EP2728279B1 - Air conditioner - Google Patents

Air conditioner Download PDF

Info

Publication number
EP2728279B1
EP2728279B1 EP13191783.3A EP13191783A EP2728279B1 EP 2728279 B1 EP2728279 B1 EP 2728279B1 EP 13191783 A EP13191783 A EP 13191783A EP 2728279 B1 EP2728279 B1 EP 2728279B1
Authority
EP
European Patent Office
Prior art keywords
refrigerant
lubricant
accumulator
compressor
liquid
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP13191783.3A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP2728279A1 (en
Inventor
Atsuhiko Yokozeki
Susumu Nakayama
Hiroaki Tsuboe
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.)
Hitachi Johnson Controls Air Conditioning Inc
Original Assignee
Johnson Controls Hitachi Air Conditioning Technology Hong Kong Ltd
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
Family has litigation
First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=49517438&utm_source=google_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=EP2728279(B1) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Application filed by Johnson Controls Hitachi Air Conditioning Technology Hong Kong Ltd filed Critical Johnson Controls Hitachi Air Conditioning Technology Hong Kong Ltd
Publication of EP2728279A1 publication Critical patent/EP2728279A1/en
Application granted granted Critical
Publication of EP2728279B1 publication Critical patent/EP2728279B1/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

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
    • 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
    • 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
    • F25B31/00—Compressor arrangements
    • F25B31/002—Lubrication
    • F25B31/004—Lubrication oil recirculating 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
    • F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
    • F25B43/006—Accumulators
    • 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
    • F25B43/02—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat for separating lubricants from the refrigerant
    • 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
    • F25B9/006—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant containing more than one component
    • 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
    • F25B2500/00—Problems to be solved
    • F25B2500/06—Damage
    • 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
    • F25B2500/00—Problems to be solved
    • F25B2500/16—Lubrication

