WO2022249288A1 - 冷凍サイクル装置 - Google Patents
冷凍サイクル装置 Download PDFInfo
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- WO2022249288A1 WO2022249288A1 PCT/JP2021/019829 JP2021019829W WO2022249288A1 WO 2022249288 A1 WO2022249288 A1 WO 2022249288A1 JP 2021019829 W JP2021019829 W JP 2021019829W WO 2022249288 A1 WO2022249288 A1 WO 2022249288A1
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- pressure
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- 238000005057 refrigeration Methods 0.000 title claims abstract description 50
- 239000003507 refrigerant Substances 0.000 claims abstract description 191
- 238000002347 injection Methods 0.000 claims abstract description 40
- 239000007924 injection Substances 0.000 claims abstract description 40
- 238000006073 displacement reaction Methods 0.000 claims abstract description 32
- 239000007788 liquid Substances 0.000 claims abstract description 25
- 238000013461 design Methods 0.000 claims description 19
- CURLTUGMZLYLDI-UHFFFAOYSA-N Carbon dioxide Chemical group O=C=O CURLTUGMZLYLDI-UHFFFAOYSA-N 0.000 claims description 12
- 229910002092 carbon dioxide Inorganic materials 0.000 claims description 6
- 230000001276 controlling effect Effects 0.000 claims description 6
- 230000001105 regulatory effect Effects 0.000 claims description 4
- 239000001569 carbon dioxide Substances 0.000 claims description 3
- 230000003247 decreasing effect Effects 0.000 claims description 3
- 230000000717 retained effect Effects 0.000 abstract 1
- 238000000034 method Methods 0.000 description 29
- 238000012545 processing Methods 0.000 description 12
- 230000005494 condensation Effects 0.000 description 7
- 238000009833 condensation Methods 0.000 description 7
- 238000010586 diagram Methods 0.000 description 7
- 230000006835 compression Effects 0.000 description 4
- 238000007906 compression Methods 0.000 description 4
- 239000002826 coolant Substances 0.000 description 3
- 238000004519 manufacturing process Methods 0.000 description 3
- 239000011555 saturated liquid Substances 0.000 description 3
- 238000003860 storage Methods 0.000 description 3
- 238000012986 modification Methods 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 229920006395 saturated elastomer Polymers 0.000 description 2
- 238000004781 supercooling Methods 0.000 description 2
- 238000012546 transfer Methods 0.000 description 2
- 238000007872 degassing Methods 0.000 description 1
- 230000008020 evaporation Effects 0.000 description 1
- 238000001704 evaporation Methods 0.000 description 1
- 239000000203 mixture Substances 0.000 description 1
- 230000003287 optical effect Effects 0.000 description 1
- 230000000630 rising effect Effects 0.000 description 1
- 239000004065 semiconductor Substances 0.000 description 1
- 238000005549 size reduction Methods 0.000 description 1
- 238000012360 testing method Methods 0.000 description 1
Images
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
- F25B1/00—Compression machines, plants or systems with non-reversible cycle
- F25B1/10—Compression machines, plants or systems with non-reversible cycle with multi-stage compression
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B49/00—Arrangement or mounting of control or safety devices
- F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
- F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
- F25B9/008—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide
-
- 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
- F25B2309/00—Gas cycle refrigeration machines
- F25B2309/06—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide
- F25B2309/061—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide with cycle highest pressure above the supercritical pressure
-
- 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
- F25B2600/00—Control issues
- F25B2600/25—Control of valves
- F25B2600/2509—Economiser valves
Definitions
- the refrigerant subcooled by the internal heat exchanger (HIC) 30 is branched into the first refrigerant and the second refrigerant by the INJ branch portion 61 .
- the first refrigerant branched at the INJ branch portion 61 flows through the refrigerant pipe 60 and is led to the expansion valve 40 .
- the expansion valve 40 expands and decompresses the first refrigerant.
- the first refrigerant expanded to the low pressure PL flows into the evaporator 50 .
- the expansion valve 40 is, for example, an electronic expansion valve. When the expansion valve 40 is an electronic expansion valve, the opening degree is adjusted under the control of the controller 90 .
- the second refrigerant branched at the INJ branching portion 61 flows through the injection pipe 76 and first flows into the INJ expansion valve 71 .
