US20150101363A1 - Refrigerant distributing device and heat exchanger including the same - Google Patents

Refrigerant distributing device and heat exchanger including the same Download PDF

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Publication number
US20150101363A1
US20150101363A1 US14/395,875 US201214395875A US2015101363A1 US 20150101363 A1 US20150101363 A1 US 20150101363A1 US 201214395875 A US201214395875 A US 201214395875A US 2015101363 A1 US2015101363 A1 US 2015101363A1
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United States
Prior art keywords
refrigerant
header
heat
chamber
heat exchanger
Prior art date
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Abandoned
Application number
US14/395,875
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English (en)
Inventor
Takuya Matsuda
Akira Ishibashi
Sangmu Lee
Takashi Okazaki
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Mitsubishi Electric Corp
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Mitsubishi Electric Corp
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Filing date
Publication date
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Assigned to MITSUBISHI ELECTRIC CORPORATION reassignment MITSUBISHI ELECTRIC CORPORATION ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: OKAZAKI, TAKASHI, LEE, SANGMU, ISHIBASHI, AKIRA, MATSUDA, TAKUYA
Publication of US20150101363A1 publication Critical patent/US20150101363A1/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
    • F25B41/00—Fluid-circulation 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
    • F25B39/00—Evaporators; Condensers
    • F25B39/02—Evaporators
    • F25B39/028—Evaporators having distributing 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
    • F25B39/00—Evaporators; Condensers
    • F25B39/04—Condensers
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/0408—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids
    • F28D1/0417—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids with particular circuits for the same heat exchange medium, e.g. with the heat exchange medium flowing through sections having different heat exchange capacities or for heating/cooling the heat exchange medium at different temperatures
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/0202—Header boxes having their inner space divided by partitions
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/0202—Header boxes having their inner space divided by partitions
    • F28F9/0204—Header boxes having their inner space divided by partitions for elongated header box, e.g. with transversal and longitudinal partitions
    • F28F9/0209—Header boxes having their inner space divided by partitions for elongated header box, e.g. with transversal and longitudinal partitions having only transversal partitions
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
    • F28F9/027—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits in the form of distribution pipes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
    • F28F9/027—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits in the form of distribution pipes
    • F28F9/0273—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits in the form of distribution pipes with multiple holes
    • 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
    • F25B2339/00—Details of evaporators; Details of condensers
    • F25B2339/04—Details of condensers
    • F25B2339/044—Condensers with an integrated receiver
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/053—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/0068—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for refrigerant cycles
    • F28D2021/0071—Evaporators

Definitions

  • the present invention relates to a refrigerant distributing device that is mounted to a heat exchanger used in a refrigeration cycle apparatus such as an air-conditioning apparatus and distributes a refrigerant, and a heat exchanger including the refrigerant distributing device, a refrigeration cycle apparatus, and an air-conditioning apparatus.
  • a heat exchanger in which a pair of headers extends in an up-down direction so as to be spaced apart from each other in a right-left direction, a plurality of flattened pipes are disposed in parallel between the pair of headers, and both end portions of each of a plurality of heat exchange pipes communicate with the pair of headers.
  • a refrigerant flows thereinto as a two-phase gas-liquid flow, and thus liquid stays in the gravitational direction within the header at an inlet side, while gas stays in an upper portion within the header.
  • the header at the inlet side is required to have a function to uniformly distribute the refrigerant.
  • a refrigerant distributing device conventionally, there is a refrigerant distributing device in which a loop-shaped flow path is formed within a header so as to be turned in an up-down direction, a flow of a two-phase refrigerant having flowed therein is circulated within the header to be made uniform, whereby the refrigerant is distributed to each of a plurality of heat-transfer pipes (see, e.g., Patent Literature 1).
  • an evaporator that allows uniform distribution of a refrigerant
  • an evaporator that has a configuration in which a pair of headers extends in a right-left direction (the horizontal direction) so as to be spaced apart from each other and a plurality of flattened pipes are disposed in parallel between the pair of headers, and in which a plurality of refrigerant inlets are provided in the header at an inlet side so as to be spaced apart from each other in the right-left direction, and a refrigerant is jetted and flowed from each refrigerant inlet into the header via an orifice (see, e.g., Patent Literature 2).
