WO2020217271A1 - Distributeur de fluide frigorigène, échangeur thermique, et dispositif à cycle frigorifique - Google Patents

Distributeur de fluide frigorigène, échangeur thermique, et dispositif à cycle frigorifique Download PDF

Info

Publication number
WO2020217271A1
WO2020217271A1 PCT/JP2019/016983 JP2019016983W WO2020217271A1 WO 2020217271 A1 WO2020217271 A1 WO 2020217271A1 JP 2019016983 W JP2019016983 W JP 2019016983W WO 2020217271 A1 WO2020217271 A1 WO 2020217271A1
Authority
WO
WIPO (PCT)
Prior art keywords
flow path
refrigerant
communication hole
distribution
distribution flow
Prior art date
Application number
PCT/JP2019/016983
Other languages
English (en)
Japanese (ja)
Inventor
繁佳 松井
真哉 東井上
篤史 高橋
Original Assignee
三菱電機株式会社
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 三菱電機株式会社 filed Critical 三菱電機株式会社
Priority to JP2021515324A priority Critical patent/JP7086279B2/ja
Priority to PCT/JP2019/016983 priority patent/WO2020217271A1/fr
Publication of WO2020217271A1 publication Critical patent/WO2020217271A1/fr

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
    • F25B39/00—Evaporators; 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
    • 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
    • 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
    • F28F9/007—Auxiliary supports for elements
    • F28F9/013—Auxiliary supports for elements for tubes or tube-assemblies
    • 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