- a gas vent pipe 74 is a bypass pipe connected between the receiver 72 and the injection pipe 76 .
- One end of the gas vent pipe 74 is connected to the upper portion of the receiver 72 , and the other end of the gas vent pipe 74 is connected between the flow control valve 73 and the internal heat exchanger (HIC) 30 .
- the gas vent pipe 74 causes the gas refrigerant in the receiver 72 to flow out to the injection pipe 76 when the on-off valve 75 is open, and stops the outflow of the gas refrigerant in the receiver 72 when the on-off valve 75 is closed. .
- the composition of the refrigerant flowing through the injection circuit 70 that is, the gas density in the refrigerant can be finely adjusted.
- the gas vent pipe 74 does not necessarily have to be provided, and may be provided only when necessary.
- a first pressure sensor 81 for measuring the intermediate pressure PM is installed between the INJ expansion valve 71 and the receiver 72 .
- the intermediate pressure PM detected by the first pressure sensor 81 is transmitted to the controller 90 .
- the intermediate pressure PM is the pressure inside the receiver 72 .
- a second pressure sensor 82 for measuring the high pressure PH is installed between the discharge port of the high-stage compressor 11 and the condenser 20. .
- the high pressure PH detected by the second pressure sensor 82 is transmitted to the controller 90 .
- the high pressure PH is the discharge pressure of the high stage compressor 11 .
- step S2 the controller 90 compares the intermediate pressure PM with the first threshold. As a result of the comparison, if the intermediate pressure PM is greater than the first threshold value, the process proceeds to step S3. On the other hand, as a result of the comparison, if the intermediate pressure PM is equal to or less than the first threshold value, the process of the flow in FIG. 4 is terminated.
- the control unit 90 may increase the displacement ratio by a predetermined constant amount, or may increase the displacement ratio by an amount corresponding to the value of the intermediate pressure PM .
- a data table is stored in advance in the storage unit of the control unit 90, in which the value of the intermediate pressure PM and the amount of increase in the displacement ratio are stored in association with each other.
- the rotational speed ratio of the high-stage compressor 11 to the low-stage compressor 12 may be increased. Specifically, at least one of the rotation speed of the low-stage compressor 12 and the rotation speed of the high-stage compressor 11 is controlled.
- step S3 the control unit 90 performs the preset first process. This reduces the intermediate pressure PM .
- the control unit 90 repeats the process of the flow of FIG. 4 at regular intervals.
- the intermediate pressure PM can be controlled so that the intermediate pressure PM becomes equal to or lower than the critical pressure PK .
- the liquid refrigerant can be reliably stored in the receiver 72 at the critical pressure PK or less.
- step S3 as the first process, the displacement ratio of the high-stage compressor 11 to the low-stage compressor 12 is simply increased without increasing the displacement of the high-stage compressor 11.
- the displacement ratio of the high-stage compressor 11 to the low-stage compressor 12 is increased.
- an increase in the condensation load of the condenser 20 can be prevented, and an excessive increase in the high pressure PH can be suppressed.
- the size of the condenser 20 can be reduced (that is, size reduction), and the manufacturing cost of the refrigeration cycle apparatus can be reduced accordingly.
- FIG. 5 is a flow chart showing the flow of processing of the control method (M2) in the refrigeration cycle apparatus according to Embodiment 1.
- FIG. 5 the high pressure PH is controlled so as not to exceed the design pressure Pcomp of the high-stage compressor 11 .
- a compressor has a design pressure Pcomp and a guaranteed pressure Pmax.
- the design pressure Pcomp is a pressure value that should be taken as a reference in the design calculation of the strength of the compressor.
- the design pressure Pcomp is set to a value equal to or greater than the maximum internal pressure P of the compressor that can occur during normal operation of the compressor.
- the design pressure Pcomp is obtained by multiplying the maximum value of the internal pressure P that can appear during normal operation of the compressor by a factor of 1 or more (for example, 1.1).
- the design pressure Pcomp is obtained by adding a certain value (for example, 0.1 Mpa) to the maximum value of the internal pressure P that can appear during normal operation of the compressor.
- the guaranteed pressure Pmax of the compressor is a legally defined value based on the design pressure Pcomp of the compressor.
- the guaranteed pressure Pmax is legally set to a value greater than the design pressure Pcomp of the compressor.
