WO2021130835A1 - Échangeur de chaleur et dispositif à cycle de réfrigération - Google Patents

Échangeur de chaleur et dispositif à cycle de réfrigération Download PDF

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Publication number
WO2021130835A1
WO2021130835A1 PCT/JP2019/050476 JP2019050476W WO2021130835A1 WO 2021130835 A1 WO2021130835 A1 WO 2021130835A1 JP 2019050476 W JP2019050476 W JP 2019050476W WO 2021130835 A1 WO2021130835 A1 WO 2021130835A1
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WIPO (PCT)
Prior art keywords
recess
flow path
plate body
header
refrigerant
Prior art date
Application number
PCT/JP2019/050476
Other languages
English (en)
Japanese (ja)
Inventor
崇史 畠田
亮輔 是澤
成浩 岡田
田中　誠
Original Assignee
東芝キヤリア株式会社
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 東芝キヤリア株式会社 filed Critical 東芝キヤリア株式会社
Priority to KR1020227006507A priority Critical patent/KR20220041164A/ko
Priority to JP2021566412A priority patent/JP7437418B2/ja
Priority to PCT/JP2019/050476 priority patent/WO2021130835A1/fr
Priority to CN201980099418.3A priority patent/CN114245860A/zh
Publication of WO2021130835A1 publication Critical patent/WO2021130835A1/fr
Priority to JP2024017036A priority patent/JP2024045455A/ja

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    • 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
    • F28D1/047—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 bent, e.g. in a serpentine or zig-zag
    • F28D1/0471—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 bent, e.g. in a serpentine or zig-zag the conduits having a non-circular cross-section
    • 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
    • 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
    • F28D1/047—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 bent, e.g. in a serpentine or zig-zag
    • 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
    • F28D1/0535—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 the conduits having a non-circular cross-section
    • F28D1/05358—Assemblies of conduits connected side by side or with individual headers, e.g. section type radiators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F19/00—Preventing the formation of deposits or corrosion, e.g. by using filters or scrapers
    • F28F19/02—Preventing the formation of deposits or corrosion, e.g. by using filters or scrapers by using coatings, e.g. vitreous or enamel coatings
    • F28F19/06—Preventing the formation of deposits or corrosion, e.g. by using filters or scrapers by using coatings, e.g. vitreous or enamel coatings of metal
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/0219—Arrangements for sealing end plates into casing or header box; Header box sub-elements
    • F28F9/0221—Header boxes or end plates formed by stacked elements

Definitions

  • Embodiments of the present invention relate to heat exchangers and refrigeration cycle devices.
  • the header type heat exchanger has a plurality of heat exchange tubes and a header.
  • a refrigerant flow path is formed inside the heat exchange tube.
  • the header is provided at the end of the heat exchange tube. Heat exchangers are required to be small and lightweight.
  • the problem to be solved by the present invention is to provide a small and lightweight heat exchanger and refrigeration cycle device.
  • the heat exchanger of the embodiment has a heat exchange tube and a header.
  • a refrigerant flow path through which the refrigerant flows is formed in the heat exchange tube.
  • Headers are provided at one end and the other end of the heat exchange tube, respectively.
  • the header includes a pair of plates laminated so that the first main surfaces face each other.
  • a recess forming a spatial flow path communicating with the refrigerant flow path is formed on at least one of the first main surfaces of the plate body.
  • FIG. 3 is a cross-sectional view of the first header of the first modification.
  • FIG. 3 is a cross-sectional view of the first header of the second modification.
  • FIG. 3 is a cross-sectional view of the first header in the second embodiment.
  • FIG. 3 is a cross-sectional view of the first header of the third modification.
  • the X direction, the Y direction and the Z direction are defined as follows.
  • the Z direction is the longitudinal direction (extending direction) of the first header and the second header.
  • the Z direction is the vertical direction
  • the + Z direction is the upward direction.
  • the X direction is the central axis direction (extending direction) of the heat exchange tube.
  • the X direction is the horizontal direction
  • the + X direction is the direction from the second header to the first header.
  • the Y direction is a direction perpendicular to the X and Z directions.
  • FIG. 1 is a schematic configuration diagram of the refrigeration cycle device of the embodiment.
  • the refrigeration cycle device 1 includes a compressor 2, a four-way valve 3, an outdoor heat exchanger (heat exchanger) 4, an expansion device 5, and an indoor heat exchanger (heat exchanger). 6 and.
  • the components of the refrigeration cycle device 1 are sequentially connected by a pipe 7.
  • the flow direction of the refrigerant (heat medium) during the cooling operation is indicated by a solid line arrow
  • the flow direction of the refrigerant during the heating operation is indicated by a broken line arrow.
  • the compressor 2 has a compressor main body 2A and an accumulator 2B.
  • the compressor body 2A compresses the low-pressure gas refrigerant taken into the inside to obtain a high-temperature and high-pressure gas refrigerant.
  • the accumulator 2B separates the gas-liquid two-phase refrigerant and supplies the gas refrigerant to the compressor main body 2A.
  • the four-way valve 3 reverses the flow direction of the refrigerant and switches between cooling operation and heating operation.
  • the refrigerant flows in the order of the compressor 2, the four-way valve 3, the outdoor heat exchanger 4, the expansion device 5, and the indoor heat exchanger 6.
  • the refrigeration cycle device 1 causes the outdoor heat exchanger 4 to function as a condenser and the indoor heat exchanger 6 to function as an evaporator to cool the room.
  • the refrigerant flows in the order of the compressor 2, the four-way valve 3, the indoor heat exchanger 6, the expansion device 5, and the outdoor heat exchanger 4.
  • the refrigeration cycle device 1 causes the indoor heat exchanger 6 to function as a condenser and the outdoor heat exchanger 4 to function as an evaporator to heat the room.