Definitions

  • the present invention relates to a refrigerant distributor, a heat exchanger provided with the refrigerant distributor, and a refrigeration cycle device provided with the heat exchanger.
  • a refrigerant distributor having a main body in which heat transfer tubes extending in the horizontal direction are arranged in the vertical direction and formed in a cylindrical shape so as to extend in the vertical direction is disclosed (see, for example, Patent Document 1).
  • the refrigerant distributor of Patent Document 1 flat tubes are inserted into the main body with equal lengths, and the flow velocity of the refrigerant in the refrigerant distributor is set to an appropriate value so that the refrigerant is evenly distributed to each heat transfer tube. It will be adjusted.
  • the insertion amount of the flat tube into the main body is adjusted so that the cross-sectional area of the effective flow path of the portion where the flat tube is inserted in the main body becomes a predetermined value.
  • the flow velocity of the refrigerant in the refrigerant distributor is adjusted to an appropriate value.
  • the present invention is for solving the above-mentioned problems, and is distributed to each heat transfer tube in order to suppress the drift in the distribution of the refrigerant against the change in the refrigerant flow rate depending on the operating state of the air conditioner.
  • An object of the present invention is to provide a refrigerant distributor, a heat exchanger, and a refrigeration cycle device having a uniform refrigerant flow rate.
  • the refrigerant distributor according to the present invention is a refrigerant distributor which is arranged at intervals in the first direction and is connected to a heat exchanger provided with a plurality of heat transfer tubes for circulating the refrigerant inside.
  • It has a formed main body, and the main body communicates with the first refrigerant inlet and extends in the first direction, and communicates with the second refrigerant inlet and is parallel to the first distribution flow path.
  • the first refrigerant inlet and the second refrigerant inlet are formed on one end side of the main body in the first direction, and in the first distribution flow path, one end to the other end of the main body.
  • the distance toward is defined as the distance A
  • the distance from one end of the main body to the other end is defined as the distance B in the second distribution flow path, at a position where the distance A and the distance B are equal.
  • the heat exchanger according to the present invention is provided with the refrigerant distributor according to the present invention.
  • the refrigeration cycle device according to the present invention is provided with the heat exchanger according to the present invention.
  • the refrigerant distributor forms a plurality of flow path shapes of the first distribution flow path and the second distribution flow path and the first communication hole group at positions where the distance A and the distance B are equal.
  • the flow path shapes of one of the communication hole portions of the above and one of the plurality of communication hole portions forming the second communication hole group at least one of the flow path shapes is different. Therefore, in the refrigerant distributor according to the present invention, a deviation with respect to the distance from the refrigerant inflow port is caused by the total flow rate of the flow rate of the refrigerant flowing through the first distribution flow path and the flow rate of the refrigerant flowing through the second distribution flow path. It can be suppressed and the flow rate of the refrigerant distributed to a plurality of heat transfer tubes can be made uniform.
  • FIG. 1 It is a refrigerant circuit diagram which shows the structure of the refrigerating cycle apparatus provided with the refrigerant distributor which concerns on Embodiment 1.
  • FIG. It is an exploded perspective view which shows the main part structure of the heat exchanger provided with the refrigerant distributor which concerns on Embodiment 1.
  • FIG. It is a side view which shows the main part structure of the heat exchanger provided with the refrigerant distributor which concerns on Embodiment 1.
  • FIG. It is sectional drawing which shows the structure of the heat transfer tube connected to the refrigerant distributor which concerns on Embodiment 1.
  • FIG. It is a conceptual diagram which shows the refrigerant distribution of the refrigerant distributor which concerns on Embodiment 1.
  • FIG. It is an exploded perspective view which shows the main part structure of the heat exchanger provided with the refrigerant distributor which concerns on Embodiment 2.
  • FIG. It is an upper sectional view which shows the structure of the refrigerant distributor which concerns on Embodiment 2.
  • FIG. It is an exploded perspective view which shows the main part structure of the heat exchanger provided with the refrigerant distributor which concerns on Embodiment 3.
  • FIG. It is sectional drawing which shows the structure of the refrigerant distributor which concerns on Embodiment 3.
  • FIG. It is a conceptual diagram which shows the refrigerant distribution of the refrigerant distributor which concerns on Embodiment 3.
  • FIG. It is an exploded perspective view which shows the main part structure of the heat exchanger provided with the refrigerant distributor which concerns on Embodiment 2.
  • FIG. It is sectional drawing which shows the structure of the refriger
  • FIG. 5 is an exploded perspective view showing a main configuration of a heat exchanger provided with a refrigerant distributor according to a fifth embodiment. It is sectional drawing which shows the structure of the refrigerant distributor which concerns on Embodiment 5. It is a perspective view of the refrigerant distributor which concerns on Embodiment 6. It is a perspective view which shows typically the internal structure of the refrigerant distributor which concerns on Embodiment 6.
  • the refrigerant distributor 50 according to the first embodiment will be described with reference to the drawings and the like.
  • the relative dimensional relationships and shapes of the constituent members may differ from the actual ones.
  • those having the same reference numerals are the same or equivalent thereof, and this shall be common to the entire text of the specification.
  • terms that indicate directions are used as appropriate for ease of understanding. For convenience of explanation, it is described as such, and does not limit the arrangement and orientation of the device or component.
  • the positional relationship between the constituent members, the extending direction of each constituent member, and the parallel direction of each constituent member are, in principle, those when the heat exchanger is installed in a usable state.
  • FIG. 1 is a refrigerant circuit diagram showing a configuration of a refrigerating cycle device 100 provided with a refrigerant distributor 50 according to the first embodiment.
  • the refrigeration cycle apparatus 100 provided with the refrigerant distributor 50 will be described with reference to FIG.
  • the arrow indicated by the dotted line indicates the direction in which the refrigerant flows in the refrigerant circuit 110 during the cooling operation
  • the arrow indicated by the solid line indicates the direction in which the refrigerant flows during the heating operation. ..
  • the air conditioner is exemplified as the refrigerating cycle device 100, but the refrigerating cycle device 100 is, for example, refrigerating a refrigerator or a freezer, a vending machine, an air conditioner, a refrigerating device, a water heater, or the like. Used for applications or air conditioning applications.
  • the refrigerating cycle device 100 has a refrigerant circuit 110 in which a compressor 101, a flow path switching device 102, an indoor heat exchanger 103, a decompression device 104, and an outdoor heat exchanger 105 are cyclically connected via a refrigerant pipe. .. Further, the refrigeration cycle device 100 has a refrigerant distributor 50 connected to either one or both of the indoor heat exchanger 103 and the outdoor heat exchanger 105. The refrigeration cycle device 100 has an outdoor unit 106 and an indoor unit 107.
  • the outdoor unit 106 includes a compressor 101, a flow path switching device 102, an outdoor heat exchanger 105, a refrigerant distributor 50 and a decompression device 104, and an outdoor blower 108 that supplies outdoor air to the outdoor heat exchanger 105.
  • the indoor unit 107 includes an indoor heat exchanger 103, a refrigerant distributor 50, and an indoor blower 109 that supplies air to the indoor heat exchanger 103.
  • the outdoor unit 106 and the indoor unit 107 are connected to each other via two extension pipes 111 and 112 which are a part of the refrigerant pipe.
  • the compressor 101 is a fluid machine that compresses and discharges the sucked refrigerant.
  • the flow path switching device 102 is, for example, a four-way valve, and is a device that switches the flow path of the refrigerant between the cooling operation and the heating operation by controlling the control device (not shown).
  • the indoor heat exchanger 103 is a heat exchanger that exchanges heat between the refrigerant circulating inside and the indoor air supplied by the indoor blower 109.
  • the indoor heat exchanger 103 functions as a condenser during the heating operation and as an evaporator during the cooling operation.
  • the pressure reducing device 104 is, for example, an expansion valve, which is a device for reducing the pressure of the refrigerant.
  • the outdoor heat exchanger 105 is a heat exchanger that exchanges heat between the refrigerant circulating inside and the air supplied by the outdoor blower 108.
  • the outdoor heat exchanger 105 functions as an evaporator during the heating operation and as a condenser during the cooling operation.
  • a heat exchanger 80 which will be described later, is used for at least one of the outdoor heat exchanger 105 and the indoor heat exchanger 103. It is desirable that the refrigerant distributor 50 connected to the heat exchanger 80 is arranged at a position in the heat exchanger 80 where the amount of the liquid phase refrigerant is larger. Specifically, the refrigerant distributor 50 is arranged on the inlet side of the heat exchanger 80 that functions as an evaporator, that is, on the outlet side of the heat exchanger 80 that functions as a condenser in the flow of the refrigerant in the refrigerant circuit 110. Is desirable.
  • the refrigerant distributor 50 is used in both the indoor heat exchanger 103 and the outdoor heat exchanger 105, but the heat of either the indoor heat exchanger 103 or the outdoor heat exchanger 105 is used. It may be used only in the exchanger.
  • FIG. 2 is an exploded perspective view showing a main configuration of the heat exchanger 80 provided with the refrigerant distributor 50 according to the first embodiment.
  • FIG. 3 is a side view showing a main configuration of the heat exchanger 80 provided with the refrigerant distributor 50 according to the first embodiment.
  • the refrigerant distributor 50 and the heat exchanger 80 according to the first embodiment will be described with reference to FIGS. 1 to 3.
  • the arrow A shown in the figure represents an example of the distance A, and the distance A is the distance from one end 51a of the main body 51 toward the other end 51b in the first distribution flow path 15a described later. ..
  • the arrow B represents an example of the distance B, and the distance B is a distance from one end 51a of the main body 51 toward the other end 51b in the second distribution flow path 16a described later.
  • the arrow F indicated by hatching indicates the direction of the refrigerant flowing through the first flow path portion 15 and the second flow path portion 16 of the refrigerant distributor 50.
  • the refrigerant distributor 50 When applied to the refrigeration cycle device 100, the refrigerant distributor 50 is connected to the inlet side of the heat transfer tube 70 when the heat exchanger 80 operates as an evaporator.
  • the heat exchanger 80 to which the refrigerant distributor 50 is connected is an air heat exchanger that exchanges heat between air and the refrigerant, and functions at least as an evaporator of the refrigeration cycle device 100.
  • the heat exchanger 80 includes a plurality of heat transfer tubes 70 for circulating a refrigerant, a refrigerant distributor 50 connected to one end of each of the plurality of heat transfer tubes 70 in the extending direction, and a refrigerant distributor 50. It has a refrigerant inflow pipe 60 attached to the lower part of the.
  • the heat transfer tube 70 is described as a flat tube, but a circular tube may be used for the heat transfer tube 70.
  • the plurality of heat transfer tubes 70 are flat tubes. Each of the plurality of heat transfer tubes 70 extends in the horizontal direction. The plurality of heat transfer tubes 70 are arranged in parallel in the vertical direction with each other. A gap 71 that serves as an air flow path is formed between two adjacent heat transfer tubes 70 among the plurality of heat transfer tubes 70. A heat transfer fin 75 may be provided between two adjacent heat transfer tubes 70.
  • a refrigerant collecting pipe having a cylindrical shape, for example, is connected to the other end of each of the plurality of heat transfer tubes 70 in the extending direction.
  • the heat exchanger 80 functions as an evaporator of the refrigeration cycle device 100
  • the refrigerant flows from one end to the other end of each of the plurality of heat transfer tubes 70.
  • the heat exchanger 80 functions as a condenser of the refrigeration cycle device 100
  • the refrigerant flows from the other end to the one end in each of the plurality of heat transfer tubes 70.
  • FIG. 4 is a cross-sectional view showing the configuration of the heat transfer tube 70 connected to the refrigerant distributor 50 according to the first embodiment.
  • FIG. 4 shows a cross section perpendicular to the extending direction of the heat transfer tube 70.
  • the heat transfer tube 70 has a unidirectionally flat cross-sectional shape such as an oval shape.
  • the heat transfer tube 70 has a first side end portion 70a and a second side end portion 70b, and a pair of flat surfaces 70c and flat surfaces 70d.
  • the first side end portion 70a is connected to one end portion of the flat surface 70c and one end portion of the flat surface 70d.
  • the second side end 70b is connected to the other end of the flat surface 70c and the other end of the flat surface 70d.
  • the first side end portion 70a is a side end portion arranged on the windward side, that is, on the front edge side in the flow of air passing through the heat exchanger.
  • the second side end portion 70b is a side end portion arranged on the leeward side, that is, the trailing edge side in the flow of air passing through the heat exchanger.
  • the direction perpendicular to the extending direction of the heat transfer tube 70 and along the flat surface 70c and the flat surface 70d may be referred to as a major axis direction of the heat transfer tube 70.
  • the long axis direction of the heat transfer tube 70 is the left-right direction.
  • the major axis dimension of the heat transfer tube 70 in the major axis direction is LA1.
  • the heat transfer tube 70 is formed with a plurality of refrigerant passages 72 arranged between the first side end portion 70a and the second side end portion 70b along the long axis direction.
  • the heat transfer tube 70 is a flat perforated tube in which a plurality of refrigerant passages 72 through which the refrigerant flows are arranged in the air flow direction.
  • Each of the plurality of refrigerant passages 72 is formed so as to extend in parallel with the extending direction of the heat transfer tube 70.
  • the refrigerant distributors 50 are arranged at intervals in the first direction and are connected to the heat exchanger 80 provided with a plurality of heat transfer tubes 70 for circulating the refrigerant inside.
  • the first direction is the arrangement direction of the plurality of heat transfer tubes 70, and is the direction in which the plurality of heat transfer tubes 70 are lined up.
  • the main body 51 of the refrigerant distributor 50 is formed so as to extend in the vertical direction along the arrangement direction of the plurality of heat transfer tubes 70.
  • the main body 51 of the refrigerant distributor 50 has two refrigerant inlets 18 of a first refrigerant inlet 18a and a second refrigerant inlet 18b formed on one side surface side in the extending direction of the plurality of heat transfer tubes 70, and the other.
  • a plurality of insertion holes 41 into which a plurality of heat transfer tubes 70 are inserted are formed on the side surface side of the above.
  • the first refrigerant inlet 18a and the second refrigerant inlet 18b are formed on one end 51a side of the main body 51 in the first direction.
  • the first refrigerant inlet 18a and the second refrigerant inlet 18b are formed side by side in a direction perpendicular to the first direction, which is the arrangement direction of the plurality of heat transfer tubes 70.
  • the center position of the first refrigerant inlet 18a and the center position of the second refrigerant inlet 18b may be at different distances from one end portion 51a.
  • the first refrigerant inflow port 18a and the second refrigerant inflow port 18b are formed, for example, in the first direction below the communication hole portion 25 formed at the lowermost side of the communication hole portions 25 described later. ing.
  • the first refrigerant inflow port 18a and the second refrigerant inflow port 18b are not limited to those formed below the communication hole portion 25 formed on the lowermost side in the first direction.
  • the main body 51 of the refrigerant distributor 50 has a first plate-shaped member 10, a second plate-shaped member 20, a third plate-shaped member 30, and a fourth plate-shaped member 40.
  • the first plate-shaped member 10, the second plate-shaped member 20, the third plate-shaped member 30, and the fourth plate-shaped member 40 are all formed by using a metal flat plate and have a long strip shape in one direction. There is.
  • the contours of the outer edges of the first plate-shaped member 10, the second plate-shaped member 20, the third plate-shaped member 30, and the fourth plate-shaped member 40 have the same shape as each other.
  • the first plate-shaped member 10, the second plate-shaped member 20, the third plate-shaped member 30, and the fourth plate-shaped member 40 have their respective plate thickness directions parallel to the extending direction of the heat transfer tube 70, that is, Each plate surface is arranged so as to be perpendicular to the extending direction of the heat transfer tube 70.
  • the first plate-shaped member 10, the second plate-shaped member 20, the third plate-shaped member 30, and the fourth plate-shaped member 40 are arranged in this order from the farthest distance from the heat transfer tube 70. It has a laminated structure.
  • the farthest distance from the heat transfer tube 70 is the first plate-shaped member 10
  • the closest distance from the heat transfer tube 70 is the fourth plate-shaped member 40.
  • the second plate-shaped member 20 is arranged between the first plate-shaped member 10 and the heat transfer tube 70, and is adjacent to the first plate-shaped member 10.
  • the third plate-shaped member 30 is arranged between the second plate-shaped member 20 and the heat transfer tube 70, and is adjacent to the second plate-shaped member 20.
  • the fourth plate-shaped member 40 is arranged between the third plate-shaped member 30 and the heat transfer tube 70, and is adjacent to the third plate-shaped member 30. One end of each of the plurality of heat transfer tubes 70 is connected to the fourth plate-shaped member 40.
  • the adjacent members of the first plate-shaped member 10, the second plate-shaped member 20, the third plate-shaped member 30, and the fourth plate-shaped member 40 are joined by brazing.
