EP3006865A1 - Kältekreislaufvorrichtung - Google Patents

Kältekreislaufvorrichtung Download PDF

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Publication number
EP3006865A1
EP3006865A1 EP13885818.8A EP13885818A EP3006865A1 EP 3006865 A1 EP3006865 A1 EP 3006865A1 EP 13885818 A EP13885818 A EP 13885818A EP 3006865 A1 EP3006865 A1 EP 3006865A1
Authority
EP
European Patent Office
Prior art keywords
heat
flow control
refrigerant
refrigeration cycle
control valve
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.)
Pending
Application number
EP13885818.8A
Other languages
English (en)
French (fr)
Other versions
EP3006865A4 (de
Inventor
Kosuke Tanaka
Ryosuke Matsui
Naomichi Tamura
Tadashi ARIYAMA
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
Publication of EP3006865A1 publication Critical patent/EP3006865A1/de
Publication of EP3006865A4 publication Critical patent/EP3006865A4/de
Pending 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
    • 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
    • F25B2400/04—Refrigeration circuit bypassing means
    • 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
    • F25B2400/24—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
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • F25B40/02—Subcoolers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B47/00—Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass
    • F25B47/02—Defrosting cycles
    • F25B47/022—Defrosting cycles hot gas defrosting
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • 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

