US20100115979A1 - Distributor and refrigerant circulation system comprising the same - Google Patents

Distributor and refrigerant circulation system comprising the same Download PDF

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Publication number
US20100115979A1
US20100115979A1 US12/611,357 US61135709A US2010115979A1 US 20100115979 A1 US20100115979 A1 US 20100115979A1 US 61135709 A US61135709 A US 61135709A US 2010115979 A1 US2010115979 A1 US 2010115979A1
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US
United States
Prior art keywords
distribution
flow passage
distributor
unit
inlet
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.)
Abandoned
Application number
US12/611,357
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English (en)
Inventor
Han Choon Lee
Hong Seong Kim
Sang Yeul Lee
Yong Cheol Sa
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.)
LG Electronics Inc
Original Assignee
LG Electronics Inc
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 LG Electronics Inc filed Critical LG Electronics Inc
Assigned to LG ELECTRONICS INC. reassignment LG ELECTRONICS INC. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: KIM, HONG SEONG, LEE, HAN CHOON, LEE, SANG YEUL, SA, YONG CHEOL
Publication of US20100115979A1 publication Critical patent/US20100115979A1/en
Abandoned 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
    • F25B39/00—Evaporators; Condensers
    • F25B39/02—Evaporators
    • F25B39/028—Evaporators having distributing means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
    • F24F1/06—Separate outdoor units, e.g. outdoor unit to be linked to a separate room comprising a compressor and a heat exchanger
    • F24F1/26—Refrigerant piping
    • F24F1/28—Refrigerant piping for connecting several separate outdoor units
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
    • F24F1/06—Separate outdoor units, e.g. outdoor unit to be linked to a separate room comprising a compressor and a heat exchanger
    • F24F1/26—Refrigerant piping
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/40—Fluid line arrangements
    • F25B41/42—Arrangements for diverging or converging flows, e.g. branch lines or junctions
    • F25B41/45—Arrangements for diverging or converging flows, e.g. branch lines or junctions for flow control on the upstream side of the diverging point, e.g. with spiral structure for generating turbulence
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/40—Fluid line arrangements
    • F25B41/42—Arrangements for diverging or converging flows, e.g. branch lines or junctions
    • F25B41/48—Arrangements for diverging or converging flows, e.g. branch lines or junctions for flow path resistance control on the downstream side of the diverging point, e.g. by an orifice