  • the first plate-shaped member 10, the second plate-shaped member 20, the third plate-shaped member 30, and the fourth plate-shaped member 40 are arranged so that their longitudinal directions are along the vertical direction.
  • FIG. 5 is a cross-sectional view showing the configuration of the refrigerant distributor 50 according to the first embodiment.
  • FIG. 5 shows a cross section of the refrigerant distributor 50 in the extending direction of the heat transfer tube 70 and the direction parallel to the major axis direction.
  • the plate thickness directions of the first plate-shaped member 10, the second plate-shaped member 20, the third plate-shaped member 30, and the fourth plate-shaped member 40 are the left-right directions in FIG. 5, and are the extending directions of the heat transfer tube 70. is there.
  • the lateral direction of each of the first plate-shaped member 10, the second plate-shaped member 20, the third plate-shaped member 30, and the fourth plate-shaped member 40 is the vertical direction of FIG. 5, and the major axis direction of the heat transfer tube 70. Is.
  • the first plate-shaped member 10 bulges in the direction away from the heat transfer tube 70 as well as the first flow path portion 15 bulging in the direction away from the heat transfer tube 70. It has two flow path portions 16.
  • the first flow path portion 15 and the second flow path portion 16 are formed in parallel in the lateral direction of the first plate-shaped member 10.
  • the first distribution flow path 15a formed in the first flow path portion 15 and the second distribution flow path 16a formed in the second flow path portion 16 are formed so as to have different flow path cross-sectional areas. Has been done.
  • the distance from one end 51a of the main body 51 to the other end 51b is defined as a distance A
  • the distance from 51a to the other end 51b is defined as the distance B.
  • the refrigerant distributor 50 has a different flow path shape so that the flow path cross-sectional areas of the first distribution flow path 15a and the second distribution flow path 16a are different at positions where the distance A and the distance B are equal.
  • the refrigerant distributor 50 may be connected to the first distribution flow path 15a at a position corresponding to the formation position of one of the communication hole portions 25, which will be described later, which is formed in plurality along the first direction.
  • the flow path shape is different so that the flow path cross-sectional area of the second distribution flow path 16a is different.
  • the first flow path portion 15 extends from one end in the longitudinal direction to the other end in the longitudinal direction of the first plate-shaped member 10 along the longitudinal direction of the first plate-shaped member 10.
  • the first flow path portion 15 is formed in a semi-cylindrical shape. Both ends of the first flow path portion 15 in the stretching direction are closed.
  • the first flow path portion 15 has a semicircular, semi-elliptical or semi-oval cross-sectional shape.
  • the cross-sectional shape of the first flow path portion 15 is not limited to a semicircular shape, a semi-elliptical shape, or a semi-oval shape, and may be, for example, a rectangular shape.
  • the first plate-shaped member 10 has a flat plate portion 11a and a flat plate portion 11b formed in a flat plate shape on both sides of the first flow path portion 15. Both the flat plate portion 11a and the flat plate portion 11b extend from one end in the longitudinal direction to the other end in the longitudinal direction of the first plate-shaped member 10 along the longitudinal direction of the first plate-shaped member 10.
  • the second flow path portion 16 extends from one end in the longitudinal direction to the other end in the longitudinal direction of the first plate-shaped member 10 along the longitudinal direction of the first plate-shaped member 10.
  • the second flow path portion 16 is formed in a semi-cylindrical shape. Both ends of the second flow path portion 16 in the stretching direction are closed.
  • the second flow path portion 16 has a semicircular, semi-elliptical or semi-oval cross-sectional shape.
  • the cross-sectional shape of the second flow path portion 16 is not limited to a semicircular shape, a semi-elliptical shape, or a semi-elliptical shape, and may be, for example, a rectangular shape.
  • the first flow path portion 15 may have a semicircular shape
  • the second flow path portion 16 may have a different shape such as a rectangular shape.
  • the first plate-shaped member 10 has a flat plate portion 11b and a flat plate portion 11c formed in a flat plate shape on both sides of the second flow path portion 16. Both the flat plate portion 11b and the flat plate portion 11c extend from one end in the longitudinal direction to the other end in the longitudinal direction of the first plate-shaped member 10 along the longitudinal direction of the first plate-shaped member 10.
  • the first flow path portion 15 and the second flow path portion 16 are arranged side by side via the flat plate portion 11b.
  • a first distribution flow path 15a extending in the vertical direction along the longitudinal direction of the first plate-shaped member 10 is formed.
  • the first distribution flow path 15a is formed so as to communicate with the first refrigerant inflow port 18a, parallel to the second distribution flow path 16a, and extend in the first direction, which is the arrangement direction of the plurality of heat transfer tubes 70. ..
  • the first distribution flow path 15a extends so as to intersect with each of the plurality of heat transfer tubes 70 when viewed in the plate thickness direction of the first plate-shaped member 10.
  • the first distribution flow path 15a has a semicircular, semi-elliptical or semi-oval cross-sectional shape.
  • the first distribution flow path 15a is a space formed in a semi-cylindrical shape, a semi-elliptical cylinder shape, or a semi-long cylindrical shape.
  • the cross-sectional shape of the first distribution flow path 15a is not limited to a semicircular shape, a semi-elliptical shape, or a semi-elliptical shape, and may be, for example, a rectangular shape.
  • the cross-sectional area of the first distribution flow path 15a is smaller than the cross-sectional area of the second distribution flow path 16a.
  • the first distribution flow path 15a communicates with the refrigerant inflow pipe 60 at the end in the extending direction.
  • the gas-liquid two-phase refrigerant flowing into the first distribution flow path 15a via the refrigerant inflow pipe 60 flows upward through the first distribution flow path 15a and is distributed to each heat transfer pipe 70 as shown by an arrow F. ..
  • the width direction of the first distribution flow path 15a is parallel to the lateral direction of the first plate-shaped member 10.
  • the dimension of the first distribution flow path 15a in the width direction is smaller than the major axis dimension LA1 of the heat transfer tube 70.
  • a second distribution flow path 16a extending in the vertical direction along the longitudinal direction of the first plate-shaped member 10 is formed.
  • the second distribution flow path 16a is formed so as to communicate with the second refrigerant inflow port 18b, parallel to the first distribution flow path 15a, and extend in the first direction, which is the arrangement direction of the plurality of heat transfer tubes 70. ..
  • the second distribution flow path 16a extends so as to intersect with each of the plurality of heat transfer tubes 70 when viewed in the plate thickness direction of the first plate-shaped member 10.
  • the second distribution flow path 16a has a semicircular, semi-elliptical or semi-oval cross-sectional shape.
  • the second distribution flow path 16a is a space formed in a semi-cylindrical shape, a semi-elliptical cylinder shape, or a semi-long cylindrical shape.
  • the cross-sectional shape of the second distribution flow path 16a is not limited to a semicircular shape, a semi-elliptical shape, or a semi-elliptical shape, and may be, for example, a rectangular shape.
  • the cross-sectional area of the second distribution flow path 16a is larger than the cross-sectional area of the first distribution flow path 15a.
  • the second distribution flow path 16a communicates with the refrigerant inflow pipe 60 at the end in the extending direction.
  • the gas-liquid two-phase refrigerant flowing into the second distribution flow path 16a via the refrigerant inflow pipe 60 flows upward through the second distribution flow path 16a and is distributed to each heat transfer pipe 70 as shown by an arrow F. ..
  • the width direction of the second distribution flow path 16a is parallel to the lateral direction of the first plate-shaped member 10.
  • the dimension of the second distribution flow path 16a in the width direction is smaller than the major axis dimension LA1 of the heat transfer tube 70.
  • the refrigerant inflow pipe 60 communicates with the lower ends of the first distribution flow path 15a and the second distribution flow path 16a.
  • the refrigerant inflow pipe 60 causes a gas-liquid two-phase refrigerant to flow into the first distribution flow path 15a and the second distribution flow path 16a.
  • the refrigerant inflow pipe 60 has a base 61, a first branch pipe 62, and a second branch pipe 63.
  • the first branch pipe 62 and the second branch pipe 63 are formed so as to be bifurcated at the end of the base portion 61.
  • the first branch pipe 62 is connected to the first flow path portion 15 and communicates with the first distribution flow path 15a
  • the second branch pipe 63 is connected to the second flow path portion 16 to communicate with the second distribution flow path 16a. Communicate with.
  • the connection position between the refrigerant inflow pipe 60 and the first flow path portion 15 and the second flow path portion 16 is the refrigerant inflow port 18 through which the refrigerant flows into the refrigerant distributor 50.
  • the heat exchanger 80 functions as a condenser, the liquid refrigerant flows downward through the first distribution flow path 15a and the second distribution flow path 16a and flows out through the refrigerant inflow pipe 60.
  • the second plate-shaped member 20 has a plurality of communication holes 25 each having a circular opening shape.
  • Each of the plurality of communication hole portions 25 forms a through hole penetrating the second plate-shaped member 20, and is provided corresponding to each of the plurality of heat transfer tubes 70.
  • Each of the plurality of communication hole portions 25 penetrates the second plate-shaped member 20 in the plate thickness direction of the second plate-shaped member 20.
  • the opening shape of the communication hole portion 25 is circular, but is not limited to a circular shape, and may be, for example, a semicircular shape, a semi-elliptical shape, a semi-elliptical shape, or a rectangular shape.
  • the flow path cross-sectional areas of the plurality of communication hole portions 25 are the same size.
  • the flow path cross-sectional areas of the plurality of communication hole portions 25 are not limited to those having the same size, and may be formed to have different sizes.
  • the cross-sectional area of each flow path of the plurality of communication hole portions 25 is based on the cross-sectional area of each flow path of the plurality of heat transfer tubes 70, that is, the sum of the cross-sectional areas of the flow paths of the plurality of refrigerant passages 72 formed in each heat transfer tube 70. Is also getting smaller.
  • the cross-sectional area of each flow path of the plurality of communication hole portions 25 is smaller than the opening area of each of the plurality of through hole portions 31, which will be described later.
  • the plurality of communication hole portions 25 are arranged in the vertical direction along the longitudinal direction of the second plate-shaped member 20. Further, two communication hole portions 25 are formed side by side along the lateral direction of the second plate-shaped member 20. That is, two rows of communication hole portions 25 formed by the plurality of communication hole portions 25 arranged in the vertical direction are formed in the lateral direction of the second plate-shaped member 20.
  • a group of a plurality of communication hole portions 25 arranged in one row is referred to as a first communication hole group 125a.
  • the first communication hole group 125a is formed along the first direction in which a plurality of heat transfer tubes 70 are arranged, and a plurality of communication hole portions for communicating each of the plurality of confluence flow paths 32 with the first distribution flow path 15a.
  • a group of a plurality of communication hole portions 25 arranged in the other row is referred to as a second communication hole group 125b.
  • the second communication hole group 125b is formed along the first direction in which a plurality of heat transfer tubes 70 are arranged, and a plurality of communication hole portions that communicate each of the plurality of confluence flow paths 32 with the second distribution flow path 16a. It is composed of 25.
  • the plurality of communication hole portions 25 of the first communication hole group 125a are formed so as to overlap the first distribution flow path 15a of the first plate-shaped member 10 when viewed in the plate thickness direction of the second plate-shaped member 20.
  • each of the plurality of communication hole portions 25 of the first communication hole group 125a is a confluence flow path 32 of the third plate-shaped member 30, which will be described later, when viewed in the plate thickness direction of the second plate-shaped member 20. It is formed so as to overlap each other.
  • each of the plurality of communication hole portions 25 of the first communication hole group 125a is formed so as to overlap each of the plurality of heat transfer tubes 70 when viewed in the plate thickness direction of the second plate-shaped member 20. Therefore, the first distribution flow path 15a of the first plate-shaped member 10 and each of the plurality of heat transfer tubes 70 communicate with each other through the plurality of communication hole portions 25 of the first communication hole group 125a.
  • the plurality of communication hole portions 25 of the second communication hole group 125b are formed so as to overlap the second distribution flow path 16a of the first plate-shaped member 10 when viewed in the plate thickness direction of the second plate-shaped member 20. Has been done. Further, each of the plurality of communication hole portions 25 of the second communication hole group 125b and the plurality of merging flow paths 32 of the third plate-shaped member 30 when viewed in the plate thickness direction of the second plate-shaped member 20. It is formed so as to overlap. Further, each of the plurality of communication hole portions 25 of the second communication hole group 125b is formed so as to overlap each of the plurality of heat transfer tubes 70 when viewed in the plate thickness direction of the second plate-shaped member 20. Therefore, the second distribution flow path 16a of the first plate-shaped member 10 and each of the plurality of heat transfer tubes 70 communicate with each other through the plurality of communication hole portions 25 of the second communication hole group 125b.
  • the second plate-shaped member 20 has a flat plate-shaped closing portion 24.
  • a part of the closing portion 24 overlaps the first distribution flow path 15a and the second distribution flow path 16a of the first plate-shaped member 10 when viewed in the plate thickness direction of the second plate-shaped member 20.
  • the closing portion 24 has a function of preventing the first distribution flow path 15a and the second distribution flow path 16a from directly communicating with each of the plurality of heat transfer tubes 70 without passing through the communication hole portion 25.
  • the third plate-shaped member 30 is arranged between the second plate-shaped member 20 and the fourth plate-shaped member 40.
  • the third plate-shaped member 30 has a plurality of through-hole portions 31.
  • Each of the plurality of through-hole portions 31 forms a through hole that penetrates the third plate-shaped member 30, and penetrates the third plate-shaped member 30 in the plate thickness direction of the third plate-shaped member 30.
  • the plurality of through-hole portions 31 are provided independently of each other corresponding to each of the plurality of heat transfer tubes 70.
  • the plurality of through-hole portions 31 are formed in parallel in the vertical direction along the longitudinal direction of the third plate-shaped member 30.
  • the through hole portion 31 has a flat opening shape similar to the outer peripheral shape of the heat transfer tube 70.
  • the opening area of each through hole portion 31 is the same as or larger than the opening area of each insertion hole 41 of the fourth plate-shaped member 40.
  • the open end of the through hole portion 31 overlaps with the outer peripheral surface of the heat transfer tube 70 or is located outside the outer peripheral surface.
  • a merging flow path 32 provided corresponding to each heat transfer tube 70 is formed inside each through hole portion 31.
  • the merging flow path 32 communicates with the plurality of heat transfer tubes 70, and the refrigerant flowing through the first distribution flow path 15a and the second distribution flow path 16a merges. It is a space.
  • One end of the heat transfer tube 70 penetrates the insertion hole 41 of the fourth plate-shaped member 40 and reaches the merging flow path 32.
  • the open ends of the plurality of refrigerant passages 72 formed at one end of the heat transfer tube 70 all face the merging passage 32.
  • Each of the plurality of refrigerant passages 72 of the heat transfer tube 70 communicates with the first distribution flow path 15a and the second distribution flow path 16a via the merging flow path 32 and the communication hole portion 25.
  • the merging flow path 32 flows through the first distribution flow path 15a, the refrigerant that has passed through the communication hole portion 25 of the first communication hole group 125a, and the second distribution flow path 16a, and flows through the communication hole of the second communication hole group 125b. This is a space where the refrigerant that has passed through the portion 25 merges.
  • the refrigerant flowing through the first distribution flow path 15a and the second distribution flow path 16a merges in the merging flow path 32, and then flows into the refrigerant passage 72 of the heat transfer tube 70.
  • the fourth plate-shaped member 40 is formed with a plurality of insertion holes 41 into which one ends of the plurality of heat transfer tubes 70 are inserted.
  • Each of the plurality of insertion holes 41 penetrates the fourth plate-shaped member 40 in the plate thickness direction of the fourth plate-shaped member 40.
  • the plurality of insertion holes 41 are arranged in parallel in the vertical direction along the longitudinal direction of the fourth plate-shaped member 40.
  • the insertion hole 41 has a flat opening shape similar to the outer peripheral shape of the heat transfer tube 70.
  • the open end of the insertion hole 41 is joined to the outer peripheral surface of the heat transfer tube 70 over the entire circumference by brazing.
  • the operation of the refrigeration cycle apparatus 100 will be described with reference to FIG.
  • the high-pressure and high-temperature gas-state refrigerant discharged from the compressor 101 flows into the indoor heat exchanger 103 via the flow path switching device 102, and the air supplied by the indoor blower 109. Heat exchange with and condenses.
  • the condensed refrigerant becomes a high-pressure liquid state, flows out from the indoor heat exchanger 103, and becomes a low-pressure gas-liquid two-phase state by the decompression device 104.
  • the low-pressure gas-liquid two-phase state refrigerant is distributed to each heat transfer tube 70 of the outdoor heat exchanger 105 by the refrigerant distributor 50, and evaporates by heat exchange with the air supplied by the outdoor blower 108.
