JP2022161501A - Heat exchanger and refrigeration cycle device - Google Patents

Heat exchanger and refrigeration cycle device Download PDF

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JP2022161501A
JP2022161501A JP2021066373A JP2021066373A JP2022161501A JP 2022161501 A JP2022161501 A JP 2022161501A JP 2021066373 A JP2021066373 A JP 2021066373A JP 2021066373 A JP2021066373 A JP 2021066373A JP 2022161501 A JP2022161501 A JP 2022161501A
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intermediate plate
heat exchanger
plate member
header
refrigerant
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JP2021066373A
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JP7564047B2 (en
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亮輔 是澤
Ryosuke Koresawa
崇史 畠田
Takashi Hatada
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Carrier Japan Corp
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Toshiba Carrier Corp
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Priority to JP2021066373A priority Critical patent/JP7564047B2/en
Priority to CN202210347331.7A priority patent/CN115200266B/en
Priority to KR1020220040854A priority patent/KR102725038B1/en
Publication of JP2022161501A publication Critical patent/JP2022161501A/en
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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
    • 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
    • F25B13/00—Compression machines, plants or systems, with reversible cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/40—Fluid line arrangements
    • 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
    • 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

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

Abstract

To provide a heat exchanger which enables reduction of manufacturing costs and enables a user to check leakage of a refrigerant easily while inhibiting thermal interference of the refrigerant filling the interior.SOLUTION: A heat exchanger has a heat exchange tube and a header. The heat exchange tube extends in a first direction and a refrigerant circulates therein. The header is connected to an end as seen in a first direction of the heat exchange tube. The header has an intermediate plate material and two end plate materials. The two end plate materials sandwich the intermediate plate material in a thickness direction of the intermediate plate material. The header forms a refrigerant space passage in the intermediate plate material. The intermediate plate material has a plate material body and a cylinder part. The plate material body is formed with a first through hole part. The cylinder part is erected in the thickness direction from a peripheral edge part of the first through hole part in the plate material body and contacts with one of the two end plate materials or the plate material body of the other intermediate plate material.SELECTED DRAWING: Figure 4

Description

本発明の実施形態は、熱交換器及び冷凍サイクル装置に関する。 An embodiment of the present invention relates to a heat exchanger and a refrigerating cycle device.

従来、冷凍サイクル装置では、熱交換器が用いられる。この種の熱交換器では、中間板材と、中間板材を挟んで両端側に位置する端部板材と、を貼り合わせることで、冷媒が流れる冷媒流路を構成する場合がある。貫通孔を開けた中間板材と端部板材とを貼り合わせて、冷媒流路内の空間である冷媒空間流路を形成している。
冷媒空間流路の体積は、貫通孔の面積と、中間板材の厚みとで決まる。そのため、ある程度の厚みを持った中間板材で冷媒空間流路を形成しなければならなく、材料管理や材料コストの面でも手間がかかっている。 Conventionally, a heat exchanger is used in a refrigeration cycle device. In this type of heat exchanger, an intermediate plate member and end plate members located on both end sides of the intermediate plate member are bonded together to form a refrigerant channel through which the refrigerant flows. A coolant space channel, which is a space within the coolant channel, is formed by bonding together an intermediate plate member having a through hole and an end plate member.
The volume of the coolant space channel is determined by the area of the through hole and the thickness of the intermediate plate. Therefore, it is necessary to form the coolant space flow path with an intermediate plate material having a certain thickness, which is troublesome in terms of material management and material cost.

また、熱交換器の冷媒空間流路内で、高温領域と低温領域のサーキット（冷媒流路）が隣り合う位置にある場合、サーキット間にスリット加工を施している。これにより、サーキット間の熱干渉を抑制している。熱干渉が生じると、冷媒流路内で冷媒の状態が変化し、熱交換器の効率が下がる。このため、熱干渉を避けることが望まれる。中間板材のサーキット間にスリットを施すには、スリットを加工するための作業領域が狭く、加工難易度が高い問題がある。
また、中間板材を２つの端部板材で挟み込んで接合するため、中間板材内で接合性が悪い場合に、冷媒の漏れを確認することが困難である。 In addition, when the circuits (refrigerant flow paths) of the high-temperature region and the low-temperature region are adjacent to each other in the refrigerant space flow path of the heat exchanger, a slit is formed between the circuits. This suppresses heat interference between circuits. When thermal interference occurs, the state of the refrigerant in the refrigerant flow path changes, reducing the efficiency of the heat exchanger. Therefore, it is desirable to avoid thermal interference. In order to form slits between the circuits of the intermediate plate, there is a problem that the working area for processing the slits is narrow and the degree of processing difficulty is high.
In addition, since the intermediate plate is sandwiched between the two end plates and joined together, it is difficult to check for leakage of the refrigerant if the joinability within the intermediate plate is poor.

国際公開第２０１５／０６３８７５号WO2015/063875

本発明が解決しようとする課題は、製造コストを低減させ、内部に充填される冷媒の熱干渉を抑制しつつ、冷媒の漏れを容易に確認できる熱交換器及び冷凍サイクル装置を提供することである。 The problem to be solved by the present invention is to provide a heat exchanger and a refrigeration cycle device that can easily check for leakage of the refrigerant while reducing the manufacturing cost and suppressing the heat interference of the refrigerant filled inside. be.

実施形態の熱交換器は、熱交換チューブと、ヘッダと、を持つ。熱交換チューブは、第１方向に延び、冷媒が流通する。前記ヘッダは、前記熱交換チューブの前記第１方向の端部に接続される。前記ヘッダは、中間板材と、２つの端部板材とを持つ。２つの端部板材は、前記中間板材を前記中間板材の厚さ方向に挟む。前記ヘッダは、前記中間板材にて冷媒空間流路を形成する。前記中間板材は、板材本体と、筒部とを持つ。板材本体は、第１貫通孔部が形成される。筒部は、前記板材本体における前記第１貫通孔部の周縁部から前記厚さ方向に立ち上がり、前記２つの端部板材のうちの一方、又は他の前記中間板材の前記板材本体に接触する。 A heat exchanger of an embodiment has heat exchange tubes and a header. The heat exchange tube extends in the first direction, through which the refrigerant flows. The header is connected to the end of the heat exchange tube in the first direction. The header has an intermediate plate and two end plates. The two end plate members sandwich the intermediate plate member in the thickness direction of the intermediate plate member. The header forms a coolant space flow path with the intermediate plate member. The intermediate plate member has a plate member body and a cylindrical portion. A first through hole is formed in the plate material body. The tubular portion rises in the thickness direction from the peripheral edge of the first through-hole portion in the plate body and contacts one of the two end plate members or the plate body of the other intermediate plate member.

第１の実施形態の冷凍サイクル装置の概略構成図。BRIEF DESCRIPTION OF THE DRAWINGS The schematic block diagram of the refrigerating-cycle apparatus of 1st Embodiment. 第１の実施形態における熱交換器の斜視図。The perspective view of the heat exchanger in 1st Embodiment. 第１の実施形態における第１ヘッダを分解した斜視図。The perspective view which decomposed|disassembled the 1st header in 1st Embodiment. 第１の実施形態における第１ヘッダの断面図。Sectional drawing of the 1st header in 1st Embodiment. 図４中のＡ１部拡大図である。5 is an enlarged view of A1 part in FIG. 4. FIG. 第２の実施形態における熱交換器を分解した斜視図。The perspective view which decomposed|disassembled the heat exchanger in 2nd Embodiment. 第２の実施形態における熱交換器の断面図。Sectional drawing of the heat exchanger in 2nd Embodiment. 第３の実施形態における熱交換器を分解した斜視図。The perspective view which decomposed|disassembled the heat exchanger in 3rd Embodiment. 第３の実施形態における第１，２中間板材及び仕切り板材の斜視図。The perspective view of the 1st, 2nd intermediate|middle board|plate material and partition board|plate material in 3rd Embodiment. 変形例の熱交換器における第１，２中間板材の斜視図。The perspective view of the 1st, 2nd intermediate|middle board|plate material in the heat exchanger of a modification. 第４の実施形態における熱交換器を分解した斜視図。The perspective view which decomposed|disassembled the heat exchanger in 4th Embodiment. 第４の実施形態における第２中間板材、仕切り板材、第１中間板材、及び第３中間板材の断面図である。It is sectional drawing of the 2nd intermediate board material, partition board material, 1st intermediate board material, and 3rd intermediate board material in 4th Embodiment.

以下、実施形態の熱交換器及び冷凍サイクル装置を、図面を参照して説明する。 Hereinafter, heat exchangers and refrigerating cycle devices according to embodiments will be described with reference to the drawings.

（第１の実施形態）
図１に示されるように、冷凍サイクル装置１は、圧縮機２と、四方弁３と、室外熱交換器（熱交換器）４と、膨張装置５と、室内熱交換器（熱交換器）６と、を有する。冷凍サイクル装置１における圧縮機２等の構成要素は、配管７によって順次接続されている。図１では、冷房運転時の冷媒（熱媒体）の流通方向が実線矢印で示され、暖房運転時の冷媒の流通方向が破線矢印で示される。 (First embodiment)
As shown in FIG. 1, 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. Components such as the compressor 2 in the refrigeration cycle apparatus 1 are connected in sequence by pipes 7 . In FIG. 1 , the flow direction of the refrigerant (heat medium) during cooling operation is indicated by a solid line arrow, and the flow direction of the refrigerant during heating operation is indicated by a broken line arrow.