Definitions

  • the present invention relates to an air conditioner.
  • a known technique uses an HFC (Hydro Fluorocarbon) refrigerant as a refrigerant for an air conditioner and PVE (Polyvinylether) oil compatible with the refrigerant as refrigerating machine oil (Patent Literature 1).
  • PVE Polyvinylether
  • a known technique sets refrigerant quality on the suction side of the compressor at 0.65 or more and 0.85 or less to reduce the discharge temperature (Patent Literature 2).
  • R32 serving as an HFC refrigerant has been expected to be an environmentally-friendly refrigerant.
  • the compatibility of the refrigerant R32 reduces with a low lubricant mixing ratio, which causes an area where the mixture of the refrigerant R32 and the lubricant is separated into the two layers of the lubricant and a liquid refrigerant.
  • a refrigerant R32 is controlled to have less refrigerant quality on the suction side of a compressor than a conventional refrigerant R410A. Accordingly, when the R32 is used, a lubricant mixing ratio in the mixture of a liquid refrigerant and a lubricant inside an accumulator provided on the suction side of the compressor becomes low. For this reason, two-layer separation is likely to occur between the liquid refrigerant and the lubricant inside the accumulator, which makes it difficult to return the lubricant to the compressor. Thus, due to a shortage of the lubricant in the compressor, a problem such as improper lubrication is caused. As a result, reliability is decreased.
  • EP 0 485 979 A2 describes a refrigerating apparatus with a refrigerant composed mainly of a fluorocarbon type refrigerant containing no chlorine and having a critical temperature of 40 DEG C or higher, and a refrigerating machine oil comprising as base oil an ester oil of one or more fatty acids.
  • EP 1 174 665 A1 describes that moisture in a refrigeration circuit is absorbed by means of a polyvinyl ether oil that has hygroscopicity and serves as a refrigerating machine oil.
  • EP 1 275 912 A1 describes a refrigerant circuit.
  • the refrigerant circuit is charged with a single refrigerant of R32 or with an R32/R125 mixed refrigerant whose R32 content is not less than 75% by weight.
  • a resin material is used, and as an refrigeration oil a synthetic oil is used.
  • GB 2 159 260 A describes a heat pump having a plurality of compressors operated in parallel.
  • the heat pump has an improved supply of oil to the compressors.
  • an object of the present invention to provide an air conditioner capable of preventing the two-layer separation between a liquid refrigerant and a lubricant and reducing the occurrence of improper lubrication.
  • an air conditioner according to the present invention is the air conditioner in which an indoor unit and an outdoor unit are connected to each other via a pipe to circulate a refrigerant, characterized in that a refrigerant made of only R32 or a mixed refrigerant containing a predetermined mass percent or more of the R32 is used as the refrigerant, and the refrigerant mixed with a predetermined level or more of a lubricant to prevent an occurrence of two-layer separation between a liquid refrigerant and the lubricant is supplied to a compressor of the outdoor unit.
  • a refrigerant mixed with a predetermined level or more of a lubricant is supplied to a compressor in a case in which the refrigerant containing at least predetermined mass percent or more of R32 serving as an HFC refrigerant is used.
  • the mixing ratio of the lubricant is set at the predetermined level or more.
  • the lubricant separated by an oil separator connected to the discharge side of the compressor is returned to the accumulator so as to satisfy a predetermined condition.
  • the mixed refrigerant containing 70 mass percent or more of the R32 is used. This is because the mixed refrigerant with a ratio of 70 mass percent or more of the R32 becomes equal to the R32 in characteristics such as GWP levels, suction wetness, and compatibility with the oil.
  • the control of the mixing ratio of the lubricant in the mixture of the refrigerant R32 and the lubricant inside the accumulator it is possible to prevent the two-layer separation between the liquid refrigerant and the lubricant inside the accumulator.
  • FIG. 1 shows a configuration example of the refrigeration cycle of an air conditioner 1 according to the embodiment.
  • the refrigeration cycle of the air conditioner 1 includes at least one outdoor unit 100 and at least one indoor unit 200.
  • a plurality of indoor units 200A and 200B are shown in FIG. 1 , but they are called the indoor units 200 unless otherwise classified.
  • FIG. 1 shows a case in which one outdoor unit 100 and two indoor units 200 are connected to each other.
  • the refrigerant cycle may include two or more outdoor units 100 and three or more indoor units 200 connected to each other.
  • the outdoor unit 100 includes, for example, an outdoor heat exchanger 101, an outdoor fan 102, an outdoor expansion valve 103, a compressor 104, an accumulator 105, an oil separator 106, an oil return capillary 107, a four-way valve 108, a supercooling heat exchanger 109, a supercooling bypass expansion valve 110, and pipes 112 to 117.
  • Each of the indoor units 200 includes, for example, an indoor heat exchanger 201, an indoor fan 202, and an indoor expansion valve 203.
  • the outdoor unit 100 and the indoor units 200 are connected to each other by a liquid pipe 121 and a gas pipe 302.
  • a refrigerant made of only R32 or a mixed refrigerant containing 70 mass percent or more of the R32 is used.
  • the compressor 104 includes, for example, a crankcase and a compressor main body (both not shown) provided inside the crankcase, and a lubricant is accumulated at the bottom of the crankcase.
  • a lubricant is accumulated at the bottom of the crankcase.
  • the lubricant inside the crankcase is pumped up by the pumping action and supplied to a part where lubrication is required. Some of the lubricant is discharged to the discharge pipe 112 together with the refrigerant.