  • the evaporated refrigerant becomes a low-pressure gas state and is sucked into the compressor 101.
  • the refrigerant flowing through the refrigerant circuit 110 flows in the opposite direction to that during the heating operation. That is, during the cooling operation of the refrigeration cycle device 100, the high-pressure and high-temperature gas-state refrigerant discharged from the compressor 101 flows into the outdoor heat exchanger 105 via the flow path switching device 102 and is supplied by the outdoor blower 108. It exchanges heat with the air and condenses.
  • the condensed refrigerant is in a high-pressure liquid state, flows out of the outdoor heat exchanger 105, and is in a low-pressure gas-liquid two-phase state by the decompression device 104.
  • the low-pressure gas-liquid two-phase state refrigerant is distributed to each heat transfer tube 70 of the indoor heat exchanger 103 by the refrigerant distributor 50, and evaporates by heat exchange with the air supplied by the indoor blower 109.
  • the evaporated refrigerant becomes a low-pressure gas state and is sucked into the compressor 101.
  • the refrigerant distributor 50 according to the first embodiment will be described by exemplifying the operation when the heat exchanger 80 functions as the evaporator of the refrigeration cycle device 100.
  • the refrigerant flowing from the decompression device 104 into the refrigerant distributor 50 of the heat exchanger 80 functioning as an evaporator is a gas-liquid two-phase refrigerant decompressed by the decompression device 104.
  • This gas-liquid two-phase refrigerant flows into the refrigerant distributor 50 from the refrigerant inflow pipe 60, and has two distribution flow paths 15a and a second distribution flow path 16a provided in parallel with the first plate-shaped member 10. It flows upward in the distribution flow path.
  • the refrigerant flowing through the two distribution channels 15a and 16a has a height corresponding to each heat transfer tube 70 via the first communication hole group 125a and the second communication hole group 125b. It will be distributed.
  • the first communication hole group 125a and the second communication hole group 125b are formed in the second plate-shaped member 20 so as to correspond to each heat transfer tube 70, and are formed with the first distribution flow path 15a and the second distribution flow path 16a. It communicates with the merging flow path 32.
  • the refrigerant flowing through the first distribution flow path 15a whose cross-sectional area of the flow path is smaller than that of the second distribution flow path 16a, has a predetermined height in the first communication hole group 125a communicating with the first distribution flow path 15a.
  • the refrigerant is distributed so as to maximize the flow rate of the refrigerant passing through the communication hole portion 25.
  • the refrigerant flowing through the second distribution flow path 16a having a larger cross-sectional area than the first distribution flow path 15a is predetermined in the second communication hole group 125b communicating with the second distribution flow path 16a.
  • the refrigerant is distributed so as to maximize the flow rate of the refrigerant passing through the communication hole portion 25 having a height of.
  • the position of the communication hole portion 25 in which the refrigerant flow rate is maximum in the second communication hole group 125b is lower than the position of the communication hole portion 25 in which the refrigerant flow rate is maximum in the first communication hole group 125a, that is, The position is close to the connection position of the refrigerant inflow pipe 60.
  • FIG. 6 is a conceptual diagram showing the refrigerant distribution of the refrigerant distributor 50 according to the first embodiment.
  • the horizontal axis represents the flow rate of the refrigerant liquid [kg / h]
  • the vertical axis represents the distance from the refrigerant inflow port 18 in the first direction in which the heat transfer tubes 70 are arranged.
  • the dotted line A shows the flow rate of the refrigerant flowing through the first distribution flow path 15a
  • the broken line B shows the flow rate of the refrigerant flowing through the second distribution flow path 16a.
  • the solid line C shows the total flow rate of the flow rate of the refrigerant flowing through the first distribution flow path 15a and the flow rate of the refrigerant flowing through the second distribution flow path 16a.
  • the alternate long and short dash line D shows a case where the total flow rate of the flow rate of the refrigerant flowing through the first distribution flow path 15a and the flow rate of the refrigerant flowing through the second distribution flow path 16a are equal in the distance from the refrigerant inlet 18. It is a dotted line.
  • the point M1 shown in FIG. 6 represents the maximum refrigerant flow rate and the distance thereof in the first distribution flow path 15a
  • the point M2 shown in FIG. 6 represents the maximum refrigerant flow rate and the distance thereof in the second distribution flow path 16a. Represents.
  • the distance between them is the first distance L1.
  • the distance is the second distance L2.
  • the refrigerant distributor 50 has a different distance between the first distance L1 and the second distance L2.
  • the position of the communication hole portion 25 in which the refrigerant flow rate is maximum in the first communication hole group 125a is the communication hole portion in which the refrigerant flow rate is maximum in the second communication hole group 125b.
  • the position is farther from the refrigerant inflow port 18 than the position of 25.
  • the position of the communication hole portion 25 where the refrigerant flow rate is maximum in the second communication hole group 125b is such that the refrigerant flow rate is maximum in the first communication hole group 125a.
  • the position is closer to the refrigerant inflow port 18 than the position of the communication hole portion 25.
  • the cross-sectional area of the first distribution flow path 15a is smaller than that of the second distribution flow path 16a. Therefore, the flow velocity of the refrigerant flowing through the first distribution flow path 15a is higher than the flow velocity of the refrigerant flowing through the second distribution flow path 16a. Therefore, the refrigerant flowing through the first distribution flow path 15a can flow to a position farther from the refrigerant inflow port 18 than the refrigerant flowing through the second distribution flow path 16a while maintaining the flow velocity. For example, when the extension direction of the first distribution flow path 15a and the second distribution flow path 16a is the vertical direction, the refrigerant flowing through the first distribution flow path 15a is larger than the refrigerant flowing through the second distribution flow path 16a.
  • the refrigerant distributor 50 controls the flow velocity of the refrigerant flowing through the first distribution flow path 15a and the flow velocity of the refrigerant flowing through the second distribution flow path 16a by the difference in the size of the flow path cross-sectional area.
  • the refrigerant that flows through the two distribution channels 15a and the second distribution channel 16a and is distributed so as to maximize the refrigerant flow rate at different distances from the refrigerant inlet 18 is a third plate-shaped member.
  • the merging flow paths 32 provided at the height of each heat transfer tube 70 are merged by 30. As shown by the solid line C in FIG. 6, the total flow rate of the refrigerant flowing through the first distribution flow path 15a and the flow rate of the refrigerant flowing through the second distribution flow path 16a approaches the alternate long and short dash line D.
  • the total flow rate of the flow rate of the refrigerant flowing through the first distribution flow path 15a and the flow rate of the refrigerant flowing through the second distribution flow path 16a suppresses the drift with respect to the distance from the refrigerant inflow port 18, and a plurality of transmissions.
  • the flow rate of the refrigerant distributed to the heat pipe 70 can be made uniform.
  • the refrigerant distributor 50 is formed so that the flow path cross-sectional area of the first distribution flow path 15a and the flow path cross-sectional area of the second distribution flow path 16a are different.
  • the refrigerant distributor 50 In the refrigerant distributor 50, a large amount of refrigerant is distributed to the lower heat transfer tube 70 by the second distribution flow path 16a having a large flow path cross-sectional area, and the upper heat transfer tube 70 is distributed by the first distribution flow path 15a having a small flow path cross-sectional area. A large amount of refrigerant is distributed to. Then, the refrigerant distributor 50 merges the refrigerant flowing through the second distribution flow path 16a and the refrigerant flowing through the first distribution flow path 15a at the merging flow path 32 and flows them through the heat transfer tubes 70. Therefore, the refrigerant distributor 50 can equalize the distribution of the refrigerant flowing into each heat transfer tube 70 and improve the performance of the heat exchanger 80.
  • the first plate-shaped member 10, the second plate-shaped member 20, the third plate-shaped member 30, and the fourth plate-shaped member 40 having the above configuration are laminated. Is formed.
  • the refrigerant distributor 50 separates the holding member into which the heat transfer tube 70 is directly inserted and the first distribution flow path 15a and the second distribution flow path 16a into separate parts, whereby the first distribution flow path 15a and the second distribution flow path 15a and the second distribution flow path 16a are separated.
  • the length of the distribution flow path 16a in the long axis direction of the flat tube can be made smaller than the long axis of the flat tube.
  • the refrigerant distributor 50 can reduce the volume inside the main body 51, and can reduce the amount of the required refrigerant sealed in the air conditioner.
  • the diameter of the main body is larger than when a circular pipe is used, so the volume of the distribution flow path is expanded and the amount of refrigerant is increased. May increase.
  • the refrigerant distributor 50 can reduce the volume inside the main body 51 and reduce the amount of the required refrigerant sealed in the air conditioner by the above configuration.
  • FIG. 7 is an exploded perspective view showing a main configuration of the heat exchanger 80 provided with the refrigerant distributor 50A according to the second embodiment.
  • FIG. 8 is an upper cross-sectional view showing the configuration of the refrigerant distributor 50A according to the second embodiment.
  • the components having the same functions and functions as those in the first embodiment are designated by the same reference numerals, and the description thereof will be omitted.
  • the configuration of the first plate-shaped member 10A is different from that of the first plate-shaped member 10 of the refrigerant distributor 50 of the first embodiment.
  • the first plate-shaped member 10A has a first flow path portion 115 forming a first distribution flow path 115a inside and a second distribution flow path 116a forming a second distribution flow path 116a inside. It has a flow path portion 116.
  • the flow path cross-sectional area of the first distribution flow path 115a decreases as it goes upward, and the flow path cross-sectional area of the second distribution flow path 116a increases as it goes upward.
  • the flow path cross-sectional area of the first distribution flow path 115a decreases as the distance from the first refrigerant inflow port 18a increases, and the second distribution flow path 116a becomes the second distribution flow path 116a.
  • the flow path cross-sectional area increases as the distance from the refrigerant inlet 18b increases.
  • the distance from one end 51a of the main body 51 to the other end 51b is defined as a distance A
  • the distance from 51a to the other end 51b is defined as the distance B.
  • the refrigerant distributor 50A has a different flow path shape so that the flow path cross-sectional areas of the first distribution flow path 115a and the second distribution flow path 116a are different at positions where the distance A and the distance B are equal.
  • the refrigerant distributor 50A has the first distribution flow path 115a and the second distribution flow path 115a at a position corresponding to the formation position of a certain communication hole portion 25 among the plurality of communication hole portions 25 formed along the first direction.
  • the flow path shape is different so that the flow path cross-sectional area of the distribution flow path 116a is different.
  • the first flow path portion 115 and the second flow path portion 116 will be described with a focus on the differences from the refrigerant distributor 50 of the first embodiment.
  • the first flow path portion 115 extends from one end in the longitudinal direction to the other end in the longitudinal direction of the first plate-shaped member 10A along the longitudinal direction of the first plate-shaped member 10A. Both ends of the first flow path portion 115 in the stretching direction are closed.
  • the first flow path portion 115 is formed in a square columnar shape in which one surface is inclined with respect to the major axis direction.
  • the first flow path portion 115 is formed so as to taper from one end to the other end on the first refrigerant inflow port 18a side in the longitudinal direction of the first plate-shaped member 10A.
  • the first flow path portion 115 has a rectangular cross-sectional shape. However, the cross-sectional shape of the first flow path portion 115 is not limited to a rectangle, and may be, for example, a semicircular shape, a semi-elliptical shape, or a semi-elliptical shape.
  • the second flow path portion 116 extends from one end in the longitudinal direction to the other end in the longitudinal direction of the first plate-shaped member 10A along the longitudinal direction of the first plate-shaped member 10A. Both ends of the second flow path portion 116 in the stretching direction are closed.
  • the second flow path portion 116 is formed in a square columnar shape in which one surface is inclined with respect to the major axis direction.
  • the second refrigerant inlet 18b is formed from one end on the side opposite to the side on which the second refrigerant inlet 18b is formed in the longitudinal direction of the first plate-shaped member 10A. It is formed so as to taper toward the other end of the side.
  • the second flow path portion 116 has a rectangular cross-sectional shape. However, the cross-sectional shape of the second flow path portion 116 is not limited to a rectangle, and may be, for example, a semicircular shape, a semi-elliptical shape, or a semi-elliptical shape.
  • the first flow path portion 115 and the second flow path portion 116 are not limited to a square columnar whose one surface is inclined with respect to the major axis direction, and for example, a truncated cone shape or a truncated pyramid cone. Other shapes such as a shape may be used. Further, the first flow path portion 115 and the second flow path portion 116 may be, for example, a square columnar whose one surface is inclined with respect to the extending direction of the heat transfer tube 70. That is, the first flow path portion 115 and the second flow path portion 116 may change the amount of protrusion of the wall in the extending direction of the heat transfer tube 70 in the longitudinal direction of the first plate-shaped member 10A.
  • first distribution flow path 115a extending in the vertical direction along the longitudinal direction of the first plate-shaped member 10A is formed inside the first flow path portion 115.
  • second distribution flow path 116a a second distribution flow path 116a extending in the vertical direction along the longitudinal direction of the first plate-shaped member 10A is formed inside the second flow path portion 116.
  • the first distribution flow path 115a and the second distribution flow path 116a extend so as to intersect with each of the plurality of heat transfer tubes 70 when viewed in the plate thickness direction of the first plate-shaped member 10A.
  • the first distribution flow path 115a and the second distribution flow path 116a have a rectangular cross-sectional shape.
  • first distribution flow path 115a and the second distribution flow path 116a are spaces formed in a rectangular parallelepiped shape.
  • the cross-sectional shapes of the first distribution flow path 115a and the second distribution flow path 116a are not limited to a rectangular shape, and may be, for example, a semicircular shape, a semi-elliptical shape, or a semi-long circular shape.
  • the cross-sectional area of the first distribution flow path 115a decreases from one end to the other end where the first refrigerant inflow port 18a is formed in the stretching direction of the first flow path portion 115.
  • the cross-sectional area of the second distribution flow path 116a increases from one end to the other end where the second refrigerant inflow port 18b is formed in the stretching direction of the first flow path portion 115.
  • the change in the cross-sectional area of the first distribution flow path 115a and the second distribution flow path 116a in the extension direction is the same as that of the first distribution flow path 115a in the long axis direction of the heat transfer tube 70.
  • the change in the cross-sectional area of the first distribution flow path 115a and the second distribution flow path 116a in the extension direction is not limited to the configuration, and for example, the first distribution flow path 115a in the extension direction of the heat transfer tube 70. And may depend on the change in size of the second distribution channel 116a.
  • the first distribution flow path 115a and the second distribution flow path 116a communicate with the refrigerant inflow pipe 60 at the end in the extending direction.
  • the gas-liquid two-phase refrigerant flowing into the first distribution flow path 115a and the second distribution flow path 116a via the refrigerant inflow pipe 60 is the first distribution flow path 115a and the second distribution flow path 116a as shown by an arrow F. Flows upward and is distributed to each heat transfer tube 70.
  • the first branch pipe 62 is connected to the first flow path portion 115 and communicates with the first distribution flow path 115a
  • the second branch pipe 63 is connected to the second flow path portion 116 and is connected to the second distribution flow path 116a. Communicate with.
  • the relationship between the first distribution flow path 115a and the second plate-shaped member 20, the third plate-shaped member 30, the fourth plate-shaped member 40, and the heat transfer tube 70 is as follows between the first distribution flow path 15a and the second plate. Since the relationship is the same as that of the shape member 20, the third plate-shaped member 30, the fourth plate-shaped member 40, and the heat transfer tube 70, the description thereof will be omitted.
  • the relationship between the second distribution flow path 116a and the second plate-shaped member 20, the third plate-shaped member 30, the fourth plate-shaped member 40, and the heat transfer tube 70 is the second distribution flow path 16a and the second. Since the relationship is the same as that of the plate-shaped member 20, the third plate-shaped member 30, the fourth plate-shaped member 40, and the heat transfer tube 70, the description thereof will be omitted.
  • the first distribution flow path 115a is formed so that the cross-sectional area of the flow path decreases as the distance from the first refrigerant inflow port 18a increases in the stretching direction of the first flow path portion 115. Therefore, the flow velocity of the refrigerant flowing through the first distribution flow path 115a increases as the distance from the first refrigerant inlet 18a, that is, toward the upward direction, increases. As a result, the refrigerant flowing through the first distribution flow path 115a has a predetermined height located above the first refrigerant inflow port 18a in the first communication hole group 125a communicating with the first distribution flow path 115a. It is distributed to each heat transfer tube 70 so that the flow rate of the refrigerant passing through the communication hole 25 is maximized.