圧縮機２は、圧縮機本体２Ａと、アキュムレータ２Ｂと、を有する。圧縮機本体２Ａは、内部に取り込まれる低圧の気体冷媒を圧縮して高温・高圧の気体冷媒にする。アキュムレータ２Ｂは、気液二相冷媒を分離して、気体冷媒を圧縮機本体２Ａに供給する。 The compressor 2 has a compressor body 2A and an accumulator 2B. The compressor main body 2A compresses the low-pressure gaseous refrigerant taken thereinto into a high-temperature, high-pressure gaseous refrigerant. The accumulator 2B separates the gas-liquid two-phase refrigerant and supplies the gas refrigerant to the compressor body 2A.

四方弁３は、冷媒の流通方向を逆転させ、冷房運転と暖房運転とを切り替える。
冷房運転時に冷媒は、圧縮機２、四方弁３、室外熱交換器４、膨張装置５、及び室内熱交換器６の順に流れる。このとき冷凍サイクル装置１は、室外熱交換器４を凝縮器として機能させ、室内熱交換器６を蒸発器として機能させ、室内を冷房する。
暖房運転時に冷媒は、圧縮機２、四方弁３、室内熱交換器６、膨張装置５、室外熱交換器４の順に流れる。このとき冷凍サイクル装置１は、室内熱交換器６を凝縮器として機能させ、室外熱交換器４を蒸発器として機能させ、室内を暖房する。 The four-way valve 3 reverses the flow direction of the refrigerant to switch between cooling operation and heating operation.
During cooling operation, the refrigerant flows through the compressor 2, the four-way valve 3, the outdoor heat exchanger 4, the expansion device 5, and the indoor heat exchanger 6 in this order. At this time, 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.
During heating operation, the refrigerant flows through the compressor 2, the four-way valve 3, the indoor heat exchanger 6, the expansion device 5, and the outdoor heat exchanger 4 in this order. At this time, 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.

凝縮器は、圧縮機２から吐出される高温・高圧の気体冷媒を、外気へ放熱させて凝縮させることにより、高圧の液体冷媒にする。
膨張装置５は、凝縮器から送り込まれる高圧の液体冷媒の圧力を下げ、低温・低圧の気液二相冷媒にする。
蒸発器は、膨張装置５から送り込まれる低温・低圧の気液二相冷媒を、外気から吸熱させて気化させることにより、低圧の気体冷媒にする。 The condenser converts the high-temperature, high-pressure gaseous refrigerant discharged from the compressor 2 into a high-pressure liquid refrigerant by radiating heat to the outside air and condensing the refrigerant.
The expansion device 5 reduces the pressure of the high-pressure liquid refrigerant sent from the condenser to convert it into a low-temperature, low-pressure gas-liquid two-phase refrigerant.
The evaporator absorbs heat from the outside air and evaporates the low-temperature, low-pressure gas-liquid two-phase refrigerant sent from the expansion device 5, thereby converting it into a low-pressure gaseous refrigerant.

このように、冷凍サイクル装置１では、作動流体である冷媒が気体冷媒と液体冷媒との間で相変化しながら循環する。冷媒は、気体冷媒から液体冷媒に相変化する過程で放熱し、液体冷媒から気体冷媒に相変化する過程で吸熱する。冷凍サイクル装置１は、冷媒の放熱又は吸熱を利用して、暖房や冷房、除霜等を行う。 Thus, in the refrigeration cycle device 1, the refrigerant, which is the working fluid, circulates while changing the phase between the gas refrigerant and the liquid refrigerant. The refrigerant releases heat during the phase change from the gas refrigerant to the liquid refrigerant, and absorbs heat during the phase change from the liquid refrigerant to the gas refrigerant. The refrigerating cycle device 1 performs heating, cooling, defrosting, etc. by utilizing the heat radiation or heat absorption of the refrigerant.

図２は、第１の実施形態の熱交換器４の斜視図である。図２に示すように、第１の実施形態の熱交換器４は、冷凍サイクル装置１の室外熱交換器４及び室内熱交換器６のうち一方又は両方に使用される。以下、熱交換器４が冷凍サイクル装置１の室外熱交換器４として使用される場合を例にして説明する。 FIG. 2 is a perspective view of the heat exchanger 4 of the first embodiment. As shown in FIG. 2 , 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 . A case where the heat exchanger 4 is used as the outdoor heat exchanger 4 of the refrigeration cycle device 1 will be described below as an example.

熱交換器４は、第１ヘッダ（ヘッダ）１０と、第２ヘッダ（ヘッダ）３０と、熱交換チューブ４０Ａ～４０Ｈと、フィン４５と、を有する。なお、図２では、熱交換器４が有する複数のフィン４５の１つを二点鎖線で示す。
本明細書において、以下のようにＸ方向、Ｙ方向、及びＺ方向を規定する。Ｚ方向は、第１ヘッダ１０及び第２ヘッダ３０が延在する一方向である。例えば、Ｚ方向は鉛直方向であり、＋Ｚ側は上側である。Ｘ方向は、熱交換チューブ４０Ａ～４０Ｈが延びる方向（第１方向。後述する中間板材１１の厚さ方向）である。例えば、Ｘ方向は水平方向であり、＋Ｘ側は第１ヘッダ１０から第２ヘッダ３０に向かう側である。Ｙ方向は、Ｘ方向及びＺ方向に垂直な方向である。 The heat exchanger 4 has a first header (header) 10 , a second header (header) 30 , heat exchange tubes 40A to 40H, and fins 45 . In FIG. 2, one of the plurality of fins 45 of the heat exchanger 4 is indicated by a chain double-dashed line.
In this specification, the X direction, Y direction, and Z direction are defined as follows. The Z direction is one direction in which the first header 10 and the second header 30 extend. For example, the Z direction is the vertical direction and the +Z side is up. The X direction is the direction in which the heat exchange tubes 40A to 40H extend (first direction; thickness direction of the intermediate plate member 11, which will be described later). For example, the X direction is the horizontal direction, and the +X side is the side from the first header 10 to the second header 30 . The Y direction is the direction perpendicular to the X and Z directions.

図３及び図４に示すように、第１ヘッダ１０は、中間板材１１と、２つの端部板材１２，１３と、を持つ。中間板材１１は、板材本体１６と、複数の筒部１７Ａ～１７Ｅと、鍔部１８Ａ～１８Ｅと、を持つ。なお、筒部１７Ａ～１７Ｅは、筒部１７Ａ，１７Ｂ，１７Ｃ，１７Ｄ，１７Ｅを意味する。鍔部１８Ａ～１８Ｅ等についても同様である。
板材本体１６は、Ｘ方向に見たときに矩形状を呈する板状である。板材本体１６は、Ｘ方向に見たとき、２つの第１辺部１６ａと、２つの第２辺部１６ｂと、を有する。２つの第１辺部１６ａは、板材本体１６におけるＺ方向に沿う外縁である。２つの第２辺部１６ｂは、板材本体１６におけるＹ方向に沿う外縁である。２つの第２辺部１６ｂは、２つの第１辺部１６ａに隣り合う。
板材本体１６には、複数の第１貫通孔部２１Ａ～２１Ｅが形成される。 As shown in FIGS. 3 and 4, the first header 10 has an intermediate plate member 11 and two end plate members 12 and 13 . The intermediate plate member 11 has a plate member body 16, a plurality of cylindrical portions 17A to 17E, and collar portions 18A to 18E. The cylindrical portions 17A to 17E mean the cylindrical portions 17A, 17B, 17C, 17D and 17E. The same applies to the flanges 18A to 18E and the like.
The plate material main body 16 has a plate shape that exhibits a rectangular shape when viewed in the X direction. The plate body 16 has two first side portions 16a and two second side portions 16b when viewed in the X direction. The two first side portions 16a are outer edges of the plate body 16 along the Z direction. The two second side portions 16b are outer edges of the plate body 16 along the Y direction. The two second side portions 16b are adjacent to the two first side portions 16a.
A plurality of first through holes 21A to 21E are formed in the plate body 16. As shown in FIG.

第１貫通孔部２１Ａは、Ｘ方向に見たときに、Ｙ方向に延びる長円形状である。ここで言う長円形状とは、互いに平行かつ向かい合う２つの直線と、これら２つの直線の端部同士をそれぞれ結ぶ湾曲凸状（例えば半円弧状、楕円弧状等）の曲線と、で構成される形状を意味する。第１貫通孔部２１Ａは、第１貫通孔部２１Ａ～２１Ｅの中で、最も＋Ｚ側の位置にある。第１貫通孔部２１Ａは、２つの第１辺部１６ａのうち、一方の近傍から他方の近傍まで延びる。
第１貫通孔部２１Ｂ，２１Ｃは、Ｘ方向に見たときに、丸みを帯びた角部を有する矩形状である。第１貫通孔部２１Ｂ，２１Ｃは、第１貫通孔部２１Ａよりも－Ｚ側の位置にある。第１貫通孔部２１Ｂ，２１Ｃは、Ｙ方向に並べるとともに、Ｙ方向に互いに間隔を空けて配置される。第１貫通孔部２１Ｃは、第１貫通孔部２１Ｂよりも＋Ｙ側に配置される。第１貫通孔部２１Ｂ，２１Ｃ全体としてのＹ方向の長さ、及び第１貫通孔部２１ＡのＹ方向の長さは、互いに同等である。 The first through hole portion 21A has an oval shape extending in the Y direction when viewed in the X direction. The oval shape referred to here is composed of two straight lines that are parallel to each other and face each other, and a curved convex shape (for example, semicircular arc shape, elliptical arc shape, etc.) that connects the ends of these two straight lines. means shape. The first through-hole portion 21A is located at the most +Z side position among the first through-hole portions 21A to 21E. The first through hole portion 21A extends from the vicinity of one of the two first side portions 16a to the vicinity of the other.
The first through holes 21B and 21C have a rectangular shape with rounded corners when viewed in the X direction. The first through hole portions 21B and 21C are located on the -Z side of the first through hole portion 21A. The first through holes 21B and 21C are arranged in the Y direction and spaced apart from each other in the Y direction. The first through-hole portion 21C is arranged on the +Y side of the first through-hole portion 21B. The Y-direction length of the first through-hole portions 21B and 21C as a whole and the Y-direction length of the first through-hole portion 21A are equal to each other.

