WO2016121103A1 - Dispositif à cycle de réfrigération - Google Patents

Dispositif à cycle de réfrigération Download PDF

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Publication number
WO2016121103A1
WO2016121103A1 PCT/JP2015/052689 JP2015052689W WO2016121103A1 WO 2016121103 A1 WO2016121103 A1 WO 2016121103A1 JP 2015052689 W JP2015052689 W JP 2015052689W WO 2016121103 A1 WO2016121103 A1 WO 2016121103A1
Authority
WO
WIPO (PCT)
Prior art keywords
heat exchanger
heat transfer
refrigeration cycle
temperature
row
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/JP2015/052689
Other languages
English (en)
Japanese (ja)
Inventor
真哉 東井上
石橋　晃
伊東　大輔
裕樹 宇賀神
繁佳 松井
中村　伸
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Mitsubishi Electric Corp
Original Assignee
Mitsubishi Electric Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Mitsubishi Electric Corp filed Critical Mitsubishi Electric Corp
Priority to JP2016571640A priority Critical patent/JPWO2016121103A1/ja
Priority to EP15880000.3A priority patent/EP3252400A4/fr
Priority to PCT/JP2015/052689 priority patent/WO2016121103A1/fr
Publication of WO2016121103A1 publication Critical patent/WO2016121103A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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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
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/053—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F27/00—Control arrangements or safety devices specially adapted for heat-exchange or heat-transfer apparatus
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/025—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple outdoor units
    • F25B2313/0253—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple outdoor 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
    • F25B2313/02741—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using one four-way valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/031—Sensor arrangements
    • F25B2313/0315—Temperature sensors near the outdoor heat exchanger
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/11—Sensor to detect if defrost is necessary