  • Patent Literature 1 Japanese Unexamined Patent Application Publication No. 2011-85324 (Abstract, FIG. 1 )
  • Patent Literature 2 Japanese Unexamined Patent Application Publication No. 2000-249428 (Abstract, FIG. 4 )
  • Patent Literature 1 Although an effect of refrigerant uniform distribution is observed at a certain level, all of the plurality of heat-transfer pipes communicate with each other in the interior of the header and thus are influenced in the interior of the header by a head difference. Therefore, the refrigerant distribution effect cannot be sufficient and further improvement thereof is desired.
  • Patent Literature 2 since the header is horizontally mounted, the header is not influenced by a head difference. However, in the case where the header is mounted so as to stand in the up-down direction, a liquid is likely to stay in a lower portion under influence of the head difference.
  • the present invention has been made in view of such points, and an object of the present invention is to provide a refrigerant distributing device that is able to uniformly distribute a refrigerant by suppressing the influence of a head difference, a heat exchanger including the refrigerant distributing device, a refrigeration cycle apparatus, and an air-conditioning apparatus.
  • a refrigerant distributing device includes: a header having a configuration in which the header is connected to one end of each of a plurality of heat-transfer pipes of a heat exchanger that flows a refrigerant in two-phase gas-liquid state in parallel to the plurality of heat-transfer pipes disposed in parallel and an interior of the header is divided, by one or more division plates, in a parallel direction in which the plurality of heat-transfer pipes are disposed, the header being mounted so as to stand in an up-down direction; and a distributor configured to distribute the refrigerant to each chamber within the header divided by the division plates and flow the refrigerant into each chamber.
  • a refrigerant distributing device that is able to uniformly distribute a refrigerant by suppressing the influence of a head difference. It is possible to obtain an effective effect particularly when the header is mounted so as to stand in the up-down direction.
  • FIG. 1 is a schematic perspective view of a heat exchanger including a refrigerant distributing device according to one embodiment of the present invention.
  • FIG. 2 is a schematic cross-sectional view of a portion of the refrigerant distributing device in FIG. 1 .
  • FIG. 3 is a perspective view showing a flattened pipe in FIG. 1 .
  • FIG. 4 is a diagram showing a refrigerant circuit of a refrigeration cycle apparatus to which the heat exchanger in FIG. 1 is applied.
  • FIG. 5 is a diagram showing another configuration example of the refrigerant distributing device.
  • FIG. 6 is a diagram illustrating the principle of determining the height of each chamber in accordance with a wind speed distribution.
  • FIG. 1 is a schematic perspective view of a heat exchanger including a refrigerant distributing device according to one embodiment of the present invention.
  • FIG. 2 is a schematic cross-sectional view of a portion of the refrigerant distributing device in FIG. 1 .
  • portions designated by the same reference signs are the same or equivalent portions, and the same applies to the entire specification.
  • the forms of constituent elements described in the entire specification are merely illustrative and not limited to these descriptions.
  • a heat exchanger 1 is a parallel-flow type heat exchanger which flows a refrigerant in parallel, and includes a pair of headers 10 ( 10 a, 10 b ) each header is spaced apart from each other in a right-left direction and stands in an up-down direction;
  • the heat exchanger 1 further includes a plurality of fins 30 and a distributor 40 .
  • the pair of headers 10 , the flattened pipes 20 , and the fins 30 is formed of aluminum or an aluminum alloy.
  • the distributor 40 is connected to the header 10 a via capillary tubes 50 and forms a refrigerant distributing device with the header 10 a.
  • the fins 30 are plate-shaped fins that are stacked between the pair of headers 10 so as to be spaced apart from each other and between which air passes.
  • the plurality of flattened pipes 20 extend through the fins 30 .
  • the fins 30 may not necessarily be plate-shaped fins.