Definitions

  • the embodiment relates to a distributor, and more particularly, to a distributor which allows inputted liquid and gaseous refrigerants to evenly flow and be discharged and a refrigerant circulation system comprising the same.
  • an air conditioner is a home appliance that cools or heats a predetermined space by using a refrigeration system using characteristics depending on changes in pressure and temperature of refrigerants.
  • FIG. 1 is a configuration diagram schematically showing a general refrigeration system.
  • the refrigeration system includes a compressor 10 that compresses the refrigerant in a high-temperature and high-pressure gaseous state, a condenser 20 that condenses refrigerant compressed by the compressor 10 into a liquid state by heat radiation using air blowing of a cooling fan 22 , a capillary tube 40 that expands the liquid refrigerant condensed by the condenser 20 into low-pressure liquid refrigerant by a throttle operation, a distributor 30 that evenly distributes the liquid refrigerant condensed by the condenser 20 to the capillary tube 40 , and an evaporator 50 that evaporates the low-temperature and low-pressure refrigerant expanded by the capillary tube 40 into low-temperature and low-pressure gaseous refrigerant at the same time when providing cool air by using evaporation latent heat while evaporating the low-temperature and low-pressure refrigerant expanded by the capillary tube 40 by air blowing of the cooling fan 52
  • the distributor 30 includes an inlet flow passage that is in communication with the capillary tube 40 and the evaporator 50 , more specifically, a plurality of distribution flow passages that are in communication with a plurality of tubes constituting the evaporator 50 .
  • the inlet flow passage and the distribution flow passages are in communication with each other, such that the liquid refrigerant that flows in the inlet flow passage through the inlet flow passage is distributed into tubes of the evaporator 50 through the distribution flow passages.
  • the refrigerant that flows in the inlet flow passage in part includes the liquid refrigerant and the gaseous refrigerant.
  • the liquid refrigerant and the gaseous refrigerant have specific gravities different from each other, the liquid refrigerant and the gaseous refrigerant that flow in the inlet flow passage through the capillary tube 40 are not evenly mixed with each other and the liquid refrigerant flows in some of the tubes of the evaporator 50 and the gaseous refrigerant flows in other tubes of the evaporator 50 through the distribution flow passage, such that the efficiency of a heat exchange cycle is deteriorated.
  • the embodiment relates to a distributor.
  • refrigerant that flows in from an inlet pipe flows through an inlet flow passage of the distributor to be thus transferred to the distribution flow passage of the distributor, such that the refrigerant flows on the distribution flow passage to be evenly distributed and transferred to a plurality of outlet pipes.
  • the refrigerant that flows in through an inlet pipe by the distributor is evenly distributed to the plurality of outlet pipes.
  • FIG. 1 is a configuration diagram of a general cooling cycle
  • FIG. 2 is a perspective view showing an embodiment of a distributor according to the present invention.
  • FIG. 3 is an exploded cross-sectional view of an embodiment of the present invention.
  • FIG. 4 is a cross-sectional view of an embodiment of the present invention.
  • FIG. 5 is a cross-sectional view showing a process in which refrigerant is distributed by an embodiment of a distributor according to the present invention.
  • FIG. 2 is a perspective of a distributor according to an embodiment of the present invention.
  • FIG. 3 is an exploded cross-sectional view according to an embodiment of the present invention.
  • FIG. 4 is a cross-sectional view according to an embodiment of the present invention.
  • the distributor 100 includes a distributor body 110 and a distributor head 120 .
  • the distributor body 110 is inserted and fixed into the distributor head 120 .
  • the distributor body 110 can be fixed with being inserted into the distributor head 120 by bonding or soldering.
  • the distributor body 110 is formed in a hollow cylindrical shape having generally the same diameter. Accordingly, an inner diameter and an outer diameter of the distributor body 110 generally have the same value. In addition, an inlet flow passage 111 and a mixed flow passage 113 are provided in the distributor body 110 .
  • the inlet flow passage 111 is provided at a central portion and a lower portion of the distributor body 110 in the figure.
  • An inlet pipe 10 (see FIG. 4 ) for transferring refrigerant expanded at low pressure in a capillary tube (not shown) is connected to a lower end in the figure, that is, to a upstream portion of the inlet flow passage 111 .
  • the capillary tube may be directly connected.
  • an upper end in the figure, that is, a downstream portion of the inlet flow passage 111 is in communication with a lower end in the figure of the mixed flow passage 113 .
  • Liquid refrigerant and some gaseous refrigerant expanded by the capillary tube flow in the inlet flow passage 111 .
  • the mixed flow passage 113 is provided at a central portion and a lower portion of the distributor body 110 in the figure.
  • the mixed flow passage 113 has a flow cross-sectional area comparatively smaller than the inlet flow passage 111 .
  • a downstream portion of the mixed flow passage 113 is in communication with an upstream portion of a distribution flow passage 121 to be described below.
  • the liquid and gaseous refrigerants that flow on the inlet flow passage 111 flow in the mixed flow passage 113 .
  • the mixed flow passage 113 has a flow cross-sectional area smaller than the inlet flow passage 111 . Accordingly, the liquid and gaseous refrigerants that flow on the inlet flow passage 111 are mixed with each other.