Definitions

  • the present invention relates to a refrigeration cycle apparatus.
  • heat exchanger constituting the refrigeration cycle apparatus
  • a heat exchanger provided with a circular heat transfer tube.
  • diameter of heat transfer tubes has been reduced, and in recent years, there are also heat exchangers in which flat multi-hole tubes are used as heat transfer tubes.
  • the cross-sectional area of the thin circular tube or the flat multi-hole tube is larger than that of a normal circular tube. Get smaller. For this reason, when a heat exchanger is comprised by the number of passes equivalent to the aspect in which the normal heat exchanger tube is used, the pressure loss in a heat exchanger tube increases and the operating efficiency of a refrigerating cycle falls.
  • Reduction of pressure loss can be realized by increasing the number of heat exchanger paths or shortening the length of one heat transfer tube.
  • the refrigerant flowing through the heat exchanger cannot flow opposite to the air, and the heat exchanger efficiency decreases.
  • a difference occurs in the amount of heat exchange between the windward side row and the leeward side row, so that the frost formation is noticeable in the windward side row particularly when the outside air is at a low temperature.
  • the frost adhering to the outdoor heat exchanger needs to be melted by periodically performing a defrosting operation.
  • the defrosting prohibition time is set longer.
  • the present invention has been made in view of the above, and an object of the present invention is to provide a refrigeration cycle apparatus capable of reducing residual frost in a multi-row heat exchanger having a distribution of heat load.
  • the refrigeration cycle apparatus of the present invention includes a circuit including a compressor, an outdoor heat exchanger, an expansion unit, and an indoor heat exchanger, and the outdoor heat exchanger includes a fan, , A first heat exchanger, and a second heat exchanger disposed downstream of the first heat exchanger with respect to the air flow generated by the fan, the first heat exchanger comprising: 1 heat transfer tube and a plurality of first fins intersecting the first heat transfer tube, the second heat exchanger includes a second heat transfer tube, and the first heat transfer tube is a first heat transfer tube Connected to a header, the second heat transfer tube is connected to a second header, and the first header and the second header are connected to a branch portion of the collecting pipe via a distribution pipe.
  • a refrigeration cycle apparatus wherein the plurality of first fins and the branch portion of the collecting pipe, Placing the first temperature sensor.
  • residual frost can be reduced in a multi-row heat exchanger having a distribution of heat load.
  • FIG. 3 shows the structure of the refrigerating-cycle apparatus of Embodiment 1 of this invention. It is a perspective view of an outdoor heat exchanger. It is a top view for demonstrating the structure of an outdoor heat exchanger. It is a graph which shows the relationship between the temperature of the refrigerant
  • FIG. 1 is a diagram showing the configuration of the refrigeration cycle apparatus of the first embodiment.
  • the refrigeration cycle apparatus 1 includes a circuit 3 in which a refrigerant circulates.
  • the circuit 3 includes at least the compressor 5, the outdoor heat exchanger 100, the expansion unit 7, and the indoor heat exchanger 9.
  • the refrigeration cycle apparatus 1 can perform both a heating operation and a cooling operation (defrosting operation), and the circuit 3 is provided with a four-way valve 11 for switching the operation.
  • FIG.1, FIG.3, FIG.6, FIG. 7 the flow of the refrigerant
  • circuit 3 will be described with reference to the direction of refrigerant flow during cooling operation. That is, in the present specification and the claims of the present application, the words of the inlet and the outlet are used on the basis of the direction in which the refrigerant flows during the cooling operation.
  • the outlet of the compressor 5 is connected to the inlet of the outdoor heat exchanger 100 via the four-way valve 11.
  • the outlet of the outdoor heat exchanger 100 is connected to the inlet of the expansion unit 7.
  • the expansion part 7 is comprised by the expansion valve, for example.
  • the outlet of the expansion part 7 is connected to the inlet of the indoor heat exchanger 9.
  • the outlet of the indoor heat exchanger 9 is connected to the inlet of the compressor 5 via a four-way valve 11.
  • the control unit 140 is connected to the four-way valve 11, and as described later, the flow path of the four-way valve 11 is switched, that is, switching between heating operation and cooling operation (defrosting operation) is performed.
  • the control unit 140 is connected to the compressor 5 and appropriately controls the operation of the compressor 5 in each of the heating operation, the cooling operation, and the defrosting operation.
  • an arrow W indicates a flow of fluid that performs heat exchange with the refrigerant.
  • an arrow W indicates a flow of air that performs heat exchange with the refrigerant.
  • a fan 9 a is provided on the windward side of the indoor heat exchanger 9. By this fan 9a, an air flow to the indoor heat exchanger 9 is positively generated.
  • the indoor heat exchanger 9 and the fan 9a are accommodated in a case of the indoor unit 15, and the indoor unit 15 is disposed in the indoor space.
  • FIG. 2 is a perspective view of the outdoor heat exchanger.
  • FIG. 3 is a plan view for explaining the configuration of the outdoor heat exchanger. Note that fins (to be described later) are not shown in FIG. 2, and heat transfer tubes (to be described later) are not shown in FIG.
