquid refrigerant separated in the refrigerant storage tank 25 flows to the outdoor heat exchanger 23 after being depressurized in the second expansion mechanism 26 or first expansion mechanism 24 functioning as an upstream-side expansion mechanism.
  • the bypass tube 30 is provided so as to connect the top part of the refrigerant storage tank 25 and the middle portion of the intake tube 31.
  • a flow rate adjustment mechanism 30a is provided in the middle of the bypass tube 30.
  • An electric expansion valve is used herein as the flow rate adjustment mechanism 30a.
  • the outlet of the bypass tube 30 may also be connected directly to the compressor 21, rather than being connected to the middle portion of the intake tube 31.
  • the liquid-side shutoff valve 27 and the gas-side shutoff valve 28 are valves provided to ports connecting with external devices and tubing (specifically, the liquid refrigerant communication tube 5 and the gas refrigerant communication tube 6).
  • the second expansion mechanism 26 is provided to an end of the liquid refrigerant tube 35.
  • the liquid-side shutoff valve 27 is provided to an end of the second gas refrigerant tube 34.
  • the outdoor unit 2 has an outdoor fan 36 for drawing outdoor air into the outdoor unit 2 and expelling the air to the exterior after the air has undergone heat exchange with the refrigerant in the outdoor heat exchanger 23.
  • the outdoor fan 36 herein is a propeller fan or the like driven by an outdoor fan motor 37.
  • the outdoor unit 2 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 a microcomputer, a memory, and the like for performing control on the outdoor unit 2, is designed to be capable of exchanging control signals and the like with an indoor-side control part 44 of the indoor unit 4 via the transmission line 8a.
  • a control part 8 for performing the operation controls for the entire air-conditioning apparatus 1 is configured by the indoor-side control part 44, the outdoor-side control part 38, and the transmission line 8a which connects the control parts 38, 44.
  • the control part 8 is designed to be capable of controlling the actions of the various devices and valves 21a, 22, 24, 26, 30a, 37, 43, etc., on the basis of various operation settings, the values detected by various sensors, and the like.
  • the refrigerant circuit 10 of the air-conditioning apparatus 1 is configured from the connection between the outdoor unit 2, the indoor unit 4, and the refrigerant communication tubes 5, 6.
  • the refrigerant circuit 10 is designed to perform a refrigeration cycle in which refrigerant flows sequentially through the compressor 21, the outdoor heat exchanger 23, the first expansion mechanism 24 as an upstream-side expansion mechanism, the refrigerant storage tank 25, the second expansion mechanism 26 as a downstream-side expansion mechanism, and the indoor heat exchanger 41.
  • the refrigerant circuit 10 is designed to perform a refrigeration cycle in which refrigerant flows sequentially through the compressor 21, the indoor heat exchanger 41, the second expansion mechanism 26 as an upstream-side expansion mechanism, the refrigerant storage tank 25, the first expansion mechanism 24 as a downstream-side expansion mechanism, and the outdoor heat exchanger 23.
  • the air-conditioning apparatus 1 is designed to be capable of performing various operations such as the air-cooling operation and the air-warming operation, by means of the control part 8 configured from the indoor-side control part 44 and the outdoor-side control part 38.
  • the air-conditioning apparatus 1 can perform an air-cooling operation and an air-warming operation as described above. The actions of the air-conditioning apparatus 1 during the air-cooling operation and the air-warming operation are described below.
  • a switch is performed in which the switching mechanism 22 is in the state shown by the dashed lines in FIG. 1 , i.e., the second port 22b and the fourth port 22d are communicated, and the first port 22a and the third port 22c are communicated.
  • the high-pressure refrigerant discharged from the compressor 21 is sent through the switching mechanism 22, the gas-side shutoff valve 28, and the gas refrigerant communication tube 6 to the indoor heat exchanger 41.
  • the high-pressure refrigerant sent to the indoor heat exchanger 41 undergoes heat exchange with indoor air and radiates heat in the indoor heat exchanger 41.