  • the second distribution flow path 116a is formed so that the cross-sectional area of the flow path increases as the distance from the second refrigerant inflow port 18b increases in the extension direction of the second flow path portion 116. Therefore, the flow velocity of the refrigerant flowing through the second distribution flow path 116a decreases as the refrigerant flows away from the second refrigerant inflow port 18b, that is, as it goes upward. As a result, the refrigerant flowing through the second distribution flow path 116a communicates with a predetermined height located below the second refrigerant inflow port 18b in the second communication hole group 125b communicating with the second distribution flow path 116a. It is distributed to each heat transfer tube 70 so that the flow rate of the refrigerant passing through the hole 25 is maximized.
  • the refrigerant distributor 50A controls the flow velocity of the refrigerant flowing through the first distribution flow path 115a and the flow velocity of the refrigerant flowing through the second distribution flow path 116a by the difference in the size of the flow path cross-sectional area. Therefore, as shown by the dotted line A and the broken line B in FIG. 6, the position of the communication hole portion 25 where the refrigerant flow rate is maximum in the first communication hole group 125a is the communication where the refrigerant flow rate is maximum in the second communication hole group 125b. The position is farther from the refrigerant inflow port 18 than the position of the hole 25. In other words, as shown by the dotted line A and the broken line B in FIG.
  • the position of the communication hole portion 25 where the refrigerant flow rate is maximum in the second communication hole group 125b is such that the refrigerant flow rate is maximum in the first communication hole group 125a.
  • the position is closer to the refrigerant inflow port 18 than the position of the communication hole portion 25.
  • the refrigerant that flows through the two distribution channels 115a and the second distribution flow path 116a and is distributed so as to maximize the refrigerant flow rate at different distances from the refrigerant inlet 18 is a third plate-shaped member.
  • the merging flow paths 32 provided at the height of each heat transfer tube 70 are merged by 30. As shown by the solid line C in FIG. 6, the total flow rate of the refrigerant flowing through the first distribution flow path 115a and the flow rate of the refrigerant flowing through the second distribution flow path 116a approaches the alternate long and short dash line D.
  • the total flow rate of the flow rate of the refrigerant flowing through the first distribution flow path 115a and the flow rate of the refrigerant flowing through the second distribution flow path 116a suppresses the drift with respect to the distance from the refrigerant inflow port 18, and a plurality of transmissions.
  • the flow rate of the refrigerant distributed to the heat pipe 70 can be made uniform.
  • the flow path cross-sectional area decreases as the first distribution flow path 115a moves away from the first refrigerant inflow port 18a, and the second distribution flow path 116a becomes It is formed so that the cross-sectional area of the flow path expands as the distance from the second refrigerant inlet 18b increases.
  • the refrigerant distributor 50 is largely distributed to the lower heat transfer tube 70 by the second distribution flow path 16a, and is largely distributed to the upper heat transfer tube 70 by the first distribution flow path 15a. Then, the refrigerant distributor 50 merges the refrigerant flowing through the second distribution flow path 16a and the refrigerant flowing through the first distribution flow path 15a at the merging flow path 32 and flows them through the heat transfer tubes 70. Therefore, the refrigerant distributor 50 can equalize the distribution of the refrigerant flowing into each heat transfer tube 70 and improve the performance of the heat exchanger 80.
  • FIG. 9 is an exploded perspective view showing a main configuration of the heat exchanger 80 provided with the refrigerant distributor 50B according to the third embodiment.
  • FIG. 10 is a cross-sectional view showing the configuration of the refrigerant distributor 50B according to the third embodiment.
  • the components having the same functions and functions as those in the first embodiment are designated by the same reference numerals, and the description thereof will be omitted.
  • the configuration of the first plate-shaped member 10B and the second plate-shaped member 20B is the first plate-shaped member 10 and the second plate-shaped member 10 of the refrigerant distributor 50 of the first embodiment. Different from member 20.
  • the first plate-shaped member 10B and the second plate-shaped member 20B will be described with a focus on the differences between the refrigerant distributors 50 of the first embodiment.
  • the first flow path portion 215 and the second flow path portion 216 extend from one end in the longitudinal direction to the other end in the longitudinal direction of the first plate-shaped member 10 along the longitudinal direction of the first plate-shaped member 10.
  • the first flow path portion 215 and the second flow path portion 216 are formed in a semi-cylindrical shape. Both ends of the first flow path portion 215 and the second flow path portion 216 in the stretching direction are closed.
  • the first flow path portion 215 and the second flow path portion 216 have a semicircular, semi-elliptical or semi-elliptical cross-sectional shape.
  • the cross-sectional shapes of the first flow path portion 215 and the second flow path portion 216 are not limited to a semicircular shape, a semi-elliptical shape, or a semi-elliptical shape, and may be, for example, a rectangular shape.
  • first distribution flow path 215a extending in the vertical direction along the longitudinal direction of the first plate-shaped member 10B is formed inside the second flow path portion 216.
  • second distribution flow path 216a extending in the vertical direction along the longitudinal direction of the first plate-shaped member 10B is formed inside the second flow path portion 216.
  • the first distribution flow path 215a and the second distribution flow path 216a extend so as to intersect with each of the plurality of heat transfer tubes 70 when viewed in the plate thickness direction of the first plate-shaped member 10B.
  • the first distribution flow path 215a and the second distribution flow path 216a have a semicircular, semi-elliptical or semi-oval cross-sectional shape. That is, the first distribution flow path 215a and the second distribution flow path 216a are spaces formed in a semi-cylindrical shape, a semi-elliptical cylinder shape, or a semi-long cylindrical shape.
  • the cross-sectional shapes of the first distribution flow path 215a and the second distribution flow path 216a are not limited to a semicircular shape, a semi-elliptical shape, or a semi-elliptical shape, and may be, for example, a rectangular shape.
  • the cross-sectional area of the first distribution flow path 215a is the same as the cross-sectional area of the second distribution flow path 216a.
  • the same size includes a size that is completely equal and a size that has a slight error from each other.
  • the first distribution flow path 215a and the second distribution flow path 216a communicate with the refrigerant inflow pipe 60 at the end in the extending direction.
  • the gas-liquid two-phase refrigerant flowing into the first distribution flow path 215a and the second distribution flow path 216a via the refrigerant inflow pipe 60 is the first distribution flow path 215a and the second distribution flow path 216a as shown by arrows F. Flows upward and is distributed to each heat transfer tube 70.
  • a refrigerant inflow pipe 60 communicates with the lower ends of the first distribution flow path 215a and the second distribution flow path 216a.
  • the first branch pipe 62 is connected to the first flow path portion 215 and communicates with the first distribution flow path 215a
  • the second branch pipe 63 is connected to the second flow path portion 216 to communicate with the second distribution flow path 216a. Communicate with.
  • a plurality of communication holes 25 are formed in the second plate-shaped member 20B.
  • the plurality of communication hole portions 25 are composed of a first communication hole portion 25a and a second communication hole portion 25b.
  • the opening diameter of the first communication hole portion 25a is smaller than that of the second communication hole portion 25b, and the flow path cross-sectional area is smaller.
  • the second communication hole portion 25b has a larger opening diameter and a larger flow path cross-sectional area than the first communication hole portion 25a.
  • the second plate-shaped member 20 has the first communication hole portion 25a arranged above the second plate-shaped member 20B in the longitudinal direction and the second communication hole portion 25b arranged below. There is. That is, in the first communication hole group 125a, the second communication hole portion 25b is formed from the intermediate position on the side of the first refrigerant inflow port 18a in the longitudinal direction of the second plate-shaped member 20B, and the first refrigerant inflow port is formed from the intermediate position.
  • the first communication hole portion 25a is formed on the side opposite to the 18a.
  • the cross-sectional area of the communication hole portion 25 provided below the second plate-shaped member 20 is larger than the cross-sectional area of the communication hole portion 25 provided above. That is, in the first communication hole group 125a, the flow path cross-sectional area of the plurality of communication holes 25 on the side close to the first refrigerant inflow port 18a in the first direction, which is the arrangement direction of the heat transfer tubes 70, is the first refrigerant flow. It is formed larger than the flow path cross-sectional area of the plurality of communication hole portions 25 on the far side of the inlet 18a.
  • the second communication hole portion 25b is arranged above the second plate-shaped member 20B in the longitudinal direction, and the first communication hole portion 25a is arranged below. There is. That is, in the second communication hole group 125b, the first communication hole portion 25a is formed from the intermediate position to the second refrigerant inflow port 18b side in the longitudinal direction of the second plate-shaped member 20B, and the second refrigerant inflow port is formed from the intermediate position.
  • a second communication hole portion 25b is formed on the side opposite to the 18b.
  • the cross-sectional area of the communication hole portion 25 provided above the second plate-shaped member 20 is larger than the cross-sectional area of the communication hole portion 25 provided below. That is, in the second communication hole group 125b, in the first direction which is the arrangement direction of the heat transfer tubes 70, the flow path cross-sectional area of the plurality of communication holes 25 on the side far from the second refrigerant inflow port 18b is the second refrigerant flow. It is formed larger than the flow path cross-sectional area of the plurality of communication hole portions 25 on the side close to the inlet 18b.
  • the distance from one end 51a of the main body 51 to the other end 51b is defined as a distance A
  • the distance from 51a to the other end 51b is defined as the distance B.
  • the refrigerant distributor 50B at a position where the distance A and the distance B are equal to each other, one of the plurality of communication hole portions 25 constituting the first communication hole group 125a and the plurality of communication hole portions 25 constituting the second communication hole group 125b are provided.
  • the shape of the flow path is different so that the cross-sectional area of one flow path is different.
  • the refrigerant distributor 50B constitutes the first communication hole group 125a at a position corresponding to the formation position of a certain communication hole portion 25 among the plurality of communication hole portions 25 formed along the first direction.
  • the flow path shape is different so that one of the plurality of communication hole portions 25 and one of the plurality of communication hole portions 25 constituting the second communication hole group 125b have different flow path cross-sectional areas.
  • the flow of the refrigerant in the refrigerant distributor 50B will be described.
  • the cross-sectional area of the communication hole portion 25 provided below the second plate-shaped member 20 is larger than the cross-sectional area of the communication hole portion 25 provided above. Therefore, the refrigerant passing through the communication hole portion 25 has a small resistance when passing through the communication hole portion 25 at the lower part of the second plate-shaped member 20, and passes through the communication hole portion 25 at the upper part of the second plate-shaped member 20. There is a lot of resistance. Therefore, in the first communication hole group 125a, the refrigerant tends to flow to the lower communication hole 25 closer to the first refrigerant inlet 18a than to the upper communication hole 25 far from the first refrigerant inlet 18a.
  • the cross-sectional area of the communication hole portion 25 provided above the second plate-shaped member 20 is larger than the cross-sectional area of the communication hole portion 25 provided below. Therefore, the refrigerant passing through the communication hole portion 25 has a large resistance when passing through the communication hole portion 25 at the lower part of the second plate-shaped member 20, and passes through the communication hole portion 25 at the upper part of the second plate-shaped member 20. The resistance is small. Therefore, in the second communication hole group 125b, the refrigerant is more likely to flow to the upper communication hole 25 far from the second refrigerant inlet 18b than the lower communication hole 25 near the second refrigerant inlet 18b.
  • FIG. 11 is a conceptual diagram showing the refrigerant distribution of the refrigerant distributor 50B according to the third embodiment.
  • the dotted line A shows the flow rate of the refrigerant flowing through the first distribution flow path 215a
  • the broken line B shows the flow rate of the refrigerant flowing through the second distribution flow path 216a
  • the solid line C shows the total flow rate of the refrigerant flowing through the first distribution flow path 215a and the flow rate of the refrigerant flowing through the second distribution flow path 216a.
  • alternate long and short dash line D is a case where the total flow rate of the refrigerant flowing through the first distribution flow path 215a and the flow rate of the refrigerant flowing through the second distribution flow path 216a is equal to the distance from the refrigerant inlet 18. It is a line showing.
  • the distance between them is the first distance L1.
  • the distance is the second distance L2.
  • the first distance L1 and the second distance L2 are different distances.
  • the refrigerant distributor 50B has the same cross-sectional area as the first distribution flow path 215a and the second distribution flow path 216a. Then, in the first communication hole group 125a, the refrigerant tends to flow to the lower communication hole portion 25 closer to the first refrigerant inflow port 18a than the upper communication hole portion 25 far from the first refrigerant inflow port 18a. Therefore, as shown by the dotted line A in FIG. 11, the refrigerant flowing through the first distribution flow path 215a communicates below the first refrigerant inflow port 18a with respect to the upper communication hole 25 far from the first refrigerant inflow port 18a. The flow rate of the refrigerant passing through the hole 25 increases.
  • the refrigerant distributor 50B has the same cross-sectional area as the first distribution flow path 215a and the second distribution flow path 216a. Then, in the second communication hole group 125b, the refrigerant tends to flow to the upper communication hole 25 far from the second refrigerant inflow port 18b than the lower communication hole 25 near the second refrigerant inflow port 18b. Therefore, as shown by the broken line B in FIG. 11, the refrigerant flowing through the second distribution flow path 216a communicates with the second refrigerant inlet 18b far from the lower communication hole 25 near the second refrigerant inlet 18b. The flow rate of the refrigerant passing through the hole 25 increases.
  • the refrigerant that flows through the two distribution channels of the first distribution flow path 215a and the second distribution flow path 216a and is distributed so as to maximize the refrigerant flow rate at different distances from the refrigerant inflow port 18 is a third plate-shaped member.
  • the merging flow paths 32 provided at the height of each heat transfer tube 70 are merged by 30. As shown by the solid line C in FIG. 11, the total flow rate of the refrigerant flowing through the first distribution flow path 215a and the flow rate of the refrigerant flowing through the second distribution flow path 216a approaches the alternate long and short dash line D.
  • the total flow rate of the flow rate of the refrigerant flowing through the first distribution flow path 215a and the flow rate of the refrigerant flowing through the second distribution flow path 216a suppresses the drift with respect to the distance from the refrigerant inflow port 18, and a plurality of transmissions.
  • the flow rate of the refrigerant distributed to the heat pipe 70 can be made uniform.
  • the plurality of communication hole portions 25 of the refrigerant distributor 50B according to the third embodiment are composed of the first communication hole portion 25a and the second communication hole portion 25b.
  • the plurality of communication hole portions 25 are not limited to two types, that is, the first communication hole portion 25a having a different flow path cross-sectional area and the second communication hole portion 25b.
  • the plurality of communication hole portions 25 constituting the first communication hole group 125a have a flow path cross-sectional area depending on the position where the communication hole portion 25 is formed from the upper side to the lower side in the longitudinal direction of the second plate-shaped member 20B. May be formed so as to be large.
  • the plurality of communication hole portions 25 constituting the second flow path hole group 126a cut the flow path from the lower side to the upper side depending on the position where the communication hole portion 25 is formed in the longitudinal direction of the second plate-shaped member 20B. It may be formed so as to have a large area.
  • the first communication hole group 125a has the flow path cross-sectional area of the plurality of communication holes 25 on the side close to the first refrigerant inflow port 18a in the arrangement direction of the heat transfer tubes 70. It is formed larger than the flow path cross-sectional area of the plurality of communication holes 25 on the far side from the first refrigerant inflow port 18a.
  • the second refrigerant group 125b has a flow path cross-sectional area of a plurality of communication holes 25 on the side farther from the second refrigerant inlet 18b in the arrangement direction of the heat transfer tubes 70.
