JP6435220B2 - Air conditioner outdoor unit - Google Patents

Air conditioner outdoor unit Download PDF

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JP6435220B2
JP6435220B2 JP2015057303A JP2015057303A JP6435220B2 JP 6435220 B2 JP6435220 B2 JP 6435220B2 JP 2015057303 A JP2015057303 A JP 2015057303A JP 2015057303 A JP2015057303 A JP 2015057303A JP 6435220 B2 JP6435220 B2 JP 6435220B2
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heat transfer
outdoor
heat exchange
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transfer tubes
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JP2016176646A (en
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高藤　亮一
亮一 高藤
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Hitachi Johnson Controls Air Conditioning Inc
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本発明は、空気調和機の室外機に関する。   The present invention relates to an outdoor unit of an air conditioner.

従来、扁平管を用いた熱交換器としては、複数の扁平管が一定間隔で水平に配置されたものが提案されている。このような熱交換器では、扁平管の平面部が水平であり、蒸発器として作用している際に凝縮水が滞留し易くなり、滞留した凝縮水が平面部に付着することで空気と冷媒との熱交換が阻害されて蒸発性能が低下したり、また着霜し易くなるという問題があった。このため、扁平管を傾斜させることにより、扁平管の平面部に水滴が滞留し難いようにした技術が提案されている（例えば、特許文献１参照）。   Conventionally, a heat exchanger using flat tubes has been proposed in which a plurality of flat tubes are arranged horizontally at regular intervals. In such a heat exchanger, the flat portion of the flat tube is horizontal, and the condensed water tends to stay when acting as an evaporator, and the accumulated condensed water adheres to the flat portion, so that air and refrigerant are retained. There was a problem that the heat exchange with the water was hindered and the evaporation performance was lowered, and frost formation was easy. For this reason, the technique which made it difficult for a water droplet to stay in the plane part of a flat tube by inclining a flat tube is proposed (for example, refer patent document 1).

特開２０１０−１４３２９号公報JP 2010-14329 A

しかしながら、特許文献１に記載の技術では、凝縮水の排水性については確保できるものの、送風機の形態による風速分布については考慮されていなかった。   However, in the technique described in Patent Document 1, although the drainage of condensed water can be ensured, the wind speed distribution due to the form of the blower has not been considered.

本発明の目的は、熱交換器の排水性を確保しつつ、さらなる性能向上を図ることが可能な空気調和機の室外機を提供するものである。   The objective of this invention is providing the outdoor unit of the air conditioner which can aim at the further performance improvement, ensuring the drainage property of a heat exchanger.

本発明は、上下方向に複数段に配置された伝熱管およびフィンを含む室外熱交換手段と、前記室外熱交換手段の下流側に配置されるプロペラファンを含む室外送風手段と、を備え、前記室外熱交換手段は、前記プロペラファンと対向して配置されるとともに、前記フィンが前記プロペラファンの中心軸に直交する上下方向に直線状に延び、前記伝熱管は扁平形状であり、かつ、前記プロペラファンの中心軸を通る仮想水平面に対して上方に位置する前記伝熱管のすべては下流側が前記仮想水平面を向くように傾斜状態で配置されていることを特徴とする。 The present invention includes an outdoor heat exchanger means including a heat transfer tube and fins arranged in a plurality of stages in the vertical direction, and the outdoor air blowing means including a propeller fan disposed on the downstream side of the outdoor heat exchange means, said The outdoor heat exchange means is disposed opposite to the propeller fan, the fins extend linearly in a vertical direction perpendicular to the central axis of the propeller fan, the heat transfer tube has a flat shape, and All of the heat transfer tubes positioned above the virtual horizontal plane passing through the central axis of the propeller fan are arranged in an inclined state so that the downstream side faces the virtual horizontal plane.

本発明によれば、熱交換器の排水性を確保しつつ、さらなる性能向上を図ることが可能な空気調和機の室外機を提供できる。   ADVANTAGE OF THE INVENTION According to this invention, the outdoor unit of the air conditioner which can aim at the further performance improvement can be provided, ensuring the drainage property of a heat exchanger.

本発明の実施形態に係る空気調和機を示す構成図である。It is a lineblock diagram showing an air harmony machine concerning an embodiment of the present invention. 室外熱交換器の概略構造を示す斜視図である。It is a perspective view which shows schematic structure of an outdoor heat exchanger. 第１実施形態における室外機の内部構造を示す側面図である。It is a side view which shows the internal structure of the outdoor unit in 1st Embodiment. 図３の熱交換部の一部拡大図である。FIG. 4 is a partially enlarged view of the heat exchange unit of FIG. 3. 第１実施形態におけるファン回転時に形成される空気の流れ図である。It is a flowchart of the air formed at the time of fan rotation in a 1st embodiment. 第２実施形態における室外機の内部構造を示す側面図である。It is a side view which shows the internal structure of the outdoor unit in 2nd Embodiment. 第２実施形態における伝熱管の周囲に形成される空気の流れを示し、（ａ）は千鳥状に配置された場合、（ｂ）はタンデム状に配置された場合である。The flow of the air formed around the heat exchanger tube in 2nd Embodiment is shown, (a) is a case where it arrange | positions in zigzag form, (b) is a case where it arrange | positions in tandem form. 第３実施形態における室外機の内部構造を示す側面図である。It is a side view which shows the internal structure of the outdoor unit in 3rd Embodiment. 第４実施形態における室外機の内部構造を示す側面図である。It is a side view which shows the internal structure of the outdoor unit in 4th Embodiment. 第５実施形態における室外機の内部構造を示す側面図である。It is a side view which shows the internal structure of the outdoor unit in 5th Embodiment. 第６実施形態における室外機の内部構造を示す側面図である。It is a side view which shows the internal structure of the outdoor unit in 6th Embodiment. 伝熱管の変形例を示す縦断面図である。It is a longitudinal cross-sectional view which shows the modification of a heat exchanger tube.

以下、本発明を実施するための形態（以下「実施形態」という）について、適宜図面を参照しながら詳細に説明する。なお、説明の便宜上、各実施形態で共通する部材については同一の符号を付して、重複する説明を省略する。なお、図１１に示す第６実施形態については、参考形態とする。
図１は、本発明の実施形態に係る空気調和機を示す構成図である。
図１に示すように、空気調和機１００は、室外機（室外ユニット）８と室内機（室内ユニット）９とが、接続配管１０，１１によって接続されることで冷房および暖房が可能な冷凍サイクルを構成している。室外機８は、圧縮機１と、流路切替手段としての四方弁２と、室外熱交換器（熱交換部）３と、冷暖房運転用の絞り装置（流量制御弁）４と、室外送風手段６と、を備えて構成されている。室内機９は、室内熱交換器５と、貫流ファンなどの室内送風手段７と、を備えて構成されている。 Hereinafter, modes for carrying out the present invention (hereinafter referred to as “embodiments”) will be described in detail with reference to the drawings as appropriate. For convenience of explanation, members common to the embodiments are denoted by the same reference numerals, and redundant description is omitted. In addition, about 6th Embodiment shown in FIG. 11, it is set as a reference form.
FIG. 1 is a configuration diagram illustrating an air conditioner according to an embodiment of the present invention.
As shown in FIG. 1, an air conditioner 100 includes an outdoor unit (outdoor unit) 8 and an indoor unit (indoor unit) 9 connected by connecting pipes 10 and 11 so that cooling and heating can be performed. Is configured. The outdoor unit 8 includes a compressor 1, a four-way valve 2 as a flow path switching unit, an outdoor heat exchanger (heat exchange unit) 3, a throttle device (flow control valve) 4 for air conditioning operation, and an outdoor air blowing unit. 6. The indoor unit 9 includes an indoor heat exchanger 5 and indoor air blowing means 7 such as a cross-flow fan.

空気調和機１００において冷房運転する場合には、破線矢印で示すように、圧縮機１で圧縮された高温・高圧のガス冷媒が四方弁２を通って室外熱交換器３に流れ、外気（空気）と熱交換することで凝縮し、高圧の液冷媒となる。液冷媒は、絞り装置４の作用で減圧され、低温低圧の気液二相状態となり、接続配管１１を通じて室内機９に流れる。室内機９に入った冷媒は、室内熱交換器５で室内空気の熱と熱交換することで蒸発する。室内熱交換器５で蒸発した冷媒は、接続配管１０を通じて、室外機８に戻り、四方弁２を通って再び圧縮機１で圧縮される。   When the air conditioner 100 performs a cooling operation, as indicated by a broken-line arrow, the high-temperature / high-pressure gas refrigerant compressed by the compressor 1 flows to the outdoor heat exchanger 3 through the four-way valve 2, and the outside air (air ) And heat exchange to become a high-pressure liquid refrigerant. The liquid refrigerant is depressurized by the action of the expansion device 4, becomes a low-temperature low-pressure gas-liquid two-phase state, and flows to the indoor unit 9 through the connection pipe 11. The refrigerant that has entered the indoor unit 9 is evaporated by exchanging heat with the heat of the indoor air in the indoor heat exchanger 5. The refrigerant evaporated in the indoor heat exchanger 5 returns to the outdoor unit 8 through the connection pipe 10, passes through the four-way valve 2, and is compressed again by the compressor 1.

空気調和機１００において暖房運転する場合には、実線矢印で示すように、圧縮機１で圧縮された高温・高圧のガス冷媒が四方弁２および接続配管１０を通って室内機９に流れる。室内機９に入ったガス冷媒は、室内熱交換器５で室内空気と熱交換することで凝縮し、高圧の液冷媒となる。高圧の液冷媒は、接続配管１１を通って室外機８に流れる。室外機８に入った高圧の液冷媒は、絞り装置４の作用で減圧され、低温低圧の気液二相状態となり、室外熱交換器３に流れ、室外空気の熱と熱交換することで蒸発し、ガス冷媒となる。室外熱交換器３でガス状となった冷媒は、四方弁２を通って再び圧縮機１で圧縮される。   When heating operation is performed in the air conditioner 100, the high-temperature and high-pressure gas refrigerant compressed by the compressor 1 flows to the indoor unit 9 through the four-way valve 2 and the connection pipe 10 as indicated by solid arrows. The gas refrigerant that has entered the indoor unit 9 is condensed by exchanging heat with the indoor air in the indoor heat exchanger 5 and becomes high-pressure liquid refrigerant. The high-pressure liquid refrigerant flows to the outdoor unit 8 through the connection pipe 11. The high-pressure liquid refrigerant entering the outdoor unit 8 is depressurized by the action of the expansion device 4, becomes a low-temperature low-pressure gas-liquid two-phase state, flows to the outdoor heat exchanger 3, and evaporates by exchanging heat with the heat of the outdoor air. And it becomes a gas refrigerant. The refrigerant that has become gaseous in the outdoor heat exchanger 3 passes through the four-way valve 2 and is compressed again by the compressor 1.