  • the condenser makes a high-pressure liquid refrigerant by radiating high-temperature and high-pressure gas refrigerant discharged from the compressor 2 to the outside air and condensing it.
  • the expansion device 5 lowers the pressure of the high-pressure liquid refrigerant sent from the condenser to make it a low-temperature / low-pressure gas-liquid two-phase refrigerant.
  • the evaporator makes a low-pressure gas-liquid refrigerant by absorbing heat from the outside air and vaporizing the low-temperature / low-pressure gas-liquid two-phase refrigerant sent from the expansion device 5.
  • the refrigerant as the working fluid circulates between the gas refrigerant and the liquid refrigerant while changing the phase.
  • the refrigerant dissipates heat in the process of phase change from gas refrigerant to liquid refrigerant, and absorbs heat in the process of phase change from liquid refrigerant to gas refrigerant.
  • the refrigeration cycle device 1 performs heating, cooling, defrosting, and the like by utilizing heat dissipation or endothermic heat of the refrigerant.
  • FIG. 2 is a perspective view of the heat exchanger of the first embodiment.
  • the heat exchanger 4 of the first embodiment is used for one or both of the outdoor heat exchanger 4 and the indoor heat exchanger 6 of the refrigeration cycle device 1.
  • the heat exchanger 4 is used as the outdoor heat exchanger 4 of the refrigeration cycle device 1 (see FIG. 1) will be described as an example.
  • the heat exchanger 4 has a first header 10, a second header 20, and a heat exchange tube (heat transfer tube) 30.
  • FIG. 3 is an exploded perspective view of the first header 10.
  • FIG. 4 is an exploded perspective view of the first header 10 and the heat exchange tube 30.
  • FIG. 5 is a cross-sectional view of the first header 10 along the XZ plane.
  • the first header 10 is configured by laminating a pair of plates 11 and 12. That is, the first header 10 is configured by laminating the first inner plate body 11 and the first outer plate body 12.
  • the first inner plate body 11 and the first outer plate body 12 are formed of a material having a high thermal conductivity and a low specific density, such as aluminum and an aluminum alloy.
  • the first inner plate body 11 and the first outer plate body 12 are substantially parallel to the YZ plane.
  • the first outer plate body 12 is laminated on the surface (first main surface 11a) on the + X direction side of the first inner plate body 11.
  • the first main surface 11a is the main surface of the first inner plate body 11 and is a surface facing the first outer plate body 12.
  • the second main surface 11b is a surface opposite to the first main surface 11a.
  • a plurality of recesses 13 are formed on the first main surface 11a of the first inner plate body 11.
  • the recess 13 is formed by a deformed portion 15 formed by bending deformation of the first inner plate body 11.
  • the recess 13 is a recess formed on the inner surface of the deformed portion 15.
  • the depth D1 of the recess 13 is larger than the thickness T1 of the first inner plate body 11.
  • the deformed portion 15 has a tray shape including a bottom plate portion 15a and a side plate portion 15b.
  • the side plate portion 15b extends from the peripheral edge of the bottom plate portion 15a while increasing its diameter in the + X direction.
  • the deformed portion 15 may have a truncated cone shape, a truncated cone shape, a truncated cone shape, or the like.
  • the deformed portion 15 can be formed by processing a flat plate. Processing methods include cold casting (embossing) and press molding.
  • a convex portion 14 having a shape corresponding to the concave portion 13 is formed on the second main surface 11b.
  • the convex portion 14 is a convex portion formed on the outer surface of the deformed portion 15.
  • the plurality of recesses 13 include the first recesses 13A to the ninth recesses 13I.
  • the first recess 13A has an oval shape when viewed from the X direction.
  • the "oval shape” is a shape composed of two straight lines parallel to each other and facing each other, and a curved convex curve (for example, a semicircle shape, an elliptical arc shape, etc.) connecting the ends of the two straight lines.
  • the major axis direction of the first recess 13A is parallel to the Y direction.
  • the first recess 13A is at the highest position among the first recess 13A to the ninth recess 13I (that is, is located at the most + Z direction side).
  • the second recess 13B to the fifth recess 13E and the eighth recess 13H have a rectangular shape when viewed from the X direction.
  • the second recess 13B to the fifth recess 13E and the eighth recess 13H have a rectangular shape having rounded corners.
  • the second recess 13B and the third recess 13C are located lower than the first recess 13A (that is, located on the ⁇ Z direction side of the first recess 13A).
  • the second recess 13B and the third recess 13C are formed side by side in the Y direction with an interval in the Y direction.
  • the third recess 13C is located on the + Y direction side with respect to the second recess 13B.
  • the fourth recess 13D is located lower than the second recess 13B (that is, located on the ⁇ Z direction side of the second recess 13B).
  • the fifth recess 13E is located lower than the third recess 13C (that is, located on the ⁇ Z direction side of the third recess 13C).
  • the fourth recess 13D and the fifth recess 13E are formed side by side in the Y direction with an interval in the Y direction.
  • the fifth recess 13E is located on the + Y direction side with respect to the fourth recess 13D.
  • the sixth recess 13F is located lower than the fourth recess 13D (that is, located on the ⁇ Z direction side of the fourth recess 13D).
  • the seventh recess 13G is located lower than the sixth recess 13F (that is, located on the ⁇ Z direction side of the sixth recess 13F).
  • the sixth recess 13F and the seventh recess 13G have an oval shape when viewed from the X direction.
  • the major axis direction of the sixth recess 13F and the seventh recess 13G is parallel to the Y direction.
  • the eighth recess 13H is located lower than the fifth recess 13E (that is, located on the ⁇ Z direction side of the fifth recess 13E).
  • the eighth recess 13H is located on the Y direction side with respect to the sixth recess 13F and the seventh recess 13G.