  • the liquid refrigerant has a specific gravity comparatively larger than the gaseous refrigerant. Therefore, for example, like a case in which the refrigerant is transferred to the inlet flow passage 111 through the inlet pipe 10 having a J or U shape, when the liquid and gaseous refrigerants that flow in the inlet flow passage 111 flow on not a linear trajectory but a curved trajectory, the liquid refrigerant flows in one portion of the inlet flow passage 111 adjacent to an inner peripheral surface of the distributor body 110 and the gaseous refrigerant flows at the rest portion of the inlet flow passage 111 .
  • liquid and gaseous refrigerants that flow on the inlet flow passage 111 which are partitioned from each other, flow in different directions to be mixed with each other while flowing on the mixed flow passage 113 having a flow cross-sectional area comparatively smaller than the inlet flow passage 111 .
  • the flow cross-sectional area of the mixed flow passage 113 is substantially reduced by a flow interference unit 115 provided on the top of the inner peripheral surface of the distributor body 110 .
  • the flow interference unit 115 extends radially on the top of the inner peripheral surface of the distributor body 110 . Therefore, a part of the downstream portion of the inlet flow passage 111 has a diameter comparatively smaller than the rest portions of the inlet flow passage 111 by the flow interference unit 115 , such that the mixed flow passage 113 may be formed.
  • one surface of the flow interference unit 115 facing the downstream portion of the inlet flow passage 111 that is, the bottom of the flow interference unit 115 in the figure is rounded.
  • This purpose is to prevent a vortex phenomenon from being generated by an edge between the inner peripheral surface of the distributor body 110 corresponding to the downstream portion of the inlet flow passage 111 and one surface of the flow interference unit 115 while the liquid and gaseous refrigerants are transferred to the mixed flow passage 113 .
  • a projection portion 117 is provided in the distributor body 110 .
  • the projection portion 117 of the distributor body 110 is provided on the inlet flow passage 111 .
  • An end portion of the inlet pipe 10 connected to the inlet flow passage 111 is suspended on the projection portion 117 of the distributor body 110 .
  • the projection portion 117 of the distributor body 110 is substantially formed by stepping the upstream portion and the downstream portion of the inlet flow passage 111 .
  • a lower portion in the figure of the distributor head 120 that is, the upstream portion is formed in a hollow cylindrical shape having an inner diameter corresponding to an outer diameter of the distributor body 110 .
  • an upper portion in the figure of the distributor head 120 that is, the downstream portion has a cone shape of which a diameter gradually increases in comparison with the lower portion in the figure the distributor head 120 .
  • the upstream portion and the downstream portion of the distributor head 120 are preferably formed integrally with each other.
  • the distribution flow passage 121 is provided in the distributor head 120 .
  • the distribution flow passage 121 is configured to distribute the liquid and gaseous refrigerants that are mixed with each other while flowing on the mixed flow passage 113 to a plurality of tubes (not shown) constituting an evaporator (not shown).
  • the distribution flow passage 121 includes a mixing unit 122 and a plurality of distribution units 123 .
  • a lower portion in the figure of the mixing unit 122 that is, the upstream portion is in communication with the mixed flow passage 113 .
  • an upper portion in the figure of the mixing unit 122 that is, the downstream portion is in communication with lower portions in the figure of the plurality of distribution units 123 , that upstream end portions.
  • the upstream portion of the mixing unit 122 has a flow cross-sectional area comparatively larger than the mixed flow passage 113 . It can be expected a phenomenon that the liquid and gaseous refrigerants that are mixed in the mixed flow passage 113 and transferred to the mixing unit 122 are once again mixed.
  • the upstream portion of the mixing unit 122 has the same flow cross-sectional area as the inlet flow passage 111 , but is not necessarily limited thereto and may have a flow cross-sectional area comparatively larger than the mixed flow passage 113 .
  • the downstream portion of the mixing unit 122 has a flow cross-sectional area that is reduced toward the distribution unit 123 . This purpose is to evenly distribute and transfer the refrigerant that flows on the mixing unit 122 to the distribution unit 123 .
  • the downstream portion of the mixing unit 122 has a cone shape using a virtual plane generally perpendicularly passing through a virtual straight line parallel to a flow direction of the refrigerant. More specifically, in the downstream portion of the mixing unit 122 , the top of the cone projected on the downstream portion of the mixing unit 122 is cut, such that a cross section in a direction where the refrigerant flows has a trapezoidal shape.
  • each lower portion in the figure that is, the upstream portion is in communication with the downstream portion of the mixing unit 122 .
  • the upstream portions of the distribution unit 123 are positioned separated from each other by a predetermined central angle on a virtual circular shape having the same circular center at the downstream portion of the mixing unit 122 corresponding to a cone-shape outer peripheral surface.
  • an upstream end portion to a downstream end portion of the distribution unit 123 extends to slope in the direction where the refrigerant flows at a predetermined angle.
  • the outlet pipe 20 (see FIG. 4 ) for transferring the refrigerant to the tube is connected to the downstream portion of the distribution unit 123 .
  • a distribution projection 125 is provided in the distributor head 120 corresponding to an inner part of the distribution flow passage 121 .