  • the refrigerant distributor 50 In the refrigerant distributor 50, a large amount of refrigerant is distributed to the lower heat transfer tube 70 by the flow path resistance of the first communication hole group 125a, and the refrigerant is distributed to the upper heat transfer tube 70 by the flow path resistance of the second communication hole group 125b. Is distributed a lot. Then, the refrigerant distributor 50 merges the refrigerant flowing through the second distribution flow path 216a and the refrigerant flowing through the first distribution flow path 215a at the merging flow path 32 and flows them through the heat transfer tubes 70. Therefore, the refrigerant distributor 50 can equalize the distribution of the refrigerant flowing into each heat transfer tube 70 and improve the performance of the heat exchanger 80.
  • FIG. 12 is an exploded perspective view showing a main configuration of the heat exchanger 80 provided with the refrigerant distributor 50C according to the fourth embodiment.
  • FIG. 13 is a cross-sectional view showing the configuration of the refrigerant distributor 50C according to the fourth embodiment.
  • the components having the same functions and functions as those in the first embodiment are designated by the same reference numerals, and the description thereof will be omitted.
  • the configuration of the second plate-shaped member 20C of the refrigerant distributor 50C according to the fourth embodiment is different from that of the second plate-shaped member 20 of the refrigerant distributor 50 of the first embodiment.
  • the refrigerant distributor 50C according to the fourth embodiment will be described focusing on the differences between the refrigerant distributor 50 of the first embodiment.
  • the second plate-shaped member 20C of the refrigerant distributor 50C according to the fourth embodiment has the same configuration as the second plate-shaped member 20B of the third embodiment. That is, a plurality of communication hole portions 25 are formed in the second plate-shaped member 20C.
  • the plurality of communication hole portions 25 are composed of a first communication hole portion 25a and a second communication hole portion 25b.
  • the opening diameter of the first communication hole portion 25a is smaller than that of the second communication hole portion 25b, and the flow path cross-sectional area is smaller.
  • the second communication hole portion 25b has a larger opening diameter and a larger flow path cross-sectional area than the first communication hole portion 25a. Therefore, the refrigerant passing through the second plate-shaped member 20C has the characteristics shown in FIG.
  • the refrigerant in the first communication hole group 125a, the refrigerant is from the upper communication hole portion 25 far from the first refrigerant inlet 18a. Also easily flows into the lower communication hole 25 near the first refrigerant inflow port 18a. Further, in the second communication hole group 125b, the refrigerant tends to flow to the upper communication hole 25 far from the second refrigerant inlet 18b than the lower communication hole 25 near the second refrigerant inlet 18b.
  • the first plate-shaped member 10 of the refrigerant distributor 50C has a first distribution flow path 15a formed in the first flow path portion 15 and a second distribution flow path formed in the second flow path portion 16.
  • 16a and 16a are formed so as to have different flow path cross-sectional areas.
  • the flow path cross-sectional area of the second distribution flow path 16a is larger than the flow path cross-sectional area of the first distribution flow path 15a
  • the flow path cross-sectional area of the first distribution flow path 15a is the second distribution flow flow. It is smaller than the flow path cross-sectional area of the road 16a. Therefore, the first plate-shaped member 10 has the characteristics shown in FIG.
  • the position of the communication hole portion 25 where the refrigerant flow rate is maximized in the first communication hole group 125a is the refrigerant flow rate in the second communication hole group 125b. Is a position farther from the first refrigerant inflow port 18a than the position of the communication hole portion 25 having the maximum value.
  • the position of the communication hole portion 25 in which the refrigerant flow rate is maximum in the second communication hole group 125a is higher than the position of the communication hole portion 25 in which the refrigerant flow rate is maximum in the first communication hole group 125a. It will be close to.
  • the refrigerant distributor 50C has the following configuration from the above-mentioned first plate-shaped member 10 and the second plate-shaped member 20C.
  • the first distribution flow path 15a has a smaller flow path cross-sectional area than the second distribution flow path 16a.
  • the communication hole portion 25 having the cross-sectional area of the communication hole portion 25 provided at the lower portion of the second plate-shaped member 20C is cut off. Larger than the area.
  • the first communication hole group 125a communicating with the first distribution flow path 15a breaks the flow paths of the plurality of communication hole portions 25 on the side close to the first refrigerant inflow port 18a in the first direction which is the arrangement direction of the heat transfer tubes 70.
  • the area is formed to be larger than the flow path cross-sectional area of the plurality of communication holes 25 on the side far from the first refrigerant inflow port 18a.
  • the second communication hole group 125b communicating with the second distribution flow path 16a having a larger flow path cross-sectional area than the first distribution flow path 15a is provided above the second plate-shaped member 20C.
  • the cross-sectional area of the communication hole portion 25 provided is larger than the cross-sectional area of the communication hole portion 25 provided at the bottom.
  • the second communication hole group 125b communicating with the second distribution flow path 16a breaks the flow paths of the plurality of communication hole portions 25 on the side far from the second refrigerant inflow port 18b in the first direction, which is the arrangement direction of the heat transfer tubes 70.
  • the area is formed larger than the flow path cross-sectional area of the plurality of communication holes 25 on the side close to the second refrigerant inflow port 18b.
  • the distance from one end 51a of the main body 51 to the other end 51b is defined as a distance A
  • the second distribution flow path 16a one end of the main body 51 is defined.
  • the distance from 51a to the other end 51b is defined as the distance B.
  • the refrigerant distributor 50C has a flow path shape of the first distribution flow path 15a and the second distribution flow path 16a at a position where the distance A and the distance B are equal, and a plurality of communication holes constituting the first communication hole group 125a.
  • the flow path shapes of one of the portions 25 and one of the plurality of communication hole portions 25 constituting the second communication hole group 125b are different so that the flow path cross-sectional areas are different.
  • the refrigerant distributor 50C has the first distribution flow path 15a and the second distribution flow path 15a at a position corresponding to the formation position of one communication hole portion 25 among the plurality of communication hole portions 25 formed along the first direction.
  • the flow path shape of the distribution flow path 16a, and the flow path shape of one of the plurality of communication hole portions 25 constituting the first communication hole group 125a and one of the plurality of communication hole portions 25 constituting the second communication hole group 125b. are different so that the cross-sectional areas of the flow paths are different.
  • the flow of the refrigerant in the refrigerant distributor 50C will be described.
  • the refrigerant distributor 50 of the first embodiment when the refrigerant flow rate is large, a large amount of refrigerant is likely to be distributed to the upper heat transfer tube 70 in the first distribution flow path 15a having a small flow path cross-sectional area. Therefore, if the flow rate of the refrigerant flowing through the refrigerant distributor 50 becomes too large, an excessively large amount of refrigerant may flow through the upper heat transfer tube 70, and the refrigerant flowing through the refrigerant distributor 50 may flow unevenly.
  • the refrigerant distributor 50C is a communication hole portion located below the cross-sectional area of the communication hole portion 25 located at the upper part of the second plate-shaped member 20C in the first communication hole group 125a communicating with the first distribution flow path 15a.
  • the flow path resistance of the communication hole portion 25 located at the upper part is increased by making it smaller than the cross-sectional area of 25. Therefore, the refrigerant distributor 50C suppresses the refrigerant flow rate from becoming excessively large at a predetermined distance from the refrigerant inflow port 18 due to the flow path resistance formed by the second plate-shaped member 20C when the refrigerant flow rate is large. be able to.
  • the refrigerant distributor 50C in the second distribution flow path 16a having a large flow path cross-sectional area, a large amount of refrigerant is likely to be distributed to the lower heat transfer tube 70, and if the flow rate becomes too small, the lower heat transfer tube 70 Excessive amount of refrigerant may flow into the refrigerant, and the refrigerant flowing through the refrigerant distributor 50 may flow unevenly.
  • the refrigerant distributor 50C has a communication hole portion located above the cross-sectional area of the communication hole portion 25 located at the lower part of the second plate-shaped member 20C in the second communication hole group 125b communicating with the second distribution flow path 16a. It is made smaller than the cross-sectional area of 25 to increase the flow path resistance of the communication hole portion 25 located at the lower part. Therefore, when the refrigerant flow rate is small, the refrigerant distributor 50C suppresses the refrigerant flow rate from becoming excessively large at a predetermined distance from the refrigerant inflow port 18 due to the flow path resistance formed by the second plate-shaped member 20C. be able to.
  • the flow path cross-sectional area of the second distribution flow path 16a is larger than the flow path cross-sectional area of the first distribution flow path 15a, and the flow path cross-sectional area of the first distribution flow path 15a. However, it is smaller than the flow path cross-sectional area of the second distribution flow path 16a.
  • the flow path cross-sectional area of the plurality of communication hole portions 25 on the side close to the first refrigerant inflow port 18a in the first direction is the first refrigerant. It is formed larger than the flow path cross-sectional area of the plurality of communication holes 25 on the far side of the inflow port 18a.
  • the flow path cross-sectional area of the plurality of communication hole portions 25 on the side far from the second refrigerant inflow port 18b in the first direction is the second refrigerant. It is formed larger than the flow path cross-sectional area of the plurality of communication hole portions 25 on the side close to the inflow port 18b.
  • the refrigerant distributor 50C has an excessively large amount of refrigerant in the upper heat transfer tube 70 in the first distribution flow path 15a in which the flow path cross-sectional area is small and a large amount of refrigerant is easily distributed to the upper heat transfer tube 70 when the refrigerant flow rate becomes large. Suppresses the uneven flow. Further, the refrigerant distributor 50C is provided to the lower heat transfer tube 70 in the second distribution flow path 16a, which has a large flow path cross-sectional area and tends to distribute a large amount of refrigerant to the lower heat transfer tube 70 when the refrigerant flow rate becomes small. It is possible to prevent an excessively large amount of refrigerant from flowing unevenly.
  • the refrigerant distributor 50C can improve the distribution robustness with respect to the refrigerant flow rate, and can expand the operating range of the air conditioner equipped with the refrigerant distributor 50C.
  • the distribution characteristics to each heat transfer tube largely depend on the flow rate of the refrigerant in the refrigerant distributor, so that the distribution robustness to the flow rate of the refrigerant that changes depending on the operating state of the air conditioner Is low.
  • the distribution robustness is a flow rate that can approach even distribution to heat transfer tubes when the flow rate of the refrigerant used in air conditioners and the like is not a specific flow rate of the refrigerant but a range of flow rates. The ability to expand the range.
  • the refrigerant distributor 50C according to the fourth embodiment can improve the distribution robustness with respect to the refrigerant flow rate as described above.
  • FIG. 14 is an exploded perspective view showing a main configuration of the heat exchanger 80 provided with the refrigerant distributor 50D according to the fifth embodiment.
  • FIG. 15 is a cross-sectional view showing the configuration of the refrigerant distributor 50D according to the fifth embodiment.
  • the white arrow AF shown in FIGS. 14 and 15 indicates the flow of wind.
  • the air flow toward the refrigerant distributor 50D is formed by, for example, the indoor blower 109 of the refrigeration cycle device 100 shown in FIG. 1 or the outdoor blower 108.
  • the arrows F1 and F2 shown by hatching indicate the flow of the refrigerant passing through the second plate-shaped member 20D and flowing into the merging flow path 32 formed in the third plate-shaped member 30. ..
  • the components having the same functions and functions as those in the first embodiment are designated by the same reference numerals, and the description thereof will be omitted.
  • the configuration of the second plate-shaped member 20D of the refrigerant distributor 50D according to the fifth embodiment is different from that of the second plate-shaped member 20 of the refrigerant distributor 50 of the first embodiment.
  • the refrigerant distributor 50D according to the fifth embodiment will be described focusing on the differences between the refrigerant distributor 50 of the first embodiment.
  • a plurality of communication holes 25 are formed in the second plate-shaped member 20D of the refrigerant distributor 50D according to the fifth embodiment.
  • the plurality of communication hole portions 25 are composed of a first communication hole portion 25a and a second communication hole portion 25b.
  • the opening diameter of the first communication hole portion 25a is smaller than that of the second communication hole portion 25b, and the flow path cross-sectional area is smaller.
  • the second communication hole portion 25b has a larger opening diameter and a larger flow path cross-sectional area than the first communication hole portion 25a.
  • the first communication hole group 125a is composed of the first communication hole portion 25a.
  • the second communication hole group 125b is composed of the second communication hole portion 25b.
  • the refrigerant distributor 50D according to the fifth embodiment is configured such that the first communication hole group 125a and the first flow path portion 15 are arranged on the side where the indoor blower 109 or the outdoor blower 108 is arranged. Has been done. That is, in the refrigerant distributor 50D according to the fifth embodiment, in the flow direction of the wind passing through the refrigerant distributor 50D, the first communication hole group 125a and the first flow path portion 15 are located on the upstream side of the wind flow. It is configured to be placed.
  • the refrigerant distributor 50D is configured such that the second communication hole group 125b and the second flow path portion 16 are arranged on the downstream side of the wind flow in the flow direction of the wind passing through the refrigerant distributor 50D. Has been done.
  • the total cross-sectional area of the first communication hole group 125a located on the windward side of the air among the two communication hole groups communicating with each of the two distribution flow paths is leeward. It is smaller than the total cross-sectional area of the second communication hole group 125b located on the side. Therefore, the flow velocity of the refrigerant in the flow of the refrigerant (arrow F1) that passes through the first communication hole group 125a and flows into the merging flow path 32 is the flow rate of the refrigerant that passes through the second communication hole group 125b and flows into the merging flow path 32. It is larger than the flow velocity of the refrigerant in (arrow F2).
  • the flow velocity of the refrigerant in the flow of the refrigerant (arrow F2) that passes through the second communication hole group 125b and flows into the merging flow path 32 is the flow rate of the refrigerant that passes through the first communication hole group 125a and flows into the merging flow path 32. It is smaller than the flow velocity of the refrigerant in (arrow F1).
  • the total cross-sectional area of the first communication hole group 125a is the sum of the cross-sectional areas of the first communication hole portions 25a constituting the first communication hole group 125a.
  • the total cross-sectional area of the second communication hole group 125b is the sum of the cross-sectional areas of the second communication hole portions 25b constituting the second communication hole group 125b.
  • the first plate-shaped member 10 of the refrigerant distributor 50D includes a first distribution flow path 15a formed in the first flow path portion 15 and a second distribution flow path 16a formed in the second flow path portion 16. Are formed so as to have different flow path cross-sectional areas from each other. Specifically, the cross-sectional area of the second distribution flow path 16a is larger than the cross-sectional area of the first distribution flow path 15a, and the cross-sectional area of the first distribution flow path 15a is larger than the cross-sectional area of the second distribution flow path 16a. Is also small. Therefore, the first plate-shaped member 10 has the characteristics shown in FIG.
  • the position of the communication hole portion 25 where the refrigerant flow rate is maximized in the first communication hole group 125a is the refrigerant flow rate in the second communication hole group 125b. Is a position farther from the refrigerant inflow port 18 than the position of the communication hole portion 25 having the maximum value.
  • the position of the communication hole portion 25 having the maximum refrigerant flow rate in the second communication hole group 125b is closer to the refrigerant inflow port 18 than the position of the communication hole portion 25 having the maximum refrigerant flow rate in the first communication hole group 125a. It becomes the position.
  • the total flow rate of the flow rate of the refrigerant flowing through the first distribution flow path 15a and the flow rate of the refrigerant flowing through the second distribution flow path 16a is suppressed from being drifted with respect to the distance from the refrigerant inlet 18, and a plurality of transmissions are performed.
  • the flow rate of the refrigerant distributed to the heat pipe 70 can be made uniform.
  • the distance from one end 51a of the main body 51 to the other end 51b is defined as a distance A
  • the second distribution flow path 16a one end of the main body 51 is defined.
  • the distance from 51a to the other end 51b is defined as the distance B.
  • the refrigerant distributor 50D has a flow path shape of the first distribution flow path 15a and the second distribution flow path 16a at a position where the distance A and the distance B are equal, and a plurality of communication holes constituting the first communication hole group 125a.
  • the flow path shapes of one of the portions 25 and one of the plurality of communication hole portions 25 constituting the second communication hole group 125b are different so that the flow path cross-sectional areas are different.