  • the ninth recess 13I has an oval shape when viewed from the X direction.
  • the major axis direction of the ninth recess 13I is parallel to the Y direction.
  • the ninth recess 13I is located lower than the seventh recess 13G and the eighth recess 13H (that is, located on the ⁇ Z direction side of the seventh recess 13G and the eighth recess 13H).
  • Two insertion portions 41 and 41 are formed in the bottom plate portion 15a of the deformed portion 15 forming the first recess 13A.
  • the insertion portion 41 penetrates the bottom plate portion 15a in the thickness direction.
  • the insertion portion 41 is formed in a slit shape parallel to the Y direction.
  • the end of the heat exchange tube 30 is inserted into the insertion portion 41 (see FIG. 5).
  • the two insertion portions 41 and 41 are formed at intervals in the Y direction.
  • Two insertion portions 41 and 41 are formed in the bottom plate portion 15a of the deformed portion 15 forming the second recess 13B to the fifth recess 13E and the eighth recess 13H, respectively.
  • the two insertion portions 41 and 41 are formed at intervals in the Z direction.
  • One insertion portion 41 is formed in each of the bottom plate portion 15a of the deformed portion 15 forming the sixth recess 13F and the seventh recess 13G.
  • Two insertion portions 41 and 41 are formed in the bottom plate portion 15a of the deformed portion 15 forming the ninth recess 13I.
  • the two insertion portions 41 and 41 are formed at intervals in the Y direction.
  • the first recess 13A and the ninth recess 13I are recesses having the same shape.
  • the first recess 13A and the ninth recess 13I have a length of two heat exchange tubes 30 described later arranged in the Y direction (or a length exceeding the length of two heat exchange tubes 30 arranged in the Y direction). It has an oval shape.
  • the second recess 13B, the third recess 13C, the fourth recess 13D, the fifth recess 13E, and the eighth recess 13H are recesses having the same shape.
  • the sixth recess 13F and the seventh recess 13G are recesses having the same shape.
  • the sixth recess 13F and the seventh recess 13G are formed smaller than the other recesses 13A, 13B, 13C, 13D, 13E, 13H and 13I.
  • the first main surface 12a is the main surface of the first outer plate body 12 and is a surface facing the first inner plate body 11.
  • the second main surface 12b is a surface opposite to the first main surface 12a.
  • a plurality of recesses 17 are formed on the first main surface 12a of the first outer plate body 12.
  • the recess 17 is formed by a deformed portion 19 formed by bending deformation of the first inner plate body 11.
  • the recess 17 is a recess formed on the inner surface of the deformed portion 19.
  • the depth D2 of the recess 17 is larger than the thickness T2 of the first outer plate body 12.
  • the deformed portion 19 has a tray shape including a bottom plate portion 19a and a side plate portion 19b.
  • the side plate portion 19b extends from the peripheral edge of the bottom plate portion 19a while increasing its diameter in the ⁇ X direction.
  • the deformed portion 19 may have a truncated cone shape, a truncated cone shape, a truncated cone shape, or the like.
  • the deformed portion 19 can be formed by processing a flat plate. Processing methods include cold casting (embossing) and press molding.
  • a convex portion 18 having a shape corresponding to the concave portion 17 is formed on the second main surface 12b.
  • the convex portion 18 is a convex portion formed on the outer surface of the deformed portion 19.
  • the plurality of recesses 17 include the first recesses 17A to the ninth recesses 17I.
  • the first recesses 17A to the ninth recesses 17I have shapes corresponding to the first recesses 13A to the ninth recesses 13I of the first inner plate body 11, respectively.
  • the first recess 17A has an oval shape when viewed from the X direction.
  • the second recess 17B to the fifth recess 17E and the eighth recess 17H have a rectangular shape (for example, a rectangular shape having rounded corners) when viewed from the X direction.
  • the sixth recess 17F and the seventh recess 17G have an oval shape when viewed from the X direction.
  • the ninth recess 17I has an oval shape when viewed from the X direction.
  • the first recesses 17A to the ninth recesses 17I are located so as to face the first recesses 13A to the ninth recesses 13I of the first inner plate body 11, respectively.
  • the first recess 17A and the ninth recess 17I are recesses having the same shape.
  • the first recess 17A and the ninth recess 17I have a length equal to or longer than a length in which two heat exchange tubes 30 described later are arranged in the Y direction (for example, a length in which two heat exchange tubes 30 are arranged in the Y direction). It has an oval shape (length).
  • the second recess 17B, the third recess 17C, the fourth recess 17D, the fifth recess 17E, and the eighth recess 17H are recesses having the same shape.
  • the sixth recess 17F and the seventh recess 17G are recesses having the same shape.
  • the sixth recess 17F and the seventh recess 17G are formed smaller than the other recesses 17A, 17B, 17C, 17D, 17E, 17H and 17I.
  • the recess 13 of the first inner plate 11 and the recess 17 of the first outer plate 12 facing the recess 13 form a head space flow path 16 (space).
  • the head space flow path 16 forms a space flow path partitioned by the recess 13 and the recess 17 facing each other.
  • the head space flow path 16 forms a plate-shaped space flow path along the YZ plane.
  • the end of the heat exchange tube 30 inserted into the insertion portion 41 opens into the head space flow path 16. Therefore, the head space flow path 16 communicates with the refrigerant flow path 34 of the heat exchange tube 30.
  • the head space flow path 16 in which the first recess 13A and the first recess 17A are partitioned is referred to as a first head space flow path 16A.
  • the head space flow path 16 in which the second recess 13B and the second recess 17B are partitioned is referred to as a second head space flow path 16B.
  • the head space flow path 16 in which the third recess 13C and the third recess 17C are partitioned is referred to as a third head space flow path 16C.
  • the head space flow path 16 in which the fourth recess 13D and the fourth recess 17D are partitioned is referred to as a fourth head space flow path 16D.