  • a low-pressure gaseous refrigerant flows in the compressor 104 from the accumulator 105 via the pipe 117.
  • the compressor 104 compresses the refrigerant to discharge a high-temperature and high-pressure gaseous refrigerant from the discharge port.
  • the high-pressure gaseous refrigerant discharged from the discharge port of the compressor 104 into the pipe 112 flows in the oil separator 106 via the pipe 112.
  • the high-temperature and high-pressure gaseous refrigerant discharged from the compressor 104 contains the lubricant.
  • the oil separator 106 collects the lubricant contained in the high-pressure gaseous refrigerant and returns the collected lubricant to the accumulator 105 via the oil return capillary 107 and the pipe 116.
  • the pipe 116 is a pipe used to connect the port on the compressor inflow port side of the four-way valve 108 and the inflow port of the accumulator 105 to each other.
  • the oil return capillary 107 as an example of a "supply oil amount control unit” is a unit used to control the flow and pressure of the lubricant returned from the oil separator 106 to the accumulator 105.
  • the four-way valve 108 is a direction switch valve used to select whether the high-pressure gaseous refrigerant is introduced into the outdoor heat exchanger 101 or the indoor heat exchangers 201 inside the indoor units 200. During a cooling operation, the four-way valve 108 causes the high-pressure gaseous refrigerant to flow in a direction as indicated by an arrow C in FIG. 1 .
  • the high-pressure gaseous refrigerant flows in the outdoor heat exchanger 101 serving as a condenser via the pipe 113 that connects the port on the outdoor heat exchanger side of the four-way valve 108 and the suction side of the outdoor heat exchanger 101 to each other.
  • the high-temperature and high-pressure gaseous refrigerant When passing through the outdoor heat exchanger 101, the high-temperature and high-pressure gaseous refrigerant is heat-exchanged with outdoor air supplied by the outdoor fan 102 for condensation and converted to a high-temperature and high-pressure liquid refrigerant (liquid refrigerant).
  • the high-temperature and high-pressure liquid refrigerant flows in the outdoor expansion valve 103 via the pipe 114 connected to the exit side of the outdoor heat exchanger 101.
  • a low-pressure liquid refrigerant flowing out from the outdoor expansion valve 103 is branched off. Among the branched liquid refrigerant, some flows in the supercooling bypass expansion valve 110 while other flows in a pipe 301 after being further cooled via the supercooling heat exchanger 109.
  • the pipe 301 is a pipe used to connect the heat exchanger 101 of the outdoor unit 100 and the heat exchangers 201 of the indoor units 200 to each other.
  • the liquid refrigerant flowing in the supercooling bypass expansion valve 110 is depressurized by the supercooling bypass expansion valve 110 and flows in the supercooling heat exchanger 109.
  • the liquid refrigerant flowing in the supercooling heat exchanger 109 is heat-exchanged with another liquid refrigerant for evaporation and converted to a low-pressure gaseous refrigerant.
  • the low-pressure gaseous refrigerant flows in the accumulator 105 via the return pipe 115 connected to the pipe 116.
  • the low-pressure liquid refrigerant supplied to the indoor units 200 is depressurized by the indoor expansion valves 203 and flows in the indoor heat exchangers 201.
  • the low-pressure liquid refrigerant flowing in the indoor heat exchangers 201 is heat-exchanged with indoor air supplied by the indoor fans 202 for evaporation and converted to a gaseous refrigerant (gas refrigerant).
  • the gas refrigerant flowing in the outdoor unit 100 flows in the accumulator 105 via the four-way valve 108 and the pipe 116.
  • the accumulator 105 accumulates a non-evaporated liquid refrigerant to prevent the liquid refrigerant from flowing in the compressor 104. This is because there is a likelihood of damage or the like to the parts of the compressor 104 when the compressor 104 compresses the liquid refrigerant.
  • the gaseous refrigerant, the liquid refrigerant, and the lubricant returned from the oil separator 106 flow in the accumulator 105.
  • the gas refrigerant and the lubricant are mixed together inside the accumulator 105 and supplied to the compressor 104.
  • the liquid refrigerant remains in the accumulator 105.
  • a heating operation will be described.
  • the flow of a refrigerant at the heating operation is indicated by an arrow H.
  • a high-temperature and high-pressure gas refrigerant discharged from the compressor 104 is supplied to the gas pipe 302 via the four-way valve 108.
  • the lubricant separated by the oil separator 106 is supplied to the accumulator 105 via the oil return capillary 107.
  • the high-temperature and high-pressure gas refrigerant from the outdoor unit 100 is supplied to the indoor units 200 via the gas pipe 302.
  • the high-temperature gas refrigerant supplied to the indoor units 200 is heat-exchanged with indoor air supplied by the indoor fans 202 for condensation and converted to a liquid refrigerant.
  • the liquid refrigerant flows out from the indoor units 200 via the indoor expansion valves 203.
  • the high-temperature and high-pressure gas refrigerant is heat-exchanged with the indoor air at the indoor heat exchangers 201 to perform the heating operation.
  • the liquid refrigerant flowing out from the indoor units 200 flows in the outdoor unit 100 via the liquid pipe 301. After passing through the outdoor expansion valve 103, the liquid refrigerant flowing in the outdoor unit 100 is branched off into two liquid refrigerants. Among the branched liquid refrigerants, some flows in the supercooling bypass expansion valve 110 and is supplied to the accumulator 105 via the pipes 115 and 116.
  • liquid refrigerant is depressurized by the outdoor expansion valve 103 and then flows in the outdoor heat exchanger 101.