  • the refrigerant distributor 50D has the first distribution flow path 15a and the second distribution flow path 15a at a position corresponding to the formation position of a certain communication hole portion 25 among the plurality of communication hole portions 25 formed along the first direction.
  • the flow path shape of the distribution flow path 16a, and the flow path shape of one of the plurality of communication hole portions 25 constituting the first communication hole group 125a and one of the plurality of communication hole portions 25 constituting the second communication hole group 125b. are different so that the cross-sectional areas of the flow paths are different.
  • the refrigerant distributor 50D is connected to the heat exchanger 80.
  • the heat transfer tube 70 constituting the heat exchanger 80 to which the refrigerant distributor 50D is connected is a flat perforated tube having a plurality of refrigerant passages 72.
  • the amount of heat conversion between the refrigerant and air is larger on the windward side of air.
  • the flow velocity of the refrigerant in the flow of the refrigerant (arrow F1) that passes through the first communication hole group 125a and flows into the merging flow path 32 flows into the merging flow path 32 through the second communication hole group 125b. It is larger than the flow velocity of the refrigerant in the flow of the refrigerant (arrow F2). That is, the refrigerant distributor 50D has a communication hole portion 25 located on the windward side in the merging flow path 32 in which the refrigerant merges through the communication hole portion 25 communicating with the first distribution flow path 15a and the second distribution flow path 16a.
  • the refrigerant distributor 50D has a large inertial force of the refrigerant, and in the heat transfer pipe 70 which is a flat pipe, more refrigerant can flow through the refrigerant passage 72 on the windward side where the heat load is large. Since the refrigerant distributor 50D can distribute the refrigerant to the heat transfer tube 70 of the heat exchanger 80 according to the heat conversion, the heat conversion capacity of the heat exchanger 80 can be improved.
  • the refrigerant distributor 50D is the total of the first communication hole group 125a located on the windward side of the air among the two communication hole groups communicating with each of the two distribution channels.
  • the cross-sectional area is smaller than the total cross-sectional area of the second communication hole group 125b located on the leeward side.
  • the refrigerant distributor 50D has a communication hole portion 25 located on the windward side in the merging flow path 32 where the refrigerants distributed by the two distribution flow paths 15a and the second distribution flow path 16a merge.
  • the flow velocity of the refrigerant flowing into the merging flow path 32 via the merging flow path 32 is made larger than that on the leeward side. Therefore, in the refrigerant distributor 50D, the refrigerant easily flows in the windward flow path of the heat transfer tube 70 having a large heat load, and the heat exchange performance of the heat exchanger 80 can be improved.
  • FIG. 16 is a perspective view of the refrigerant distributor 50E according to the sixth embodiment.
  • FIG. 17 is a perspective view schematically showing the internal configuration of the refrigerant distributor 50E according to the sixth embodiment.
  • FIG. 18 is a cross-sectional view showing the configuration of the refrigerant distributor 50E according to the sixth embodiment.
  • FIG. 19 is a vertical cross-sectional view showing the configuration of the refrigerant distributor 50E according to the sixth embodiment.
  • the refrigerant distributor 50E according to the sixth embodiment will be described with reference to FIGS. 16 to 19.
  • the components having the same functions and functions as those in the first embodiment are designated by the same reference numerals, and the description thereof will be omitted.
  • the main body 51 of the refrigerant distributors 50 to the refrigerant distributor 50D of the first to fifth embodiments is configured by laminating the first plate-shaped members 10 to the fourth plate-shaped members 40.
  • the main body 52 of the refrigerant distributor 50E of the sixth embodiment is configured by using a tubular member.
  • the refrigerant distributor 50E has a main body 52 extending in the arrangement direction of the heat transfer tubes 70.
  • the main body 52 of the refrigerant distributor 50E includes a tubular portion 90 extending in the arrangement direction of the heat transfer pipe 70, a first space S1 connected to the refrigerant inflow pipe 60 in the hollow portion of the tubular portion 90, and a plurality of heat transfer tubes 70. It has a first wall portion 91 that partitions the second space S2 connected to the above.
  • the main body 52 of the refrigerant distributor 50E has a second wall portion 92 for partitioning the first space S1 into the first distribution flow path 315a and the second distribution flow path 316a, and the heat transfer tube 70 for the second space S2.
  • the main body 52 of the refrigerant distributor 50E has a lid portion 94 that closes both ends of the tubular portion 90, respectively.
  • the tubular portion 90 is formed in a hollow cylindrical shape extending in the arrangement direction of the heat transfer tubes 70.
  • the tubular portion 90 is not limited to a cylindrical shape, and may be a tubular shape, for example, a rectangular parallelepiped box shape.
  • the first wall portion 91 has a strip-like shape that is long in one direction.
  • the first wall portion 91 is a plate-shaped portion extending in the arrangement direction of the plurality of heat transfer tubes 70, and the longitudinal direction of the first wall portion 91 is the arrangement direction of the plurality of heat transfer tubes 70. Further, the lateral direction of the first wall portion 91 is the major axis direction of the heat transfer tube 70, and the plate thickness direction of the first wall portion 91 is the extension direction of the heat transfer tube 70.
  • the first wall portion 91 has a communication hole portion 25. Therefore, the first wall portion 91 exhibits the same function as any one of the second plate-shaped member 20, the second plate-shaped member 20B, the second plate-shaped member 20C, and the second plate-shaped member 20D described above.
  • the communication hole portion 25 of the first wall portion 91 constitutes the first communication hole group 125a and the second communication hole group 125b in the same manner as the second plate-shaped member 20 and the like.
  • the first wall portion 91 divides the hollow portion of the tubular portion 90 into the first space S1 and the second space S2. The first space S1 and the second space S2 communicate with each other through the communication hole portion 25.
  • the second wall portion 92 has a strip-like shape that is long in one direction.
  • the second wall portion 92 is a plate-shaped portion extending in the arrangement direction of the plurality of heat transfer tubes 70, and the longitudinal direction of the second wall portion 92 is the arrangement direction of the plurality of heat transfer tubes 70. Further, the lateral direction of the second wall portion 92 is the extending direction of the heat transfer tube 70, and the plate thickness direction of the second wall portion 92 is the major axis direction of the heat transfer tube 70.
  • the second wall portion 92 divides the first space S1 into a first distribution flow path 315a and a second distribution flow path 316a.
  • the first distribution flow path 315a is formed in the first flow path portion 315 composed of the tubular portion 90, the first wall portion 91, the second wall portion 92, and the lid portion 94.
  • the second distribution flow path 316a is formed in the second flow path portion 316 composed of the tubular portion 90, the first wall portion 91, the second wall portion 92, and the lid portion 94. There is.
  • the first distribution flow path 315a and the second distribution flow path 316a have the same configuration as the first distribution flow path 15a and the second distribution flow path 16a described above, and exhibit the same functions. That is, the flow path cross-sectional area of the first distribution flow path 315a and the flow path cross-sectional area of the second distribution flow path 316a are formed so as to be different. Further, the first flow path portion 315 and the second flow path portion 316 have the same configuration as the first flow path portion 15 and the second flow path portion 16 described above, and exhibit the same functions.
  • a refrigerant inflow pipe 60 is connected to the first flow path portion 315 and the second flow path portion 316.
  • the distance from one end 51a of the main body 51 to the other end 51b is defined as a distance A
  • the distance from 51a to the other end 51b is defined as the distance B.
  • the refrigerant distributor 50E has a different flow path shape so that the flow path cross-sectional areas of the first distribution flow path 315a and the second distribution flow path 316a are different at positions where the distance A and the distance B are equal.
  • the refrigerant distributor 50E has a first distribution flow path 315a and a second at a position corresponding to the formation position of a certain communication hole portion 25 among the plurality of communication hole portions 25 formed along the first direction.
  • the flow path shape is different so that the flow path cross-sectional area of the distribution flow path 316a is different.
  • the formation position of the second wall portion 92 is moved in the major axis direction of the heat transfer tube 70, and the flow path cross-sectional areas of the first distribution flow path 315a and the second distribution flow path 316a are the same size. It may be formed in the air.
  • the third wall portion 93 is a plate-shaped member.
  • the third wall portion 93 is the extending direction of the heat transfer tube 70 and the major axis direction of the heat transfer tube 70.
  • a plurality of the third wall portions 93 are provided in the hollow portion of the tubular portion 90, and the plurality of third wall portions 93 are arranged in the arrangement direction of the plurality of heat transfer tubes 70.
  • the plurality of third wall portions 93 partition the second space S2 in the arrangement direction of the heat transfer tubes 70, and form a confluence flow path 32.
  • the merging flow path 32 is formed by a tubular portion 90, a first wall portion 91, and a third wall portion 93.
  • the merging flow path 32 is formed by a tubular portion 90, a first wall portion 91, a third wall portion 93, and a lid portion 94.
  • the lid portion 94 closes both ends of the tubular portion 90 in the extending direction.
  • the lid portion 94 may be a plate-shaped member as long as it closes both ends of the tubular portion 90 in the extending direction, or may be a member that covers the end portions of the tubular portion 90.
  • the refrigerant distributor 50E has the same basic configurations and functions as the refrigerant distributor 50 and the like, such as the first distribution flow path 15a and the second distribution flow path 16a, the communication hole portion 25, and the merging flow path 32.
  • the refrigerant distributor 50E exerts the same function as the refrigerant distributor 50 and the like, and exerts the same action and effect.
  • FIG. 20 is a perspective view schematically showing an internal configuration of a modified example of the refrigerant distributor 50E according to the sixth embodiment.
  • the second wall portion 92a is tilted in the major axis direction of the heat transfer tube 70. Therefore, the first distribution flow path 315a and the second distribution flow path 316a have the same configuration as the first distribution flow path 115a and the second distribution flow path 116a of the refrigerant distributor 50A according to the second embodiment. That is, the flow path cross-sectional area of the first distribution flow path 315a of the refrigerant distributor 50E decreases as it goes upward, and the flow path cross-sectional area of the second distribution flow path 316a increases as it goes upward.
  • the refrigerant distributor 50E of the modified example exhibits the same functions and effects as the refrigerant distributor 50A of the second embodiment.
  • the distance from one end 51a of the main body 51 to the other end 51b is defined as a distance A in the first distribution flow path 315a, and in the second distribution flow path 316a, as in the second embodiment.
  • the distance from one end 51a of the main body 51 to the other end 51b is defined as the distance B.
  • the refrigerant distributor 50E has a different flow path shape so that the flow path cross-sectional areas of the first distribution flow path 315a and the second distribution flow path 316a are different at positions where the distance A and the distance B are equal.
  • the refrigerant distributor 50E has a first distribution flow path 315a and a second at a position corresponding to the formation position of a certain communication hole portion 25 among the plurality of communication hole portions 25 formed along the first direction.
  • the flow path shape is different so that the flow path cross-sectional area of the distribution flow path 316a is different.
  • FIG. 21 is a conceptual diagram of a modified example of the first wall portion 91 of the refrigerant distributor 50E according to the sixth embodiment.
  • the first wall portion 91a is a modified example of the first wall portion 91, and has the same configuration as the second plate-shaped member 20B. That is, the first wall portion 91a has different formation positions of the first communication hole portion 25a and the second communication hole portion 25b in the first communication hole group 125a and the second communication hole group 125b.
  • FIG. 22 is a conceptual diagram of another modification of the first wall portion 91 of the refrigerant distributor 50E according to the sixth embodiment.
  • the first wall portion 91b is a modified example of the first wall portion 91, and has the same configuration as the second plate-shaped member 20D of the refrigerant distributor 50D according to the fifth embodiment. That is, the first wall portion 91a has a first communication hole portion 25a in the first communication hole group 125a and a second communication hole portion 25b in the second communication hole group 125b.
  • the refrigerant distributor 50E includes the position where the second wall portion 92 is formed, the inclination of the second wall portion 92, and the communication holes forming the first communication hole group 125a and the second communication hole group 125b formed in the first wall portion 91. By combining the types of the parts 25 and the like, the same function as the refrigerant distributor 50 is exhibited. Similarly, the refrigerant distributor 50E exerts the same functions as the refrigerant distributor 50A to the refrigerant distributor 50D by combining the second wall portion 92 and the communication hole portion 25 of the first wall portion 91. Therefore, the refrigerant distributor 50E can exert the same effect as the refrigerant distributor 50D from the refrigerant distributors 50 of the first to fifth embodiments described above.
  • the configurations of the refrigerant distributor 50, the refrigerant distributor 50A, the refrigerant distributor 50B, the refrigerant distributor 50C, the refrigerant distributor 50D and the refrigerant distributor 50E described above have the following features.
  • the refrigerant distributor 50 or the like has at least one flow path having a flow path shape between the first distribution flow path 15a and the second distribution flow path 16a and a flow path shape between the first communication hole group 125a and the second communication hole group 125b. It is formed so that the shape is different.
  • the refrigerant distributor 50 and the like have the communication hole portion 25 and the refrigerant inflow port 18 in which the flow rate of the refrigerant passing through the plurality of communication hole portions 25 is maximized in the first direction which is the arrangement direction of the heat transfer tubes 70.
  • the distance between them is different between the first communication hole group 125a and the second communication hole group 125b.
  • the distance from one end 51a of the main body 51 to the other end 51b is defined as a distance A
  • the second distribution flow path from one end 51a of the main body 51.
  • the distance toward the other end 51b is defined as the distance B.
  • the refrigerant distributor 50, the refrigerant distributor 50A, the refrigerant distributor 50B, the refrigerant distributor 50C, the refrigerant distributor 50D and the refrigerant distributor 50E are the first distribution flow path and the second distribution flow path at positions where the distance A and the distance B are equal.
  • the refrigerant distributor has a first distribution flow path and a second distribution flow at a position corresponding to the formation position of a certain communication hole portion 25 among the plurality of communication hole portions 25 formed along the first direction.
  • the refrigerant distributor 50, the refrigerant distributor 50A, the refrigerant distributor 50B, the refrigerant distributor 50C, the refrigerant distributor 50D, and the refrigerant distributor 50E have different distances from the first distance L1 and the second distance L2 described above. It is configured as follows. As a result, the total flow rate of the flow rate of the refrigerant flowing through the first distribution flow path 15a and the flow rate of the refrigerant flowing through the second distribution flow path 16a suppresses the drift with respect to the distance from the refrigerant inlet 18, and a plurality of flow rates. The flow rate of the refrigerant distributed to the heat transfer tube 70 can be made uniform.
  • the refrigerant distributor 50 and the like when the refrigerant distributor is applied over a plurality of heat exchangers through which refrigerants in different flow rate ranges flow, the first plate-shaped member 10 or the communication hole portion 25 constituting the distribution flow path is formed. It can be dealt with by replacing any of the second plate-shaped members 20. That is, in the refrigerant distributor 50 and the like, the manufacturing cost can be reduced because the flow rate range for uniform refrigerant distribution can be changed by replacing the first plate-shaped member 10 or the second plate-shaped member 20.
  • the heat exchanger 80 is provided with the refrigerant distributor according to any one of the first to sixth embodiments. Therefore, the heat exchanger 80 has the same effect as that of any of the first to sixth embodiments. Further, the refrigeration cycle device 100 includes the refrigerant distributor according to any one of the first to sixth embodiments. Therefore, the refrigeration cycle device 100 can obtain the same effect as that of any one of the first to sixth embodiments.
  • each of the above embodiments 1 to 6 can be implemented in combination with each other.
  • the configuration shown in the above embodiment is an example, and can be combined with another known technique, and a part of the configuration is omitted or changed without departing from the gist. It is also possible.
  • the arrangement direction of the heat transfer tubes 70 is described as the vertical direction in the vertical direction, but the arrangement direction of the heat transfer tubes 70 is the horizontal direction. May be good. Further, the arrangement direction of the heat transfer tubes 70 may be inclined with respect to the vertical direction.
  • the refrigerant distributor 50 and the like according to the first to sixth embodiments may be a vertical type in which the main body 51 extends in the vertical direction or a horizontal type in which the main body 51 extends in the horizontal direction. Further, the refrigerant distributor 50 and the like according to the first to sixth embodiments may have a configuration in which the main body 51 is tilted with respect to the vertical direction.