  • the fins 30 may be, for example, wave-shaped fins that are stacked in the up-down direction alternately with the flattened pipes 20 , and in short, may be fins that are disposed so as to allow air to pass therethrough in an air passing direction.
  • each flattened pipe 20 has a plurality of through holes 20 a serving as refrigerant flow paths.
  • the interior of the header 10 a is divided by one or more division plates 11 in the up-down direction into a plurality of chambers 12 .
  • eight chambers 12 are formed by seven division plates 11 .
  • a plurality of through holes 13 are formed so as to be aligned in the up-down direction.
  • the flattened pipe 20 is connected to each through hole 13 .
  • each chamber 12 is connected to the distributor 40 via the capillary tube 50 .
  • the distributor 40 includes therein an orifice (not shown) that reduces a flow of the refrigerant.
  • the distributor 40 causes a two-phase gas-liquid flow entering thereinto to be a spray flow (uniform flow) by passing the refrigerant through the orifice, thereby making the refrigerant into a state where uniform distribution of the refrigerant is easy.
  • the refrigerant made into a spray flow is uniformly distributed to the respective capillary tubes 50 and flows thereinto, and flows into the respective chambers 12 through the capillary tubes 50 .
  • Each capillary tube 50 adjusts the pressure loss therein with its specifications (length, inner diameter), thereby adjusting a distribution ratio to each chamber 12 of the header 10 a.
  • the specifications of all of the capillary tubes 50 are the same, and thus the refrigerant is flowed into each chamber 12 in the same amount.
  • the flattened pipes 20 , the fins 30 , and the pair of headers 10 are simultaneously joined by means of brazing in a furnace in an assembled state, and then the distributor 40 and each respective capillary tube 50 are connected to each other.
  • FIG. 4 is a diagram showing a refrigerant circuit of a refrigeration cycle apparatus to which the heat exchanger in FIG. 1 is applied.
  • a refrigeration cycle apparatus 60 includes a compressor 61 , a condenser 62 , an expansion valve 63 as a pressure reducing device, and an evaporator 64 .
  • the heat exchanger 1 is used in at least one of the condenser 62 and the evaporator 64 .
  • a gas refrigerant discharged from the compressor 61 flows into the condenser 62 , exchanges heat with air passing through the condenser 62 , to become a high-pressure liquid refrigerant, and flows out therefrom.
  • the high-pressure liquid refrigerant having flowed out of the condenser 62 is reduced in pressure by the expansion valve 63 to become a low-pressure two-phase gas-liquid refrigerant, and flows into the evaporator 64 .
  • the low-pressure two-phase gas-liquid refrigerant having flowed into the evaporator 64 exchanges heat with air passing through the evaporator 64 , to become a low-pressure gas refrigerant, and is sucked into the compressor 61 again.
  • FIG. 1 a solid arrow indicates the flow of the refrigerant in the case where the heat exchanger 1 is used as an evaporator.
  • the flow of the two-phase gas-liquid refrigerant having flowed out of the expansion valve 63 first enters into the distributor 40 and is made into a spray flow.
  • the refrigerant made into a spray flow is uniformly distributed to the respective capillary tubes 50 and flows thereinto.
  • the refrigerant having passed through the respective capillary tubes 50 flows into the respective chambers 12 of the header 10 a.
  • the division plates 11 are provided to divide the interior of the header 10 a, and the refrigerant is flowed into each chamber 12 at which the head difference is small.
  • the effect of the head difference on the refrigerant having flowed into each chamber 12 is reduced, and the refrigerant in each chamber 12 is uniformly distributed to each flattened pipe 20 connected to the chamber 12 and flows thereinto.
  • each flattened pipe 20 flows through the through holes 20 a of the flattened pipe 20 toward the header 10 b, joins each other in the header 10 b, and flows out of the heat exchanger 1 through an external connection pipe 14 .
  • FIG. 1 a dotted arrow indicates the flow of the refrigerant in the case where the heat exchanger 1 is used as a condenser.
  • the refrigerant is in a gas state, uniform distribution of the refrigerant is easy.