図２は、室外熱交換器の概略構造を示す斜視図である。
図２に示すように、室外熱交換器３は、クロスフィンチューブ型であり、板厚方向に所定の間隔を置いて設けられた複数の板状フィン（冷却フィン）１２と、各板状フィン１２を板厚方向に貫通し、所定間隔で上下方向に複数段（図２では、１０段）に配置された伝熱管１３と、を含む熱交換部３Ｓ，３Ｓを備えている。また、熱交換部３Ｓ，３Ｓは、空気の流れ方向Ａに沿って２列に配置されて構成されている。 FIG. 2 is a perspective view showing a schematic structure of the outdoor heat exchanger.
As shown in FIG. 2, the outdoor heat exchanger 3 is a cross fin tube type, a plurality of plate fins (cooling fins) 12 provided at predetermined intervals in the plate thickness direction, and each plate fin. 12 is provided with heat exchange parts 3S and 3S including heat transfer tubes 13 that penetrate through the sheet 12 in the plate thickness direction and are arranged in a plurality of stages (10 stages in FIG. 2) in the vertical direction at a predetermined interval. Moreover, the heat exchange parts 3S and 3S are arranged in two rows along the air flow direction A.

板状フィン１２と伝熱管１３とは、板状フィン１２に挿通された伝熱管１３を液圧または機械的に拡管することにより密着している。なお、図示省略しているが、伝熱管１３の端部には、他の伝熱管１３の端部とリターンベンドを介して溶接などで接続され、冷媒流路を構成している。また、伝熱管１３の段数は、１０段に限定されるものではなく、９段以下であっても、１１段以上であってもよい。   The plate-like fins 12 and the heat transfer tubes 13 are in close contact with each other by expanding the heat transfer tubes 13 inserted through the plate-like fins 12 either hydraulically or mechanically. Although not shown, the end of the heat transfer tube 13 is connected to the end of the other heat transfer tube 13 by welding or the like via a return bend to constitute a refrigerant flow path. Further, the number of stages of the heat transfer tubes 13 is not limited to 10 stages, and may be 9 stages or less or 11 stages or more.

例えば、板状フィン１２は、アルミニウム合金などの金属製の薄板（例えば、厚さ０．１ｍｍ）によって形成されている。伝熱管１３は、アルミニウム合金などの金属製であり、伝熱管１３の一部である上下に平行に配置された平面部１３ａ，１３ｂと、長手方向の両端に配置されて平面部１３ａ，１３ｂ同士を繋ぐ曲面部１３ｃ，１３ｄと、を備えた扁平形状である。また、伝熱管１３は、内部が複数の隔壁で区画された流路を備えている。   For example, the plate-like fins 12 are formed of a thin metal plate (for example, a thickness of 0.1 mm) such as an aluminum alloy. The heat transfer tube 13 is made of a metal such as an aluminum alloy. The heat transfer tubes 13 are part of the heat transfer tube 13 and are arranged in parallel in the vertical direction, and the flat portions 13a and 13b are arranged at both ends in the longitudinal direction. It is a flat shape provided with curved surface portions 13c and 13d that connect the two. In addition, the heat transfer tube 13 includes a flow path that is internally partitioned by a plurality of partition walls.

なお、室外熱交換器３の構成としては、図２に示すような板状フィン１２と伝熱管１３との組み合わせに限定されるものではなく、扁平管（伝熱管１３）と扁平管（伝熱管１３）との間に、波型（ひだ状）のフィンを溶着したものでもよく、また櫛歯状に切り欠かれた板状フィンに伝熱管１３を挿入して溶着したものであってもよい。   The configuration of the outdoor heat exchanger 3 is not limited to the combination of the plate-like fins 12 and the heat transfer tubes 13 as shown in FIG. 2, but a flat tube (heat transfer tube 13) and a flat tube (heat transfer tube). 13) may be one in which corrugated (pleated) fins are welded, or may be one in which the heat transfer tubes 13 are inserted into and welded to plate-like fins notched in a comb shape. .

（第１実施形態）
図３は、第１実施形態における室外機の内部構造を示す側面図、図４は、図３の熱交換部の一部拡大図である。なお、図３では、圧縮機１、四方弁２および絞り装置４の図示を省略している。また、図４（ａ）〜（ｇ）は、熱交換部３Ａのプロペラファン６０の中心軸Ｏよりも上側の伝熱管１３について、中心軸Ｏに近い側から順に示したものである。 (First embodiment)
FIG. 3 is a side view showing the internal structure of the outdoor unit in the first embodiment, and FIG. 4 is a partially enlarged view of the heat exchange section of FIG. 3, illustration of the compressor 1, the four-way valve 2, and the expansion device 4 is omitted. 4A to 4G show the heat transfer tubes 13 on the upper side of the central axis O of the propeller fan 60 of the heat exchange unit 3A in order from the side closer to the central axis O.

図３に示すように、室外機８は、室外熱交換器３（室外熱交換手段）および室外送風手段６が四角箱型の筺体２１内に収容されて構成されている。また、筺体２１内において、室外熱交換器３が後側（背面側）に配置され、室外送風手段６が前側（正面側）に配置されている。   As shown in FIG. 3, the outdoor unit 8 is configured such that an outdoor heat exchanger 3 (outdoor heat exchange means) and an outdoor air blowing means 6 are accommodated in a square box-type housing 21. Moreover, in the housing 21, the outdoor heat exchanger 3 is arrange | positioned at the rear side (back side), and the outdoor ventilation means 6 is arrange | positioned at the front side (front side).

室外送風手段６は、軸流ファンであるプロペラファン（送風機）６０およびベルマウス６１によって構成されている。プロペラファン６０は、回転中心に設けられた円筒状のボス６０ａと、このボス６０ａの周囲に設けられた複数枚の羽根６０ｂとによって構成され、図示しない電動機によって回転駆動される。ベルマウス６１は、プロペラファン６０の軸方向に沿う略円筒形状であり、羽根６０ｂの外周に沿って配置されている。 Chamber outside the blowing means 6 is constituted by a propeller fan (air blower) 60 and the bell mouth 61 is a axial fan. The propeller fan 60 includes a cylindrical boss 60a provided at the rotation center and a plurality of blades 60b provided around the boss 60a, and is rotated by an electric motor (not shown). The bell mouth 61 has a substantially cylindrical shape along the axial direction of the propeller fan 60, and is arranged along the outer periphery of the blade 60b.

室外熱交換器３は、プロペラファン６０と対向して配置されている。なお、室外熱交換器３の形状は、平板状のものに限定されず、Ｌ字状、コ字状など従来からある形状を採用することもできる。   The outdoor heat exchanger 3 is disposed to face the propeller fan 60. The shape of the outdoor heat exchanger 3 is not limited to a flat plate shape, and a conventional shape such as an L shape or a U shape can also be adopted.

また、室外熱交換器３は、熱交換部３Ａ，３Ｂが空気の流れ方向（図４参照）に沿って配置され、熱交換部３Ａの前面と熱交換部３Ｂの背面とが互いに接するように配置されている。また、室外熱交換器３は、プロペラファン６０の直径Ｒよりも上下方向に長く形成され、室外熱交換器３の上端３ａがプロペラファン６０の上端６０ｃの上方に位置し、室外熱交換器３の下端３ｂがプロペラファン６０の下端６０ｄの下方に位置している。また、図示していないが、室外熱交換器３は、プロペラファン６０の直径Ｒよりも左右方向（図３の紙面垂直方向）に長く形成されている。つまり、室外熱交換器３は、プロペラファン６０の軸方向からの平面視において、プロペラファン６０の全体が室外熱交換器３（熱交換部３Ａ，３Ｂ）に含まれるように配置されている。   Further, the outdoor heat exchanger 3 has the heat exchange units 3A and 3B arranged along the air flow direction (see FIG. 4) so that the front surface of the heat exchange unit 3A and the back surface of the heat exchange unit 3B are in contact with each other. Has been placed. The outdoor heat exchanger 3 is formed longer in the vertical direction than the diameter R of the propeller fan 60, the upper end 3 a of the outdoor heat exchanger 3 is positioned above the upper end 60 c of the propeller fan 60, and the outdoor heat exchanger 3 The lower end 3b of the propeller fan 60 is positioned below the lower end 60d of the propeller fan 60. Although not shown, the outdoor heat exchanger 3 is longer than the diameter R of the propeller fan 60 in the left-right direction (the direction perpendicular to the plane of FIG. 3). That is, the outdoor heat exchanger 3 is arranged so that the entire propeller fan 60 is included in the outdoor heat exchanger 3 (heat exchange units 3A and 3B) in a plan view from the axial direction of the propeller fan 60.

熱交換部３Ａにおいては、プロペラファン６０の中心軸Ｏを通る仮想水平面Ｓ（図３では、線状に図示）を基準にして、上側に複数段（図３では、７段）の伝熱管１３Ａ，１３Ｂ，１３Ｃ，１３Ｄ，１３Ｅ，１３Ｆ，１３Ｇが配置され、下側に複数段（図３では、７段）の伝熱管１３Ｈ，１３Ｉ，１３Ｊ，１３Ｋ，１３Ｌ，１３Ｍ，１３Ｎが配置されている。また、伝熱管１３Ａ〜１３Ｇ（１３Ｈ〜１３Ｎ）は、上下方向に等間隔に配置されている。   In the heat exchanging section 3A, a heat transfer tube 13A having a plurality of stages (seven stages in FIG. 3) on the upper side with reference to a virtual horizontal plane S (shown linearly in FIG. 3) passing through the central axis O of the propeller fan 60. , 13B, 13C, 13D, 13E, 13F, and 13G are arranged, and a plurality of stages (seven stages in FIG. 3) of heat transfer tubes 13H, 13I, 13J, 13K, 13L, 13M, and 13N are arranged on the lower side. . Further, the heat transfer tubes 13A to 13G (13H to 13N) are arranged at equal intervals in the vertical direction.