Landscapes

  • 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)

Abstract

L'objectif de la présente invention est de fournir un distributeur de fluide frigorigène, un échangeur de chaleur et un dispositif à cycle frigorifique dans lesquels, par rapport à un changement du débit d'un fluide frigorigène qui dépend de l'état de fonctionnement d'un climatiseur, un écoulement irrégulier dans la distribution du fluide frigorigène est empêché et les débits du fluide frigorigène distribué aux tubes de transfert de chaleur sont rendus uniformes. À cet effet, la présente invention concerne un distributeur de fluide frigorigène raccordé à un échangeur de chaleur pourvu d'une pluralité de tubes de transfert de chaleur agencés dans une première direction. Le distributeur de fluide frigorigène présente un corps dans lequel un premier orifice d'admission de fluide frigorigène et un second orifice d'admission de fluide frigorigène sont formés sur un côté de surface latérale, et une pluralité de trous d'insertion dans lesquels la pluralité de tubes de transfert de chaleur sont insérés sont formés sur l'autre côté de surface latérale. Dans le corps, il y est formé un premier trajet d'écoulement de distribution communiquant avec le premier orifice d'admission de fluide frigorigène et s'étendant dans la première direction, une pluralité de trajets d'écoulement de fusion qui communiquent avec le second orifice d'admission de fluide frigorigène et dans lesquels le fluide frigorigène qui s'est écoulé à travers le premier trajet d'écoulement de distribution et un second trajet d'écoulement de distribution fusionnent, un premier groupe de trous de communication configuré à partir d'une pluralité de sections de trou de communication par l'intermédiaire desquels le premier trajet d'écoulement de distribution et chacun de la pluralité de trajets d'écoulement de fusion communiquent, et un second groupe de trous de communication configuré à partir d'une pluralité de sections de trou de communication par l'intermédiaire desquels le second trajet d'écoulement de distribution et chacun de la pluralité de trajets d'écoulement de fusion communiquent. Le premier orifice d'admission de fluide frigorigène et le second orifice d'admission de fluide frigorigène sont formés sur un côté d'extrémité du corps par rapport à la première direction. Prenant une distance A comme la distance dans le premier trajet d'écoulement de distribution d'une extrémité à l'autre extrémité du corps, et une distance B comme la distance dans le second trajet d'écoulement de distribution d'une extrémité à l'autre extrémité du corps, à des positions auxquelles la distance A et la distance B sont égales, il existe une différence entre la forme de trajet d'écoulement du premier trajet d'écoulement de distribution et le second trajet d'écoulement de distribution et la forme de trajet d'écoulement de l'une de la pluralité de sections de trou de communication constituant le premier groupe de trous de communication et/ou l'une de la pluralité de sections de trou de communication constituant le second groupe de trous de communication.
PCT/JP2019/016983 2019-04-22 2019-04-22 Distributeur de fluide frigorigène, échangeur thermique, et dispositif à cycle frigorifique WO2020217271A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
JP2021515324A JP7086279B2 (ja) 2019-04-22 2019-04-22 冷媒分配器、熱交換器及び冷凍サイクル装置
PCT/JP2019/016983 WO2020217271A1 (fr) 2019-04-22 2019-04-22 Distributeur de fluide frigorigène, échangeur thermique, et dispositif à cycle frigorifique

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2019/016983 WO2020217271A1 (fr) 2019-04-22 2019-04-22 Distributeur de fluide frigorigène, échangeur thermique, et dispositif à cycle frigorifique

Publications (1)

Publication Number Publication Date
WO2020217271A1 true WO2020217271A1 (fr) 2020-10-29

Family

ID=72941580

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2019/016983 WO2020217271A1 (fr) 2019-04-22 2019-04-22 Distributeur de fluide frigorigène, échangeur thermique, et dispositif à cycle frigorifique

Country Status (2)

Country Link
JP (1) JP7086279B2 (fr)
WO (1) WO2020217271A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11506434B2 (en) * 2016-12-07 2022-11-22 Johnson Controls Tyco IP Holdings LLP Adjustable inlet header for heat exchanger of an HVAC system
WO2023062800A1 (fr) * 2021-10-15 2023-04-20 三菱電機株式会社 Distributeur, échangeur de chaleur et dispositif de thermopompe

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH05346297A (ja) * 1992-06-15 1993-12-27 Nippon Light Metal Co Ltd 熱交換器
JP2004003810A (ja) * 2002-04-03 2004-01-08 Denso Corp 熱交換器
EP2108909A1 (fr) * 2008-04-07 2009-10-14 Delphi Technologies, Inc. Échangeur thermique fourni avec un bloc de fixation
JP2014533819A (ja) * 2011-11-18 2014-12-15 エルジー エレクトロニクス インコーポレイティド 熱交換器
WO2017149989A1 (fr) * 2016-02-29 2017-09-08 三菱重工業株式会社 Échangeur de chaleur et climatiseur
WO2017150126A1 (fr) * 2016-02-29 2017-09-08 三菱重工業株式会社 Échangeur de chaleur et climatiseur
WO2019026436A1 (fr) * 2017-08-02 2019-02-07 三菱重工サーマルシステムズ株式会社 Échangeur de chaleur

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102006057036A1 (de) 2006-12-04 2008-06-05 Bayer Cropscience Ag Biphenylsubstituierte spirocyclische Ketoenole
JP2017044428A (ja) * 2015-08-27 2017-03-02 株式会社東芝 熱交換器、分流部品、および熱交換装置

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH05346297A (ja) * 1992-06-15 1993-12-27 Nippon Light Metal Co Ltd 熱交換器
JP2004003810A (ja) * 2002-04-03 2004-01-08 Denso Corp 熱交換器
EP2108909A1 (fr) * 2008-04-07 2009-10-14 Delphi Technologies, Inc. Échangeur thermique fourni avec un bloc de fixation
JP2014533819A (ja) * 2011-11-18 2014-12-15 エルジー エレクトロニクス インコーポレイティド 熱交換器
WO2017149989A1 (fr) * 2016-02-29 2017-09-08 三菱重工業株式会社 Échangeur de chaleur et climatiseur
WO2017150126A1 (fr) * 2016-02-29 2017-09-08 三菱重工業株式会社 Échangeur de chaleur et climatiseur
WO2019026436A1 (fr) * 2017-08-02 2019-02-07 三菱重工サーマルシステムズ株式会社 Échangeur de chaleur

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11506434B2 (en) * 2016-12-07 2022-11-22 Johnson Controls Tyco IP Holdings LLP Adjustable inlet header for heat exchanger of an HVAC system
WO2023062800A1 (fr) * 2021-10-15 2023-04-20 三菱電機株式会社 Distributeur, échangeur de chaleur et dispositif de thermopompe
GB2625961A (en) * 2021-10-15 2024-07-03 Mitsubishi Electric Corp Distributor, heat exchanger, and heat pump device

Also Published As

Publication number Publication date
JPWO2020217271A1 (ja) 2021-10-21
JP7086279B2 (ja) 2022-06-17

Similar Documents

Publication Publication Date Title
US10041710B2 (en) Heat exchanger and air conditioner
JP6138264B2 (ja) 積層型ヘッダー、熱交換器、及び、空気調和装置
JPH09170850A (ja) 冷媒蒸発器
JP7097986B2 (ja) 熱交換器及び冷凍サイクル装置
US9951996B2 (en) Refrigerant evaporator
JP6890509B2 (ja) 空気調和機
EP2092262B1 (fr) Injection de vapeur de réfrigérant pour une amélioration de distribution dans des collecteurs d'échangeur de chaleur à écoulements en parallèle
JP7086279B2 (ja) 冷媒分配器、熱交換器及び冷凍サイクル装置
JP7278430B2 (ja) 熱交換器及び冷凍サイクル装置
JP6946105B2 (ja) 熱交換器
JP6169199B2 (ja) 熱交換器及び冷凍サイクル装置
JP7086264B2 (ja) 熱交換器、室外機、及び冷凍サイクル装置
CN203785346U (zh) 膨胀阀及使用该膨胀阀的制冷循环装置
JP3633030B2 (ja) 冷房装置用蒸発器
WO2021192903A1 (fr) Échangeur de chaleur
KR20190143091A (ko) 응축기
CN114729795A (zh) 热交换器
JP7146139B1 (ja) 熱交換器及び空気調和装置
WO2023218621A1 (fr) Échangeur de chaleur et appareil à cycle frigorifique
JP7399286B2 (ja) 熱交換器および冷凍サイクル装置
WO2021192192A1 (fr) Échangeur de chaleur, unité d'échangeur de chaleur et dispositif à cycle frigorifique
US20230375283A1 (en) Heat exchanger and refrigeration cycle apparatus
JP7327213B2 (ja) 熱交換器
WO2021192902A1 (fr) Échangeur de chaleur
WO2021005682A1 (fr) Distributeur de fluide frigorigène, échangeur de chaleur, unité d'échangeur de chaleur et dispositif à cycle frigorifique

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 19925591

Country of ref document: EP

Kind code of ref document: A1

ENP Entry into the national phase

Ref document number: 2021515324

Country of ref document: JP

Kind code of ref document: A

NENP Non-entry into the national phase

Ref country code: DE

122 Ep: pct application non-entry in european phase

Ref document number: 19925591

Country of ref document: EP

Kind code of ref document: A1