  • the indoor air is thereby heated. Because the capacity of the indoor heat exchanger 41 is greater than the capacity of the outdoor heat exchanger 23, most of the liquid refrigerant is accommodated in the indoor heat exchanger 41 during the air-warming operation.
  • the high-pressure refrigerant that has radiated heat in the indoor heat exchanger 41 is sent through the liquid refrigerant communication tube 5 and the liquid-side shutoff valve 27 to the second expansion mechanism 26 functioning as an upstream-side expansion mechanism.
  • the refrigerant sent to the second expansion mechanism 26 is depressurized to an intermediate pressure by the second expansion mechanism 26, and is then sent to the refrigerant storage tank 25.
  • the refrigerant just before entering the refrigerant storage tank 25 includes a gas component produced when the refrigerant is depressurized in the second expansion mechanism 26, but after entering the refrigerant storage tank 25, the refrigerant is divided into a liquid component and a gas component, the liquid refrigerant is stored in the lower side, and the gas refrigerant is stored in the upper side.
  • the flow rate adjustment mechanism 30a of the bypass tube 30 is controlled to an open state, the gas refrigerant in the refrigerant storage tank 25 passes through the bypass tube 30 and heads to the intake tube 31 of the compressor 21.
  • the liquid refrigerant in the refrigerant storage tank 25 is sent to the outdoor heat exchanger 23 after being depressurized to a low pressure by the first expansion mechanism 24 functioning as a downstream-side expansion mechanism.
  • the low-pressure refrigerant sent to the outdoor heat exchanger 23 undergoes heat exchange with outdoor air supplied by the outdoor fan 36 and evaporates in the outdoor heat exchanger 23.
  • the refrigerant flowing into the outdoor heat exchanger 23 is reduced by the gas-liquid separating process in the refrigerant storage tank 25, as well as the process of drawing the gas-liquid separated gas refrigerant through the bypass tube 30 into the compressor 21. Therefore, the flow rate of refrigerant flowing through the outdoor heat exchanger 23 decreases, pressure loss can be reduced proportionately, and the depressurization loss in the refrigeration cycle can therefore be reduced.
  • the low-pressure refrigerant evaporated in the outdoor heat exchanger 23 is drawn through the switching mechanism 22 back into the compressor 21.
  • a switch is performed in which the switching mechanism 22 is in the state shown by the solid lines in FIG. 1 , i.e., the second port 22b and the third port 22c are communicated, and the first port 22a and the fourth port 22d are communicated.
  • the high-pressure refrigerant discharged from the compressor 21 is sent through the switching mechanism 22 to the outdoor heat exchanger 23.
  • the high-pressure refrigerant sent to the outdoor heat exchanger 23 undergoes heat exchange with outdoor air and radiates heat in the outdoor heat exchanger 23.
  • the high-pressure refrigerant that has radiated heat in the outdoor heat exchanger 23 is sent to the first expansion mechanism 24 functioning as an upstream-side expansion mechanism, depressurized to an intermediate pressure by the first expansion mechanism 24, and then sent to the refrigerant storage tank 25. Because the capacity of the outdoor heat exchanger 23 is equal to or less than the capacity of the indoor heat exchanger 41 here, the outdoor heat exchanger 23 is not able to accommodate all of the liquid refrigerant during the air-cooling operation. Therefore, the liquid refrigerant that could not be accommodated in the outdoor heat exchanger 23 is accumulated in the refrigerant storage tank 25, and the refrigerant storage tank 25 is filled with liquid refrigerant.
  • the refrigerant just before entering the refrigerant storage tank 25 includes a gas component produced when the refrigerant is depressurized in the first expansion mechanism 24, but after entering the refrigerant storage tank 25, the refrigerant is divided into a liquid component and a gas component, the liquid refrigerant is stored in the lower side, and the gas refrigerant is stored in the upper side.
  • the flow rate adjustment mechanism 30a of the bypass tube 30 is controlled to an open state, the gas refrigerant in the refrigerant storage tank 25 passes through the bypass tube 30 and heads to the intake tube 31 of the compressor 21.