  • a refrigerant distributing device such as a distributor is unnecessary, and a configuration is provided in which the flow of the gas refrigerant having flowed out of the compressor 61 is directly flowed into the header 10 b.
  • each flattened pipe 20 flows through the through holes 20 a of the flattened pipe 20 toward the header 10 a and flows into each chamber 12 of the header 10 a.
  • the refrigerant having flowed into each chamber 12 flows into the distributor 40 via each capillary tube 50 , joins each other therein, and flows out of the heat exchanger 1 .
  • a two-phase refrigerant flow having entered thereinto is uniformly distributed by the distributor 40 , and the uniformly distributed refrigerant is flowed into each chamber 12 at which the head difference is reduced.
  • the effect of the head difference on the refrigerant having flowed into each chamber 12 is reduced, thereby allowing the refrigerant to be uniformly distributed and flowed into each flattened pipe 20 to suppress a drift. Therefore, use of the refrigerant distributing device including the distributor 40 and the header 10 a allows the capacity of the evaporator to be maximized to increase the heat exchange efficiency of the heat exchanger 1 as an evaporator.
  • each division plate 11 may be determined in consideration of the head difference that allows uniform distribution. Provision of only a minimum necessary number of division plates 11 allows cost reduction.
  • the refrigerant distributing device and the heat exchanger according to the present invention are not limited to the structure shown in FIG. 1 , and various changes such as (1) to (4) below may be made without departing from the scope of the present invention.
  • a drift suppression member for suppressing a distribution drift may further be provided at a refrigerant inflow portion of each chamber 12 .
  • any member that is able to suppress a distribution drift may be used as the drift suppression member, and, for example, an orifice 70 may be provided as shown in FIG. 5 .
  • the orifice 70 is provided at a connection port, at each chamber 12 , connected to the capillary tube 50 and has a through hole 71 with a smaller inner diameter than that of the capillary tube 50 .
  • the orifice 70 further reduces the flow of the refrigerant having flowed thereinto from the capillary tube 50 , by means of the through hole 71 , thereby promoting making the refrigerant into a spray flow.
  • the promotion of making the refrigerant into a spray flow makes distribution of the refrigerant to each flattened pipe 20 in the chamber 12 to be more uniform, thereby allowing a distribution drift to be further suppressed.
  • each chamber 12 may be determined in accordance with a wind speed distribution at the heat exchanger 1 .
  • the wind speed of air blown from a fan to the heat exchanger 1 is not necessarily uniform over the entire surface of the heat exchanger 1 , and a wind speed distribution exists therein.
  • a wind speed distribution exists therein.
  • the wind speed is higher at the upper portion of the heat exchanger 1 than at a lower portion thereof.
  • the heat exchanger 1 is used as an evaporator, the refrigerant passing through a portion where the wind speed is high progresses in gasification further than the refrigerant passing through a portion where the wind speed is low, and is easily dried.
  • the refrigerant having passed through the portion where the wind speed is high has higher quality than that of the refrigerant having passed through the portion where the wind speed is low, and the state of the refrigerant flowing into the header 10 b is varied.
  • the state of the refrigerant flowing out of the external connection pipe 14 is not stable.
  • the heights of the chambers 12 are decreased such that a heat-exchange region per chamber is reduced in size, whereby the number of flattened pipes connected to the chamber 12 is decreased. This will be specifically described below with reference to FIG. 6 .
  • FIG. 6 is a diagram illustrating the principle of determining the height of each chamber in accordance with a wind speed distribution and shows here a case where a wind speed at the upper side is high and a wind speed at the lower side is low.
  • the height of each chamber 12 A at the upper side at which the wind speed is high is made smaller than the height of each chamber 12 B at the lower side at which the wind speed is low, so that the number of the flattened pipes connected to each chamber 12 A is made smaller than the number of the flattened pipes connected to each chamber 12 B.
  • a heat-exchange region A at the chamber 12 A side is smaller than a heat-exchange region B at the chamber 12 B side, and the heat transfer area is small, so to speak. Therefore, the substantial heat exchange amount is substantially the same in the heat-exchange region A and the heat-exchange region B, and it is possible to make the refrigerant state at an outlet to be uniform.