- the damage pressure Pbr that may damage the compressor is a value with a tolerance on the high pressure side with respect to the guaranteed pressure Pmax. That is, the failure pressure Pbr is a value larger than the guaranteed pressure Pmax.
- the failure pressure Pbr can be obtained by a compressor endurance test or the like.
- step S11 the control unit 90 acquires the detected value of the high pressure PH from the second pressure sensor .
- the second threshold is, for example, the design pressure Pcomp of the high-stage compressor 11.
- the design pressure Pcomp is obtained by multiplying the maximum value of the internal pressure P that can appear during normal operation of the high-stage compressor 11 by a factor of 1 or more (for example, 1.1).
- the design pressure Pcomp is obtained by adding a certain value (for example, 0.1 Mpa) to the maximum value of the internal pressure P that can appear during normal operation of the high stage compressor 11 .
- step S13 the control unit 90 performs the preset second process. This reduces the high pressure PH .
- the control unit 90 In parallel with the processing of the flow of FIG. 4, the control unit 90 repeatedly performs the processing of the flow of FIG. 5 at regular intervals. However, it is desirable to delay the start timing of the processing of the flow of FIG. 5 by a preset time length from the start timing of the processing of the flow of FIG. Therefore, specifically, for example, the processing of the flow of FIG. 4 and the processing of the flow of FIG. 5 are alternately performed.
- the high pressure PH can be controlled so that the high pressure PH does not exceed the design pressure Pcomp of the high-stage compressor 11 .
- FIG. 6 is a ph diagram showing the refrigeration cycle of the refrigeration cycle apparatus according to Embodiment 1.
- FIG. 6 the horizontal axis indicates the specific enthalpy, and the vertical axis indicates the refrigerant pressure.
- Points A to J in FIG. 6 correspond to the points shown on the refrigerant circuit diagram of FIG.
- points C and C1 are actually the same, they are shown slightly shifted for the sake of explanation.
- the high-stage compressor 11 sucks the refrigerant at intermediate pressure PM (state of point J) and compresses it to high pressure PH (state of point A).
- the high-temperature and high-pressure gas refrigerant releases heat to the air and is condensed to become a high-pressure PH refrigerant (state of point B).
- the high-pressure refrigerant passes through an internal heat exchanger (HIC) 30 in the direction of arrow P1 in FIG. 1 and enters a state with an increased degree of subcooling (states of points C and C1).
- HIC internal heat exchanger
- the remaining refrigerant (state of point C) that has passed through the internal heat exchanger (HIC) 30 flows into the expansion valve 40 .
- the high-pressure PH refrigerant is decompressed to the low-pressure PL , and becomes gas-liquid two-phase refrigerant (state of point D).
- the low-pressure P L two-phase refrigerant (state of point D) flows into the evaporator 50 .
- the low-pressure PL two-phase refrigerant absorbs heat from the air and evaporates to become a low-pressure PL gas refrigerant (state of point E).
- This low-pressure P L gas refrigerant flows into the low-stage compressor 12 .
- the low-stage compressor 12 sucks the refrigerant at the low pressure PL and compresses it to the intermediate pressure PM (state of point F).
- the intermediate pressure PM gas refrigerant (state of point F) discharged from the low-stage compressor 12 is the intermediate pressure PM two-phase refrigerant ( state of point I) and merge (state of point J). This refrigerant is sucked into the high stage compressor 11 and repeats the same cycle again.
- Embodiment 1 even if the CO2 refrigerant is used, at least part of it can be reliably stored as liquid refrigerant in the receiver 72 at a critical pressure PK or lower.
- the high pressure PH which is the discharge pressure of the high-stage compressor 11, can be prevented from excessively rising, and the increase in the condensation load of the condenser 20 can be suppressed.
- Embodiment 1 an increase in the condensation load of the condenser 20 can be suppressed in this way, so the size of the condenser 20 can be reduced.
- the manufacturing cost of the condenser 20 is reduced accordingly, and as a result, the manufacturing cost of the entire refrigeration cycle apparatus can be reduced.
- the refrigeration cycle apparatus according to Embodiment 1 which can control the intermediate pressure PM so as not to exceed the critical pressure PK , is particularly effective when CO 2 is used as the refrigerant.