  • the liquid refrigerant in the refrigerant storage tank 25 is sent through the liquid-side shutoff valve 27 and the liquid refrigerant communication tube 5 to the indoor heat exchanger 41 after being depressurized to a low pressure by the second expansion mechanism 26 functioning as a downstream-side expansion mechanism.
  • the low-pressure refrigerant sent to the indoor heat exchanger 41 undergoes heat exchange with indoor air and evaporates in the indoor heat exchanger 41.
  • the indoor air is thereby cooled.
  • the refrigerant flowing into the indoor heat exchanger 41 is reduced by the gas-liquid separating process in the refrigerant storage tank 25, as well as the process of drawing the gas-liquid separated gas refrigerant through the bypass tube 30 into the compressor 21. Therefore, the flow rate of refrigerant flowing through the indoor heat exchanger 41 decreases, pressure loss can be reduced proportionately, and the depressurization loss in the refrigeration cycle can therefore be reduced.
  • the low-pressure refrigerant evaporated in the indoor heat exchanger 41 is drawn through the gas refrigerant communication tube 6, the gas-side shutoff valve 28, and the switching mechanism 22 back into the compressor 21.
  • the air-conditioning apparatus 1 of the present embodiment has the following characteristics.
  • the indoor heat exchanger 41 is a cross-fin type heat exchanger
  • the outdoor heat exchanger 23 is a stacked heat exchanger
  • the capacity of the outdoor heat exchanger 23 is 100% or less of the capacity of the indoor heat exchanger 41.
  • the refrigerant storage tank 25 for storing refrigerant depressurized by an upstream-side expansion mechanism is provided between one of the first expansion mechanism 24 and the second expansion mechanism 26 as an upstream-side expansion mechanism, and the other of the first expansion mechanism 24 and the second expansion mechanism 26 as a downstream-side expansion mechanism, as described above.
  • the excess refrigerant that can no longer be accommodated in the outdoor heat exchanger 23 during the air-cooling operation is then accommodated in the refrigerant storage tank 25 positioned in the vicinity of the downstream side of the outdoor heat exchanger 23.
  • bypass tube 30 is provided as described above.
  • the bypass tube 30 is designed to lead the gas component of the refrigerant accumulated in the refrigerant storage tank 25 to either the compressor 21 or the intake tube 31 of the compressor 21.
  • refrigerant depressurized in one of the first expansion mechanism 24 and the second expansion mechanism 26 as an upstream-side expansion mechanism is separated into a liquid component and a gas component in the refrigerant storage tank 25, and the gas component heads toward the bypass tube 30.
  • the gas component which does not contribute to evaporation, thereby ceases to flow into the outdoor heat exchanger 23 functioning as an evaporator of refrigerant during the air-warming operation in the air-conditioning apparatus 1, it is therefore possible to proportionately reduce the flow rate of refrigerant flowing through the outdoor heat exchanger 23 functioning as an evaporator of refrigerant, and the depressurization loss in the refrigeration cycle can be reduced.
  • refrigerant that has passed through the flow rate adjustment mechanism 30a converges with refrigerant which has evaporated in the indoor heat exchanger 41 and/or the outdoor heat exchanger 23, and then heads to the compressor 21 or the intake tube 31 of the compressor 21.
  • the flow rate adjustment mechanism 30a is an electric expansion valve
  • the state of the refrigerant just before being drawn into the compressor 21 can be adjusted more optimally by controlling the valve opening degree.
  • the refrigerant circulation flow rate i.e. the flow rate of refrigerant flowing through the indoor heat exchanger 41 can be controlled according to the refrigeration load on the indoor heat exchanger 41 side.
  • a container for storing refrigerant is employed as the refrigerant storage tank 25, but refrigerant storage is not limited as such, and a cyclone-type gas-liquid separator such as the one shown in FIG. 5 may be employed, for example.
  • the refrigerant storage tank 25 of the present modification has primarily a cylindrical container 251, a first connecting tube 252, a second connecting tube 253, and a third connecting tube 254.