また、伝熱管１３Ａ〜１３Ｇは、長手方向の下流側Ｐ１（曲面部１３ｄ）が中心軸Ｏ側を向くように傾斜して配置される。換言すると、伝熱管１３Ａ〜１３Ｇは、空気吸込み側の曲面部１３ｃが上向きで、逆側の曲面部１３ｄが下向きとなるように、傾斜状態で配置される。   Further, the heat transfer tubes 13A to 13G are arranged to be inclined so that the downstream side P1 (curved surface portion 13d) in the longitudinal direction faces the central axis O side. In other words, the heat transfer tubes 13A to 13G are arranged in an inclined state so that the curved surface portion 13c on the air suction side faces upward and the curved surface portion 13d on the opposite side faces downward.

また、伝熱管１３Ｈ〜１３Ｎは、長手方向の下流側Ｐ２（曲面部１３ｄ）が中心軸Ｏ側を向くように傾斜して配置される。換言すると、伝熱管１３Ｈ〜１３Ｎは、空気吸込み側の曲面部１３ｃが下向きで、逆側の曲面部１３ｄが上向きとなるように、傾斜状態で配置される。   Further, the heat transfer tubes 13H to 13N are disposed so as to be inclined so that the downstream side P2 (curved surface portion 13d) in the longitudinal direction faces the central axis O side. In other words, the heat transfer tubes 13H to 13N are arranged in an inclined state so that the curved surface portion 13c on the air suction side faces downward and the curved surface portion 13d on the opposite side faces upward.

図４（ａ）〜（ｇ）に示すように、伝熱管１３Ａ〜１３Ｇの仮想水平面Ｓ（図３参照）に対する傾斜角度をそれぞれα１，α２，α３，α４，α５，α６，α７としたときに、α１＜α２＜α３＜α４＜α５＜α６＜α７の関係が成り立つように設定されている。つまり、伝熱管１３Ａ〜１３Ｇは、プロペラファン６０の中心軸Ｏから離れるほど仮想水平面Ｓに対する傾斜角度が大きくなるように設定されている。   As shown in FIGS. 4A to 4G, when the inclination angles of the heat transfer tubes 13A to 13G with respect to the virtual horizontal plane S (see FIG. 3) are α1, α2, α3, α4, α5, α6, α7, respectively. , Α1 <α2 <α3 <α4 <α5 <α6 <α7. That is, the heat transfer tubes 13 </ b> A to 13 </ b> G are set so that the inclination angle with respect to the virtual horizontal plane S increases as the distance from the central axis O of the propeller fan 60 increases.

また、伝熱管１３Ｈ〜１３Ｎは、中心軸Ｏを通る仮想水平面Ｓを基準にして上下対称に構成されている。よって、伝熱管１３Ｈ〜１３Ｎの傾斜角度についても、伝熱管１３Ａ〜１３Ｇの傾斜角度α１〜α７と同様な傾斜状態で配置されている。つまり、伝熱管１３Ｈ〜１３Ｎは、プロペラファン６０の中心軸Ｏから離れるほど仮想水平面Ｓに対する傾斜角度が大きくなるように設定されている。   Further, the heat transfer tubes 13H to 13N are configured vertically symmetrical with respect to a virtual horizontal plane S passing through the central axis O. Therefore, the inclination angles of the heat transfer tubes 13H to 13N are also arranged in an inclined state similar to the inclination angles α1 to α7 of the heat transfer tubes 13A to 13G. That is, the heat transfer tubes 13 </ b> H to 13 </ b> N are set such that the inclination angle with respect to the virtual horizontal plane S increases as the distance from the central axis O of the propeller fan 60 increases.

このように、熱交換部３Ａにおいて、伝熱管１３Ａ〜１３Ｇと伝熱管１３Ｈ〜１３Ｎとは、中心軸Ｏを通る仮想水平面Ｓに対して上下対称に構成されている。また、熱交換部３Ａの空気の流れ方向の下流側に配置される熱交換部３Ｂについても、熱交換部３Ａと同様にして構成されている。   Thus, in the heat exchanging unit 3A, the heat transfer tubes 13A to 13G and the heat transfer tubes 13H to 13N are configured vertically symmetrically with respect to the virtual horizontal plane S passing through the central axis O. Further, the heat exchange unit 3B disposed on the downstream side in the air flow direction of the heat exchange unit 3A is also configured in the same manner as the heat exchange unit 3A.

なお、本実施形態では、中心軸Ｏが、室外熱交換器３の高さ方向（上下方向）の中心Ｐと一致するように構成されているが、必ずしも一致させる必要はない（上下非対称であってもよい）。例えば、室外熱交換器３の上端３ａとプロペラファン６０の上端６０ｃとの長さＬ１（図３参照）が、室外熱交換器３の下端３ｂとプロペラファン６０の下端６０ｄとの長さＬ２（図３参照）よりも長く形成されている場合、室外熱交換器３の下端側に位置する伝熱管１３の傾斜角度よりも、室外熱交換器３の上端側に位置する伝熱管１３の傾斜角度が大きくなるように設定される。   In the present embodiment, the central axis O is configured to coincide with the center P in the height direction (vertical direction) of the outdoor heat exchanger 3, but it is not always necessary to be coincident (asymmetrical in the vertical direction). May be) For example, the length L1 (see FIG. 3) between the upper end 3a of the outdoor heat exchanger 3 and the upper end 60c of the propeller fan 60 is equal to the length L2 between the lower end 3b of the outdoor heat exchanger 3 and the lower end 60d of the propeller fan 60 (see FIG. 3). 3), the inclination angle of the heat transfer tube 13 positioned on the upper end side of the outdoor heat exchanger 3 is larger than the inclination angle of the heat transfer tube 13 positioned on the lower end side of the outdoor heat exchanger 3. Is set to be large.

図５は、第１実施形態におけるファン回転時に形成される空気の流れ図である。
図５に示すように、室外機８では、プロペラファン６０とベルマウス６１とによって室外送風手段６が構成されているので、プロペラファン６０が回転することで、室外機８の背面側から空気を巻き込むようにして吸い込まれる。すなわち、室外熱交換器３の中心軸Ｏより上側では、室外熱交換器３の上端３ａよりも上側の空気を取り込み、室外熱交換器３の中心軸Ｏより下側では、室外熱交換器３の下端３ｂよりも下側の空気を取り込むように、空気の流れが形成される。すなわち、プロペラファン６０の中心軸Ｏに近い側においては、矢印Ａ１，Ａ２で示すように、仮想水平面Ｓに対する空気の流入角度が小さく、中心軸Ｏに遠くなるにつれて矢印Ａ３，Ａ４で示すように、仮想水平面Ｓに対する空気の流入角度が大きくなる。 FIG. 5 is a flow chart of air formed when the fan rotates in the first embodiment.
As shown in FIG. 5, in the outdoor unit 8, the outdoor air blowing means 6 is configured by the propeller fan 60 and the bell mouth 61, so that the air is drawn from the back side of the outdoor unit 8 by the rotation of the propeller fan 60. It is sucked like it is involved. That is, air above the upper end 3 a of the outdoor heat exchanger 3 is taken in above the central axis O of the outdoor heat exchanger 3, and the outdoor heat exchanger 3 is below the central axis O of the outdoor heat exchanger 3. An air flow is formed so as to take in air below the lower end 3b of the. That is, on the side close to the central axis O of the propeller fan 60, as indicated by arrows A1 and A2, the air inflow angle with respect to the virtual horizontal plane S is small, and as the distance from the central axis O increases, as indicated by arrows A3 and A4. The air inflow angle with respect to the virtual horizontal plane S is increased.

このように、通常、プロペラファン６０の直径Ｒよりも室外熱交換器３の高さが高く（大きく）形成されているため、プロペラファン６０の外側に配置される部分の室外熱交換器３にも空気が十分に流れるように、プロペラファン６０が形成する空気流れがプロペラファン６０の上流側で広く、下流側で絞られるように、羽根６０ｂの角度が調整されている。したがって、図５に示すように、室外熱交換器３の上流側での空気の流れ方向は、中心軸Ｏの上側で矢印Ａ３方向、下側で矢印Ａ４方向となり、空気が上下方向から中心軸Ｏに向かって斜めに流入する。このとき、空気が流入する角度は、中心軸Ｏから離れるほど中心軸Ｏを通る水平面（仮想水平面Ｓ）に対して大きくなる。   Thus, since the height of the outdoor heat exchanger 3 is normally higher (larger) than the diameter R of the propeller fan 60, the portion of the outdoor heat exchanger 3 arranged outside the propeller fan 60 is In addition, the angle of the blade 60b is adjusted so that the air flow formed by the propeller fan 60 is wide on the upstream side of the propeller fan 60 and is throttled on the downstream side so that the air flows sufficiently. Therefore, as shown in FIG. 5, the air flow direction on the upstream side of the outdoor heat exchanger 3 is the arrow A3 direction on the upper side of the central axis O, the arrow A4 direction on the lower side, and the air flows from the vertical direction to the central axis. It flows obliquely toward O. At this time, the angle at which air flows in increases with respect to the horizontal plane (virtual horizontal plane S) passing through the central axis O as the distance from the central axis O increases.

そこで、図３および図４において説明したように、第１実施形態では、空気の流入角度分布に合うように、中心軸Ｏから離れた位置の伝熱管１３ほど仮想水平面Ｓに対する角度を大きくしている。例えば、伝熱管１３Ａ〜１３Ｇにおいては、中心軸Ｏに近い側から一段毎に３°ずつ増加している。   Therefore, as described in FIGS. 3 and 4, in the first embodiment, the angle with respect to the virtual horizontal plane S is increased in the heat transfer tube 13 at a position away from the central axis O so as to match the air flow angle distribution. Yes. For example, in the heat transfer tubes 13 </ b> A to 13 </ b> G, the angle increases by 3 ° for each stage from the side near the central axis O.