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
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- Chemical & Material Sciences (AREA)
- Chemical Kinetics & Catalysis (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
Abstract
Description
図1は、実施の形態1に係る冷凍サイクル装置の構成を示す冷媒回路図である。冷凍サイクル装置は、図1に示すように、メイン回路として、圧縮機10、凝縮器20、内部熱交換器(HIC(Heat Inter Changer))30、膨張弁40、および、蒸発器50が、冷媒配管60によって接続された冷媒回路を有している。圧縮機10は、高段圧縮機11と低段圧縮機12とを有している。
まず、制御方法(M1)について説明する。図4は、実施の形態1に係る冷凍サイクル装置における制御方法(M1)の処理の流れを示すフローチャートである。図4においては、中間圧PMが第1閾値以下になるように制御する。
制御部90は、第1処理として、低段圧縮機12に対する高段圧縮機11の押しのけ量の比を増加させる。すなわち、制御部90は、低段圧縮機12の押しのけ量に対する、高段圧縮機11の押しのけ量の比を増加させる。ここで、低段圧縮機12および高段圧縮機11の押しのけ量は、下記の式(2)で算出される。すなわち、低段圧縮機12と高段圧縮機11との回転数の比だけでなく、低段圧縮機12と高段圧縮機11との容積の比も考慮に入れている。
高段圧縮機の押しのけ量=高段圧縮機の容積×高段圧縮機の回転数
(1)
制御部90は、第2処理として、流量調整弁73の開度を低減する。
Claims (11)
- 制御部と、
冷媒を第1圧力から前記第1圧力より高い中間圧まで圧縮する低段圧縮機と、
前記中間圧の前記冷媒を前記中間圧から前記中間圧より高い第2圧力まで圧縮する高段圧縮機と、
前記第2圧力にされた前記冷媒を空気と熱交換させる凝縮器と、
前記凝縮器から流出された前記冷媒を第1冷媒と第2冷媒とに分岐するINJ分岐部と、
前記INJ分岐部で分岐された前記第1冷媒を膨張させて前記第1圧力まで減圧する膨張弁と、
前記膨張弁から流出された前記第1冷媒を空気と熱交換させて、前記第1圧力の前記第1冷媒を前記低段圧縮機に向かって流出する蒸発器と、
前記低段圧縮機の吐出口と前記高段圧縮機の吸入口との間に配置されたINJ合流部と、
前記INJ分岐部と前記INJ合流部との間に接続され、前記INJ分岐部で分岐された前記第2冷媒を前記高段圧縮機に吸入させるインジェクション回路と、
を備え、
前記インジェクション回路は、
前記第2冷媒を膨張させるINJ膨張弁と、
前記INJ膨張弁によって膨張された前記第2冷媒を液冷媒とガス冷媒とに分離して貯留し、貯留した前記液冷媒を前記INJ合流部に向かって流出させるレシーバと、
を備え、
前記制御部は、前記低段圧縮機の押しのけ量に対する前記高段圧縮機の押しのけ量の比を制御し、
前記低段圧縮機の前記押しのけ量は、前記低段圧縮機の容積と回転数とを乗算した値であり、
前記高段圧縮機の前記押しのけ量は、前記高段圧縮機の容積と回転数とを乗算した値である、
冷凍サイクル装置。 - 前記制御部は、前記低段圧縮機の押しのけ量に対する前記高段圧縮機の押しのけ量の比を制御することで、前記レシーバの内部圧力である中間圧を第1閾値以下になるように制御する、
請求項1に記載の冷凍サイクル装置。 - 前記制御部は、
前記低段圧縮機の押しのけ量に対する前記高段圧縮機の押しのけ量の比を増加させることで、前記中間圧を低下させる、
請求項2に記載の冷凍サイクル装置。 - 前記第1閾値は、前記冷媒の臨界点の圧力である臨界圧である、
請求項2または3に記載の冷凍サイクル装置。 - 前記冷媒は、二酸化炭素である、
請求項1~4のいずれか1項に記載の冷凍サイクル装置。 - 前記インジェクション回路は、
前記レシーバと前記INJ合流部との間に配置され、前記レシーバから流出される前記液冷媒の流出量を調整する流量調整弁を
備え、
前記制御部は、前記流量調整弁の開度を制御することで、前記第2圧力を第2閾値以下になるように制御する、
請求項1~5のいずれか1項に記載の冷凍サイクル装置。 - 前記制御部は、
前記流量調整弁の開度を低減することで、前記第2圧力を低減させる、
請求項6に記載の冷凍サイクル装置。 - 前記第2閾値は、前記高段圧縮機の設計圧力である、
請求項6または7に記載の冷凍サイクル装置。 - 前記凝縮器と前記INJ分岐部との間に配置され、前記凝縮器から流出された前記冷媒に過冷却を与える内部熱交換器を備え、
前記INJ分岐部は、前記内部熱交換器から流出された前記冷媒を前記第1冷媒と前記第2冷媒とに分岐し、
前記レシーバは、前記液冷媒を前記内部熱交換器を介して前記INJ合流部に向かって流出する、
請求項1~8のいずれか1項に記載の冷凍サイクル装置。 - 前記INJ膨張弁と前記レシーバとの間に配置され、前記レシーバの内部圧力である前記中間圧を検出する第1圧力センサを備え、
前記制御部は、前記第1圧力センサで検出された前記中間圧に基づいて、前記中間圧を第1閾値以下になるように制御する、