  • the head space flow path 16 in which the fifth recess 13E and the fifth recess 17E are partitioned is referred to as a fifth head space flow path 16E.
  • the head space flow path 16 in which the sixth recess 13F and the sixth recess 17F are partitioned is referred to as a sixth head space flow path 16F.
  • the head space flow path 16 in which the seventh recess 13G and the seventh recess 17G are partitioned is referred to as the seventh head space flow path 16G.
  • the head space flow path 16 in which the eighth recess 13H and the eighth recess 17H are partitioned is referred to as an eighth head space flow path 16H.
  • the head space flow path 16 in which the ninth recess 13I and the ninth recess 17I are partitioned is referred to as a ninth head space flow path 16I.
  • the first head space flow path 16A and the ninth head space flow path 16I form a space flow path portion having the same shape.
  • the first head space flow path 16A and the ninth head space flow path 16I have a length equal to or longer than the length of two heat exchange tubes 30 described later arranged in the Y direction (for example, two heat exchange tubes 30 in the Y direction). It has an oval shape (length exceeding the arranged length).
  • the second head space flow path 16B, the third head space flow path 16C, and the fourth head space flow path 16D form a space flow path portion having the same shape.
  • the third head space flow path 16C, the fifth head space flow path 16E, and the eighth head space flow path 16H form a space flow path portion having the same shape.
  • the sixth head space flow path 16F and the seventh head space flow path 16G form a space flow path portion having the same shape.
  • the sixth head space flow path 16F and the seventh head space flow path 16G are formed smaller than the other head space flow paths 16A, 16B, 16C, 16D, 16E, 16H and 16I.
  • an insertion portion 42 is formed in the bottom plate portion 19a of the deformed portion 19 forming the sixth recess 17F.
  • the insertion portion 42 has a circular shape.
  • a tubular first refrigerant port 51 is inserted into the insertion portion 42 (see FIG. 2).
  • the end of the first refrigerant port 51 opens inside the sixth head space flow path 16F. This opening serves as an introduction port for introducing the refrigerant into the heat exchanger 4 or an outlet for leading out the refrigerant from the heat exchanger 4.
  • An insertion portion 43 is formed in the bottom plate portion 19a of the deformed portion 19 forming the seventh recess 17G.
  • the insertion portion 43 has a circular shape, and is formed to have the same size and shape as the insertion portion 42.
  • a tubular second refrigerant port 52 is inserted into the insertion portion 43 (see FIG. 2).
  • the end of the second refrigerant port 52 opens inside the seventh head space flow path 16G. This opening serves as an introduction port for introducing the refrigerant into the heat exchanger 4 or an outlet for leading out the refrigerant from the heat exchanger 4.
  • An insertion portion 44 is formed in the bottom plate portion 19a of the deformed portion 19 forming the third recess 17C.
  • the insertion portion 44 has a circular shape and is formed larger than the insertion portions 42 and 43.
  • a tubular third refrigerant port 53 is inserted into the insertion portion 44 (see FIG. 2).
  • the end of the third refrigerant port 53 opens inside the third head space flow path 16C. This opening serves as an introduction port for introducing the refrigerant into the heat exchanger 4 or an outlet for leading out the refrigerant from the heat exchanger 4.
  • the pressure of the head space flow path 16 is defined as "P".
  • the thickness of the first inner plate body 11 and the first outer plate body 12 be "T”.
  • L be the thickness dimension (dimension in the X direction) of the head space flow path 16.
  • the material proof stress ⁇ of the first inner plate body 11 and the first outer plate body 12 preferably satisfies the following formula (1).
  • the pressure resistance of the first header 10 can be ensured.
  • FIG. 6 is an exploded perspective view of the second header 20.
  • FIG. 7 is a cross-sectional view of the second header 20 along the XZ plane.
  • the second header 20 is configured by laminating a pair of plates 21 and 22. That is, the second header 20 is configured by laminating the second inner plate body 21 and the second outer plate body 22.
  • the second inner plate body 21 and the second outer plate body 22 are formed of a material having a high thermal conductivity and a low specific density, such as aluminum and an aluminum alloy.
  • the second inner plate body 21 and the second outer plate body 22 are substantially parallel to the YZ plane.
  • the second outer plate body 22 is laminated on the surface (first main surface 21a) on the ⁇ X direction side of the second inner plate body 21.
  • the first main surface 21a is the main surface of the second inner plate body 21 and is a surface facing the second outer plate body 22.
  • the second main surface 21b is a surface opposite to the first main surface 21a.
  • a plurality of recesses 23 are formed on the first main surface 21a of the second inner plate body 21.
  • the recess 23 is formed by a deformed portion 25 formed by bending deformation of the second inner plate body 21.
  • the recess 23 is a recess formed on the inner surface of the deformed portion 25.
  • the depth D3 of the recess 23 is larger than the thickness T3 of the second inner plate body 21.
  • the deformed portion 25 has a tray shape including a bottom plate portion 25a and a side plate portion 25b.
  • the side plate portion 25b extends from the peripheral edge of the bottom plate portion 25a while increasing its diameter in the ⁇ X direction.
  • the deformed portion 25 may have a truncated cone shape, a truncated cone shape, a truncated cone shape, or the like.
  • the deformed portion 25 can be formed by processing a flat plate body. Processing methods include cold casting (embossing) and press molding.
  • a convex portion 24 having a shape corresponding to the concave portion 23 is formed on the second main surface 21b.
  • the convex portion 24 is a convex portion formed on the outer surface of the deformed portion 25.
  • the plurality of recesses 23 include the first recess 23A to the eighth recess 23H.
  • the first recess 23A to the eighth recess 23H have a rectangular shape when viewed from the X direction.
  • the first recess 23A and the second recess 23B are formed side by side in the Y direction.