続いて、このように構成された空気調和装置の室外機８の動作について、図１〜図５を参照して説明する。
暖房運転時においては、冷媒が実線方向（図１参照）に流れるように四方弁２を切換え、冷媒を図１の実線矢印方向(図１の時計回り方向)に、圧縮機１、四方弁２、室内熱交換器５、絞り装置４、室外熱交換器３の順に流す。このとき、絞り装置４は、空調負荷に応じた適度な開度に調整され、凝縮器として働く室内熱交換器５で十分に凝縮して液化した冷媒は絞り装置４で気液二相流となって、室外熱交換器３に流入する。 Then, operation | movement of the outdoor unit 8 of the air conditioning apparatus comprised in this way is demonstrated with reference to FIGS.
During the heating operation, the four-way valve 2 is switched so that the refrigerant flows in the direction of the solid line (see FIG. 1), and the compressor 1 and the four-way valve 2 are switched in the direction of the solid arrow in FIG. Then, the indoor heat exchanger 5, the expansion device 4, and the outdoor heat exchanger 3 are flowed in this order. At this time, the expansion device 4 is adjusted to an appropriate opening degree corresponding to the air conditioning load, and the refrigerant sufficiently condensed and liquefied by the indoor heat exchanger 5 acting as a condenser is converted into a gas-liquid two-phase flow by the expansion device 4. And flows into the outdoor heat exchanger 3.

室外送風手段６であるプロペラファン６０は、所定の回転速度で回転しており、矢印Ａ１〜Ａ４で示すように外気（空気）が室外熱交換器３に流入する。ところで、伝熱管１３の仮想水平面Ｓに対する傾斜角度が０°である（伝熱管１３と仮想水平面Ｓとが平行である）と、特にプロペラファン６０の中心軸Ｏから遠い側に位置する伝熱管１３では、流入した空気が伝熱管に衝突して、空気の流れ方向が大きく変わり、空気の流れに剥離（かい離）が生じる。そこで、第１実施形態では、図３および図４に示すように、伝熱管１３（１３Ａ〜１３Ｎ）の平面部１３ａを傾斜させることで、プロペラファン６０への空気の流れを整流することが可能になる。これにより、プロペラファン６０の動力を減少させることができるだけでなく、伝熱管１３（１３Ａ〜１３Ｎ）を通過する上下の風速分布が均一化されるため、熱交換性能が向上する。   The propeller fan 60 that is the outdoor air blowing means 6 rotates at a predetermined rotational speed, and the outside air (air) flows into the outdoor heat exchanger 3 as indicated by arrows A1 to A4. By the way, when the inclination angle of the heat transfer tube 13 with respect to the virtual horizontal plane S is 0 ° (the heat transfer tube 13 and the virtual horizontal plane S are parallel), the heat transfer tube 13 located on the far side from the central axis O of the propeller fan 60 in particular. Then, the inflowing air collides with the heat transfer tube, the direction of air flow changes significantly, and separation (separation) occurs in the air flow. Therefore, in the first embodiment, as shown in FIGS. 3 and 4, the air flow to the propeller fan 60 can be rectified by inclining the flat surface portion 13 a of the heat transfer tubes 13 (13 </ b> A to 13 </ b> N). become. Thereby, not only can the power of the propeller fan 60 be reduced, but also the vertical wind speed distribution passing through the heat transfer tubes 13 (13A to 13N) is made uniform, so that the heat exchange performance is improved.

流入した空気は、伝熱管１３（１３Ａ〜１３Ｎ）を介して冷媒と熱交換し、空気の温度が低下する。例えば、外気温度が７℃のとき、伝熱管１３の温度を１℃とすると、空気はおよそ３℃程度まで低下する。このとき、空気に水分が含まれていると、伝熱管１３の表面で空気が露点温度まで冷やされた際に水分が結露し、水滴となる。第１実施形態のように、伝熱管１３の平面部１３ａを傾斜させることで、水滴が平面部１３ａの傾斜に沿って流れ、滞留することがないため、通風抵抗はほとんど増加しない。また、伝熱管１３の平面部１３ａを傾斜配置したことで、伝熱管１３に水滴が滞留するのを低減でき、空気と冷媒との熱交換が阻害されて蒸発性能が低下したり、また着霜し易くなるのを防止できる。その後、冷媒は、蒸発器として働く室外熱交換器３で十分蒸発してガス化した後、圧縮機１に戻る。   The air that flows in exchanges heat with the refrigerant through the heat transfer tubes 13 (13A to 13N), and the temperature of the air decreases. For example, when the outside air temperature is 7 ° C. and the temperature of the heat transfer tube 13 is 1 ° C., the air drops to about 3 ° C. At this time, if moisture is contained in the air, when the air is cooled to the dew point temperature on the surface of the heat transfer tube 13, the moisture is condensed to form water droplets. As in the first embodiment, by inclining the flat portion 13a of the heat transfer tube 13, water drops do not flow and stay along the inclined portion of the flat portion 13a, so that the ventilation resistance hardly increases. In addition, since the flat surface portion 13a of the heat transfer tube 13 is inclined, it is possible to reduce the retention of water droplets in the heat transfer tube 13, the heat exchange between the air and the refrigerant is hindered, and the evaporation performance is lowered. Can be prevented. Thereafter, the refrigerant sufficiently evaporates and gasifies in the outdoor heat exchanger 3 that functions as an evaporator, and then returns to the compressor 1.

一方、冷房運転時においては、四方弁２を冷媒が図１の破線矢印方向に流れるように切換え、冷媒を図１の破線矢印方向(図１の反時計回り方向)に、圧縮機１、四方弁２、凝縮器として働く室外熱交換器３、絞り装置４、蒸発器として働く室内熱交換器５の順に流す。このとき、圧縮機１を出た高温、高圧のガス冷媒は、凝縮器として働く室外熱交換器３に流入する。   On the other hand, during the cooling operation, the four-way valve 2 is switched so that the refrigerant flows in the direction of the broken line arrow in FIG. 1, and the refrigerant is moved in the direction of the broken line arrow in FIG. 1 (counterclockwise direction in FIG. 1). It flows in order of the valve 2, the outdoor heat exchanger 3 that works as a condenser, the expansion device 4, and the indoor heat exchanger 5 that works as an evaporator. At this time, the high-temperature and high-pressure gas refrigerant exiting the compressor 1 flows into the outdoor heat exchanger 3 that functions as a condenser.

図５に示すように、室外送風手段６であるプロペラファン６０は、所定の回転速度で回転しており、矢印Ａ１〜Ａ４で示すように空気が室外熱交換器３に流入する。図３および図４に示すように、伝熱管１３の平面部１３ａを傾斜させることで、伝熱管１３の傾斜角度が空気の流入角度に近づくので、プロペラファン６０への空気の流れを整流でき（空気の剥離を低減でき）、プロペラファン６０の動力を低減させることができ、また伝熱管１３（１３Ａ〜１３Ｎ）を通過する上下の風速分布が均一化されるため、熱交換性能が向上する。   As shown in FIG. 5, the propeller fan 60 that is the outdoor air blowing means 6 rotates at a predetermined rotational speed, and air flows into the outdoor heat exchanger 3 as indicated by arrows A1 to A4. As shown in FIGS. 3 and 4, by inclining the flat surface portion 13 a of the heat transfer tube 13, the inclination angle of the heat transfer tube 13 approaches the air inflow angle, so that the air flow to the propeller fan 60 can be rectified ( Air separation can be reduced), the power of the propeller fan 60 can be reduced, and the vertical wind speed distribution passing through the heat transfer tubes 13 (13A to 13N) is made uniform, so that the heat exchange performance is improved.

流入した空気は、伝熱管１３（１３Ａ〜１３Ｎ）を介して冷媒と熱交換し、空気の温度が低下する。例えば、外気温度が３５℃のとき、伝熱管１３の温度を４５℃とすると、空気はおよそ４０℃程度まで上昇する。その後、冷媒は、絞り装置弁４によって空調負荷に応じた適度な開度に調整され、室外熱交換器３によって十分に凝縮して液化し、絞り装置４によって減圧膨張して蒸発器として働く室内熱交換器５で十分蒸発して、圧縮機１に戻る。   The air that flows in exchanges heat with the refrigerant through the heat transfer tubes 13 (13A to 13N), and the temperature of the air decreases. For example, when the outside air temperature is 35 ° C. and the temperature of the heat transfer tube 13 is 45 ° C., the air rises to about 40 ° C. Thereafter, the refrigerant is adjusted to an appropriate degree of opening according to the air conditioning load by the expansion device valve 4, sufficiently condensed and liquefied by the outdoor heat exchanger 3, and decompressed and expanded by the expansion device 4 to serve as an evaporator. It evaporates sufficiently in the heat exchanger 5 and returns to the compressor 1.

なお、伝熱管１３の傾斜角度は、プロペラファン６０の直径Ｒと室外熱交換器３の高さ（大きさ）、室外熱交換器３の通風抵抗やプロペラファン６０の性能によって適正角度があるため、実験や流れ解析により微調整することが好ましい（以下の実施形態においても同様）。   The inclination angle of the heat transfer tube 13 has an appropriate angle depending on the diameter R of the propeller fan 60, the height (size) of the outdoor heat exchanger 3, the ventilation resistance of the outdoor heat exchanger 3, and the performance of the propeller fan 60. It is preferable to make fine adjustments by experiment or flow analysis (the same applies to the following embodiments).