請求項2または請求項2に従属する請求項3~9のいずれか1項に記載の冷凍サイクル装置。 - 前記高段圧縮機の吐出口側に配置され、前記高段圧縮機の吐出圧力である前記第2圧力を検出する第2圧力センサを備え、
前記制御部は、前記第2圧力センサで検出された前記第2圧力に基づいて、前記第2圧力を第2閾値以下になるように制御する、
請求項6~8のいずれか1項に記載の冷凍サイクル装置。
Priority Applications (4)
Application Number | Priority Date | Filing Date | Title |
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CN202180098288.9A CN117321352A (zh) | 2021-05-25 | 2021-05-25 | 制冷循环装置 |
PCT/JP2021/019829 WO2022249288A1 (ja) | 2021-05-25 | 2021-05-25 | 冷凍サイクル装置 |
JP2023523766A JP7466771B2 (ja) | 2021-05-25 | 2021-05-25 | 冷凍サイクル装置 |
EP21942943.8A EP4350247A1 (en) | 2021-05-25 | 2021-05-25 | Refrigeration cycle device |
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PCT/JP2021/019829 WO2022249288A1 (ja) | 2021-05-25 | 2021-05-25 | 冷凍サイクル装置 |
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JP (1) | JP7466771B2 (ja) |
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WO (1) | WO2022249288A1 (ja) |
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JP2012247154A (ja) | 2011-05-30 | 2012-12-13 | Denso Corp | 複数段圧縮式冷凍サイクル装置 |
JP2018132223A (ja) * | 2017-02-14 | 2018-08-23 | パナソニックIpマネジメント株式会社 | 冷凍装置 |
WO2020208752A1 (ja) * | 2019-04-10 | 2020-10-15 | 三菱電機株式会社 | 室外ユニット、冷凍サイクル装置および冷凍機 |
WO2021048899A1 (ja) * | 2019-09-09 | 2021-03-18 | 三菱電機株式会社 | 室外ユニット及び冷凍サイクル装置 |
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2021
- 2021-05-25 WO PCT/JP2021/019829 patent/WO2022249288A1/ja active Application Filing
- 2021-05-25 EP EP21942943.8A patent/EP4350247A1/en active Pending
- 2021-05-25 CN CN202180098288.9A patent/CN117321352A/zh active Pending
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Patent Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2012088040A (ja) * | 2008-09-30 | 2012-05-10 | Daikin Industries Ltd | 冷凍装置 |
JP2012247154A (ja) | 2011-05-30 | 2012-12-13 | Denso Corp | 複数段圧縮式冷凍サイクル装置 |
JP2018132223A (ja) * | 2017-02-14 | 2018-08-23 | パナソニックIpマネジメント株式会社 | 冷凍装置 |
WO2020208752A1 (ja) * | 2019-04-10 | 2020-10-15 | 三菱電機株式会社 | 室外ユニット、冷凍サイクル装置および冷凍機 |
WO2021048899A1 (ja) * | 2019-09-09 | 2021-03-18 | 三菱電機株式会社 | 室外ユニット及び冷凍サイクル装置 |
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JP7466771B2 (ja) | 2024-04-12 |
EP4350247A1 (en) | 2024-04-10 |
JPWO2022249288A1 (ja) | 2022-12-01 |
CN117321352A (zh) | 2023-12-29 |
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