  • the outdoor heat exchanger 100 includes a fan 100a, an upwind row 101 that is a first heat exchanger, and a downwind row 102 that is a second heat exchanger.
  • the leeward row 102 is disposed further downwind than the leeward row 101 with respect to the airflow generated by the fan 100a. That is, the fan 100 a is disposed on the windward side of the windward row 101 and the leeward row 102, and the windward row 101 is disposed on the windward side of the leeward row 102.
  • the air flow to the windward row 101 and the leeward row 102 is positively generated by the fan 100a.
  • the outdoor heat exchanger 100 (the windward row 101, the leeward row 102, the fan 100a), the compressor 5, the expansion unit 7, the four-way valve 11, and the control unit 140 are accommodated in a case of the outdoor unit 17.
  • the windward row 101 includes a windward heat transfer tube 111 that is a plurality of first heat transfer tubes, and a windward fin 113 that is a plurality of first fins that intersect the plurality of windward heat transfer tubes 111.
  • the leeward row 102 includes a leeward heat transfer tube 112 that is a plurality of second heat transfer tubes and a leeward fin 114 that is a plurality of second fins that intersect the plurality of leeward heat transfer tubes 112.
  • Each of the plurality of upwind heat transfer tubes 111 and the plurality of downwind heat transfer tubes 112 is a flat tube or a circular tube having a diameter of 4 mm or less.
  • the windward row 101 and the leeward row 102 are arranged in a direction along the air flow W that performs heat exchange with the refrigerant, that is, the alignment direction Z.
  • the windward row 101 is closer to the air intake surface 17 a of the case of the outdoor unit 17 than the leeward row 102.
  • the leeward row 102 is closer to the air discharge surface 17 b provided in the case of the outdoor unit 17 than the windward row 101.
  • the plurality of windward heat transfer tubes 111 are arranged in the vertical direction Y perpendicular to both the longitudinal direction, that is, the flow direction X in the heat transfer tube and the alignment direction Z.
  • the plurality of leeward heat transfer tubes 112 are also arranged in the vertical direction Y perpendicular to both the longitudinal direction, that is, the heat transfer tube flow direction X and the alignment direction Z.
  • the heat transfer tube flow direction X is orthogonal to both the alignment direction Z and the vertical direction Y.
  • the plurality of windward fins 113 intersect with the plurality of windward heat transfer tubes 111 in plan view. More specifically, each of the plurality of upwind fins 113 extends in the alignment direction Z orthogonal to the flow direction X in the heat transfer tube.
  • the plurality of leeward fins 114 intersect with the plurality of leeward heat transfer tubes 112 in plan view. More specifically, each of the plurality of leeward fins 114 extends in an alignment direction Z orthogonal to the flow direction X in the heat transfer tube.
  • the inlet ends of the plurality of windward heat transfer tubes 111 are connected to a common windward inlet header 103, and the outlet ends of the plurality of windward heat transfer tubes 111 are connected to a common windward outlet header 105. Further, the inlet ends of the plurality of leeward heat transfer tubes 112 are connected to a common leeward inlet header 104, and the 112 outlet ends of the plurality of leeward heat transfer tubes are connected to a common leeward outlet header 106.
  • the windward inlet header 103 and the leeward inlet header 104 are connected to a branching portion 123a of the inlet collecting pipe 123 via a plurality of (two in the first embodiment) inlet distribution pipes 121. Further, the windward outlet header 105 and the leeward outlet header 106 are connected to the branch portion 127a of the outlet collecting pipe 127 via a plurality of (two in the first embodiment) outlet distribution pipes 125. .
  • the refrigeration cycle apparatus 1 further includes a first temperature sensor 131.
  • the first temperature sensor 131 is arranged between the windward fin 113a closest to the branching portion 127a of the outlet collecting pipe 127 and the outlet collecting pipe 127.
  • the windward outlet distribution pipe 125 is provided between the windward outlet header 105 and the branching portion 127a of the outlet collecting pipe 127. In other words, with respect to the direction in which the refrigerant flows during the cooling operation, it is provided at a position downstream of the windward outlet header 105 and upstream of the branching portion 127a of the outlet collecting pipe 127.
  • the control unit 140 determines the end of the defrosting operation based on the temperature detected by the first temperature sensor 131.
  • the heating operation will be described.
  • the refrigerant flows as shown by dotted arrows in the figure.
  • the high-temperature and high-pressure gas refrigerant sent from the compressor 5 passes through the four-way valve 11 and flows into the indoor heat exchanger 9.
  • the refrigerant that has flowed into the indoor heat exchanger 9 is cooled by heat exchange with room air, and then flows into the expansion section 7 where the pressure is reduced.
  • the decompressed low-temperature refrigerant flows into the outdoor heat exchanger 100.
  • the refrigerant flowing into the outdoor heat exchanger 100 flows into the windward outlet header 105 and the leeward outlet header 106 through the outlet collecting pipe 127 and the branching portion 127a shown in FIG.
  • the refrigerant that has flowed into the windward outlet header 105 and the leeward outlet header 106 flows separately into a plurality of windward heat transfer tubes 111 and a plurality of windward heat transfer tubes 112, respectively.