  • the liquid refrigerant is heat-exchanged with outdoor air supplied by the outdoor fan 102 for evaporation and converted to a gas refrigerant.
  • the gas refrigerant flows in the accumulator 105 via the four-way valve 108 and the pipe 116. As described above, the gas refrigerant and the lubricant flow in the accumulator 105 to be mixed together, and the gas refrigerant containing the lubricant is supplied to the compressor 104.
  • FIG. 2 shows the accumulator 105 inside the outdoor unit 100 of the refrigeration cycle in FIG. 1 .
  • the introduction pipe 116 is a pipe used to introduce the gas refrigerant and/or the lubricant into the accumulator 105.
  • the delivery pipe 117 has a substantially U-shape on the tip end side thereof and is a pipe used to supply the gas refrigerant mixed with the lubricant from the accumulator 105 to the compressor 104.
  • the delivery pipe 117 is attached to the accumulator 105 with the U-shaped curve thereof positioned on the bottom side of the accumulator 105.
  • the U-shaped curve of the delivery pipe 117 is soaked in the liquid refrigerant accumulated in the accumulator 105.
  • the delivery pipe 117 has a first liquid return port 121A at the U-shaped curve thereof.
  • the delivery pipe 117 has a second liquid return port 121B positioned on an upper side than the first liquid return port 121A.
  • the delivery pipe 117 has, on the upper side thereof, a pressure equalization hole 122 positioned on the upper side of the accumulator 105 and used to control pressure inside the delivery pipe 117.
  • the refrigerant and lubricant flowing in the accumulator 105 via the introduction pipe 116 are separated into the liquid and gas.
  • the gas refrigerant is supplied to the compressor 104 via the delivery pipe 117. With the circulation of the gas refrigerant, the liquid is sucked in the delivery pipe 117 from the first liquid return port 121A and supplied from the accumulator 105 to the compressor 104 at a predetermined liquid mixing ratio.
  • the liquid level of the accumulator 105 is above the second liquid return port 121B, the liquid is also sucked from the second liquid return port 121B, which increases the liquid mixing ratio.
  • the liquid mixing ratio is controlled by the hole diameters of the two liquid return ports 121A and 121B and the hole diameter of the pressure equalization hole 122.
  • a conventional refrigerant R410A is replaced with the refrigerant R32 having a lower GWP.
  • the use of the R32 as a refrigerant results in an increase in the discharge temperature of the compressor 104 by 10 to 15°C.
  • the suction quality of the compressor 104 is kept at a lower level than in the past to prevent the increase in the discharge temperature.
  • the accumulator 105 of the embodiment accumulates a greater amount of the liquid refrigerant than the conventional refrigerant R410A.
  • the lubricant mixing ratio in the mixture accumulated at the lower part of the accumulator 105 becomes low.
  • FIG. 3 shows the mixing characteristics of the refrigerant and the lubricant in a case in which the R32 is used as a refrigerant. If the lubricant mixing ratio becomes 40% or less in the refrigerant R32, a two-layer separation area including the layers of the liquid refrigerant and the lubricant occurs at low temperature. That is, the liquid refrigerant is accumulated on the lower side of the accumulator 105, and the layer of the lubricant is formed on the layer of the liquid refrigerant.
  • the mixture is separated into the liquid refrigerant and the lubricant on the lower side of the accumulator 105. If the density of the lubricant is lower than that of the liquid refrigerant, the lubricant floats on the upper side. When floating on the upper side of the liquid refrigerant, the lubricant is not sucked in the delivery pipe 117 from the first liquid return port 121A, which reduces the amount of the lubricant supplied to the compressor 104. The reduction in the amount of the lubricant supplied to the compressor 104 causes a problem such as improper lubrication. As a result, reliability may be decreased.
  • the shape (such as the pipe area and pipe length) of the oil return capillary 107 is designed such that a predetermined amount or more of the lubricant collected by the oil separator 106 is returned to the accumulator 105.
  • a method for setting the design is as follows.
  • the oil return ratio x of the lubricant flowing through the oil return capillary 107 is found by the following formula (1) .
  • the ratio R of the liquid flowing from the accumulator 105 to the compressor 104 is controlled by the hole diameters of the liquid return ports 121A and 121B and the hole diameter of the pressure equalization hole 122 of the delivery pipe 117 of the accumulator 105.
  • the circulation ratio y of the lubricant flowing from the oil separator 106 to the refrigeration cycle depends on the characteristics of the compressor 104 and the oil separator 106.
  • the use of the R32 as a refrigerant requires an increase in the amount of the liquid refrigerant accumulated in the accumulator 105, which reduces the lubricant mixing ratio.
  • a greater amount of the lubricant collected by the oil separator 106 is returned to the accumulator 105 than in the past. Therefore, the lubricant mixing ratio in the accumulator 105 can be increased to a predetermined level (40% or more and preferably 50% or more).
  • means for returning the lubricant from the oil separator to the accumulator is not limited to the oil return capillary but may be replaced by other means.
  • the present invention can be expressed as, for example, "the outdoor unit for the air conditioner that uses the refrigerant made of only the R32 or the mixed refrigerant containing a predetermined mass percent or more of the R32 as a refrigerant and supplies to the compressor the refrigerant mixed with a predetermined level or more of the lubricant to prevent the occurrence of the two-layer separation between the liquid refrigerant and the lubricant.”