第１貫通孔部２１Ｄ，２１Ｅは、Ｘ方向に見たときに、Ｙ方向に延びる長円形状である。第１貫通孔部２１Ｄ，２１Ｅは、第１貫通孔部２１Ｂ，２１Ｃよりも－Ｚ側の位置にある。第１貫通孔部２１Ｄ，２１Ｅは、Ｙ方向に並べるとともに、Ｙ方向に互いに間隔を空けて配置される。第１貫通孔部２１Ｅは、第１貫通孔部２１Ｄよりも＋Ｙ側に配置される。
第１貫通孔部２１ＤのＹ方向の長さ、及び第１貫通孔部２１ＢのＹ方向の長さは、互いに同等である。第１貫通孔部２１ＥのＹ方向の長さ、及び第１貫通孔部２１ＣのＹ方向の長さは、互いに同等である。 The first through-holes 21D and 21E have an oval shape extending in the Y direction when viewed in the X direction. The first through-hole portions 21D and 21E are positioned on the -Z side of the first through-hole portions 21B and 21C. The first through holes 21D and 21E are arranged in the Y direction and spaced apart from each other in the Y direction. The first through-hole portion 21E is arranged on the +Y side of the first through-hole portion 21D.
The Y-direction length of the first through-hole portion 21D and the Y-direction length of the first through-hole portion 21B are equal to each other. The Y-direction length of the first through-hole portion 21E and the Y-direction length of the first through-hole portion 21C are equal to each other.

筒部１７Ａは、筒状であり、第１貫通孔部２１Ａと同軸に配置される。筒部１７Ａは、板材本体１６における第１貫通孔部２１Ａの周縁部からＸ方向の＋Ｘ側に立ち上がる。筒部１７Ｂ～１７Ｅは、筒部１７Ａと同様に構成される。筒部１７Ｂ～１７Ｅは、板材本体１６における第１貫通孔部２１Ｂ～２１Ｅの周縁部から＋Ｘ側にそれぞれ立ち上がる。
鍔部１８Ａは、筒部１７Ａが立ち上がる先端部から、筒部１７Ａの径方向外側に、筒部１７Ａの全周にわたって突出する。鍔部１８Ｂ～１８Ｅは、鍔部１８Ａと同様に構成される。鍔部１８Ｂ～１８Ｅは、筒部１７Ｂ～１７Ｅが立ち上がる先端部から、筒部１７Ｂ～１７Ｅの径方向外側に、筒部１７Ｂ～１７Ｅの全周にわたってそれぞれ突出する。
板材本体１６から筒部１７Ａ及び鍔部１８Ａが全体として＋Ｘ側に立ち上がる長さ、及び板材本体１６から筒部１７Ｂ及び鍔部１８Ｂが全体として＋Ｘ側に立ち上がる長さは、互いに同等である。板材本体１６から筒部１７Ｃ～１７Ｅ及び鍔部１８Ｃ～１８Ｅが全体として＋Ｘ側に立ち上がる長さについても、同様である。 The tubular portion 17A has a tubular shape and is arranged coaxially with the first through hole portion 21A. The cylindrical portion 17A rises from the periphery of the first through-hole portion 21A in the plate material body 16 to the +X side in the X direction. The tubular portions 17B to 17E are configured similarly to the tubular portion 17A. The tubular portions 17B to 17E rise from the peripheral edge portions of the first through-hole portions 21B to 21E in the plate material body 16 to the +X side, respectively.
The collar portion 18A protrudes radially outwardly of the cylindrical portion 17A from the rising tip portion of the cylindrical portion 17A over the entire circumference of the cylindrical portion 17A. The flanges 18B to 18E are configured similarly to the flange 18A. The flanges 18B to 18E protrude radially outward of the cylindrical portions 17B to 17E from the rising tip portions of the cylindrical portions 17B to 17E over the entire circumference of the cylindrical portions 17B to 17E.
The total length of the cylindrical portion 17A and the flange portion 18A rising from the plate material body 16 to the +X side and the total length of the cylindrical portion 17B and the flange portion 18B rising from the plate material body 16 to the +X side are equal to each other. The same applies to the lengths of the cylindrical portions 17C to 17E and the collar portions 18C to 18E as a whole rising from the plate material body 16 toward the +X side.

例えば、第１貫通孔部２１Ａ～２１Ｅ、筒部１７Ａ～１７Ｅ、及び鍔部１８Ａ～１８Ｅは、板状の部材をリフレア加工することで形成される。板状の部材の母材は、アルミニウム、アルミニウム合金等の、熱伝導率が高く比重が小さい材料で形成される。
母材の第１主面には、ロウ材を含む層が形成されることが好ましい。母材における、第１主面とは反対の第２主面には、耐食処理層が形成される（耐食処理が施されている）ことが好ましい。例えば、耐食処理層には、ＪＩＳ規格により規定されるAl-Zn-Mg系の熱処理型のアルミニウム合金である、Ａ７０７２に形成された耐食被膜が用いられる。
板状の部材の第１主面が－Ｘ側を向くように配置した状態で、板状の部材にリフレア加工すること等により、第１貫通孔部２１Ａ～２１Ｅ、筒部１７Ａ～１７Ｅ、及び鍔部１８Ａ～１８Ｅが形成される。
図４に示すように、中間板材１１において、板状の部材の第１主面に対応する面を、符号１１ｃで示す。中間板材１１において、板状の部材の第２主面に対応する面を、符号１１ｄで示す。 For example, the first through holes 21A to 21E, the cylinders 17A to 17E, and the flanges 18A to 18E are formed by reflaring a plate-shaped member. The base material of the plate-shaped member is formed of a material with high thermal conductivity and low specific gravity, such as aluminum or aluminum alloy.
A layer containing brazing material is preferably formed on the first main surface of the base material. It is preferable that a corrosion-resistant treatment layer be formed (corrosion-resistant treatment is applied) on the second main surface opposite to the first main surface of the base material. For example, as the corrosion-resistant layer, a corrosion-resistant film formed of A7072, which is an Al-Zn-Mg-based heat-treated aluminum alloy defined by JIS, is used.
The first through-holes 21A to 21E, the cylindrical portions 17A to 17E, and the Collar portions 18A to 18E are formed.
As shown in FIG. 4, in the intermediate plate member 11, the surface corresponding to the first main surface of the plate-shaped member is denoted by reference numeral 11c. In the intermediate plate member 11, the surface corresponding to the second main surface of the plate-shaped member is denoted by reference numeral 11d.

図３及び図４に示すように、端部板材１２，１３は、Ｘ方向に見たときにそれぞれ矩形状を呈する板状である。Ｘ方向に見たときに、端部板材１２，１３、及び中間板材１１の板材本体１６は、互いにほぼ重なる。
端部板材１２は、Ｘ方向に見たとき、２つの第１辺部１２ａと、２つの第２辺部１２ｂと、を有する。２つの第１辺部１２ａは、端部板材１２におけるＺ方向に沿う外縁である。２つの第２辺部１２ｂは、端部板材１２におけるＹ方向に沿う外縁である。２つの第２辺部１２ｂは、２つの第１辺部１２ａに隣り合う。
図３に示すように、端部板材１２における－Ｚ側の端部には、２つの差込み孔部２４Ａ，２４Ｂが形成される。差込み孔部２４Ａ，２４Ｂは、Ｘ方向に見たときに円形状である。差込み孔部２４Ａ，２４Ｂは、端部板材１２をＸ方向に貫通する。
差込み孔部２４Ａ，２４Ｂは、Ｙ方向に並べるとともに、Ｙ方向に互いに間隔を空けて配置される。差込み孔部２４Ｂは、差込み孔部２４Ａよりも＋Ｙ側に配置される。
Ｘ方向に見たときに、差込み孔部２４Ａは中間板材１１の第１貫通孔部２１Ｄ内に配置される。同様に、Ｘ方向に見たときに、差込み孔部２４Ｂは中間板材１１の第１貫通孔部２１Ｅ内に配置される。 As shown in FIGS. 3 and 4, the end plate members 12 and 13 are plate-shaped, each having a rectangular shape when viewed in the X direction. When viewed in the X direction, the plate material bodies 16 of the end plates 12, 13 and the intermediate plate 11 substantially overlap each other.
The end plate member 12 has two first side portions 12a and two second side portions 12b when viewed in the X direction. The two first side portions 12a are outer edges of the end plate member 12 along the Z direction. The two second side portions 12b are outer edges of the end plate member 12 along the Y direction. The two second side portions 12b are adjacent to the two first side portions 12a.
As shown in FIG. 3, two insertion holes 24A and 24B are formed at the end of the end plate 12 on the -Z side. The insertion holes 24A and 24B are circular when viewed in the X direction. The insertion holes 24A and 24B pass through the end plate 12 in the X direction.
The insertion holes 24A and 24B are arranged in the Y direction and spaced apart from each other in the Y direction. The insertion hole portion 24B is arranged on the +Y side of the insertion hole portion 24A.
The insertion hole portion 24A is arranged in the first through hole portion 21D of the intermediate plate member 11 when viewed in the X direction. Similarly, the insertion hole portion 24B is arranged in the first through hole portion 21E of the intermediate plate member 11 when viewed in the X direction.