Definitions

  • the present invention relates to a refrigeration cycle apparatus including a heat storage device in a refrigerant circuit.
  • a refrigeration cycle apparatus having a heat storage device arranged in a refrigerant circuit, and using heat stored in the heat storage device to quickly start a heating operation or shorten a defrosting operation period when heating is started or when an outdoor heat exchanger is defrosted in a low outside air temperature environment.
  • the refrigeration cycle apparatus has, for example, a system having a heating unit, for example, additionally arranged in the heat storage device as a heat source for the heat storage to drive the heating unit in the heat storing operation, a configuration of transferring exhaust heat from a shell of a compressor to a heat storage material to perform the heat storing operation, or a configuration of using refrigerant discharged from the compressor as a heat source (see, for example, Patent Literatures 1 and 2).
  • the related-art heat storage device has problems in that the heating unit that is an external heat source prepared for the heat storage device requires additional equipment and electric power, that using the exhaust heat from the shell of the compressor for the heat storage device deteriorates starting performance of the heating, and that using the heat, to be stored, from the refrigerant discharged from the compressor also deteriorates the starting performance of the heating.
  • the present invention has been made to solve the above-mentioned problems, and has an object to provide a refrigeration cycle apparatus that requires no external heat source, uses necessary heat from a refrigeration cycle as a heat-storage heat source, stores heat in a heat storage device without adversely affecting starting performance of heating, shortens a defrosting operation period, and improves the comfort in a room.
  • a refrigeration cycle apparatus includes a compressor, a use-side heat exchanger, a heat source-side flow control valve, and a heat source-side heat exchanger.
  • the refrigeration cycle apparatus is configured to circulate refrigerant through in an order of the compressor, the use-side heat exchanger, the heat source-side flow control valve, and the heat source-side heat exchanger in a heating operation.
  • the refrigeration cycle apparatus further includes a heat storage device connected between the use-side heat exchanger and the heat source-side flow control valve. The heat storage device is configured to store heat through heat exchange with the circulating refrigerant.
  • a liquid refrigerant transferred heat to the use-side heat exchanger to contribute to a heating operation is used as a heat source. Consequently, the heat storage device can be heated without providing another heat source for heating the heat storage device. Further, exhaust heat from a shell of the compressor in the refrigeration cycle or heat of refrigerant discharged from the compressor is not used as a heat source. Consequently, a refrigeration cycle apparatus capable of quickly starting a heating operation can be provided.
  • Fig. 1 is a structural diagram of a refrigeration cycle apparatus according to Embodiment 1.
  • a compressor 1, a heat source-side heat exchanger 2, a heat source-side flow control valve 3, a four-way valve 4, a use-side heat exchanger 5, and a heat storage device 6 are connected via refrigerant pipes 7 to construct a refrigeration cycle apparatus.
  • the heat storage device 6 of the refrigeration cycle apparatus is connected between the use-side heat exchanger 5 and the heat source-side flow control valve 3.
  • gas refrigerant discharged from the compressor 1 is condensed by the use-side heat exchanger 5 to become liquid refrigerant.
  • the high-pressure liquid refrigerant discharged from the use-side heat exchanger 5 passes through the heat storage device 6.
  • the heat storage device 6 stores heat from the high-pressure liquid refrigerant.
  • the high-pressure liquid refrigerant transfers heat to the heat storage device 6 to be subcooled, passes through the heat source-side flow control valve 3, and is evaporated by the heat source-side heat exchanger 2, followed by being sucked into the compressor 1.
  • Fig. 2 is a Mollier chart in the heating and heat storing operation.
  • the high-pressure liquid refrigerant condensed by the use-side heat exchanger 5 subsequently passes through the heat storage device 6 and is subcooled.
  • the opening degree of the heat source-side flow control valve 3 is controlled based on the degree of subcooling of the refrigerant at an outlet of the use-side heat exchanger 5 or the degree of superheat of the refrigerant at an outlet of the heat source-side heat exchanger 2.
  • the high-pressure liquid refrigerant that has transferred heat to the use-side heat exchanger 5 to contribute to the heating operation is used as a heat source. Consequently, the heat storage device 6 can be heated without providing another heat source for heating the heat storage device 6. Further, exhaust heat from a shell of the compressor in the refrigeration cycle or heat of the refrigerant discharged from the compressor is not used, and hence starting performance of the heating operation is not deteriorated.
  • the four-way valve 4 is switched from the heating and heat storing operation to the defrosting operation so that the gas refrigerant discharged from the compressor 1 is sent to the heat source-side heat exchanger 2 and condensed, to thereby defrost the heat source-side heat exchanger 2.
  • the condensed liquid refrigerant is sent to the heat storage device 6 via the heat source-side flow control valve 3, and is evaporated due to the heat stored in the heating and heat storing operation.
  • the evaporated gas refrigerant passes through the use-side heat exchanger 5 and is sucked into the compressor 1.
  • the opening degree of the heat source-side flow control valve 3 in the defrosting operation is at the maximum.
  • Fig. 3 shows a change in heating capacity in comparison between the case where the defrosting operation of the heat source-side heat exchanger 2 is performed with the heat stored in the heat storage device 6 as described above and the case where the defrosting operation is performed with a refrigeration cycle without the heat storage device 6.
  • the defrosting operation by the refrigeration cycle with the heat storage device 6 has a shorter defrosting period than the defrosting operation by the refrigeration cycle without the heat storage device 6, and the heating operation is resumed in a shorter period of time from the start of the defrosting operation.