  • the third recess 23C is located on the ⁇ Z direction side of the first recess 23A.
  • the fourth recess 23D is located on the ⁇ Z direction side of the second recess 23B.
  • the third recess 23C and the fourth recess 23D are formed side by side in the Y direction.
  • the fifth recess 23E is located on the ⁇ Z direction side of the third recess 23C.
  • the sixth recess 23F is located on the ⁇ Z direction side of the fourth recess 23D.
  • the fifth recess 23E and the sixth recess 23F are formed side by side in the Y direction.
  • the seventh recess 23G is located on the ⁇ Z direction side of the fifth recess 23E.
  • the eighth recess 23H is located on the ⁇ Z direction side of the sixth recess 23F.
  • the seventh recess 23G and the eighth recess 23H are formed side by side in the Y direction.
  • Two insertion portions 45 and 45 are formed in the bottom plate portion 25a of the deformed portion 25 forming the first recess 23A to the eighth recess 23H, respectively.
  • the insertion portion 45 is formed in a slit shape parallel to the Y direction.
  • the end of the heat exchange tube 30 is inserted into the insertion portion 45 (see FIG. 7).
  • the two insertion portions 45, 45 are formed at intervals in the Z direction.
  • the first main surface 22a is the main surface of the second outer plate body 22 and is a surface facing the second inner plate body 21.
  • the second main surface 22b is a surface opposite to the first main surface 22a.
  • a plurality of recesses 27 are formed on the first main surface 22a of the second outer plate body 22.
  • the recess 27 is formed by a deformed portion 29 formed by bending deformation of the second inner plate body 21.
  • the recess 27 is a recess formed on the inner surface of the deformed portion 29.
  • the depth D4 of the recess 27 is larger than the thickness T4 of the second outer plate body 22.
  • the deformed portion 29 has a tray shape including a bottom plate portion 29a and a side plate portion 29b.
  • the side plate portion 29b extends from the peripheral edge of the bottom plate portion 29a while increasing its diameter in the + X direction.
  • the deformed portion 29 may have a truncated cone shape, a truncated cone shape, a truncated cone shape, or the like.
  • the deformed portion 29 can be formed by processing a flat plate. Processing methods include cold casting (embossing) and press molding.
  • a convex portion 28 having a shape corresponding to the concave portion 27 is formed on the second main surface 21b.
  • the convex portion 28 is a convex portion formed on the outer surface of the deformed portion 29.
  • the plurality of recesses 27 include the first recess 27A to the eighth recess 27H.
  • the first recess 27A to the ninth recess 27I have shapes corresponding to the first recess 23A to the eighth recess 27H of the second inner plate body 21, respectively.
  • the first recess 27A to the eighth recess 27H have a rectangular shape when viewed from the X direction.
  • the first recess 27A to the eighth recess 27H are located so as to face the first recess 23A to the eighth recess 23H of the second inner plate body 21, respectively.
  • the recess 23 of the second inner plate 21 and the corresponding recess 27 of the second outer plate 22 form a head space flow path 26 (space).
  • the head space flow path 26 forms a space flow path in a space partitioned by the recess 23 and the recess 27.
  • the head space flow path 26 forms a space flow path in a plate-like space along the YZ plane.
  • the head space flow path 26 in which the first recess 23A and the first recess 27A are partitioned is referred to as a first head space flow path 26A.
  • the head space flow path 26 in which the second recess 23B and the second recess 27B are partitioned is referred to as a second head space flow path 26B.
  • the head space flow path 26 in which the third recess 23C and the third recess 27C are partitioned is referred to as a third head space flow path 26C.
  • the head space flow path 26 that divides the fourth recess 23D and the fourth recess 27D is referred to as a fourth head space flow path 26D.
  • the head space flow path 26 in which the fifth recess 23E and the fifth recess 27E are partitioned is referred to as a fifth head space flow path 26E.
  • the head space flow path 26 in which the sixth recess 23F and the sixth recess 27F are partitioned is referred to as a sixth head space flow path 26F.
  • the head space flow path 26 in which the seventh recess 23G and the seventh recess 27G are partitioned is referred to as the seventh head space flow path 26G.
  • the head space flow path 26 in which the eighth recess 23H and the eighth recess 27H are partitioned is referred to as an eighth head space flow path 26H.
  • the first header 10 and the second header 20 are arranged side by side so as to be separated from each other in the X direction.
  • the heat exchange tube 30 is made of a material having a high thermal conductivity and a low specific density, such as aluminum and an aluminum alloy.
  • the heat exchange tube 30 is formed in a flat tubular shape. That is, the heat exchange tube 30 has a larger dimension in the Y direction than the dimension in the Z direction.
  • the shape of the cross section (YZ cross section) of the heat exchange tube 30 orthogonal to the length direction is an oval shape.
  • the heat exchange tube 30 extends in the X direction.
  • a refrigerant flow path 34 is formed inside the heat exchange tube 30 (see FIG. 5). The refrigerant flow path 34 is formed over the entire length of the heat exchange tube 30.
  • At least a part of the plurality of heat exchange tubes 30 is arranged in parallel at intervals in the Z direction.
  • the end of the heat exchange tube 30 in the + X direction is inserted into the insertion portion 41 formed in the first header 10 (see FIG. 5).
  • the end of the refrigerant flow path 34 of the heat exchange tube 30 in the + X direction opens inside the head space flow path 16 of the first header 10. Therefore, the head space flow path 16 communicates with the refrigerant flow path 34 of the heat exchange tube 30.
  • the end of the heat exchange tube 30 in the ⁇ X direction is inserted into the insertion portion 45 formed in the second header 20 (see FIG. 7).
  • the end portion of the refrigerant flow path 34 of the heat exchange tube 30 in the ⁇ X direction opens inside the head space flow path 26 of the second header 20. Therefore, the head space flow path 26 communicates with the refrigerant flow path 34 of the heat exchange tube 30.