端部板材１２と同様に、端部板材１３は、Ｘ方向に見たとき、２つの第１辺部１３ａと、２つの第２辺部１３ｂと、を有する。
端部板材１３には、複数の差込み孔部２６Ａ～２６Ｈが形成される。差込み孔部２６Ａ～２６Ｈは、Ｘ方向に見たときに、Ｙ方向に延びる長円形状である。
差込み孔部２６Ａ，２６Ｂは、差込み孔部２６Ａ～２６Ｅの中で、最も＋Ｚ側の位置にある。差込み孔部２６Ａ，２６Ｂは、Ｙ方向に並べるとともに、Ｙ方向に互いに間隔を空けて配置される。差込み孔部２６Ｂは、差込み孔部２６Ａよりも＋Ｙ側に配置される。
差込み孔部２６Ａ，２６Ｃ，２６Ｅ，２６Ｇは、Ｚ方向に並べるとともに、Ｚ方向にこの順で互いに間隔を空けて配置される。差込み孔部２６Ｂ，２６Ｄ，２６Ｆ，２６Ｈは、Ｚ方向に並べるとともに、Ｚ方向にこの順で互いに間隔を空けて配置される。 Similar to the end plate member 12, the end plate member 13 has two first side portions 13a and two second side portions 13b when viewed in the X direction.
The end plate member 13 is formed with a plurality of insertion holes 26A to 26H. The insertion holes 26A to 26H have an oval shape extending in the Y direction when viewed in the X direction.
The insertion holes 26A and 26B are located on the most +Z side among the insertion holes 26A to 26E. The insertion holes 26A and 26B are arranged in the Y direction and spaced apart from each other in the Y direction. The insertion hole portion 26B is arranged on the +Y side of the insertion hole portion 26A.
The insertion holes 26A, 26C, 26E, and 26G are arranged in the Z direction and spaced from each other in this order in the Z direction. The insertion holes 26B, 26D, 26F, and 26H are arranged in the Z direction and spaced from each other in this order in the Z direction.

Ｘ方向に見たときに、差込み孔部２６Ａ，２６Ｂは中間板材１１の第１貫通孔部２１Ａ内に配置される。同様に、Ｘ方向に見たときに、差込み孔部２６Ｃ，２６Ｅは中間板材１１の第１貫通孔部２１Ｂ内に配置される。Ｘ方向に見たときに、差込み孔部２６Ｄ，２６Ｆは中間板材１１の第１貫通孔部２１Ｃ内に配置される。Ｘ方向に見たときに、差込み孔部２６Ｇは中間板材１１の第１貫通孔部２１Ｄ内に配置される。Ｘ方向に見たときに、差込み孔部２６Ｈは中間板材１１の第１貫通孔部２１Ｅ内に配置される。 The insertion holes 26A and 26B are arranged in the first through hole 21A of the intermediate plate 11 when viewed in the X direction. Similarly, the insertion holes 26C and 26E are arranged in the first through hole 21B of the intermediate plate 11 when viewed in the X direction. The insertion holes 26D and 26F are arranged in the first through hole 21C of the intermediate plate 11 when viewed in the X direction. The insertion hole portion 26G is arranged in the first through hole portion 21D of the intermediate plate member 11 when viewed in the X direction. The insertion hole portion 26H is arranged in the first through hole portion 21E of the intermediate plate member 11 when viewed in the X direction.

端部板材１２，１３は、前記板状の部材により形成される。このとき、端部板材１２において第１主面が＋Ｘ側を向き、端部板材１３において第１主面が－Ｘ側を向くように配置される。
図４に示すように、端部板材１２，１３において、板状の部材の第１主面に対応する面を、符号１２ｃ，１３ｃで示す。端部板材１２，１３において、板状の部材の第２主面に対応する面を、符号１２ｄ，１３ｄで示す。
２つの端部板材１２，１３における第１ヘッダ１０の外側の面には、耐食処理が施されている。 The end plates 12 and 13 are formed of the plate-shaped members. At this time, the first main surface of the end plate member 12 faces the +X side, and the first main surface of the end plate member 13 faces the -X side.
As shown in FIG. 4, in the end plates 12 and 13, the surfaces corresponding to the first main surfaces of the plate-like members are denoted by reference numerals 12c and 13c. In the end plate members 12 and 13, the surfaces corresponding to the second main surfaces of the plate-like members are denoted by reference numerals 12d and 13d.
The outer surfaces of the first header 10 of the two end plates 12 and 13 are subjected to anti-corrosion treatment.

図４及び図５に示すように、端部板材１２，１３は、中間板材１１をＸ方向に挟む。
端部板材１２は、中間板材１１の板材本体１６に、板材本体１６の－Ｘ側から接触する。なお、本明細書において、接触するとは、直接的に接触することを意味するだけでなく、他の部材を介して間接的に接触することも意味する。
端部板材１２と板材本体１６とは、ロウ付けにより固定される。このロウ付けには、中間板材１１の第１主面１１ｃ、及び端部板材１２の第１主面１２ｃに設けられたロウ材を含む層が用いられる。
中間板材１１の鍔部１８Ａ～１８Ｅは、端部板材１３に、端部板材１３の－Ｘ側からそれぞれ接触する。中間板材１１の筒部１７Ａ～１７Ｅは、端部板材１３に、端部板材１３の－Ｘ側から鍔部１８Ａ～１８Ｅを介してそれぞれ接触する。
端部板材１３と鍔部１８Ａ～１８Ｅとは、ロウ付けにより固定される。このロウ付けには、中間板材１１の第１主面１１ｃ、及び端部板材１３の第１主面１３ｃに設けられたロウ材を含む層が用いられる。 As shown in FIGS. 4 and 5, the end plates 12 and 13 sandwich the intermediate plate 11 in the X direction.
The end plate member 12 contacts the plate member body 16 of the intermediate plate member 11 from the -X side of the plate member body 16 . In this specification, contact means not only direct contact but also indirect contact via another member.
The end plate material 12 and the plate material body 16 are fixed by brazing. For this brazing, a layer containing brazing material provided on the first main surface 11c of the intermediate plate member 11 and the first main surface 12c of the end plate member 12 is used.
The flanges 18A to 18E of the intermediate plate member 11 contact the end plate member 13 from the -X side of the end plate member 13, respectively. The cylindrical portions 17A to 17E of the intermediate plate member 11 contact the end plate member 13 from the -X side of the end plate member 13 via the collar portions 18A to 18E, respectively.
The end plate 13 and the flanges 18A to 18E are fixed by brazing. For this brazing, a layer containing brazing material provided on the first main surface 11c of the intermediate plate member 11 and the first main surface 13c of the end plate member 13 is used.

図２に示すように、第２ヘッダ３０は、第１ヘッダ１０と同様に構成される。第２ヘッダ３０は、中間板材１１、端部板材１２，１３と同様に構成された中間板材（不図示）、端部板材３２，３３を有する。
端部板材３３には、図示しない差込み孔が形成される。 As shown in FIG. 2, the second header 30 is constructed similarly to the first header 10 . The second header 30 has an intermediate plate member (not shown) configured similarly to the intermediate plate member 11 and the end plate members 12 and 13 , and end plate members 32 and 33 .
An insertion hole (not shown) is formed in the end plate member 33 .

熱交換チューブ４０Ａ～４０Ｈは、偏平管状に形成されて、Ｘ方向に延びる。すなわち、熱交換チューブ４０Ａ～４０ＨのＺ方向の長さよりも、熱交換チューブ４０Ａ～４０ＨのＹ方向の長さが長い。熱交換チューブ４０Ａ～４０Ｈは、アルミニウム、アルミニウム合金等の、熱伝導率が高く比重が小さい材料で形成される。
熱交換チューブ４０Ａ～４０Ｈの－Ｘ側の端部は、端部板材１３の差込み孔部２６Ａ～２６Ｈ内にそれぞれ配置される。熱交換チューブ４０Ａ～４０Ｈの－Ｘ側の端部は、中間板材１１の複数の筒部１７Ａ～１７Ｅに差し込まれる。
熱交換チューブ４０Ａ～４０Ｈの＋Ｘ側の端部は、第２ヘッダ３０の端部板材３３の差込み孔内にそれぞれ配置される。
熱交換チューブ４０Ａ～４０Ｈ内には、冷媒がそれぞれ流通する。 The heat exchange tubes 40A-40H are formed in a flat tubular shape and extend in the X direction. That is, the length of the heat exchange tubes 40A to 40H in the Y direction is longer than the length of the heat exchange tubes 40A to 40H in the Z direction. The heat exchange tubes 40A to 40H are made of a material with high thermal conductivity and low specific gravity, such as aluminum or aluminum alloy.
The −X side ends of the heat exchange tubes 40A to 40H are arranged in the insertion holes 26A to 26H of the end plate member 13, respectively. The −X side ends of the heat exchange tubes 40A to 40H are inserted into the plurality of tubular portions 17A to 17E of the intermediate plate member 11, respectively.
The +X side ends of the heat exchange tubes 40A to 40H are arranged in the insertion holes of the end plate member 33 of the second header 30, respectively.
A refrigerant flows through each of the heat exchange tubes 40A to 40H.

フィン４５は、アルミニウム、アルミニウム合金等により、薄板状に形成される。フィン４５には、Ｙ方向に延びるスリット４６が複数形成される。各スリット４６は、－Ｙ側に開口する。各スリット４６は、熱交換チューブ４０Ａ～４０Ｈに嵌め合う。 The fins 45 are made of aluminum, aluminum alloy, or the like and formed into a thin plate. A plurality of slits 46 extending in the Y direction are formed in the fin 45 . Each slit 46 opens on the -Y side. Each slit 46 fits into a heat exchange tube 40A-40H.