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Power Engineering (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Lubricants (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
EP13191783.3A 2012-11-06 2013-11-06 Air conditioner Active EP2728279B1 (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2012244492A JP5927633B2 (ja) 2012-11-06 2012-11-06 空気調和機

Publications (2)

Publication Number Publication Date
EP2728279A1 EP2728279A1 (en) 2014-05-07
EP2728279B1 true EP2728279B1 (en) 2018-01-10

Family

ID=49517438

Family Applications (1)

Application Number Title Priority Date Filing Date
EP13191783.3A Active EP2728279B1 (en) 2012-11-06 2013-11-06 Air conditioner

Country Status (4)

Country Link
EP (1) EP2728279B1 (zh)
JP (1) JP5927633B2 (zh)
CN (2) CN106382768B (zh)
ES (1) ES2661868T3 (zh)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR20160030998A (ko) * 2013-09-05 2016-03-21 도시바 캐리어 가부시키가이샤 압축기 및 냉동 사이클 장치
JP6736910B2 (ja) * 2016-02-25 2020-08-05 ダイキン工業株式会社 冷凍装置
JP2018194200A (ja) * 2017-05-15 2018-12-06 パナソニックＩｐマネジメント株式会社 冷凍サイクル装置およびそれを備えた液体循環装置
US11162705B2 (en) 2019-08-29 2021-11-02 Hitachi-Johnson Controls Air Conditioning, Inc Refrigeration cycle control
CN114111112B (zh) * 2021-12-01 2023-06-20 天津双昊车用空调有限公司 一种气液分离的自适应回油工艺

Family Cites Families (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS60245960A (ja) * 1984-05-18 1985-12-05 三菱電機株式会社 空気調和機の冷凍サイクル
JP2967574B2 (ja) * 1990-11-16 1999-10-25 株式会社日立製作所 冷凍装置
JPH08159569A (ja) * 1994-11-30 1996-06-21 Sanyo Electric Co Ltd 冷凍装置
JP3658993B2 (ja) 1998-05-13 2005-06-15 株式会社日立製作所 冷媒圧縮機および冷凍装置
JP3956589B2 (ja) 1999-10-18 2007-08-08 ダイキン工業株式会社 冷凍装置
JP4836305B2 (ja) * 2000-02-16 2011-12-14 ダイキン工業株式会社 冷凍装置
JP4815656B2 (ja) * 2000-04-19 2011-11-16 ダイキン工業株式会社 冷凍装置
JP4039921B2 (ja) * 2002-09-11 2008-01-30 三洋電機株式会社 遷臨界冷媒サイクル装置
JP4295530B2 (ja) * 2003-03-04 2009-07-15 東芝キヤリア株式会社 空気調和装置
JP2005083704A (ja) * 2003-09-10 2005-03-31 Mitsubishi Electric Corp 冷凍サイクル、空気調和機
JP5502459B2 (ja) * 2009-12-25 2014-05-28 三洋電機株式会社 冷凍装置
JP2011208860A (ja) * 2010-03-29 2011-10-20 Hitachi Appliances Inc 空気調和機

Non-Patent Citations (1)

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

Also Published As

Publication number Publication date
JP2014092339A (ja) 2014-05-19
CN106382768B (zh) 2019-07-30
CN106382768A (zh) 2017-02-08
EP2728279A1 (en) 2014-05-07
CN103808070B (zh) 2016-09-21
ES2661868T3 (es) 2018-04-04
CN103808070A (zh) 2014-05-21
JP5927633B2 (ja) 2016-06-01