以上説明したように、第１実施形態では、伝熱管１３Ａ〜１３Ｎが扁平形状であって、プロペラファン６０の中心軸Ｏを通る仮想水平面Ｓに対して当該伝熱管１３Ａ〜１３Ｎの長手方向の下流側Ｐ１，Ｐ２が中心軸Ｏ（仮想水平面Ｓ）を向くように傾斜している。これにより、室外熱交換器３が蒸発器として作用している際に発生する湿り空気の凝縮水をスムーズに下方に流すことができ、凝縮水の滞留による通風抵抗の増加を最小限に抑えることができる。なお、室外熱交換器３の中心軸Ｏより上側では、伝熱管１３Ａ〜１３Ｇに付着した凝縮水が、平面部１３ａに沿って流れ、筺体２１の内側に落下し、中心軸Ｏより下側では、伝熱管１３Ｈ〜１３Ｎに付着した凝縮水が、平面部１３ａに沿って流れ、筺体２１の外側に落下する。   As described above, in the first embodiment, the heat transfer tubes 13 </ b> A to 13 </ b> N are flat and downstream in the longitudinal direction of the heat transfer tubes 13 </ b> A to 13 </ b> N with respect to the virtual horizontal plane S passing through the central axis O of the propeller fan 60. The sides P1 and P2 are inclined so as to face the central axis O (virtual horizontal plane S). Thereby, the condensed water of the humid air generated when the outdoor heat exchanger 3 acts as an evaporator can be smoothly flowed downward, and the increase in ventilation resistance due to the retention of the condensed water is minimized. Can do. In addition, the condensed water adhering to the heat transfer tubes 13A to 13G flows along the flat portion 13a on the upper side from the central axis O of the outdoor heat exchanger 3, falls to the inside of the housing 21, and below the central axis O. The condensed water adhering to the heat transfer tubes 13H to 13N flows along the flat portion 13a and falls to the outside of the housing 21.

また、第１実施形態によれば、前記のように伝熱管１３Ａ〜１３Ｎを傾斜して配置したことで、プロペラファン６０への空気の流れを整流し、プロペラファン６０に必要な動力を低減することができる。さらに、伝熱管１３（１３Ａ〜１３Ｎ）を通過する上下の風速分布が均一化されるため、熱交換性能が向上する。   Moreover, according to 1st Embodiment, by arrange | positioning the heat exchanger tubes 13A-13N inclining as mentioned above, the flow of the air to the propeller fan 60 is rectified, and the motive power required for the propeller fan 60 is reduced. be able to. Furthermore, since the upper and lower wind speed distributions passing through the heat transfer tubes 13 (13A to 13N) are made uniform, the heat exchange performance is improved.

ところで、前記したように、プロペラファン６０の中心軸Ｏに近い側で空気の流入角度が小さく（図４の矢印Ａ１，Ａ２参照）、中心軸Ｏに遠くなるにつれて流入角度（図４の矢印Ａ３，Ａ４参照）が大きくなる。そこで、第１実施形態では、各段毎（１段毎）に、伝熱管１３Ａ〜１３Ｇ（１３Ｈ〜１３Ｎ）の仮想水平面Ｓに対する傾斜角度を、中心軸Ｏから離れるほど大きくしているので、各高さ位置における空気の流入角度に合わせることができ、プロペラファン６０への空気の流れをさらに整流でき、熱交換性能をさらに向上できる。   By the way, as described above, the inflow angle of air is small on the side close to the central axis O of the propeller fan 60 (see arrows A1 and A2 in FIG. 4), and the inflow angle (arrow A3 in FIG. 4) becomes farther away from the central axis O. , A4) increases. Therefore, in the first embodiment, the inclination angle of the heat transfer tubes 13A to 13G (13H to 13N) with respect to the virtual horizontal plane S is increased as the distance from the central axis O increases. It is possible to match the air inflow angle at the height position, further rectify the air flow to the propeller fan 60, and further improve the heat exchange performance.

また、第１実施形態では、熱交換部３Ａ，３Ｂが中心軸Ｏを通る仮想水平面Ｓに対して上下対称に構成されているので、中心軸Ｏより上側だけでなく、中心軸Ｏより下側についても室外熱交換器３が蒸発器として作用している際に発生する湿り空気の凝縮水をスムーズに下方に流すことができ、凝縮水の滞留による通風抵抗の増加を最小限に抑えることができる。また、プロペラファン６０への空気の流れを整流し、プロペラファン６０に必要な動力を低減することができるとともに、室外熱交換器３を通過する上下の風速分布が均一化されるため、熱交換性能が向上する。このように、室外熱交換器３の上下方向の全体における熱交換性能を向上できる。   In the first embodiment, since the heat exchanging parts 3A and 3B are configured vertically symmetrically with respect to the virtual horizontal plane S passing through the central axis O, not only above the central axis O but also below the central axis O. In addition, it is possible to smoothly flow the condensed water of the humid air generated when the outdoor heat exchanger 3 acts as an evaporator, and to minimize the increase in ventilation resistance due to the condensate water retention it can. In addition, the flow of air to the propeller fan 60 can be rectified to reduce the power required for the propeller fan 60, and the vertical wind speed distribution passing through the outdoor heat exchanger 3 is made uniform. Performance is improved. Thus, the heat exchange performance in the entire vertical direction of the outdoor heat exchanger 3 can be improved.

（第２実施形態）
図６は、第２実施形態における室外機の内部構造を示す側面図、図７は、第２実施形態における伝熱管の周囲に形成される空気の流れを示し、（ａ）は千鳥状に配置された場合、（ｂ）はタンデム状に配置された場合である。第２実施形態の空気調和機の室外機８Ａは、第１実施形態の室外熱交換器３に替えて室外熱交換器３０としたものである。 (Second Embodiment)
FIG. 6 is a side view showing the internal structure of the outdoor unit in the second embodiment, FIG. 7 shows the air flow formed around the heat transfer tube in the second embodiment, and (a) is arranged in a staggered manner. In this case, (b) is a case where they are arranged in tandem. The outdoor unit 8A of the air conditioner of the second embodiment is an outdoor heat exchanger 30 instead of the outdoor heat exchanger 3 of the first embodiment.

図６に示すように、室外熱交換器３０は、熱交換部３０Ａ（一の熱交換部）の各伝熱管１３Ａ〜１３Ｇの延長線Ｅ１〜Ｅ７（１点鎖線参照）上に熱交換部３０Ｂ（他の熱交換部）の各伝熱管１３Ａ´〜１３Ｇ´が配置されないように構成されている。なお、熱交換部３０Ａ，３０Ｂは、第１実施形態の熱交換部３Ａ，３Ｂと基本的な構成は同じである。   As shown in FIG. 6, the outdoor heat exchanger 30 includes a heat exchanging unit 30B on the extension lines E1 to E7 (see the one-dot chain line) of the heat transfer tubes 13A to 13G of the heat exchanging unit 30A (one heat exchanging unit). It is comprised so that each heat exchanger tube 13A '-13G' of (other heat exchange part) may not be arrange | positioned. The heat exchange units 30A and 30B have the same basic configuration as the heat exchange units 3A and 3B of the first embodiment.

すなわち、熱交換部３０Ａの伝熱管１３Ａの延長線Ｅ１と伝熱管１３Ｂの延長線Ｅ２との中間に熱交換部３０Ｂの伝熱管１３Ａ´が位置している。また、熱交換部３０Ａの伝熱管１３Ｂの延長線Ｅ２と伝熱管１３Ｃの延長線Ｅ３との中間に熱交換部３０Ｂの伝熱管１３Ｂ´が位置している。また、熱交換部３０Ａの伝熱管１３Ｃの延長線Ｅ３と伝熱管１３Ｄの延長線Ｅ４との中間に熱交換部３０Ｂの伝熱管１３Ｃ´が位置している。また、熱交換部３０Ａの伝熱管１３Ｄの延長線Ｅ４と伝熱管１３Ｅの延長線Ｅ５との中間に熱交換部３０Ｂの伝熱管１３Ｄ´が位置している。また、熱交換部３０Ａの伝熱管１３Ｅの延長線Ｅ５と伝熱管１３Ｆの延長線Ｅ６との中間に熱交換部３０Ｂの伝熱管１３Ｅ´が位置している。また、熱交換部３０Ａの伝熱管１３Ｆの延長線Ｅ６と伝熱管１３Ｇの延長線Ｅ７との中間に熱交換部３０Ｂの伝熱管１３Ｆ´が位置している。また、熱交換部３０Ｂの伝熱管１３Ｇ´は、熱交換部３０Ａの伝熱管１３Ｇの延長線Ｅ７よりも上側に位置している。なお、図６に示す実施形態では、熱交換部３０Ｂの伝熱管１３Ａ´〜１３Ｇ´が、熱交換部３０Ａの伝熱管１３Ａ〜１３Ｇよりも高い位置に配置（上側にオフセットして配置）されているが、その逆に配置（下側にオフセットして配置）されていてもよい。   That is, the heat transfer tube 13A ′ of the heat exchange unit 30B is positioned between the extension line E1 of the heat transfer tube 13A of the heat exchange unit 30A and the extension line E2 of the heat transfer tube 13B. Further, the heat transfer tube 13B ′ of the heat exchange unit 30B is located between the extension line E2 of the heat transfer tube 13B of the heat exchange unit 30A and the extension line E3 of the heat transfer tube 13C. Further, the heat transfer tube 13C ′ of the heat exchange unit 30B is located between the extension line E3 of the heat transfer tube 13C of the heat exchange unit 30A and the extension line E4 of the heat transfer tube 13D. Further, the heat transfer tube 13D ′ of the heat exchange unit 30B is located between the extension line E4 of the heat transfer tube 13D of the heat exchange unit 30A and the extension line E5 of the heat transfer tube 13E. Further, the heat transfer tube 13E ′ of the heat exchange unit 30B is located between the extension line E5 of the heat transfer tube 13E of the heat exchange unit 30A and the extension line E6 of the heat transfer tube 13F. Further, the heat transfer tube 13F ′ of the heat exchange unit 30B is located between the extension line E6 of the heat transfer tube 13F of the heat exchange unit 30A and the extension line E7 of the heat transfer tube 13G. Further, the heat transfer tube 13G ′ of the heat exchange unit 30B is located above the extension line E7 of the heat transfer tube 13G of the heat exchange unit 30A. In the embodiment shown in FIG. 6, the heat transfer tubes 13A ′ to 13G ′ of the heat exchange unit 30B are arranged at positions higher than the heat transfer tubes 13A to 13G of the heat exchange unit 30A (offset upward). However, it may be arranged in reverse (offset downward).