図３に示すように、第１ヘッダ１０の端部板材１２の差込み孔部２４Ａには、管状の第１冷媒ポート５０Ａの端部が配置される。第１ヘッダ１０の端部板材１２の差込み孔部２４Ｂには、管状の第２冷媒ポート５０Ｂの端部が配置される。 As shown in FIG. 3 , an end of a tubular first refrigerant port 50A is arranged in the insertion hole 24A of the end plate 12 of the first header 10 . An end portion of a tubular second coolant port 50B is arranged in the insertion hole portion 24B of the end plate member 12 of the first header 10 .

以上のように構成された熱交換器４では、例えば第１冷媒ポート５０Ａから流れ込んだ冷媒は、以下のように流れる。
すなわち、冷媒は、筒部１７Ｄを通して、熱交換チューブ４０Ｇ、熱交換チューブ４０Ｅ、筒部１７Ｂ、熱交換チューブ４０Ｃ、熱交換チューブ４０Ａ、筒部１７Ａ内にこの順に流れ込む。さらにこの冷媒は、熱交換チューブ４０Ｂ、熱交換チューブ４０Ｄ、筒部１７Ｃ、熱交換チューブ４０Ｆ、熱交換チューブ４０Ｈ、筒部１７Ｅを通して、第２冷媒ポート５０Ｂから流れ出る。 In the heat exchanger 4 configured as described above, for example, the refrigerant flowing from the first refrigerant port 50A flows as follows.
That is, the refrigerant flows through the tubular portion 17D into the heat exchange tubes 40G, the heat exchange tubes 40E, the tubular portion 17B, the heat exchange tubes 40C, the heat exchange tubes 40A, and the tubular portion 17A in this order. Furthermore, this refrigerant flows out from the second refrigerant port 50B through the heat exchange tubes 40B, the heat exchange tubes 40D, the tubular portion 17C, the heat exchange tubes 40F, the heat exchange tubes 40H, and the tubular portion 17E.

図４に示すように、室外熱交換器４では、第１ヘッダ１０の中間板材１１及び端部板材１２，１３、第２ヘッダ３０の中間板材及び端部板材３２，３３により、内部に冷媒を流すための冷媒流路５５が形成される。
冷媒流路５５内において、冷媒が実際に流れる空間が、冷媒空間流路５５ａである。すなわち、冷媒空間流路５５ａは、第１ヘッダ１０の中間板材１１及び端部板材１２，１３、第２ヘッダ３０の中間板材及び端部板材３２，３３により形成される。 As shown in FIG. 4, in the outdoor heat exchanger 4, the intermediate plate member 11 and the end plate members 12 and 13 of the first header 10 and the intermediate plate member and the end plate members 32 and 33 of the second header 30 flow the refrigerant inside. A coolant channel 55 is formed for the flow.
A space in which the coolant actually flows in the coolant channel 55 is a coolant space channel 55a. That is, the coolant space channel 55 a is formed by the intermediate plate member 11 and the end plate members 12 and 13 of the first header 10 and the intermediate plate member and the end plate members 32 and 33 of the second header 30 .

以上説明したように、本実施形態の熱交換器４では、図５に示すように、筒部１７Ａの径方向外側に、筒部１７Ａを覆う空間層Ｓ１が形成される。一般的に、この空間層にある空気の熱伝導率は、中間板材及び端部板材が形成される材料の熱伝導率よりも小さい。このため、例えば中間板材１１に複数の筒部１７Ａ，１７Ｂが形成され、熱交換器４内に冷媒が充填された場合に、筒部１７Ａ，１７Ｂのうち、筒部１７Ａ内の冷媒と、筒部１７Ｂ内の冷媒との熱干渉を、抑制することができる。
筒部１７Ａの径方向外側に空間層Ｓ１が形成されるため、筒部が、その径方向外側まで延びる場合に比べて、中間板材１１の製造に要する材料コストを低減させることができる。
筒部１７Ａの径方向外側に空間層Ｓ１が形成されるため、例えば熱交換器４内に冷媒が充填されたときに、鍔部１８Ａを介して筒部１７Ａと端部板材１３とが接触する部分であって充填された冷媒近傍の部分Ｐ１を、熱交換器４の外側から目視により確認しやすくなる。部分Ｐ１の径方向外側に冷媒の漏れ確認用の石鹸水等を塗布して、その石鹸水の泡立ちを目視により確認する。このように、冷媒の漏れを容易に確認することができる。
以上のように、熱交換器４の製造コストを低減させ、内部に充填される冷媒の熱干渉を抑制しつつ、冷媒の漏れを容易に確認することができる。 As described above, in the heat exchanger 4 of the present embodiment, as shown in FIG. 5, the space layer S1 covering the cylindrical portion 17A is formed radially outside the cylindrical portion 17A. Generally, the thermal conductivity of the air in this space layer is less than the thermal conductivity of the material from which the intermediate and end plates are made. Therefore, for example, when a plurality of tubular portions 17A and 17B are formed in the intermediate plate member 11 and the refrigerant is filled in the heat exchanger 4, the refrigerant in the tubular portion 17A and the tubular portion 17A among the tubular portions 17A and 17B Thermal interference with the refrigerant in the portion 17B can be suppressed.
Since the space layer S1 is formed on the radially outer side of the tubular portion 17A, the material cost required for manufacturing the intermediate plate member 11 can be reduced compared to the case where the tubular portion extends radially outward.
Since the space layer S1 is formed radially outward of the cylindrical portion 17A, for example, when the heat exchanger 4 is filled with refrigerant, the cylindrical portion 17A and the end plate member 13 come into contact with each other via the flange portion 18A. It becomes easy to visually confirm the portion P1 in the vicinity of the filled refrigerant from the outside of the heat exchanger 4 . Soapy water or the like for checking refrigerant leakage is applied to the radially outer side of the portion P1, and the foaming of the soapy water is visually confirmed. In this way, refrigerant leakage can be easily confirmed.
As described above, it is possible to reduce the manufacturing cost of the heat exchanger 4, suppress the heat interference of the refrigerant filled inside, and easily check for refrigerant leakage.

中間板材１１に筒部１７Ａが形成されるため、中間板材をＸ方向に厚くする必要が無い。中間板材１１の製造に用いる板状の部材の厚さ、及び端部板材１２，１３の製造に用いる板状の部材の厚さを、互いに等しくすることができ、製造に用いる材料の管理が容易になる。 Since the cylindrical portion 17A is formed on the intermediate plate member 11, there is no need to increase the thickness of the intermediate plate member in the X direction. The thickness of the plate-shaped member used for manufacturing the intermediate plate member 11 and the thickness of the plate-shaped member used for manufacturing the end plate members 12 and 13 can be made equal to each other, making it easy to manage the materials used for manufacturing. become.

熱交換器４は、鍔部１８Ａを持つ。筒部１７Ａと端部板材１３との接触面積に比べて、鍔部１８Ａと端部板材１３との接触面積が広くなる。このため、接触面積が広く確保されて、中間板材１１と端部板材１３との接合を確実に行うことができる。接合における信頼性を向上させることができる。
また、本実施形態の冷凍サイクル装置１では、製造コストを低減させ、内部に充填される冷媒の熱干渉を抑制しつつ、冷媒の漏れを容易に確認することができる熱交換器４を用いて、冷凍サイクル装置１を構成することができる。 The heat exchanger 4 has a collar portion 18A. The contact area between the flange portion 18A and the end plate member 13 is larger than the contact area between the cylindrical portion 17A and the end plate member 13 . Therefore, a large contact area is ensured, and the intermediate plate member 11 and the end plate member 13 can be reliably joined. Reliability in bonding can be improved.
Further, in the refrigeration cycle apparatus 1 of the present embodiment, the heat exchanger 4 is used to reduce the manufacturing cost and suppress the thermal interference of the refrigerant filled inside, and to easily check the leakage of the refrigerant. , the refrigeration cycle device 1 can be configured.

なお、第１ヘッダ１０は、２つの端部板材１２，１３によりＸ方向に挟まれる中間板材１１を複数持ってもよい。これら複数の中間板材１１は、互いに同一形状である。複数の中間板材１１における筒部１７Ａは、Ｘ方向に並べて配置される。この場合、複数の中間板材１１における最も＋Ｘ側の中間板材１１以外の中間板材１１に設けられた鍔部１８Ａは、この中間板材１１に対して＋Ｘ側に隣り合う他の中間板材１１の板材本体１６に、この板材本体１６の－Ｘ側から接触する。
また、複数の中間板材１１における最も＋Ｘ側の中間板材１１以外の筒部１７Ａは、この中間板材１１に対して＋Ｘ側に隣り合う他の中間板材１１の板材本体１６に、この板材本体１６の－Ｘ側から鍔部１８Ａを介して接触する。
筒部１７Ｂ～１７Ｅについても、筒部１７Ａと同様である。 In addition, the first header 10 may have a plurality of intermediate plates 11 sandwiched between the two end plates 12 and 13 in the X direction. These intermediate plate members 11 have the same shape. The cylindrical portions 17A of the plurality of intermediate plate members 11 are arranged side by side in the X direction. In this case, the flange portion 18A provided on the intermediate plate member 11 other than the intermediate plate member 11 closest to the +X side among the plurality of intermediate plate members 11 is the plate material main body of the other intermediate plate member 11 adjacent to the intermediate plate member 11 on the +X side. 16 is contacted from the -X side of this plate material body 16 .
Further, the tubular portion 17A of the plurality of intermediate plate members 11 other than the intermediate plate member 11 closest to the +X side is attached to the plate member main body 16 of the other intermediate plate member 11 adjacent to the intermediate plate member 11 on the +X side. Contact is made from the -X side through the collar portion 18A.
The tubular portions 17B to 17E are similar to the tubular portion 17A.