  • the gap between the first header 10 and the second header 20 and the heat exchange tube 30 is sealed by brazing or the like.
  • the specific procedure for brazing is as follows. Row is applied to the inner surfaces of the first header 10 and the second header 20.
  • the heat exchange tube 30 is inserted into the first header 10 and the second header 20, and the heat exchanger 4 is assembled.
  • the assembled heat exchanger 4 is heated in the furnace. The heating melts the wax on the inner surfaces of the first header 10 and the second header 20.
  • the molten wax closes the gap between the first header 10 and the second header 20 and the heat exchange tube 30.
  • the heat exchanger 4 is cooled and the wax solidifies. As a result, the first header 10 and the second header 20 and the heat exchange tube 30 are fixed.
  • An outside air flow path along the Y direction is formed between the heat exchange tubes 30 adjacent to each other on the top and bottom.
  • the heat exchanger 4 circulates the outside air through the outside air flow path by a blower fan (not shown) or the like.
  • the heat exchanger 4 exchanges heat between the outside air flowing through the outside air flow path and the refrigerant flowing through the refrigerant flow path 34.
  • the heat exchange is indirectly performed via the heat exchange tube 30.
  • the outdoor heat exchanger 4 functions as a condenser.
  • the gaseous refrigerant flowing out of the compressor 2 flows into the outdoor heat exchanger 4.
  • the refrigerant flows into the inside of the first header 10 from the first refrigerant port 51 and the second refrigerant port 52.
  • the refrigerant that has flowed from the first refrigerant port 51 into the sixth head space flow path 16F flows through the heat exchange tube 30 (30F) in the ⁇ X direction and flows into the lower part of the fifth head space flow path 26E of the second header 20. ..
  • the refrigerant flows from the upper part of the fifth head space flow path 26E through the heat exchange tube 30 (30D2) in the + X direction, and flows into the lower part of the fourth head space flow path 16D of the first header 10.
  • the refrigerant flows from the upper part of the fourth head space flow path 16D through the heat exchange tube 30 (30D1) in the ⁇ X direction, and flows into the lower part of the third head space flow path 26C of the second header 20.
  • the refrigerant flows from the upper part of the third head space flow path 26C through the heat exchange tube 30 (30B2) in the + X direction, and flows into the lower part of the second head space flow path 16B of the first header 10.
  • the refrigerant flows from the upper part of the second head space flow path 16B through the heat exchange tube 30 (30B1) in the ⁇ X direction, and flows into the lower part of the first head space flow path 26A of the second header 20.
  • the refrigerant flows from the upper part of the first head space flow path 26A through the heat exchange tube 30 (30A1) in the + X direction and flows into the first head space flow path 16A of the first header 10.
  • the refrigerant flows from the first head space flow path 16A through the heat exchange tube 30 (30A2) in the ⁇ X direction and flows into the upper part of the second head space flow path 26B of the second header 20.
  • the refrigerant flows from the lower part of the second head space flow path 26B through the heat exchange tube 30 (30C1) in the + X direction and flows into the third head space flow path 16C of the first header 10.
  • the refrigerant flows out from the third head space flow path 16C through the third refrigerant port 53.
  • the refrigerant that has flowed from the second refrigerant port 52 into the seventh head space flow path 16G flows through the heat exchange tube 30 (30G) in the ⁇ X direction and flows into the upper part of the seventh head space flow path 26G of the second header 20. ..
  • the refrigerant flows from the lower part of the 7th head space flow path 26G through the heat exchange tube 30 (30I1) in the + X direction and flows into the 9th head space flow path 16I of the first header 10.
  • the refrigerant flows from the 9th head space flow path 16I through the heat exchange tube 30 (30I2) in the ⁇ X direction and flows into the lower part of the 8th head space flow path 26H of the second header 20.
  • the refrigerant flows from the upper part of the eighth head space flow path 26H through the heat exchange tube 30 (30H2) in the + X direction, and flows into the lower part of the eighth head space flow path 16H of the first header 10.
  • the refrigerant flows from the upper part of the eighth head space flow path 16H through the heat exchange tube 30 (30H1) in the ⁇ X direction, and flows into the lower part of the sixth head space flow path 26F of the second header 20.
  • the refrigerant flows from the upper part of the sixth head space flow path 26F through the heat exchange tube 30 (30E2) in the + X direction, and flows into the lower part of the fifth head space flow path 16E of the first header 10.
  • the refrigerant flows from the upper part of the fifth head space flow path 16E through the heat exchange tube 30 (30E1) in the ⁇ X direction, and flows into the lower part of the fourth head space flow path 26D of the second header 20.
  • the refrigerant flows from the upper part of the fourth head space flow path 26D through the heat exchange tube 30 (30C2) in the + X direction, and flows into the third head space flow path 16C of the first header 10.
  • the refrigerant flows out from the third head space flow path 16C through the third refrigerant port 53.
  • the gaseous refrigerant dissipates heat to the outside air and condenses in the process of flowing through the heat exchange tube 30.
  • the condensed refrigerant becomes a liquid refrigerant and flows out from the third refrigerant port 53 to the outside of the heat exchanger 4.
  • the refrigerant flows in the opposite direction to the above. That is, the liquid refrigerant flows into the third head space flow path 16C from the third refrigerant port 53, and the gas-liquid two-phase refrigerant flows out from the first refrigerant port 51 and the second refrigerant port 52.