また、前記と同様に、熱交換部３０Ａの伝熱管１３Ｈの延長線（不図示、以下同様）と伝熱管１３Ｉの延長線との中間に熱交換部３０Ｂの伝熱管１３Ｈ´が位置している。また、熱交換部３０Ａの伝熱管１３Ｉの延長線と伝熱管１３Ｊの延長線との中間に熱交換部３０Ｂの伝熱管１３Ｉ´が位置している。また、熱交換部３０Ａの伝熱管１３Ｊの延長線と伝熱管１３Ｋの延長線との中間に熱交換部３０Ｂの伝熱管１３Ｊ´が位置している。また、熱交換部３０Ａの伝熱管１３Ｋの延長線と伝熱管１３Ｌの延長線との中間に熱交換部３０Ｂの伝熱管１３Ｋ´が位置している。また、熱交換部３０Ａの伝熱管１３Ｌの延長線と伝熱管１３Ｍの延長線との中間に熱交換部３０Ｂの伝熱管１３Ｌ´が位置している。また、熱交換部３０Ａの伝熱管１３Ｍの延長線と伝熱管１３Ｎの延長線との中間に熱交換部３０Ｂの伝熱管１３Ｍ´が位置している。また、熱交換部３０Ｂの伝熱管１３Ｎ´は、熱交換部３０Ａの伝熱管１３Ｎの延長線よりも下側に位置している。なお、図５に示す実施形態では、熱交換部３０Ｂの伝熱管１３Ｈ´〜１３Ｎ´が、熱交換部３０Ａの伝熱管１３Ｈ〜１３Ｎよりも低い位置に配置（下側にオフセットして配置）されているが、その逆に配置（上側にオフセットして配置）されていてもよい。   In the same manner as described above, the heat transfer tube 13H ′ of the heat exchange unit 30B is located between the extension line of the heat transfer tube 13H of the heat exchange unit 30A (not shown, the same applies hereinafter) and the extension line of the heat transfer tube 13I. . Further, the heat transfer tube 13I ′ of the heat exchange unit 30B is positioned between the extension line of the heat transfer tube 13I of the heat exchange unit 30A and the extension line of the heat transfer tube 13J. Further, the heat transfer tube 13J ′ of the heat exchange unit 30B is located between the extension line of the heat transfer tube 13J of the heat exchange unit 30A and the extension line of the heat transfer tube 13K. Further, the heat transfer tube 13K ′ of the heat exchange unit 30B is positioned between the extension line of the heat transfer tube 13K of the heat exchange unit 30A and the extension line of the heat transfer tube 13L. Further, the heat transfer tube 13L ′ of the heat exchange unit 30B is located between the extension line of the heat transfer tube 13L of the heat exchange unit 30A and the extension line of the heat transfer tube 13M. Further, the heat transfer tube 13M ′ of the heat exchange unit 30B is located between the extension line of the heat transfer tube 13M of the heat exchange unit 30A and the extension line of the heat transfer tube 13N. Further, the heat transfer tube 13N ′ of the heat exchange unit 30B is positioned below the extension line of the heat transfer tube 13N of the heat exchange unit 30A. In the embodiment shown in FIG. 5, the heat transfer tubes 13H ′ to 13N ′ of the heat exchange unit 30B are arranged at positions lower than the heat transfer tubes 13H to 13N of the heat exchange unit 30A (offset downward). However, the arrangement may be reversed (offset on the upper side).

ところで、図７（ｂ）に示すように、一方の熱交換部の伝熱管１３と他方の熱交換部の伝熱管１３をタンデム状に配置、換言すると一方の伝熱管１３の長手方向と他方の伝熱管１３の長手方向とが直線上に位置するように配置すると、流入した空気が、矢印Ａ１０で示すように、上流側の伝熱管１３の平面部１３ａを通過した後に下流側の伝熱管１３の平面部１３ａを通過する。また、流入した空気は、矢印Ａ１１で示すように、上流側の伝熱管１３の平面部１３ｂを通過した後に下流側の伝熱管１３の平面部１３ｂを通過する。このような配置の場合、一方の熱交換部の伝熱管１３と他方の熱交換部の伝熱管１３との間に空気が流れ難くなる空間が形成されるので、熱交換性能が低下する。   By the way, as shown in FIG.7 (b), the heat exchanger tube 13 of one heat exchange part and the heat exchanger tube 13 of the other heat exchange part are arrange | positioned in a tandem form, in other words, the longitudinal direction of one heat exchanger tube 13, and the other If it arrange | positions so that the longitudinal direction of the heat exchanger tube 13 may be located on a straight line, as shown by arrow A10, the air which flowed in passes through the plane part 13a of the upstream heat exchanger tube 13, and then the downstream heat exchanger tube 13 Passes through the flat portion 13a. Further, as shown by an arrow A <b> 11, the inflowing air passes through the flat portion 13 b of the downstream heat transfer tube 13 after passing through the flat portion 13 b of the upstream heat transfer tube 13. In such an arrangement, a space in which air hardly flows is formed between the heat transfer tube 13 of one heat exchange unit and the heat transfer tube 13 of the other heat exchange unit, so that the heat exchange performance is lowered.

そこで、図７（ａ）に示すように、熱交換部３０Ａ（一方の熱交換部）の伝熱管１３Ａ〜１３Ｎと熱交換部３０Ｂ（他方の熱交換部）の伝熱管１３Ａ´〜１３Ｎ´とを千鳥状に（互い違いに）配置することで、流入した空気が、矢印Ａ５で示すように、熱交換部３０Ａの図示上側の伝熱管１３の平面部１３ｂを通過した後に熱交換部３０Ｂの伝熱管１３の平面部１３ａを通過する。また、流入した空気は、矢印Ａ６で示すように、熱交換部３０Ａの図示下側の伝熱管１３の平面部１３ａを通過した後に熱交換部３０Ｂの伝熱管１３の平面部１３ｂを通過する。このように、熱交換部３０Ａの伝熱管１３と熱交換部３０Ｂの伝熱管１３との間に空気の流れが生じるので、熱交換性能が低下するのを抑制することができる。   Therefore, as shown in FIG. 7A, the heat transfer tubes 13A to 13N of the heat exchange unit 30A (one heat exchange unit) and the heat transfer tubes 13A 'to 13N' of the heat exchange unit 30B (the other heat exchange unit) Are arranged in a zigzag pattern (in a staggered manner), so that the air that has flowed in passes through the flat surface portion 13b of the heat transfer tube 13 on the upper side of the heat exchange portion 30A as shown by the arrow A5, and then is transferred to the heat exchange portion 30B. It passes through the flat portion 13a of the heat tube 13. Further, as shown by an arrow A6, the inflowing air passes through the flat portion 13b of the heat transfer tube 13 of the heat exchange portion 30B after passing through the flat portion 13a of the heat transfer tube 13 on the lower side of the heat exchange portion 30A in the drawing. As described above, since an air flow is generated between the heat transfer tube 13 of the heat exchange unit 30A and the heat transfer tube 13 of the heat exchange unit 30B, it is possible to suppress deterioration of the heat exchange performance.

（第３実施形態）
図８は、第３実施形態における室外機の内部構造を示す側面図である。
図８に示すように、第３実施形態の空気調和機の室外機８Ｂは、伝熱管１３Ａ〜１３Ｇ（１３Ｈ〜１３Ｎ）を一定間隔で複数段とした室外熱交換器３（第１実施形態）に替えて、室外熱交換器４０としたものである。なお、室外熱交換器４０において、熱交換部４０Ａと熱交換部４０Ｂとは同様の構成であるので、以下では、熱交換部４０Ａのみについて説明する。 (Third embodiment)
FIG. 8 is a side view showing the internal structure of the outdoor unit in the third embodiment.
As shown in FIG. 8, the outdoor unit 8B of the air conditioner of the third embodiment is an outdoor heat exchanger 3 (first embodiment) in which the heat transfer tubes 13A to 13G (13H to 13N) are arranged in a plurality of stages at regular intervals. Instead of this, an outdoor heat exchanger 40 is provided. In addition, in the outdoor heat exchanger 40, since the heat exchange part 40A and the heat exchange part 40B are the same structures, below, only the heat exchange part 40A is demonstrated.

ところで、プロペラファン６０が作る空気の流れは、プロペラファン６０に近いほど（周囲に対して中心軸Ｏに近くなればなるほど）速くなり、中心軸Ｏ付近に流れ易い分布が形成される。そこで、第３実施形態では、熱交換部４０Ａにおいて、プロペラファン６０の中心軸Ｏに近い側の隣り合う伝熱管１３同士の距離Ｌ１０（例えば、伝熱管１３Ａと伝熱管１３Ｂとの距離、伝熱管１３Ｂと伝熱管１３Ｃとの距離）を、中心軸Ｏから遠い側の伝熱管１３同士の距離Ｌ２０（例えば、伝熱管１３Ｃと伝熱管１３Ｄとの距離、伝熱管１３Ｄと伝熱管１３Ｅとの距離、伝熱管１３Ｅと伝熱管１３Ｆとの距離、伝熱管１３Ｆと伝熱管１３Ｇとの距離）よりも狭めたものである（Ｌ１０＜Ｌ２０）。   By the way, the air flow produced by the propeller fan 60 becomes faster as it is closer to the propeller fan 60 (as it is closer to the central axis O with respect to the surroundings), and a distribution that easily flows near the central axis O is formed. Therefore, in the third embodiment, in the heat exchanging unit 40A, the distance L10 between adjacent heat transfer tubes 13 on the side close to the central axis O of the propeller fan 60 (for example, the distance between the heat transfer tube 13A and the heat transfer tube 13B, the heat transfer tube) 13B and the distance between the heat transfer tubes 13C), the distance L20 between the heat transfer tubes 13 on the far side from the central axis O (for example, the distance between the heat transfer tubes 13C and 13D, the distance between the heat transfer tubes 13D and 13E, This is narrower than the distance between the heat transfer tube 13E and the heat transfer tube 13F and the distance between the heat transfer tube 13F and the heat transfer tube 13G (L10 <L20).

これにより、第１実施形態の効果に加えて、中心軸Ｏ側の空気の流れが抑えられるので、その分中心軸Ｏから遠い側に空気が流れ易くなり、室外熱交換器３を通過する上下の風速分布がより均一化され、熱交換器性能が向上する。   Thereby, in addition to the effect of 1st Embodiment, since the flow of the air by the side of the central axis O is suppressed, air becomes easy to flow to the side far from the central axis O, and the upper and lower sides which pass the outdoor heat exchanger 3 are equivalent to it. The wind speed distribution of the air is made more uniform, and the heat exchanger performance is improved.