  • a part of the downstream portion of the mixing unit 122 excluding a portion which is in communication with the upstream end portion of the distribution unit 123 is projected in a direction opposite to the flowing direction of the refrigerant to form the distribution projection 125 .
  • the distribution projection 125 has the cone shape as a whole, but the shape of the distribution projection 125 is not limited thereto.
  • the distribution projection 125 is configured to evenly distribute the refrigerant that flows on the mixing unit 122 to the distribution unit 123 . That is, the refrigerant that flows on the distribution unit 123 flows substantially toward the distribution unit 123 by the distribution projection 125 . Further, the distribution projection 125 serves to reduce the flow cross-sectional area of the downstream portion of the mixing unit 122 which is in communication with the distribution unit 123 toward the distribution unit 123 .
  • a projection portion 127 is provided in the distributor head 120 .
  • the projection portion 127 of the distributor head 120 is provided on the distribution unit 123 adjacent to the downstream end portion of the distribution unit 123 .
  • the projection portion 127 of the distributor head 120 is a location on which an end portion of the outlet pipe 20 connected to the downstream end portion of the distribution unit 123 is suspended.
  • the projection portion 127 of the distributor head 120 is formed by stepping the distribution unit 123 .
  • FIG. 5 is a cross-sectional view showing a process in which refrigerant is distributed by an embodiment of a distributor according to the present invention.
  • refrigerant expanded in a capillary tube is first transferred to an inlet flow passage 111 through an inlet pipe 10 .
  • most of refrigerants transferred to the inlet flow passage 111 are a liquid refrigerant (indicated by solid lines in the figure), but some of refrigerants are transferred to the inlet flow passage 111 as a gaseous refrigerant (indicated by dot lines in the figure).
  • liquid refrigerant will flow on a part of the inlet flow passage 111 mainly adjacent to an inner surface of the distributor body 110 and the gaseous refrigerant will flow on the rest part of the inlet flow passage 111 by a difference in centrifugal force depending on a difference in specific gravity between the liquid refrigerant and the gaseous refrigerant.
  • the liquid and gaseous refrigerants that flow on the inlet flow passage 111 are transferred to the mixed flow passage 113 .
  • the liquid and gaseous refrigerants transferred to the mixed flow passage 113 are mixed with each other to be transferred to the distribution flow passage 121 while flowing on the mixed flow passage 113 .
  • the mixed flow passage 113 has a flow cross-sectional area comparatively smaller than the distribution flow passage 121 as described above. Accordingly, the liquid and gaseous refrigerants are mixed with each other to be transferred to the distribution flow passage 121 while flowing on the mixed flow passage 113 .
  • the liquid and gaseous refrigerants transferred to the distribution flow passage 121 are remixed in the mixing unit 122 of the distribution flow passage 121 having the flow cross-sectional area comparatively larger than the mixed flow passage 113 .
  • the liquid and gaseous refrigerants that are remixed in the mixing unit 122 are transferred to the outlet pipe connected to the distribution unit 123 through the distribution unit 123 of the distribution flow passage 121 .
  • the flow cross-sectional area of the downstream portion of the mixing unit 122 is reduced toward the distribution unit 123 by the distribution projection 125 . Further, the refrigerant that flows on the mixing unit 122 is substantially guided to the distribution unit 123 by the distribution projection 125 . Accordingly, the refrigerant that flows on the mixing unit 122 can be evenly distributed to the outlet pipe 20 through the distribution unit 123 .
  • the refrigerant that flows on the outlet pipe 20 is transferred to tubes of an evaporator (not shown) connected to the outlet pipe 20 .
  • the refrigerant transferred to the evaporator by circulating a compressor (not shown), a condenser (not shown), a capillary tube (not shown), a distributor (not shown), and an evaporator in sequence to drive a refrigeration cycle.
  • a component forming the mixed flow passage is referred to as a flow interference unit, but its name is not limited to the flow interference unit. That is, when an inlet direction of the refrigerant that flows in the inlet flow passage can be substantially changed, although the component is referred to as another name, for example, a direction converting unit, the component will be substantially the same component.
  • one surface of the flow interference unit facing the inlet flow passage is rounded, but is not limited thereto. That is, one surface of the flow interference unit facing the inlet flow passage may be perpendicular to the flowing direction of the refrigerant that flows on the inlet flow passage.
  • a refrigerant that flows in through an inlet pipe is evenly distributed and discharged to a plurality of outlet pipes. Accordingly, according to the present invention, the refrigerant that is evenly distributed to the outlet pipe is transferred to a plurality of tubes constituting, for example, an evaporator, such that it can be expected an effect in which the efficiency of a refrigeration cycle is substantially increased.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Details Of Heat-Exchange And Heat-Transfer (AREA)
  • Branch Pipes, Bends, And The Like (AREA)
US12/611,357 2008-11-10 2009-11-03 Distributor and refrigerant circulation system comprising the same Abandoned US20100115979A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
KR10-2008-0111315 2008-11-10
KR1020080111315A KR101547353B1 (ko) 2008-11-10 2008-11-10 분배기 및 이를 포함하는 냉매순환시스템