Similar Documents

Publication Publication Date Title
EP2728279B1 (en) Air conditioner
KR100952037B1 (ko) 냉동장치
KR100990570B1 (ko) 냉동장치
CN117515934A (zh) Hvacr系统的润滑剂管理
KR101309325B1 (ko) 냉동 사이클 장치
CN106662365B (zh) 基于改进的直接膨胀式蒸发器的冷冻器系统
KR102099665B1 (ko) 냉동 사이클의 오일 복귀 회로 및 오일 복귀 방법
KR20070046967A (ko) 냉동장치
EP2873935A1 (en) Freezer
KR20080111146A (ko) 냉동장치
US9791176B2 (en) Refrigeration apparatus
EP3306098B1 (en) Refrigeration cycle system
JP3882841B2 (ja) 空気調和装置、熱源ユニット、及び空気調和装置の更新方法
JP2013024447A (ja) 冷凍装置
JP5940489B2 (ja) 空気調和装置
CN112648754B (zh) 一种空调循环系统及其循环方法
JP2015158317A (ja) 空気調和装置
JP6507121B2 (ja) 空気調和機
JP2008082674A (ja) 過冷却装置
JP2009036508A (ja) 過冷却装置
JPH10246521A (ja) 冷凍・空調装置、及び冷媒回路組立方法
JP2008082676A (ja) 過冷却装置
JP5193450B2 (ja) 過冷却装置
JP2008082677A (ja) 過冷却装置
JP2009024998A (ja) 過冷却装置

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20131213

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

AX Request for extension of the european patent

Extension state: BA ME

RAP1 Party data changed (applicant data changed or rights of an application transferred)

Owner name: JOHNSON CONTROLS-HITACHI AIR CONDITIONING TECHNOLO

RIC1 Information provided on ipc code assigned before grant

Ipc: F25B 9/00 20060101AFI20170613BHEP

Ipc: F25B 31/00 20060101ALI20170613BHEP

Ipc: F25B 43/00 20060101ALI20170613BHEP

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

INTG Intention to grant announced

Effective date: 20170725

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

Ref country code: AT

Ref legal event code: REF

Ref document number: 962831

Country of ref document: AT

Kind code of ref document: T

Effective date: 20180115

REG Reference to a national code

Ref country code: DE

Ref legal event code: R082

Ref document number: 602013032046

Country of ref document: DE

Representative=s name: MERH-IP MATIAS ERNY REICHL HOFFMANN PATENTANWA, DE

Ref country code: DE

Ref legal event code: R081

Ref document number: 602013032046

Country of ref document: DE

Owner name: HITACHI-JOHNSON CONTROLS AIR CONDITIONING, INC, JP

Free format text: FORMER OWNER: JOHNSON CONTROLS-HITACHI AIR CONDITIONING TECHNOLOGY (HONG KONG) LTD., HONG KONG, HK

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 602013032046

Country of ref document: DE

RAP2 Party data changed (patent owner data changed or rights of a patent transferred)

Owner name: HITACHI-JOHNSON CONTROLS AIR CONDITIONING, INC.

REG Reference to a national code

Ref country code: ES

Ref legal event code: FG2A

Ref document number: 2661868

Country of ref document: ES

Kind code of ref document: T3

Effective date: 20180404

REG Reference to a national code

Ref country code: NL

Ref legal event code: MP

Effective date: 20180110

REG Reference to a national code

Ref country code: AT

Ref legal event code: MK05

Ref document number: 962831

Country of ref document: AT

Kind code of ref document: T

Effective date: 20180110

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: NL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180110

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180110

Ref country code: CY

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180110

Ref country code: HR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180110

Ref country code: NO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180410

Ref country code: FI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180110

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: BG

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180410

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180411

Ref country code: PL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180110

Ref country code: LV

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180110

Ref country code: SE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180110

Ref country code: AT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180110

Ref country code: RS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180110

Ref country code: IS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180510

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 602013032046

Country of ref document: DE

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 6

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: EE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180110

Ref country code: AL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180110

Ref country code: RO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180110

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180110

Ref country code: CZ

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180110

Ref country code: SM

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180110

Ref country code: SK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180110

26N No opposition filed

Effective date: 20181011

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180110

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MC

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180110

Ref country code: LU

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20181106

REG Reference to a national code

Ref country code: BE

Ref legal event code: MM

Effective date: 20181130

REG Reference to a national code

Ref country code: IE

Ref legal event code: MM4A

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LI

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20181130

Ref country code: CH

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20181130

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20181106

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: BE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20181130

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20181106

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: TR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180110

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: PT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180110

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MK

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20180110

Ref country code: HU

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT; INVALID AB INITIO

Effective date: 20131106

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 20231019

Year of fee payment: 11

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: ES

Payment date: 20231201

Year of fee payment: 11

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: IT

Payment date: 20231019

Year of fee payment: 11

Ref country code: FR

Payment date: 20231019

Year of fee payment: 11

Ref country code: DE

Payment date: 20231019

Year of fee payment: 11