  • the first connecting tube 252 is linked in the tangential direction of the circumferential side wall of the cylindrical container 251, communicating the interior of the cylindrical container 251 and the second expansion mechanism 26 or first expansion mechanism 24 as a downstream-side expansion mechanism.
  • the second connecting tube 253 is linked to the bottom wall of the cylindrical container 251, communicating the interior of the cylindrical container 251 and the first expansion mechanism 24 or second expansion mechanism 26 as an upstream-side expansion mechanism.
  • the third connecting tube 254 is linked to the top wall of the cylindrical container 251, communicating the interior of the cylindrical container 251 and the bypass tube 30.
  • the liquid refrigerant falls due to gravity, accumulates in the lower side, and flows out of the cylindrical container 251 through the second connecting tube 253.
  • the gas refrigerant rises while swirling, accumulates in the upper side, and flows out of the cylindrical container 251 through the third connecting tube 254.
  • gas-liquid separation can be efficiently performed because a cyclone-type gas-liquid separator is employed as the refrigerant storage tank 25 as described above.
  • the refrigerant storage tank 25 composed of a gas-liquid separator has both a refrigerant storage function of accumulating liquid refrigerant and a function of separating the liquid component and gas component, thereby contributing to simplifying the apparatus configuration because there is no need to provide both a refrigerant storage container and a gas-liquid separator.
  • the outdoor heat exchanger 23 is a stacked heat exchanger having a plurality of flat tubes 231 and corrugated fins 232.
  • the plurality of flat tubes 231 are arrayed so as to be superposed set apart by gaps, and the corrugated fins 232 are enclosed between adjacent flat tubes 231.
  • the outdoor heat exchanger 23 is not limited to the configurations in the above embodiment and Modification 1, and may be a stacked heat exchanger having a plurality of flat tubes 231 arrayed so as to be superposed set apart by gaps, and fins 236 in which notches 236a are formed, the flat tubes 231 being inserted into the notches, as shown in FIGS. 6 and 7 , for example.
  • the outdoor heat exchanger 23 is a stacked heat exchanger having a plurality of flat tubes 231 and corrugated fins 232.
  • the plurality of flat tubes 231 are arrayed so as to be superposed set apart by gaps, and the corrugated fins 232 are enclosed between adjacent flat tubes 231.
  • the outdoor heat exchanger 23 is not limited to the configurations in the above embodiment and Modification 1, and may have a configuration in which the flat tubes are molded into serpentine shapes and the fins are enclosed between the mutually adjacent surfaces of the flat tubes, for example.
  • the outdoor heat exchanger 23 is a stacked heat exchanger having a plurality of flat tubes 231, corrugated fins 232, and/or fins 236 in which notches 236a are formed.
  • the outdoor heat exchanger 23 and the indoor heat exchanger 41 may both be cross-fin type heat exchangers, configured such that the diameter of the heat transfer tubes in the outdoor heat exchanger 23 is less than the diameter of the heat transfer tubes in the indoor heat exchanger 41.
  • refrigerator oil sealed with the refrigerant in order to lubricate the compressor 21 tends to have extremely low solubility in low-temperature conditions. Therefore, at a low pressure in the refrigeration cycle, the solubility of the refrigerator oil greatly decreases due to the decrease in refrigerant temperature.
  • the air-cooling operation in the refrigerant circuit 10 there is low pressure in the refrigeration cycle in the circuit portion beginning after passing through the second expansion mechanism 26 functioning as a downstream-side expansion mechanism and leading through the indoor heat exchanger 41 up to intake in the compressor 21.
  • the refrigerator oil when R32 is used as the refrigerant could be ether-based synthetic oil having any compatibility with R32, mineral oil or alkyl benzene-based synthetic oil having no compatibility with R32, or the like. With ether-based synthetic oil, compatibility is lost when the temperature decreases to about -5°C, and with mineral oil or alkyl benzene-based synthetic oil, there is no compatibility at conditions of higher temperature than ether-based synthetic oil.