  • the head space flow paths 16 and 26 through which the refrigerant flows are formed in the first header 10 and the second header 20 by the recesses 13, 17, 23 and 27 (FIGS. 5 and 5 and). (See FIG. 7). Therefore, the structures of the first header 10 and the second header 20 can be simplified. Therefore, a small and lightweight heat exchanger 4 can be obtained. Since the first header 10 and the second header 20 are made of plate members 11 to 14, they can be made smaller and lighter than the cylindrical header. Therefore, the heat exchanger 4 can be made smaller and lighter. Since the heat exchanger 4 is small and lightweight, it is also excellent in terms of storability in a housing such as an outdoor unit. Since the head space flow paths 16 and 26 capable of flowing the refrigerant in just proportion can be designed for the first header 10 and the second header 20, the amount of refrigerant used can be suppressed.
  • a heat exchanger using a cylindrical header is assumed. Since this heat exchanger uses a header having a large outer diameter, it is difficult to reduce the size and weight. In particular, when a flat heat exchange tube is used to improve heat exchange efficiency, a head having a large outer diameter is required, which makes it difficult to reduce the size and weight. With a cylindrical header, the internal space becomes large and the amount of refrigerant used may increase.
  • a heat exchanger without a header is assumed.
  • a meandering heat exchange tube in which straight portions and curved portions are alternately formed is used.
  • the radius of curvature can be reduced by using a circular tubular heat exchange tube only in the curved portion.
  • miniaturization is not easy.
  • the first header 10 is provided with refrigerant ports 51 and 52 having a refrigerant inlet and a refrigerant port 53 having a refrigerant outlet (see FIG. 2). Since the refrigerant ports 51 to 53 are all provided in the first header 10, the heat exchanger 4 can be miniaturized as compared with the case where the refrigerant ports are distributed in the two headers. Therefore, the heat exchanger 4 is excellent in terms of storability in the housing.
  • FIG. 8 is a cross-sectional view taken along the XZ plane of the first header 10A of the first modification.
  • the above-mentioned configurations are designated by the same reference numerals and the description thereof will be omitted.
  • the first inner plate body 111 is used instead of the first inner plate body 11 (see FIG. 5).
  • the first outer plate body 112 is used instead of the first outer plate body 12 (see FIG. 5).
  • the first inner plate body 111 includes a plate body main portion 113 and a coating layer 114.
  • the plate body main portion 113 is made of a material containing aluminum (aluminum, aluminum alloy, etc.).
  • the coating layer 114 is provided on the outer surface 113b (second main surface) of the plate body main portion 113.
  • the outer surface 113b is a surface opposite to the first main surface 111a facing the first outer plate body 112.
  • the coating layer 114 is made of a metal material containing Zn.
  • the coating layer 114 is made of a 7000 series aluminum alloy.
  • the Zn content (content rate) of the coating layer 114 is higher than the Zn content (content rate) of the plate body main portion 113.
  • the first outer plate body 112 includes a plate body main portion 115 and a coating layer 116.
  • the plate body main portion 115 is made of a material containing aluminum (aluminum, aluminum alloy, etc.).
  • the coating layer 116 is provided on the outer surface 115b (second main surface) of the plate body main portion 115.
  • the outer surface 115b is a surface opposite to the first main surface 112a facing the first inner plate body 111.
  • the coating layer 116 is made of a metal material containing Zn.
  • the coating layer 116 is made of a 7000 series aluminum alloy.
  • the Zn content (content rate) of the coating layer 116 is higher than the Zn content (content rate) of the plate body main portion 115.
  • the first inner plate body 111 and the first outer plate body 112 can be manufactured by using a clad material (laminated plate material) on which a coating layer containing Zn is previously formed.
  • the coating layer can also be formed by thermal spraying.
  • a plate having a coating layer can be used as in the case of the first header 10A.
  • the corrosion resistance of the first header 10A can be improved.
  • FIG. 9 is a cross-sectional view of the first header 10B of the second modification along the XZ plane.
  • the above-mentioned configurations are designated by the same reference numerals and the description thereof will be omitted.
  • the first header 10B the first inner plate body 211 is used instead of the first inner plate body 11 (see FIG. 5).
  • the first outer plate body 212 is used instead of the first outer plate body 12 (see FIG. 5).
  • the first inner plate body 211 includes a plate body main portion 213 and a low melting point layer 214.
  • the plate body main portion 213 is made of a material containing aluminum (aluminum, aluminum alloy, etc.).
  • the low melting point layer 214 is provided on the inner surface 213a (first main surface) of the plate body main portion 213.
  • the low melting point layer 214 is made of a metal material containing Si.
  • the low melting point layer 214 is made of a 4000 series aluminum alloy.
  • the Si content (content rate) of the low melting point layer 214 is higher than the Si content (content rate) of the plate body main portion 213.
  • the melting point of the constituent material of the low melting point layer 214 is lower than the melting point of the constituent material of the plate body main portion 213.
  • the first outer plate body 212 includes a plate body main portion 215 and a low melting point layer 216.
  • the plate body main portion 215 is made of a material containing aluminum (aluminum, aluminum alloy, etc.).
  • the low melting point layer 216 is provided on the inner surface 215a (first main surface) of the plate body main portion 215.
  • the low melting point layer 216 is made of a metal material containing Si.
  • the low melting point layer 216 is composed of a 4000 series aluminum alloy.
  • the Si content (content rate) of the low melting point layer 216 is higher than the Si content (content rate) of the plate body main portion 215.
  • the melting point of the constituent material of the low melting point layer 216 is lower than the melting point of the constituent material of the plate body main portion 215.
  • the first inner plate body 212 and the first outer plate body 212 can be manufactured by using a clad material (laminated plate material) on which a low melting point layer containing Si is formed in advance.
  • the low melting point layer may be formed by laminating a clad sheet made of a low melting point material on the main part of the plate body.
  • a plate having a low melting point layer can be used as in the case of the first header 10B.
  • the low melting point layers 214 and 216 function as brazing to seal the gap between the first header 10 and the second header 20 and the heat exchange tube 30, so that the brazing work becomes easy. ..