  • the types of the heat storage device 6 include a type in which the heat storage device 6 is incorporated into an outdoor unit and a type in which the heat storage device 6 is interposed in the middle of the refrigerant pipe outside the outdoor unit.
  • the heat storage device 6 When the heat storage device 6 is installed outside, if the heat storage device 6 is installed at a lower part of the outdoor unit, defrosting capacity can be enhanced without increasing the installation area in a plan view. Further, when the heat storage device 6 is arranged outside the outdoor unit, the heat storage device 6 can be employed in an existing outdoor unit.
  • any one of a sensible heat storage material and a latent heat storage material can be employed.
  • the latent heat storage material is preferred in terms of heat capacity.
  • a latent heat storage material having a melting point of 0 degrees C or higher such as paraffin and polyethyleneglycol, is suitable.
  • the use of a latent heat storage material having a melting point of 0 degrees C or higher can secure a sufficient heat amount in the defrosting operation.
  • a refrigerant passage in the heat storage device 6 may have any shape as long as the refrigerant passage can be brought into contact with the heat storage material with a large area to transfer heat.
  • a heat transfer tube having a spiral shape and a plate type heat exchanger shape are conceivable.
  • a refrigeration cycle apparatus differs from the refrigeration cycle apparatus according to Embodiment 1 in that the refrigeration cycle apparatus according to Embodiment 2 includes a plurality of use-side heat exchangers 5 and use-side flow control valves 8 corresponding to the plurality of use-side heat exchangers 5.
  • Fig. 4 is a structural diagram of the refrigeration cycle apparatus according to Embodiment 2.
  • the compressor 1, the heat source-side heat exchanger 2, the heat source-side flow control valve 3, the four-way valve 4, the use-side heat exchangers 5, the use-side flow control valves 8, and the heat storage device 6 are connected via the refrigerant pipes 7 to construct a refrigeration cycle apparatus.
  • the heat storage device 6 of the refrigeration cycle apparatus is connected between the use-side flow control valves 8 and the heat source-side flow control valve 3.
  • gas refrigerant discharged from the compressor 1 is condensed by the use-side heat exchangers 5 to become liquid refrigerant.
  • the high-pressure liquid refrigerant discharged from the use-side heat exchangers 5 passes through the heat storage device 6 via the use-side flow control valves 8.
  • the heat storage device 6 stores heat from the high-pressure liquid refrigerant.
  • the high-pressure liquid refrigerant transfers heat to the heat storage device 6 to be subcooled, passes through the heat source-side flow control valve 3, and is evaporated by the heat source-side heat exchanger 2, followed by being sucked into the compressor 1.
  • Fig. 5 is a Mollier chart in the heating and heat storing operation.
  • the high-pressure liquid refrigerant condensed by the use-side heat exchangers 5 is reduced in pressure by the use-side flow control valves 8 for the first stage, and thereafter has an intermediate pressure between a condensing pressure and an evaporating pressure, followed by passing through the heat storage device 6 to be subcooled.
  • the refrigerant is reduced in pressure by the heat source-side flow control valve 3 for the second stage, and is evaporated by the heat source-side heat exchanger 2.
  • the opening degree of the use-side flow control valve 8 is controlled based on the degree of subcooling of the refrigerant at the outlet of the use-side heat exchanger 5 or the degree of superheat of the refrigerant at the outlet of the heat source-side heat exchanger 2. Further, the opening degree of the heat source-side flow control valve 3 is controlled so that the refrigerant that transfers heat to the heat storage device 6 arranged on the upstream side of the heat source-side flow control valve 3 has the intermediate pressure between the condensing pressure and the evaporating pressure.
  • the high-pressure liquid refrigerant that has transferred heat to the plurality of use-side heat exchangers 5 to contribute to the heating operation and is reduced in pressure by the use-side flow control valves 8 to have the intermediate pressure is used as a heat source. Consequently, the heat storage device 6 can be heated without providing another heat source for heating the heat storage device 6. Further, similarly to Embodiment 1, exhaust heat from a shell of the compressor in the refrigeration cycle or heat of the refrigerant discharged from the compressor is not used, and hence starting performance of the heating operation is not deteriorated.
  • Embodiment 2 The flow of the refrigerant is the same as in Embodiment 1. In Embodiment 2, however, both the opening degrees of the heat source-side flow control valve 3 and the use-side flow control valves 8 are controlled to be at the maximum to perform the defrosting operation.
  • Embodiment 3 a bypass refrigerant circuit is provided in the refrigeration cycle apparatus according to Embodiment 2, to thereby enable the heating operation and the defrosting operation to be performed simultaneously.
  • Fig. 6 is a structural diagram of the refrigeration cycle apparatus according to Embodiment 3.
  • the compressor 1, the heat source-side heat exchanger 2, the heat source-side flow control valve 3, the four-way valve 4, the use-side heat exchangers 5, the use-side flow control valves 8, and the heat storage device 6 incorporating a heat-storage heat exchanger 6a and a heat-transfer heat exchanger 6b are connected via the refrigerant pipes 7 to construct a refrigeration cycle apparatus.
  • This refrigeration cycle apparatus further includes a first bypass circuit 9 connected from the discharge side of the compressor 1 to the refrigerant inlet side of the heat source-side heat exchanger 2, a first bypass flow control valve 10 provided to the first bypass circuit 9, a second bypass circuit 11 that branches from the refrigerant pipe 7 between the use-side flow control valves 8 and the heat storage device 6, passes through the heat-transfer heat exchanger 6b, and is connected to a suction refrigerant pipe of the compressor 1, and a second bypass flow control valve 12 provided to the second bypass circuit 11.