  • the amount of the refrigerant flowing into each chamber 12 is the same and the refrigerant state at the outlet is made uniform by changing the heights of the chambers 12 .
  • the following case may be employed. Specifically, the height of each chamber 12 is made the same, and the distribution amount of the refrigerant flowing into each chamber 12 is changed.
  • the distribution amount of the refrigerant flowing into each chamber 12 may be determined in accordance with a wind speed distribution, and the specifications (length, inner diameter) of each capillary tube 50 may be determined such that the determined distribution amount is achieved.
  • the capillary tubes 50 are selected such that the distribution amount for each chamber 12 to which the flattened pipes 20 located at the portion where the wind speed is high are connected is large and the distribution amount for each chamber 12 to which the flattened pipes 20 at the portion where the wind speed is low are connected is small.
  • the entire heat exchanger 1 has substantially an I shape.
  • the entire heat exchanger 1 may have substantially an L shape, substantially a U shape, or substantially a rectangular shape. Which shape the heat exchanger 1 has may be determined in accordance with a mounting space, within a housing, for the heat exchanger 1 in which the heat exchanger 1 is mounted.
  • the heat exchanger 1 may have a shape that maximizes use of the mounting space to allow the heat exchanger 1 to be densely mounted.
  • each heat-transfer pipe is a flattened pipe, but may not necessarily be a flattened pipe and may be a circular pipe.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Details Of Heat-Exchange And Heat-Transfer (AREA)
US14/395,875 2012-04-26 2012-04-26 Refrigerant distributing device and heat exchanger including the same Abandoned US20150101363A1 (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2012/002860 WO2013160952A1 (ja) 2012-04-26 2012-04-26 冷媒分配器及びこの冷媒分配器を備えた熱交換器

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US20150101363A1 true US20150101363A1 (en) 2015-04-16

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US (1) US20150101363A1 (ja)
EP (1) EP2853843B1 (ja)
JP (1) JP5901748B2 (ja)
CN (2) CN104272040B (ja)
ES (1) ES2784132T3 (ja)
WO (1) WO2013160952A1 (ja)

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US20170153050A1 (en) * 2013-11-25 2017-06-01 Samsung Electronics Co., Ltd. Air conditioner
US10168083B2 (en) 2014-07-11 2019-01-01 Hangzhou Sanhua Research Institute Co., Ltd. Refrigeration system and heat exchanger thereof
US20190078817A1 (en) * 2016-05-19 2019-03-14 Mitsubishi Electric Corporation Outdoor unit and refrigeration cycle apparatus including the same
US10578377B2 (en) * 2016-03-31 2020-03-03 Mitsubishi Electric Corporation Heat exchanger and refrigeration cycle apparatus
US10760832B2 (en) * 2016-09-12 2020-09-01 Mitsubishi Electric Corporation Air-conditioning apparatus
US11181305B2 (en) * 2018-01-31 2021-11-23 Daikin Industries, Ltd. Heat exchanger or refrigeration apparatus including heat exchanger
US11236954B2 (en) * 2017-01-25 2022-02-01 Hitachi-Johnson Controls Air Conditioning, Inc. Heat exchanger and air-conditioner
US11326787B2 (en) * 2017-09-25 2022-05-10 Mitsubishi Electric Corporation Refrigerant distributor and air-conditioning apparatus
US20220357115A1 (en) * 2019-06-26 2022-11-10 Valeo Autosystemy Sp. Z O.O. Heat exchanger
US20230106747A1 (en) * 2018-01-31 2023-04-06 Daikin Industries, Ltd. Heat exchanger or refrigeration apparatus including heat exchanger

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JP6273838B2 (ja) * 2013-12-27 2018-02-07 ダイキン工業株式会社 熱交換器
JP6213362B2 (ja) * 2014-04-17 2017-10-18 株式会社デンソー 熱交換器および熱交換器の製造方法
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