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US20100115979A1 true US20100115979A1 (en) 2010-05-13

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US12/611,357 Abandoned US20100115979A1 (en) 2008-11-10 2009-11-03 Distributor and refrigerant circulation system comprising the same

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US (1) US20100115979A1 (fr)
EP (1) EP2184564A3 (fr)
KR (1) KR101547353B1 (fr)
CN (1) CN101738026A (fr)

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20130087204A1 (en) * 2011-10-07 2013-04-11 Trane International Inc. Pressure Correcting Distributor For Heating and Cooling Systems
US20140290298A1 (en) * 2010-02-10 2014-10-02 Mitsubishi Electric Corporation Refrigeration cycle apparatus
US20150000332A1 (en) * 2012-02-10 2015-01-01 Daikin Industries, Ltd. Air conditioner
JP2015001335A (ja) * 2013-06-14 2015-01-05 三菱電機株式会社 冷媒分流器、及び、冷凍サイクル装置
US20160054037A1 (en) * 2013-04-09 2016-02-25 BSH Hausgeräte GmbH Refrigeration Device Comprising an Evaporator
US10161656B2 (en) * 2014-08-14 2018-12-25 Lg Electronics Inc. Air conditioner having a bending tube which alters the flow of the refrigerant prior to entering the distributor
JP2020008214A (ja) * 2018-07-06 2020-01-16 株式会社コロナ 冷房装置
US20220412620A1 (en) * 2020-03-03 2022-12-29 Japan Climate Systems Corporation Refrigerant distributor

Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AU2012202150B1 (en) 2012-04-13 2013-07-11 Process Development Centre Pty Ltd. A flow distributor
KR20160002702U (ko) 2015-01-26 2016-08-03 곽현만 공기조화기의 냉매 분배기
KR20180089657A (ko) 2017-02-01 2018-08-09 엘지전자 주식회사 분배기 및 이를 포함하는 공기 조화기
CN106885400A (zh) * 2017-04-12 2017-06-23 广东美的暖通设备有限公司 制冷装置的分配器的均流结构及分配器
KR200490115Y1 (ko) 2017-05-16 2019-09-26 곽현만 공기조화기의 냉매 분배기
KR20190031673A (ko) 2017-09-18 2019-03-27 곽현만 공기조화기용 냉매 분배기와 그 성형방법
CN109631426B (zh) * 2019-01-22 2024-07-23 杭州沈氏节能科技股份有限公司 分液器及具有其的制冷系统
KR102405378B1 (ko) * 2020-10-27 2022-06-03 이진환 자동조절 냉매 분배기
KR20230162191A (ko) 2022-05-20 2023-11-28 오재윤 유체 분배기

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US5243838A (en) * 1989-08-18 1993-09-14 Matsushita Refrigeration Company Refrigerant shunt
US7174726B2 (en) * 2003-08-07 2007-02-13 Parker-Hannifin Corporation Adjustable nozzle distributor
US20070245769A1 (en) * 2006-04-21 2007-10-25 Parker Christian D Fluid expansion-distribution assembly
US7600393B2 (en) * 2005-03-09 2009-10-13 Lg Electronics Inc. Refrigerant distributing device for multi-type air conditioner

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Publication number Priority date Publication date Assignee Title
US2787138A (en) * 1955-04-18 1957-04-02 Betz Corp Fluid mixing device
US4662391A (en) * 1984-10-05 1987-05-05 Chevron Research Company Method and apparatus for splitting a liquid-vapor mixture
US5243838A (en) * 1989-08-18 1993-09-14 Matsushita Refrigeration Company Refrigerant shunt
US7174726B2 (en) * 2003-08-07 2007-02-13 Parker-Hannifin Corporation Adjustable nozzle distributor
US7600393B2 (en) * 2005-03-09 2009-10-13 Lg Electronics Inc. Refrigerant distributing device for multi-type air conditioner
US20070245769A1 (en) * 2006-04-21 2007-10-25 Parker Christian D Fluid expansion-distribution assembly

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20140290298A1 (en) * 2010-02-10 2014-10-02 Mitsubishi Electric Corporation Refrigeration cycle apparatus
US9285142B2 (en) * 2010-02-10 2016-03-15 Mitsubishi Electric Corporation Refrigeration cycle apparatus
US20130087204A1 (en) * 2011-10-07 2013-04-11 Trane International Inc. Pressure Correcting Distributor For Heating and Cooling Systems
US8931509B2 (en) * 2011-10-07 2015-01-13 Trane International Inc. Pressure correcting distributor for heating and cooling systems
US20150000332A1 (en) * 2012-02-10 2015-01-01 Daikin Industries, Ltd. Air conditioner
US9765999B2 (en) * 2012-02-10 2017-09-19 Daikin Industries, Ltd. Air conditioner
US20160054037A1 (en) * 2013-04-09 2016-02-25 BSH Hausgeräte GmbH Refrigeration Device Comprising an Evaporator
JP2015001335A (ja) * 2013-06-14 2015-01-05 三菱電機株式会社 冷媒分流器、及び、冷凍サイクル装置
US10161656B2 (en) * 2014-08-14 2018-12-25 Lg Electronics Inc. Air conditioner having a bending tube which alters the flow of the refrigerant prior to entering the distributor
JP2020008214A (ja) * 2018-07-06 2020-01-16 株式会社コロナ 冷房装置
JP7105123B2 (ja) 2018-07-06 2022-07-22 株式会社コロナ 冷房装置
US20220412620A1 (en) * 2020-03-03 2022-12-29 Japan Climate Systems Corporation Refrigerant distributor

Also Published As

Publication number Publication date
EP2184564A3 (fr) 2014-09-24
EP2184564A2 (fr) 2010-05-12
CN101738026A (zh) 2010-06-16
KR20100052346A (ko) 2010-05-19
KR101547353B1 (ko) 2015-08-25

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