  • Embodiment 3 When the refrigeration cycle apparatus according to Embodiment 3 performs a heating operation, the first bypass flow control valve 10 and the second bypass flow control valve 12 are fully closed and the refrigeration cycle apparatus operates in the same manner as in Embodiment 2.
  • Gas refrigerant discharged from the compressor 1 is condensed by the use-side heat exchangers 5 to become liquid refrigerant.
  • the high-pressure liquid refrigerant discharged from the use-side heat exchangers 5 passes through the heat-storage heat exchanger 6a in the heat storage device 6 via the use-side flow control valves 8. At this time, the heat storage device 6 stores heat from the high-pressure liquid refrigerant.
  • the high-pressure liquid refrigerant transfers heat to the heat storage device 6 to be subcooled, passes through the heat source-side flow control valve 3, and is evaporated by the heat source-side heat exchanger 2, followed by being sucked into the compressor 1.
  • a Mollier chart in the heating and heat storing operation according to Embodiment 3 is as shown in Fig. 5 similarly to Embodiment 2.
  • the high-pressure liquid refrigerant condensed by the use-side heat exchangers 5 is reduced in pressure by the use-side flow control valves 8 for the first stage, and thereafter has an intermediate pressure between a condensing pressure and an evaporating pressure, followed by passing through the heat storage device 6 to be subcooled. Then, the refrigerant is reduced in pressure by the heat source-side flow control valve 3 for the second stage, and is evaporated by the heat source-side heat exchanger 2.
  • the opening degree of the use-side flow control valve 8 is controlled based on the degree of subcooling of the refrigerant at the outlet of the use-side heat exchanger 5 or the degree of superheat of the refrigerant at the outlet of the heat source-side heat exchanger 2. Further, the opening degree of the heat source-side flow control valve 3 is controlled so that the refrigerant that transfers heat to the heat storage device 6 arranged on the upstream side of the heat source-side flow control valve 3 has the intermediate pressure between the condensing pressure and the evaporating pressure.
  • the heat source-side flow control valve 3 is fully closed and the first bypass flow control valve 10 and the second bypass flow control valve 12 are opened so that the refrigerant circuit branches to a heating circuit for circulating the gas refrigerant discharged from the compressor 1 to the use-side heat exchangers 5, the second bypass circuit 11, and the compressor 1, and a defrosting circuit for circulating the gas refrigerant discharged from the compressor 1 to the first bypass circuit 9, the heat source-side heat exchanger 2, and the compressor 1, to thereby perform the heating operation and the defrosting operation simultaneously.
  • Fig. 7 is a Mollier chart in the heating and defrosting operation.
  • the gas refrigerant discharged from the compressor 1 is separated into two refrigerants.
  • One refrigerant is condensed by the use-side heat exchangers 5, reduced in pressure by the use-side flow control valves 8 and the second bypass flow control valve 12, evaporated by the heat-transfer heat exchanger 6b of the heat storage device 6, and sucked into the compressor 1.
  • the other refrigerant separated from the gas refrigerant discharged from the compressor 1 is reduced in pressure by the first bypass flow control valve 10, and thereafter condensed by the heat source-side heat exchanger 2, to thereby defrost the heat source-side heat exchanger 2.
  • Fig. 8 shows a change in heating capacity in comparison between the case where the defrosting operation is performed with the refrigeration cycle apparatus including the bypass circuit for the heating and defrosting operation and the heat storage device 6 as described above and the case where the defrosting operation is performed with a refrigeration cycle without the heat storage device 6.
  • the defrosting operation by the refrigeration cycle including the bypass circuit for the heating and defrosting operation and the heat storage device 6 can enable the heating operation to be performed even during the defrosting operation, unlike the refrigeration cycle without the heat storage device 6. Consequently, the comfort in the room in the defrosting operation is improved.
  • Embodiments 1 to 3 are the embodiments in which the heating operation or the defrosting operation is assumed. However, when the heat storage device 6 is caused to function in a cooling operation, low-temperature low-pressure refrigerant passes through the heat storage device 6 to store cooling energy in the heat storage material, and hence starting performance of the cooling operation is deteriorated.
  • a refrigeration cycle apparatus is provided with a heat storage device bypass circuit 13 for bypassing the low-temperature low-pressure refrigerant arranged for the heat storage device 6 to control a reduction in capacity at the start of the cooling operation.
  • Fig. 9 is an illustration of the refrigeration cycle apparatus according to Embodiment 4.
  • the heat storage device bypass circuit 13 for allowing the refrigerant to flow from the heat source-side heat exchanger 2 to the use-side heat exchanger 5 is provided for the heat storage device 6.
  • a check valve 14 is arranged to regulate the flow of the refrigerant.
  • a check valve 15 for preventing the refrigerant from flowing from the heat source-side heat exchanger 2 toward the heat storage device 6 is arranged to regulate the flow of the refrigerant.
  • the refrigerant flows from the heat source-side heat exchanger 2 to the use-side heat exchanger 5 so that the low-temperature low-pressure refrigerant bypasses the heat storage device 6, and hence the reduction in capacity at the start of the cooling operation can be controlled.
  • the heat storage device bypass circuit 13 of Embodiment 4 can be applied for the heat storage device 6 of Embodiments 1 to 3.
  • the refrigerant to be employed in the refrigeration cycle apparatus is not particularly limited.
  • any one of natural refrigerants such as carbon dioxide, hydrocarbons, and helium, and refrigerants such as R410A, R32, R407C, R404A, and HFO1234yf may be employed.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
EP13885818.8A 2013-05-31 2013-05-31 Kältekreislaufvorrichtung Pending EP3006865A4 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2013/065207 WO2014192138A1 (ja) 2013-05-31 2013-05-31 冷凍サイクル装置