この変形例の熱交換器では、複数の中間板材１１により、筒部１７Ａ内の空間層をＸ方向に長く連ねることができる。
例えば、前記板状の部材における加工上の制約により、筒部１７ＡにおけるＸ方向の長さが短くなる場合であっても、複数の中間板材１１を用いることにより、冷媒空間流路５５ａの体積を増やすことができる。 In the heat exchanger of this modified example, the plurality of intermediate plate members 11 can extend the space layers in the cylindrical portion 17A in the X direction.
For example, even if the X-direction length of the cylindrical portion 17A is shortened due to processing restrictions on the plate-shaped member, the volume of the coolant space flow path 55a can be reduced by using a plurality of intermediate plate members 11. can be increased.

なお、中間板材１１に形成される第１貫通孔部の数に制限は無く、１つでもよい。筒部１７Ａ～１７Ｅに鍔部１８Ａ～１８Ｅが設けられなくてもよい。 The number of first through holes formed in the intermediate plate member 11 is not limited, and may be one. The flanges 18A to 18E may not be provided on the tubular portions 17A to 17E.

（第２の実施形態）
次に、本発明の第２実施形態について図６及び図７を参照しながら説明するが、前記実施形態と同一の部位には同一の符号を付してその説明は省略し、異なる点についてのみ説明する。
図６及び図７に示すように、本実施形態の熱交換器６１の第１ヘッダ１０Ａは、第１の実施形態の熱交換器４の第１ヘッダ１０の各構成に加えて、立ち上がり壁６２を持つ。立ち上がり壁６２は、端部板材１２の外周縁と端部板材１３の外周縁とを、端部板材１２，１３の全周にわたって連結する。
より詳しく説明すると、立ち上がり壁６２は、２つの第１壁片６３と、２つの第２壁片６４と、を持つ。 (Second embodiment)
Next, a second embodiment of the present invention will be described with reference to FIGS. 6 and 7. Parts that are the same as those of the above embodiment are denoted by the same reference numerals, and description thereof will be omitted. explain.
As shown in FIGS. 6 and 7, the first header 10A of the heat exchanger 61 of the present embodiment has upstanding walls 62 in addition to each configuration of the first header 10 of the heat exchanger 4 of the first embodiment. have. The rising wall 62 connects the outer peripheral edge of the end plate member 12 and the outer peripheral edge of the end plate member 13 over the entire circumference of the end plate members 12 and 13 .
More specifically, the rising wall 62 has two first wall pieces 63 and two second wall pieces 64 .

２つの第１壁片６３は、端部板材１３における２つの第１辺部１３ａに設けられる。２つの第１壁片６３は、Ｘ方向の－Ｘ側に延びて、端部板材１２の外周縁に達する。
２つの第２壁片６４は、端部板材１２における２つの第２辺部１２ｂに設けられる。２つの第２壁片６４は、Ｘ方向の＋Ｘ側に延びて、端部板材１３の外周縁に達する。
端部板材１３及び２つの第１壁片６３は、前記板状の部材を折り曲げて形成される。端部板材１３及び２つの第１壁片６３は、全体としてＵ字状に折れ曲がった形状である。端部板材１２及び２つの第２壁片６４は、前記板状の部材を折り曲げて形成される。端部板材１２及び２つの第２壁片６４は、全体としてＵ字状に折れ曲がった形状である。
端部板材１２，１３及び立ち上がり壁６２における第１ヘッダ１０Ａの外側の面には、耐食処理が施されている。 The two first wall pieces 63 are provided on the two first side portions 13 a of the end plate member 13 . The two first wall pieces 63 extend to the −X side in the X direction and reach the outer edge of the end plate member 12 .
The two second wall pieces 64 are provided on the two second side portions 12 b of the end plate member 12 . The two second wall pieces 64 extend to the +X side in the X direction and reach the outer edge of the end plate member 13 .
The end plate member 13 and the two first wall pieces 63 are formed by bending the plate-shaped member. The end plate member 13 and the two first wall pieces 63 are bent in a U shape as a whole. The end plate member 12 and the two second wall pieces 64 are formed by bending the plate-shaped member. The end plate member 12 and the two second wall pieces 64 are bent in a U shape as a whole.
The end plates 12 and 13 and the rising wall 62 are subjected to anti-corrosion treatment on the outer surfaces of the first header 10A.

以上説明したように、本実施形態の熱交換器６１では、熱交換器６１の製造コストを低減させ、内部に充填される冷媒の熱干渉を抑制しつつ、冷媒の漏れを容易に確認することができる。
さらに、熱交換器６１が立ち上がり壁６２を持つ。従って、端部板材１２，１３の間の筒部１７Ａに、凝縮水、雨水、ゴミ等が付着し、付着した部分が腐食するのを抑制することができる。このため、熱交換器６１内に冷媒が充填された場合には、腐食が冷媒のリークにつながるのを抑制することができる。 As described above, in the heat exchanger 61 of the present embodiment, the manufacturing cost of the heat exchanger 61 can be reduced, the heat interference of the refrigerant charged inside can be suppressed, and leakage of the refrigerant can be easily confirmed. can be done.
Furthermore, the heat exchanger 61 has raised walls 62 . Therefore, it is possible to prevent condensed water, rainwater, dust, etc. from adhering to the tubular portion 17A between the end plate members 12 and 13 and corroding the adhering portion. Therefore, when the heat exchanger 61 is filled with the refrigerant, it is possible to prevent the corrosion from leaking the refrigerant.

立ち上がり壁６２は、２つの第１壁片６３と、２つの第２壁片６４と、を持つ。端部板材１３及び２つの第１壁片６３、端部板材１２及び２つの第２壁片６４が、それぞれ全体としてＵ字状に折れ曲がった形状である。従って、互いに同様の構成の端部板材１３及び２つの第１壁片６３、端部板材１２及び２つの第２壁片６４を用いて、立ち上がり壁６２を構成することができる。
端部板材１２，１３及び立ち上がり壁６２における第１ヘッダ１０Ａ（熱交換器６１）の外側の面には、耐食処理が施されている。このため、第１ヘッダ１０Ａの外側から端部板材１２，１３及び立ち上がり壁６２に雨水等が付着したときに、この雨水等により端部板材１２，１３及び立ち上がり壁６２が腐食するのを抑制することができる。 The rising wall 62 has two first wall pieces 63 and two second wall pieces 64 . The end plate member 13 and the two first wall pieces 63, and the end plate member 12 and the two second wall pieces 64 are bent in a U shape as a whole. Therefore, the rising wall 62 can be configured by using the end plate member 13 and the two first wall pieces 63 and the end plate member 12 and the two second wall pieces 64 having the same configuration.
The end plates 12 and 13 and the rising wall 62 on the outside of the first header 10A (heat exchanger 61) are subjected to anti-corrosion treatment. Therefore, when rainwater or the like adheres to the end plate members 12 and 13 and the rising wall 62 from the outside of the first header 10A, corrosion of the end plate members 12 and 13 and the rising wall 62 due to the rainwater or the like is suppressed. be able to.

なお、端部板材１２，１３において、２つの第１壁片６３及び２つの第２壁片６４が設けられる位置は限定されない。例えば、２つの第１壁片６３及び２つの第２壁片６４が端部板材１２に設けられてもよい。
前記板状の部材において、第２主面に耐食処理層が形成されなくてもよい。 In addition, the positions where the two first wall pieces 63 and the two second wall pieces 64 are provided in the end plate members 12 and 13 are not limited. For example, two first wall pieces 63 and two second wall pieces 64 may be provided on the end plate 12 .
In the plate-like member, the corrosion-resistant layer may not be formed on the second main surface.

（第３の実施形態）
次に、本発明の第３実施形態について図８から図１０を参照しながら説明するが、前記実施形態と同一の部位には同一の符号を付してその説明は省略し、異なる点についてのみ説明する。なお、後述する図の一部では、前記実施形態から形状を変更した部分のみに符号を付している。
図８に示すように、本実施形態の熱交換器７１の第１ヘッダ１０Ｂは、第２の実施形態の熱交換器６１の第１ヘッダ１０Ａにおける中間板材１１に代えて、第１中間板材（中間板材）７２、第２中間板材（中間板材）１１Ａ、及び仕切り板材７３を持つ。
第１中間板材７２、仕切り板材７３、及び第２中間板材１１Ａは、端部板材１２と端部板材１３との間に－Ｘ側から＋Ｘ側に向かってこの順で配置される。すなわち、仕切り板材７３は、第１中間板材７２と第２中間板材１１Ａとの間に挟まれる。
例えば、第２中間板材１１Ａは、中間板材１１と同一の構成である。 (Third embodiment)
Next, a third embodiment of the present invention will be described with reference to FIGS. 8 to 10. Parts that are the same as those of the above embodiment are denoted by the same reference numerals, and description thereof will be omitted. explain. It should be noted that in some of the drawings described later, reference numerals are given only to portions whose shape is changed from the above-described embodiment.
As shown in FIG. 8, the first header 10B of the heat exchanger 71 of the present embodiment has a first intermediate plate member ( It has an intermediate plate member) 72, a second intermediate plate member (intermediate plate member) 11A, and a partition plate member 73.
The first intermediate plate member 72, the partition plate member 73, and the second intermediate plate member 11A are arranged in this order between the end plate members 12 and 13 from the -X side to the +X side. That is, the partition plate member 73 is sandwiched between the first intermediate plate member 72 and the second intermediate plate member 11A.
For example, the second intermediate plate member 11A has the same configuration as the intermediate plate member 11 .