  • coolant flows through the windward heat exchanger tube 111 and the leeward heat exchanger tube 112, it is heated and evaporated by the air sent out by the fan 100a.
  • outdoor heat exchanger 100 in the first embodiment has a plurality of rows in a direction (alignment direction Z) substantially parallel to the flow of fluid (air) that exchanges heat with the refrigerant, and fluid that exchanges heat with the refrigerant.
  • the outdoor heat exchanger 100 is a multi-row direct flow type heat exchanger.
  • FIG. 4 indicates the alignment direction Z shown in FIGS. 2 and 3, and the vertical axis indicates the temperature t.
  • the temperature of the refrigerant flowing through the windward row 101 and the leeward row 102 is substantially the same. This is because the refrigerant flowing through the heat exchanger flows in a saturated state.
  • the air temperature ta is cooled by heat exchange with the refrigerant when passing through the windward row 101, and the temperature decreases. Further, when the temperature of the fins or heat transfer tube surfaces of the heat exchanger is equal to or lower than the dew point temperature of air, dew is generated on the fin surfaces or heat transfer tube surfaces, and the humidity of the air is also reduced. Therefore, the temperature and humidity of the air flowing in the leeward row 102 are lower than the temperature and humidity of the air flowing in the leeward row 101.
  • the upwind row 101 Since the magnitude of the heat exchange amount in the heat exchanger is determined by the difference between the refrigerant temperature and the air temperature or humidity, the upwind row 101 has a larger heat exchange amount than the downwind row 102.
  • the temperature of the air when the temperature of the air is lowered, the temperature of the refrigerant is also lowered.
  • the temperature of the fins or the heat transfer tubes is less than 0 degrees, water vapor in the air adheres to the heat exchanger as frost. Therefore, if no countermeasure is taken, more frost adheres to the upwind row 101 having a large amount of heat exchange, and the frost amount becomes uneven in the upwind row 101 and the downwind row 102.
  • the defrosting operation is performed in the following manner.
  • the four-way valve 11 in FIG. 3 is switched and a high-temperature and high-pressure refrigerant is caused to flow through the outdoor heat exchanger 100. That is, the refrigerant flow is in the opposite direction to that during heating operation.
  • FIG. 5 shows the temperature of the refrigerant in the outdoor heat exchanger 100 during the defrosting operation.
  • the horizontal axis in FIG. 5 indicates time S, and the vertical axis indicates the refrigerant temperature T. 5 indicates the temperature TA1 detected by the first temperature sensor 131 during the defrosting operation, and the dotted line in FIG. 5 indicates the outlet temperature TB of the leeward heat transfer tube 112 in the leeward row 102.
  • the temperature of the outdoor heat exchanger 100 increases due to the supply of the high-temperature refrigerant, and the frost starts to melt at around 0 ° C. Due to the influence of latent heat for a while during the melting, The temperature stays at 0 degrees. When the frost melting is almost finished, the temperature rises again, and the defrosting operation is finished at the set defrosting finish temperature Tf.
  • the temperature of the windward row 101 with a large amount of frost formation is less likely to rise than the temperature of the leeward row 102. Therefore, when the temperature of the leeward row 102 is sufficiently increased, for example, when the outlet temperature TB of the leeward row 102 exceeds the defrosting termination temperature Tf (time SB), the defrosting operation is finished. In this case, the temperature of the windward row 101 has not yet risen sufficiently, and frost in the windward row 101 may not be removed properly.
  • the temperature TA1 detected by the first temperature sensor 131 disposed between the windward fin 113a closest to the branching portion 127a of the outlet collecting pipe 127 and the outlet collecting pipe 127 is defrosted.
  • time SA time SA
  • the defrosting operation is ended. In other words, the defrosting operation is continued until the temperature TA1 detected by the first temperature sensor 131 exceeds the defrosting end temperature Tf.
  • the control unit 140 ends the defrosting operation based on the temperature detected by the first temperature sensor 131. Thereby, in both the upwind row 101 and the downwind row 102, it is possible to obtain a state in which frost is sufficiently melted.
  • a second temperature sensor 231 is provided.
  • the second temperature sensor 231 is disposed between the leeward fin 114 a closest to the branch portion 127 a of the outlet collecting pipe 127 and the outlet collecting pipe 127.
  • the leeward side outlet distribution pipe 125 is provided between the leeward outlet header 106 and the branch portion 127a of the outlet collecting pipe 127.
  • the second temperature sensor 231 is also connected to the control unit 140.
  • the control unit 140 ends the defrosting operation. That is, the defrosting operation is ended when the temperature TA2> the defrosting end temperature Tf and the temperature TA1> the defrosting end temperature Tf are satisfied.
  • FIG. 7 is a diagram of the same mode as that of FIG.
  • this Embodiment 3 shall be the same as that of Embodiment 1 mentioned above except the part demonstrated below.
  • a third temperature sensor 331 is provided.
  • the third temperature sensor 331 is disposed in the outlet collecting pipe 127.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Other Air-Conditioning Systems (AREA)