  • FIG. 10 is a cross-sectional view taken along the XZ plane of the first header 10C in the heat exchanger of the second embodiment.
  • the above-mentioned configurations are designated by the same reference numerals and the description thereof will be omitted.
  • an intermediate plate body 313 is laminated between the first inner plate body 11 (see FIG. 5) and the first outer plate body 12 (see FIG. 5).
  • the intermediate plate body 313 is made of a material containing aluminum (aluminum, aluminum alloy, etc.).
  • the intermediate plate body 313 is formed with an insertion portion 314 that overlaps the recesses 13 and 17 when viewed from the X direction.
  • the recesses 13 and 17 and the insertion portion 314 form a head space flow path 316.
  • the second header similarly to the first header 10C, a configuration in which an intermediate plate body is laminated between the second inner plate body and the second outer plate body can be adopted.
  • the degree of freedom in designing the head space flow path 316 can be increased.
  • the volume of the head space flow path 316 can be increased by increasing the X-direction dimension of the head space flow path 316.
  • FIG. 11 is a cross-sectional view of the first header 10D of the third modification along the XZ plane.
  • the above-mentioned configurations are designated by the same reference numerals and the description thereof will be omitted.
  • a flat plate-shaped first outer plate body 412 is used instead of the first outer plate body 12 (see FIG. 5).
  • the recess 13 and the first outer plate body 412 form a head space flow path 416. Since the first header 10D uses a flat plate-shaped first outer plate body 412, the structure is simple. Therefore, it is advantageous in terms of miniaturization and cost reduction.
  • the structure of the header can be simplified because a space through which the refrigerant flows is formed in the header by the recesses. Therefore, a small and lightweight heat exchanger can be obtained. Since the header is made of a plate material, it can be made smaller and lighter than a cylindrical header. Therefore, the heat exchanger can be made smaller and lighter. Since the heat exchanger is small and lightweight, it is also excellent in terms of storability in a housing such as an outdoor unit. Since the header can design a space in which the refrigerant can flow in just proportion, the amount of refrigerant used can be suppressed.
  • Refrigeration cycle device 4 Outdoor heat exchanger (heat exchanger) 10 First header (header) 11,111,211 1st inner plate body (plate body) 11a First main surface 12, 112, 212 First outer plate body (plate body) 12a 1st main surface 13, 23, 17, 27 recess 20 2nd header 21 2nd inner plate body (plate body) 21a 1st main surface 22 2nd outer plate body (plate body) 22a First main surface 30 Heat exchange tube 34 Refrigerant flow path 113b Outer surface (second main surface) 115b outer surface (second main surface) 313 Intermediate plate

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Abstract

Un échangeur de chaleur selon ce mode de réalisation comprend des tubes d'échange de chaleur et des collecteurs. Des passages de fluide frigorigène à travers lesquels s'écoule un fluide frigorigène sont formés dans les tubes d'échange de chaleur. Les collecteurs sont respectivement disposés sur l'une et l'autre des sections d'extrémité des tubes d'échange de chaleur. Les collecteurs comprennent chacun une paire de corps de plaque qui sont stratifiés de telle sorte que des premières surfaces principales de ceux-ci se font face. Une section évidée formant un passage spatial qui est en communication avec les passages de fluide frigorigène est formée dans la première surface principale d'au moins l'un des corps de plaque.
PCT/JP2019/050476 2019-12-24 2019-12-24 Échangeur de chaleur et dispositif à cycle de réfrigération WO2021130835A1 (fr)

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KR1020227006507A KR20220041164A (ko) 2019-12-24 2019-12-24 열교환기 및 냉동 사이클 장치
JP2021566412A JP7437418B2 (ja) 2019-12-24 2019-12-24 熱交換器および冷凍サイクル装置
PCT/JP2019/050476 WO2021130835A1 (fr) 2019-12-24 2019-12-24 Échangeur de chaleur et dispositif à cycle de réfrigération
CN201980099418.3A CN114245860A (zh) 2019-12-24 2019-12-24 热交换器及制冷循环装置
JP2024017036A JP2024045455A (ja) 2019-12-24 2024-02-07 熱交換器および冷凍サイクル装置

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Citations (2)

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Publication number Priority date Publication date Assignee Title
JPH04121595A (ja) * 1990-09-12 1992-04-22 Zexel Corp 熱交換器
JP2011085343A (ja) * 2009-10-16 2011-04-28 Mitsubishi Heavy Ind Ltd 熱交換器およびこれを備えた車両用空気調和装置

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JP5263489B2 (ja) 2007-05-31 2013-08-14 株式会社三洋物産 遊技機
CN101161839A (zh) * 2007-11-20 2008-04-16 林小港 一种热交换钎焊覆层合金板的制备方法
DE102011003609A1 (de) * 2011-02-03 2012-08-09 J. Eberspächer GmbH & Co. KG Rippenrohrwärmeübertrager
JP5920175B2 (ja) * 2012-11-13 2016-05-18 株式会社デンソー 熱交換器
JP6090580B2 (ja) 2013-09-26 2017-03-08 トヨタ自動車株式会社 車両用認証方法、車両用認証装置、および携帯機
CN104279888A (zh) * 2014-10-11 2015-01-14 新昌县儒岙镇锦云机械厂 换热器
KR102126311B1 (ko) * 2017-08-25 2020-06-24 한온시스템 주식회사 증발기

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH04121595A (ja) * 1990-09-12 1992-04-22 Zexel Corp 熱交換器
JP2011085343A (ja) * 2009-10-16 2011-04-28 Mitsubishi Heavy Ind Ltd 熱交換器およびこれを備えた車両用空気調和装置

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KR20220041164A (ko) 2022-03-31
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JPWO2021130835A1 (fr) 2021-07-01

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