  • R32 is used as the refrigerant in a conventional refrigeration apparatus having a refrigerant storage tank on the intake side of the compressor, for example, the refrigerant and the refrigerator oil separate into two layers in the refrigerant storage tank which has a low pressure in the refrigeration cycle, and the refrigerator oil has difficulty returning to the compressor.
  • a refrigerant storage tank 25 is provided between the first and second expansion mechanisms 24, 26 as an upstream-side expansion mechanism and a downstream-side expansion mechanism as indicated in the above embodiment and Modifications 1 to 4, two-layer separation is less likely to occur in the intake side of the compressor 21 and refrigerator oil returns more readily to the compressor 21, in comparison to cases in which the refrigerant storage tank is provided to the intake side of the compressor 21.
  • the refrigerant storage tank 25 being provided between the first and second expansion mechanisms 24, 26 as an upstream-side expansion mechanism and a downstream-side expansion mechanism, it is possible to resolve not only the problem of excess refrigerant produced by the capacity of the outdoor heat exchanger 23 being equal to or less than the capacity of the indoor heat exchanger 41, due to factors such as a stacked heat exchanger being used as the outdoor heat exchanger 23, but also the problem of oil returning to the compressor 21, caused by using R32 as the refrigerant.
  • the present invention is widely applicable in refrigeration apparatuses that can perform a cooling operation and a heating operation.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Analytical Chemistry (AREA)
  • Chemical & Material Sciences (AREA)
  • Power Engineering (AREA)
  • Air Conditioning Control Device (AREA)
  • Other Air-Conditioning Systems (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
  • Devices That Are Associated With Refrigeration Equipment (AREA)
  • Air Filters, Heat-Exchange Apparatuses, And Housings Of Air-Conditioning Units (AREA)
EP12859176.5A 2011-12-20 2012-12-19 Kühlvorrichtung Active EP2801770B1 (de)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
JP2011278427 2011-12-20
JP2012074660A JP5403095B2 (ja) 2011-12-20 2012-03-28 冷凍装置
PCT/JP2012/082912 WO2013094638A1 (ja) 2011-12-20 2012-12-19 冷凍装置

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EP2801770A1 true EP2801770A1 (de) 2014-11-12
EP2801770A4 EP2801770A4 (de) 2015-09-16
EP2801770B1 EP2801770B1 (de) 2020-04-01

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EP4040083A4 (de) * 2019-09-30 2022-11-16 Daikin Industries, Ltd. Gefriervorrichtung

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JP5858022B2 (ja) * 2013-10-24 2016-02-10 ダイキン工業株式会社 空気調和装置
CN105940276A (zh) * 2014-01-23 2016-09-14 三菱电机株式会社 热泵装置
JP6865846B2 (ja) * 2017-10-10 2021-04-28 三菱電機株式会社 空気調和装置
US11280529B2 (en) * 2019-06-10 2022-03-22 Trane International Inc. Refrigerant volume control
JP6828790B1 (ja) * 2019-10-31 2021-02-10 ダイキン工業株式会社 冷凍装置
JP7372556B2 (ja) * 2021-09-30 2023-11-01 ダイキン工業株式会社 冷媒容器および冷凍サイクル装置

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CN103998875A (zh) 2014-08-20
JP5403095B2 (ja) 2014-01-29
ES2797450T3 (es) 2020-12-02
BR112014014557A2 (pt) 2017-06-13
JP2013148328A (ja) 2013-08-01
EP2801770B1 (de) 2020-04-01
KR20140102313A (ko) 2014-08-21
US20140360223A1 (en) 2014-12-11
AU2012354761A1 (en) 2014-08-07
BR112014014557B1 (pt) 2022-01-11
CN103998875B (zh) 2015-09-02
EP2801770A4 (de) 2015-09-16
KR101452690B1 (ko) 2014-10-22
WO2013094638A1 (ja) 2013-06-27
AU2012354761B2 (en) 2015-10-29

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