（第４実施形態）
図９は、第４実施形態における室外機の内部構造を示す側面図である。
図９に示すように、第４実施形態の空気調和機の室外機８Ｃは、伝熱管群１３Ｐ，１３Ｑ，１３Ｒ，１３Ｓの仮想水平面Ｓに対する傾斜角度を、中心軸Ｏから離れるほど大きくしている。なお、熱交換部５０Ａと熱交換部５０Ｂは、同様の構成であるので、以下では熱交換部５０Ａのみについて説明する。なお、伝熱管群１３Ｐ，１３Ｑ，１３Ｒ，１３Ｓの伝熱管１３の段数は、一例であって、本実施形態に限定されるものではない。 (Fourth embodiment)
FIG. 9 is a side view showing the internal structure of the outdoor unit in the fourth embodiment.
As shown in FIG. 9, in the outdoor unit 8C of the air conditioner of the fourth embodiment, the inclination angle of the heat transfer tube groups 13P, 13Q, 13R, and 13S with respect to the virtual horizontal plane S is increased as the distance from the central axis O increases. . In addition, since the heat exchange part 50A and the heat exchange part 50B are the same structures, below, only the heat exchange part 50A is demonstrated. The number of stages of the heat transfer tubes 13 in the heat transfer tube groups 13P, 13Q, 13R, and 13S is an example, and is not limited to the present embodiment.

伝熱管群１３Ｐは、３本の伝熱管１３で構成され、いずれの伝熱管１３も仮想水平面Ｓに対して傾斜角度β１に設定されている。伝熱管群１３Ｑは、３本の伝熱管１３で構成され、いずれの伝熱管１３も仮想水平面Ｓに対して傾斜角度β１よりも大きい傾斜角度β２に設定されている。伝熱管群１３Ｒは、４本の伝熱管１３で構成され、いずれの伝熱管１３も仮想水平面Ｓに対して傾斜角度β２よりも大きい傾斜角度β３に設定されている。伝熱管群１３Ｓは、いずれの伝熱管１３も仮想水平面Ｓに対して傾斜角度β３よりも大きい傾斜角度β４に設定されている（β１＜β２＜β３＜β４）。   The heat transfer tube group 13 </ b> P includes three heat transfer tubes 13, and all the heat transfer tubes 13 are set to the inclination angle β <b> 1 with respect to the virtual horizontal plane S. The heat transfer tube group 13Q includes three heat transfer tubes 13, and each heat transfer tube 13 is set to an inclination angle β2 that is larger than the inclination angle β1 with respect to the virtual horizontal plane S. The heat transfer tube group 13 </ b> R includes four heat transfer tubes 13, and all the heat transfer tubes 13 are set to an inclination angle β <b> 3 that is larger than the inclination angle β <b> 2 with respect to the virtual horizontal plane S. In the heat transfer tube group 13S, any of the heat transfer tubes 13 is set to have an inclination angle β4 larger than the inclination angle β3 with respect to the virtual horizontal plane S (β1 <β2 <β3 <β4).

例えば、伝熱管群１３Ｐの傾斜角度β１を５°、伝熱管群１３Ｑの傾斜角度β２を１０°、伝熱管群１３Ｒの傾斜角度β３を１５°、伝熱管群１３Ｓの傾斜角度β４を２０°というように、伝熱管群１３Ｐ，１３Ｑ，１３Ｒ，１３Ｓの各伝熱管１３に対して同じ角度が適用される。   For example, the inclination angle β1 of the heat transfer tube group 13P is 5 °, the inclination angle β2 of the heat transfer tube group 13Q is 10 °, the inclination angle β3 of the heat transfer tube group 13R is 15 °, and the inclination angle β4 of the heat transfer tube group 13S is 20 °. Thus, the same angle is applied to each heat transfer tube 13 of the heat transfer tube group 13P, 13Q, 13R, 13S.

このように、第４実施形態では、伝熱管群１３Ｐ，１３Ｑ，１３Ｒ，１３Ｓ毎に、仮想水平面Ｓに対する傾斜角度を、中心軸Ｏから離れるほど大きくしている。これにより、各高さ位置における空気の流入角度に伝熱管１３の傾斜角度β１，β２，β３，β４を近づけることができ、プロペラファン６０への空気の流れを整流でき、熱交換性能を向上できる。   Thus, in the fourth embodiment, the inclination angle with respect to the virtual horizontal plane S is increased with increasing distance from the central axis O for each of the heat transfer tube groups 13P, 13Q, 13R, and 13S. Thereby, the inclination angles β1, β2, β3, β4 of the heat transfer tubes 13 can be brought close to the air inflow angle at each height position, the air flow to the propeller fan 60 can be rectified, and the heat exchange performance can be improved. .

図１０は、第５実施形態における室外機の内部構造を示す側面図である。
図１０に示すように、第５実施形態の空気調和機の室外機８Ｄは、熱交換部６０Ａ，６０Ｂにおいて、伝熱管１３の傾斜角度γをひとつの角度に固定し、中心軸Ｏを通る仮想水平面Ｓに対して上下対称に構成したものである。傾斜角度γは、例えば、１５°に設定される。 FIG. 10 is a side view showing the internal structure of the outdoor unit in the fifth embodiment.
As shown in FIG. 10, the outdoor unit 8D of the air conditioner according to the fifth embodiment has a virtual angle that passes through the central axis O while fixing the inclination angle γ of the heat transfer tube 13 to one angle in the heat exchange units 60A and 60B. It is configured to be vertically symmetrical with respect to the horizontal plane S. The inclination angle γ is set to 15 °, for example.

このように、第５実施形態では、伝熱管１３の傾斜角度γをひとつの角度に固定することで、第１実施形態の効果に加えて、室外熱交換器３を製造する際の作り勝手を向上できる（作り易くなる）。   As described above, in the fifth embodiment, by fixing the inclination angle γ of the heat transfer tube 13 to one angle, in addition to the effects of the first embodiment, the ease of making the outdoor heat exchanger 3 can be improved. Can improve (becomes easier to make).

（第６実施形態）
図１１は、第６実施形態における室外機の内部構造を示す側面図である。
図１１に示すように、第６実施形態の空気調和機の室外機８Ｅは、上下に２分割された熱交換部７０Ａ，７０Ｂを備えるものである。熱交換部７０Ａは、側面視（縦断面視）において細長四角形状を呈する板状フィン１２の延在方向Ｓ１に沿って複数段に配置された伝熱管１３を備えている。伝熱管１３は、扁平形状であり、該伝熱管１３の長手方向が延在方向Ｓ１に対して直交するように配置されている。また、各伝熱管１３は、等間隔に配置されている。その他の熱交換部７０Ｂについても、熱交換部７０Ａと同一形状である。 (Sixth embodiment)
FIG. 11 is a side view showing the internal structure of the outdoor unit in the sixth embodiment.
As shown in FIG. 11, the outdoor unit 8E of the air conditioner according to the sixth embodiment includes heat exchange units 70A and 70B that are divided into two parts in the vertical direction. 70 A of heat exchange parts are provided with the heat exchanger tube 13 arrange | positioned in multiple steps along extension direction S1 of the plate-like fin 12 which exhibits a long and thin square shape in a side view (longitudinal section view). The heat transfer tube 13 has a flat shape, and is arranged so that the longitudinal direction of the heat transfer tube 13 is orthogonal to the extending direction S1. Moreover, each heat exchanger tube 13 is arrange | positioned at equal intervals. The other heat exchange unit 70B has the same shape as the heat exchange unit 70A.

また、熱交換部７０Ａ，７０Ｂは、プロペラファン６０の中心軸Ｏを通る仮想水平面Ｓを基準に分割して配置され、当該熱交換部７０Ａ，７０Ｂが傾斜した状態で配置されることで、各伝熱管１３の長手方向の下流側が中心軸Ｏを向くように構成されている。また、仮想水平面Ｓの上下において、熱交換部７０Ａにおける伝熱管１３の傾斜角度と、熱交換部７０Ｂにおける伝熱管１３の傾斜角度は対称に構成されている。また、傾斜角度は、第１実施形態と同様に決めることができる。なお、空気調和機の室外機８Ｅとしての運転動作も第１実施形態と同様である。   Further, the heat exchanging units 70A and 70B are divided and arranged on the basis of the virtual horizontal plane S passing through the central axis O of the propeller fan 60, and the heat exchanging units 70A and 70B are arranged in an inclined state. The downstream side in the longitudinal direction of the heat transfer tube 13 is configured to face the central axis O. In addition, above and below the virtual horizontal plane S, the inclination angle of the heat transfer tube 13 in the heat exchange unit 70A and the inclination angle of the heat transfer tube 13 in the heat exchange unit 70B are configured symmetrically. Further, the inclination angle can be determined in the same manner as in the first embodiment. In addition, the operation | movement operation | movement as the outdoor unit 8E of an air conditioner is the same as that of 1st Embodiment.

このように、第６実施形態によれば、第１実施形態と同様の効果が得られるとともに、熱交換部７０Ａ，７０Ｂを同様の構成にできるので、室外熱交換器７０の作り勝手を向上できる。また、室外熱交換器７０を製作後に傾斜角度の調整が可能となるため、より最適な角度にすることが可能になる。   As described above, according to the sixth embodiment, the same effects as those of the first embodiment can be obtained, and the heat exchange units 70A and 70B can be configured in the same manner, so that the ease of making the outdoor heat exchanger 70 can be improved. . Further, since the inclination angle can be adjusted after the outdoor heat exchanger 70 is manufactured, a more optimal angle can be obtained.