例えば、第１中間板材７２は、中間板材１１の第１貫通孔部２１Ｃ、筒部１７Ｃ、及び鍔部１８Ｃに代えて、第１貫通孔部２１Ｆ、筒部１７Ｆ、及び鍔部１８Ｆを持つ。
第１貫通孔部２１Ｆは、中間板材１１の板材本体１６において第１貫通孔部２１Ｃが形成される位置に形成される。第１貫通孔部２１Ｆは、Ｘ方向に見たときにＴ字状である。第１中間板材７２の第１貫通孔部２１Ｆの形状、及び第２中間板材１１Ａの第１貫通孔部２１Ｃの形状は、互いに異なる。第１中間板材７２の第１貫通孔部２１Ｆの外形は、第２中間板材１１Ａの第１貫通孔部２１Ｃの外形よりも小さい。
筒部１７Ｆは、板材本体１６における第１貫通孔部２１Ｆの周縁部からＸ方向の＋Ｘ側に立ち上がる。鍔部１８Ｆは、筒部１７Ｆが立ち上がる先端部から、筒部１７Ｆの径方向外側に、筒部１７Ｆの全周にわたって突出する。
板材本体１６から筒部１７Ｆ及び鍔部１８Ｆが全体として＋Ｘ側に立ち上がる長さ、及び板材本体１６から筒部１７Ａ及び鍔部１８Ａが全体として＋Ｘ側に立ち上がる長さは、互いに同等である。 For example, the first intermediate plate member 72 has a first through hole portion 21F, a tubular portion 17F, and a flange portion 18F instead of the first through hole portion 21C, the tubular portion 17C, and the flange portion 18C of the intermediate plate member 11 .
The first through hole portion 21</b>F is formed at a position where the first through hole portion 21</b>C is formed in the plate material body 16 of the intermediate plate member 11 . The first through hole portion 21F is T-shaped when viewed in the X direction. The shape of the first through-hole portion 21F of the first intermediate plate member 72 and the shape of the first through-hole portion 21C of the second intermediate plate member 11A are different from each other. The outer shape of the first through-hole portion 21F of the first intermediate plate member 72 is smaller than the outer shape of the first through-hole portion 21C of the second intermediate plate member 11A.
The cylindrical portion 17F rises from the periphery of the first through-hole portion 21F in the plate material body 16 to the +X side in the X direction. The collar portion 18F protrudes radially outwardly of the cylindrical portion 17F from the rising tip portion of the cylindrical portion 17F over the entire circumference of the cylindrical portion 17F.
The total length of the cylindrical portion 17F and the collar portion 18F rising from the plate body 16 to the +X side and the total length of the cylindrical portion 17A and the collar portion 18A rising from the plate body 16 to the +X side are equal to each other.

仕切り板材７３は、Ｘ方向に見たときに矩形状を呈する板状である。仕切り板材７３には、複数の第２貫通孔部７５Ａ～７５Ｅが形成される。
第２貫通孔部７５Ａ，７５Ｂ，７５Ｄ，７５Ｅは、前記第１貫通孔部２１Ａ，２１Ｂ，２１Ｄ，２１Ｅと同様にそれぞれ形成される。
仕切り板材７３の第２貫通孔部７５Ｃは、第１中間板材７２の第１貫通孔部２１Ｆと同一形状である。Ｘ方向に見たときに、第２貫通孔部７５Ｃは、第１中間板材７２の第１貫通孔部２１Ｆに重なる。Ｘ方向に見たときに、第２貫通孔部７５Ｃ及び第１貫通孔部２１Ｆは、第２中間板材１１Ａの第１貫通孔部２１Ｃの内周縁内にそれぞれ配置される。ここで言う内周縁内とは、内周縁の内側だけでなく、内周縁上も含む意味である。
第１中間板材７２の筒部１７Ｆは、第２中間板材１１Ａの板材本体１６に向かって延びて、仕切り板材７３に鍔部１８Ｆを介して接触する。 The partition plate member 73 has a rectangular plate shape when viewed in the X direction. The partition plate member 73 is formed with a plurality of second through holes 75A to 75E.
The second through holes 75A, 75B, 75D and 75E are formed in the same manner as the first through holes 21A, 21B, 21D and 21E.
The second through hole portion 75C of the partition plate member 73 has the same shape as the first through hole portion 21F of the first intermediate plate member 72 . The second through hole portion 75C overlaps the first through hole portion 21F of the first intermediate plate member 72 when viewed in the X direction. When viewed in the X direction, the second through hole portion 75C and the first through hole portion 21F are arranged within the inner peripheral edge of the first through hole portion 21C of the second intermediate plate member 11A. The term "within the inner peripheral edge" as used herein means not only the inner side of the inner peripheral edge, but also the area on the inner peripheral edge.
The cylindrical portion 17F of the first intermediate plate member 72 extends toward the plate member main body 16 of the second intermediate plate member 11A and contacts the partition plate member 73 via the collar portion 18F.

以上のように構成された熱交換器７１では、図９に示すように、第１中間板材７２の鍔部１８Ｆと、仕切り板材７３における第２貫通孔部７５Ｃの周縁部との間から、冷媒が第１ヘッダ１０Ｂ（熱交換器７１）の外部に漏れ難い。仕切り板材７３における第２貫通孔部７５Ｃの周縁部と、第２中間板材１１Ａの板材本体１６における第１貫通孔部２１Ｃの周縁部との間から、冷媒が第１ヘッダ１０Ｂの外部に漏れ難い。 In the heat exchanger 71 configured as described above, as shown in FIG. 9, the refrigerant flows from between the flange portion 18F of the first intermediate plate member 72 and the peripheral portion of the second through-hole portion 75C of the partition plate member 73. is less likely to leak to the outside of the first header 10B (heat exchanger 71). The coolant is less likely to leak outside the first header 10B from between the peripheral edge portion of the second through hole portion 75C in the partition plate member 73 and the peripheral edge portion of the first through hole portion 21C in the plate body 16 of the second intermediate plate member 11A. .

一方で、本実施形態の熱交換器７１に対して、仕切り板材７３を備えない変形例の熱交換器８１を、図１０を用いて説明する。
比較例の熱交換器８１では、第１中間板材７２の鍔部１８Ｆと、第２中間板材１１Ａの板材本体１６における第１貫通孔部２１Ｃの周縁部との間に隙間Ｓ３が形成される。この隙間Ｓ３を通して、冷媒が第１ヘッダの外部に漏れる。 On the other hand, a modified heat exchanger 81 that does not include the partition plate member 73 in contrast to the heat exchanger 71 of the present embodiment will be described with reference to FIG. 10 .
In the heat exchanger 81 of the comparative example, a gap S3 is formed between the flange portion 18F of the first intermediate plate member 72 and the peripheral portion of the first through hole portion 21C in the plate member body 16 of the second intermediate plate member 11A. Refrigerant leaks to the outside of the first header through this gap S3.

以上説明したように、本実施形態の熱交換器７１では、熱交換器７１の製造コストを低減させ、内部に充填される冷媒の熱干渉を抑制しつつ、冷媒の漏れを容易に確認することができる。
さらに、第１，２中間板材７２，１１Ａの第１貫通孔部２１Ｆ，２１Ｃ同士が互いに異なる形状であっても、例えば、熱交換器７１内に充填された冷媒が、熱交換器７１の外部に漏れるのを抑制することができる。そして、第１貫通孔部２１Ｆ，２１Ｃの形状を調節することにより、熱交換器７１の圧力損失を調節することができる。 As described above, in the heat exchanger 71 of the present embodiment, the manufacturing cost of the heat exchanger 71 can be reduced, the heat interference of the refrigerant charged inside can be suppressed, and leakage of the refrigerant can be easily confirmed. can be done.
Furthermore, even if the first through-hole portions 21F and 21C of the first and second intermediate plate members 72 and 11A have different shapes, for example, the refrigerant filled in the heat exchanger 71 may can be prevented from leaking into By adjusting the shape of the first through-hole portions 21F and 21C, the pressure loss of the heat exchanger 71 can be adjusted.

（第４の実施形態）
次に、本発明の第４実施形態について図１１及び図１２を参照しながら説明するが、前記実施形態と同一の部位には同一の符号を付してその説明は省略し、異なる点についてのみ説明する。
図１１及び図１２に示すように、本実施形態の熱交換器８１の第１ヘッダ１０Ｃは、第３の実施形態の熱交換器７１の第１ヘッダ１０Ｂの各構成に加えて、第３中間板材（中間板材）１１Ｂを持つ。なお、図１１では、説明の便宜のため、第１ヘッダ１０Ｃの各構成のうち＋Ｙ側の部分のみを示す。
第３中間板材１１Ｂは、第２中間板材１１Ａと同一の構成である。第３中間板材１１Ｂは、端部板材１２と第１中間板材７２との間に配置される。 (Fourth embodiment)
Next, a fourth embodiment of the present invention will be described with reference to FIGS. 11 and 12. Parts that are the same as those of the above embodiment are denoted by the same reference numerals, and description thereof will be omitted. explain.
As shown in FIGS. 11 and 12, the first header 10C of the heat exchanger 81 of the present embodiment includes each configuration of the first header 10B of the heat exchanger 71 of the third embodiment, in addition to the third intermediate It has a plate (intermediate plate) 11B. For convenience of explanation, FIG. 11 shows only the +Y side portion of each configuration of the first header 10C.
The third intermediate plate member 11B has the same configuration as the second intermediate plate member 11A. The third intermediate plate member 11B is arranged between the end plate member 12 and the first intermediate plate member 72 .