Abstract

L'invention concerne un dispositif à cycle de réfrigération 1 équipé d'un circuit 3 qui comprend un compresseur 5, un échangeur de chaleur extérieur 100, une unité d'expansion 7, et un échangeur de chaleur intérieur 9. L'échangeur de chaleur extérieur 100 est équipé d'un ventilateur 100a, d'une rangée face au vent 101, et d'une rangée sous le vent 102. La rangée face au vent 101 est équipée de premiers tubes de transfert de chaleur 111 et de multiples premières ailettes 113 coupant le premier tube de transfert de chaleur 111. Un premier capteur de température 131 est agencé entre les multiples premières ailettes et une partie de ramification 125 d'une conduite collectrice 127.
PCT/JP2015/052689 2015-01-30 2015-01-30 Dispositif à cycle de réfrigération Ceased WO2016121103A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
JP2016571640A JPWO2016121103A1 (ja) 2015-01-30 2015-01-30 冷凍サイクル装置
EP15880000.3A EP3252400A4 (fr) 2015-01-30 2015-01-30 Dispositif à cycle de réfrigération
PCT/JP2015/052689 WO2016121103A1 (fr) 2015-01-30 2015-01-30 Dispositif à cycle de réfrigération

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2015/052689 WO2016121103A1 (fr) 2015-01-30 2015-01-30 Dispositif à cycle de réfrigération

Publications (1)

Publication Number Publication Date
WO2016121103A1 true WO2016121103A1 (fr) 2016-08-04

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PCT/JP2015/052689 Ceased WO2016121103A1 (fr) 2015-01-30 2015-01-30 Dispositif à cycle de réfrigération

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EP (1) EP3252400A4 (fr)
JP (1) JPWO2016121103A1 (fr)
WO (1) WO2016121103A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN106322847A (zh) * 2016-10-17 2017-01-11 珠海格力电器股份有限公司 多排换热器和包括该多排换热器的空调器

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JPS6214281U (fr) * 1985-07-12 1987-01-28
JPS6250467U (fr) * 1985-09-17 1987-03-28
JPS6369963U (fr) * 1986-10-22 1988-05-11
JP2005226866A (ja) * 2004-02-10 2005-08-25 Denso Corp 冷凍サイクル装置
JP2006284134A (ja) * 2005-04-04 2006-10-19 Matsushita Electric Ind Co Ltd 熱交換器
JP2014066420A (ja) * 2012-09-26 2014-04-17 Hitachi Appliances Inc 冷凍装置

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN106322847A (zh) * 2016-10-17 2017-01-11 珠海格力电器股份有限公司 多排换热器和包括该多排换热器的空调器

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EP3252400A4 (fr) 2018-10-10
JPWO2016121103A1 (ja) 2017-04-27
EP3252400A1 (fr) 2017-12-06

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