Publications (2)

Publication Number Publication Date
EP3006865A1 true EP3006865A1 (de) 2016-04-13
EP3006865A4 EP3006865A4 (de) 2017-01-11

Family

ID=51988206

Family Applications (1)

Application Number Title Priority Date Filing Date
EP13885818.8A Pending EP3006865A4 (de) 2013-05-31 2013-05-31 Kältekreislaufvorrichtung

Country Status (3)

Country Link
EP (1) EP3006865A4 (de)
JP (1) JP6433422B2 (de)
WO (1) WO2014192138A1 (de)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN107238249A (zh) * 2017-07-27 2017-10-10 钱娟娟 蓄能化霜冰箱

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPWO2017037891A1 (ja) * 2015-09-02 2018-04-19 三菱電機株式会社 冷凍サイクル装置
JP6989788B2 (ja) * 2019-07-09 2022-01-12 ダイキン工業株式会社 冷凍サイクル装置
WO2023026344A1 (ja) * 2021-08-24 2023-03-02 株式会社日本イトミック ヒートポンプ装置

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS61119074U (de) * 1985-12-11 1986-07-26
JP2522919B2 (ja) * 1986-07-02 1996-08-07 三洋電機株式会社 空気調和機
JP2503637B2 (ja) 1989-03-22 1996-06-05 ダイキン工業株式会社 冷凍装置用圧縮機
JPH03164668A (ja) * 1989-11-24 1991-07-16 Mitsubishi Electric Corp ヒートポンプ装置
JP2000291985A (ja) 1999-04-07 2000-10-20 Daikin Ind Ltd 空気調和装置
JP2002147879A (ja) * 2000-11-14 2002-05-22 Hitachi Ltd 多室形空気調和機およびその除霜制御方法
JP4923794B2 (ja) * 2006-07-06 2012-04-25 ダイキン工業株式会社 空気調和装置
JP2009287903A (ja) * 2008-06-02 2009-12-10 Kansai Electric Power Co Inc:The 蓄熱式ヒートポンプ装置

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN107238249A (zh) * 2017-07-27 2017-10-10 钱娟娟 蓄能化霜冰箱
CN107238249B (zh) * 2017-07-27 2019-11-26 浙江雪村制冷设备有限公司 蓄能化霜冰箱

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JPWO2014192138A1 (ja) 2017-02-23
JP6433422B2 (ja) 2018-12-05
EP3006865A4 (de) 2017-01-11
WO2014192138A1 (ja) 2014-12-04

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