図１０に示すように、第１ヘッダ１０Ｃが仕切り板材７３を備えない場合には、第１中間板材７２の鍔部１８Ｆと、第２中間板材１１Ａの板材本体１６における第１貫通孔部２１Ｃの周縁部との間に前記隙間Ｓ３が形成される。このため、第１ヘッダ１０Ｃの外部に冷媒を漏らさないために、仕切り板材７３が必要である。
一方で、図１１及び図１２に示すように、Ｘ方向に見たときに、第１中間板材７２の第１貫通孔部２１Ｆは、第３中間板材１１Ｂの第１貫通孔部２１Ｃの内周縁内に配置される。このため、第３中間板材１１Ｂの鍔部１８Ｃは第１中間板材７２の板材本体１６に全周にわたって接触する。このため、第３中間板材１１Ｂと第１中間板材７２との間に、仕切り板材７３は不要である。 As shown in FIG. 10, when the first header 10C does not include the partition plate member 73, the flange portion 18F of the first intermediate plate member 72 and the first through hole portion 21C of the plate member main body 16 of the second intermediate plate member 11A are separated. The gap S3 is formed between the peripheral portion. Therefore, the partition plate member 73 is necessary to prevent the coolant from leaking outside the first header 10C.
On the other hand, as shown in FIGS. 11 and 12, when viewed in the X direction, the first through hole portion 21F of the first intermediate plate member 72 is aligned with the inner peripheral edge of the first through hole portion 21C of the third intermediate plate member 11B. placed within. Therefore, the flange portion 18C of the third intermediate plate member 11B contacts the plate member main body 16 of the first intermediate plate member 72 over the entire circumference. Therefore, the partition plate member 73 is not required between the third intermediate plate member 11B and the first intermediate plate member 72 .

以上説明した少なくともひとつの実施形態によれば、筒部１７Ａ～１７Ｆを持つことにより、製造コストを低減させ、内部に充填される冷媒の熱干渉を抑制しつつ、冷媒の漏れを容易に確認することができる。 According to at least one embodiment described above, by having the tubular portions 17A to 17F, the manufacturing cost can be reduced, the heat interference of the refrigerant filled inside can be suppressed, and the leakage of the refrigerant can be easily confirmed. be able to.

本発明のいくつかの実施形態を説明したが、これらの実施形態は、例として提示したものであり、発明の範囲を限定することは意図していない。これら実施形態は、その他の様々な形態で実施されることが可能であり、発明の要旨を逸脱しない範囲で、種々の省略、置き換え、変更を行うことができる。これら実施形態やその変形は、発明の範囲や要旨に含まれると同様に、特許請求の範囲に記載された発明とその均等の範囲に含まれるものである。 While several embodiments of the invention have been described, these embodiments have been presented by way of example and are not intended to limit the scope of the invention. These embodiments can be implemented in various other forms, and various omissions, replacements, and modifications can be made without departing from the scope of the invention. These embodiments and their modifications are included in the scope and spirit of the invention as well as the scope of the invention described in the claims and equivalents thereof.

４，６１，７１，８１…室外熱交換器（熱交換器）、６…室内熱交換器（熱交換器）、１０，１０Ａ，１０Ｂ，１０Ｃ…第１ヘッダ（ヘッダ）、１１…中間板材、１１Ａ…第２中間板材（中間板材）、１１Ｂ…第３中間板材（中間板材）、１２，１３，３２，３３…端部板材、１２ａ，１３ａ…第１辺部、１２ｂ，１３ｂ…第２辺部、１６…板材本体、１７Ａ～１７Ｆ…筒部、１８Ａ～１８Ｆ…鍔部、２１Ａ～２１Ｆ…第１貫通孔部、３０…第２ヘッダ（ヘッダ）、６２…立ち上がり壁、６３…第１壁片、６４…第２壁片、７２…第１中間板材（中間板材）、７３…仕切り板材、７５Ａ～７５Ｅ…第２貫通孔部、Ｘ…方向（第１方向。中間板材の厚さ方向） 4, 61, 71, 81... outdoor heat exchanger (heat exchanger), 6... indoor heat exchanger (heat exchanger), 10, 10A, 10B, 10C... first header (header), 11... intermediate plate, 11A... second intermediate plate (intermediate plate), 11B... third intermediate plate (intermediate plate), 12, 13, 32, 33... end plate, 12a, 13a... first side, 12b, 13b... second side Parts 16... Plate main body 17A to 17F... Cylindrical part 18A to 18F... Collar part 21A to 21F... First through hole part 30... Second header (header) 62... Rising wall 63... First wall Piece 64 Second wall piece 72 First intermediate plate (intermediate plate) 73 Partition plate 75A to 75E Second through hole X direction (first direction; thickness direction of intermediate plate)

Claims (8)

第１方向に延び、冷媒が流通する熱交換チューブと、
前記熱交換チューブの前記第１方向の端部に接続され、中間板材と、前記中間板材を前記中間板材の厚さ方向に挟む２つの端部板材とを有し、前記中間板材にて冷媒空間流路を形成するヘッダと、
を備える熱交換器において、
前記中間板材は、
第１貫通孔部が形成された板材本体と、
前記板材本体における前記第１貫通孔部の周縁部から前記厚さ方向に立ち上がり、前記２つの端部板材のうちの一方、又は他の前記中間板材の前記板材本体に接触する筒部と、
を有する、熱交換器。 a heat exchange tube extending in a first direction and through which a refrigerant flows;
An intermediate plate connected to the end of the heat exchange tube in the first direction, and two end plates sandwiching the intermediate plate in the thickness direction of the intermediate plate, the intermediate plate forming a refrigerant space. a header forming a flow path;
In a heat exchanger comprising
The intermediate plate material is
a plate body in which a first through hole is formed;
a cylindrical portion that rises in the thickness direction from the peripheral edge portion of the first through-hole portion in the plate body and contacts one of the two end plate members or the plate body of the other intermediate plate;
A heat exchanger. 前記中間板材は、前記筒部が立ち上がる先端部から径方向外側に突出する鍔部を有し、
前記鍔部は、前記２つの端部板材のうちの一方、又は他の前記中間板材の前記板材本体に接触する、請求項１に記載の熱交換器。 The intermediate plate member has a collar portion that protrudes radially outward from a tip portion at which the cylindrical portion rises,
2. The heat exchanger according to claim 1, wherein the collar contacts the plate body of one of the two end plates or the other of the intermediate plates. 前記ヘッダは、前記２つの端部板材のうちの一方の外周縁と他方の外周縁とを、前記２つの端部板材の全周にわたって連結する立ち上がり壁を有する、請求項１又は２に記載の熱交換器。 3. The header according to claim 1 or 2, wherein the header has a rising wall that connects the outer peripheral edge of one of the two end plate members and the outer peripheral edge of the other over the entire circumference of the two end plate members. Heat exchanger. 前記２つの端部板材は、前記厚さ方向に見たときにそれぞれ矩形状を呈し、
前記立ち上がり壁は、
前記２つの端部板材のうちの一方における前記厚さ方向に見たときの２つの第１辺部に設けられ、前記厚さ方向に延びて、前記２つの端部板材のうちの他方の外周縁に達する２つの第１壁片と、
前記２つの端部板材のうちの前記他方における前記厚さ方向に見たときの、前記２つの第１辺部に隣り合う２つの第２辺部に設けられ、前記厚さ方向に延びて、前記２つの端部板材のうちの前記一方の外周縁に達する２つの第２壁片と、
を有する、請求項３に記載の熱交換器。 The two end plates each exhibit a rectangular shape when viewed in the thickness direction,
The rising wall is
provided at two first side portions of one of the two end plates when viewed in the thickness direction, extending in the thickness direction, and extending to the outside of the other of the two end plates two first wall pieces reaching the periphery;
Provided on two second side portions adjacent to the two first side portions when viewed in the thickness direction of the other of the two end plates, and extending in the thickness direction, two second wall pieces reaching the outer peripheral edge of the one of the two end plates;
4. The heat exchanger of claim 3, comprising: 前記２つの端部板材及び前記立ち上がり壁における外側の面には、耐食処理が施されている、請求項３又は４に記載の熱交換器。 5. The heat exchanger according to claim 3 or 4, wherein outer surfaces of said two end plates and said rising wall are subjected to anti-corrosion treatment. 前記ヘッダは、前記中間板材として、互いに同一形状の複数の前記中間板材を有し、
前記複数の前記中間板材における前記筒部は、前記厚さ方向に並べて配置される、請求項１から５のいずれか一項に記載の熱交換器。 the header includes a plurality of intermediate plate members having the same shape as the intermediate plate members;
The heat exchanger according to any one of claims 1 to 5, wherein the cylindrical portions of the plurality of intermediate plate members are arranged side by side in the thickness direction. 前記ヘッダは、前記中間板材として、前記第１貫通孔部の形状が互いに異なる第１中間板材及び第２中間板材を有し、
前記第１中間板材と前記第２中間板材との間に挟まれ、第２貫通孔部が形成された仕切り板材を備え、
前記厚さ方向に見たときに、前記第１中間板材の前記第１貫通孔部は、前記第２中間板材の前記第１貫通孔部の内周縁内に配置され、
前記第１中間板材の前記筒部は、前記第２中間板材の前記板材本体に向かって延びて、前記仕切り板材に接触し、
前記第２貫通孔部は、前記第１中間板材の前記第１貫通孔部と同一形状である、請求項１から６のいずれか一項に記載の熱交換器。 the header includes, as the intermediate plate members, a first intermediate plate member and a second intermediate plate member having first through-hole portions with different shapes,
A partition plate sandwiched between the first intermediate plate and the second intermediate plate and having a second through hole formed thereon,
When viewed in the thickness direction, the first through-hole portion of the first intermediate plate member is arranged within the inner peripheral edge of the first through-hole portion of the second intermediate plate member,
the cylindrical portion of the first intermediate plate extends toward the plate body of the second intermediate plate and contacts the partition plate;
The heat exchanger according to any one of claims 1 to 6, wherein the second through hole has the same shape as the first through hole of the first intermediate plate. 請求項１から７のいずれか一項に記載の熱交換器を備える冷凍サイクル装置。 A refrigeration cycle apparatus comprising the heat exchanger according to any one of claims 1 to 7.
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