なお、第６実施形態では、仮想水平面Ｓを基準にして、熱交換部７０Ａ，７０Ｂとして２分割した場合を例に挙げて説明したが、プロペラファン６０の風速分布に応じて、プロペラファン６０の中心軸Ｏを通る仮想水平面Ｓを基準にして４分割としてもよく、それ以上の分割数にしてもよい。また、仮想水平面Ｓを基準にして上下の分割数を同じする構成に限定されるものではなく、上下で分割数を変えてもよい。   In the sixth embodiment, the case where the heat exchange units 70A and 70B are divided into two parts with reference to the virtual horizontal plane S has been described as an example. However, according to the wind speed distribution of the propeller fan 60, the propeller fan 60 With reference to the virtual horizontal plane S passing through the central axis O, the number of divisions may be four or more. Further, the number of divisions in the upper and lower parts is not limited to the same with respect to the virtual horizontal plane S, and the number of divisions may be changed in the upper and lower parts.

図１２は、伝熱管の形状の変形例を示す縦断面図である。
図１２に示すように、伝熱管１３０は、１３ａ，１３ｂを有する扁平形状の伝熱管１３（図２参照）に替えて、扁平形状である翼形状としたものである。この伝熱管１３０は、例えば、前縁１３０ａから後縁１３０ｂに向けて、厚みが徐々に薄くなる形状である。このような形状であっても、伝熱管１３０の上面１３０ｃに付着した凝縮水の滞留を抑制できるとともに、プロペラファン６０への空気を整流できる。なお、図１２では、伝熱管１３０の断面形状を翼形状としたが、扁平形状であり、かつ、凝縮水の滞留を抑制できるものであれば、断面視扁平な楕円形状などであってもよい。 FIG. 12 is a longitudinal sectional view showing a modification of the shape of the heat transfer tube.
As shown in FIG. 12, the heat transfer tube 130 has a flat blade shape instead of the flat heat transfer tube 13 (see FIG. 2) having 13 a and 13 b. For example, the heat transfer tube 130 has a shape in which the thickness gradually decreases from the front edge 130a toward the rear edge 130b. Even if it is such a shape, while the condensate water adhering to the upper surface 130c of the heat exchanger tube 130 can be suppressed, the air to the propeller fan 60 can be rectified. In FIG. 12, the cross-sectional shape of the heat transfer tube 130 is a blade shape, but may be an elliptical shape that is flat in cross section as long as it has a flat shape and can suppress the retention of condensed water. .

なお、本発明は前記した実施形態に限定されるものではなく、本発明の趣旨を逸脱しない範囲において種々変更することができる。例えば、第１実施形態ないし第６実施形態の複数を選択して適用してもよい。また、図１２に示す伝熱管１３０を第１実施形態ないし第６実施形態に適用してもよい。   In addition, this invention is not limited to above-described embodiment, In the range which does not deviate from the meaning of this invention, it can change variously. For example, a plurality of the first to sixth embodiments may be selected and applied. Moreover, you may apply the heat exchanger tube 130 shown in FIG. 12 to 1st Embodiment thru | or 6th Embodiment.

１ 圧縮機
２ 四方弁
３ 室外熱交換器（室外熱交換手段）
４ 冷暖房用の絞り装置（流量制御弁)
５ 室内熱交換器
６ 室外送風手段
７ 室内送風手段
８ 室外ユニット
９ 室内ユニット
１０、１１ 接続配管
１２ 板状フィン
１３，１３Ａ〜１３Ｎ，１３Ａ´〜１３Ｎ´，１３Ｐ〜１３Ｓ 伝熱管
１３ａ，１３ｂ 平面部
６０ プロペラファン
６１ ベルマウス
α１〜α７，β１〜β４ 傾斜角度
Ａ，Ａ１、Ａ２ 空気の流れ方向
Ｏ 中心軸
Ｓ 仮想水平面 1 Compressor 2 Four-way valve 3 Outdoor heat exchanger (outdoor heat exchange means)
4 Throttle device for air conditioning (flow control valve)
DESCRIPTION OF SYMBOLS 5 Indoor heat exchanger 6 Outdoor ventilation means 7 Indoor ventilation means 8 Outdoor unit 9 Indoor unit 10, 11 Connection piping 12 Plate-like fin 13, 13A-13N, 13A'-13N ', 13P-13S Heat transfer pipe 13a, 13b Plane part 60 Propeller fan 61 Bellmouth α1-α7, β1-β4 Inclination angle A, A1, A2 Air flow direction O Central axis S Virtual horizontal plane

Claims (7)

上下方向に複数段に配置された伝熱管およびフィンを含む室外熱交換手段と、
前記室外熱交換手段の下流側に配置されるプロペラファンを含む室外送風手段と、を備え、
前記室外熱交換手段は、前記プロペラファンと対向して配置されるとともに、前記フィンが前記プロペラファンの中心軸に直交する上下方向に直線状に延び、
前記伝熱管は扁平形状であり、かつ、前記プロペラファンの中心軸を通る仮想水平面に対して上方に位置する前記伝熱管のすべては下流側が前記仮想水平面を向くように傾斜状態で配置されていることを特徴とする空気調和機の室外機。 Outdoor heat exchange means including heat transfer tubes and fins arranged in a plurality of stages in the vertical direction;
An outdoor air blowing means including a propeller fan disposed on the downstream side of the outdoor heat exchange means,
The outdoor heat exchanging means is arranged to face the propeller fan, and the fins extend linearly in the vertical direction perpendicular to the central axis of the propeller fan,
The heat transfer tubes have a flat shape, and all of the heat transfer tubes located above the virtual horizontal plane passing through the central axis of the propeller fan are arranged in an inclined state so that the downstream side faces the virtual horizontal plane. An air conditioner outdoor unit characterized by the above. 上下方向に複数段に配置された伝熱管およびフィンを含む室外熱交換手段と、
前記室外熱交換手段の下流側に配置されるプロペラファンを含む室外送風手段と、を備え、
前記室外熱交換手段は、前記プロペラファンと対向して配置されるとともに、前記フィンが前記プロペラファンの中心軸に直交する上下方向に直線状に延び、
前記伝熱管は扁平形状であり、かつ、前記プロペラファンの中心軸を通る仮想水平面に対して下方に位置する前記伝熱管のすべては下流側が上方を向くように傾斜状態で配置されていることを特徴とする空気調和機の室外機。 Outdoor heat exchange means including heat transfer tubes and fins arranged in a plurality of stages in the vertical direction;
An outdoor air blowing means including a propeller fan disposed on the downstream side of the outdoor heat exchange means,
The outdoor heat exchanging means is arranged to face the propeller fan, and the fins extend linearly in the vertical direction perpendicular to the central axis of the propeller fan,
The heat transfer tubes have a flat shape, and all of the heat transfer tubes located below the virtual horizontal plane passing through the central axis of the propeller fan are arranged in an inclined state so that the downstream side faces upward. A featured outdoor unit of an air conditioner. 前記伝熱管は、各段毎または複数段毎に、前記中心軸から離れるほど前記仮想水平面に対する傾斜角度が大きいことを特徴とする請求項１又は２に記載の空気調和機の室外機。   3. The outdoor unit for an air conditioner according to claim 1, wherein the heat transfer tube has a larger inclination angle with respect to the virtual horizontal plane as the distance from the central axis increases at each stage or every plurality of stages. 前記室外熱交換手段は、前記中心軸を通る前記仮想水平面を基準にして上下対称に構成されていることを特徴とする請求項１から請求項３のいずれか１項に記載の空気調和機の室外機。 The air conditioner according to any one of claims 1 to 3 , wherein the outdoor heat exchange means is configured to be vertically symmetrical with respect to the virtual horizontal plane passing through the central axis. Outdoor unit. 前記室外熱交換手段は、空気の流れ方向に沿って複数列に配置され、一の前記室外熱交換手段の前記伝熱管の延長線上に他の前記室外熱交換手段の前記伝熱管が配置されていないことを特徴とする請求項１から請求項４のいずれか１項に記載の空気調和機の室外機。 The outdoor heat exchange means are arranged in a plurality of rows along the flow direction of the air, the heat transfer tubes of the other of the outdoor heat exchanger means is disposed on the extension of the heat transfer tube one of the outdoor heat exchange means It is not, The outdoor unit of the air conditioner of any one of Claims 1-4 characterized by the above-mentioned. 前記中心軸に近い側における前記伝熱管同士の間隔は、前記中心軸から遠い側における前記伝熱管同士の間隔よりも狭いことを特徴とする請求項１から請求項５のいずれか１項に記載の空気調和機の室外機。 Spacing of the heat transfer tubes between the side closer to the central axis, according to any one of claims 1 to 5, characterized in that narrower than the interval of the heat transfer tubes between the side farther from the central axis the outdoor unit of an air conditioner. 前記伝熱管は、前記上下方向の断面視において翼形状であることを特徴とする請求項１から請求項６のいずれか１項に記載の空気調和機の室外機。 The heat transfer tubes, an outdoor unit of an air conditioner according to any one of claims 1 to 6, characterized in that in a cross-sectional view of the vertical direction is wing-shaped.
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EP3534103B1 (en) * 2016-10-28 2020-12-23 Mitsubishi Electric Corporation Heat exchanger and refrigeration cycle device
CN110462326B (en) * 2017-04-04 2021-03-19 三菱电机株式会社 Heat exchanger and refrigeration cycle device
EP3842698A4 (en) * 2018-08-23 2021-11-03 Mitsubishi Electric Corporation Heat exchanger unit, and refrigeration cycle device
JP7229255B2 (en) * 2018-08-23 2023-02-27 三菱電機株式会社 Outdoor unit and refrigeration cycle device
WO2024014381A1 (en) * 2022-07-15 2024-01-18 ダイキン工業株式会社 Heat source unit, and refrigeration device

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4062401A (en) * 1976-05-03 1977-12-13 International Harvester Company Toroidal multifluid segmented heat exchanger
JPH0525173U (en) * 1991-09-11 1993-04-02 三菱重工業株式会社 Air heat exchanger
JPH05312352A (en) * 1992-05-07 1993-11-22 Mitsubishi Heavy Ind Ltd Air-conditioning machine and heat exchanging device
JP2002139282A (en) * 2000-10-31 2002-05-17 Mitsubishi Electric Corp Heat exchanger, refrigerating air conditioner and manufacturing method of heat exchanger
JP4952196B2 (en) * 2005-12-07 2012-06-13 パナソニック株式会社 Heat exchanger
EP2235467A4 (en) * 2007-12-18 2013-10-23 Carrier Corp Heat exchanger for shedding water
JP2010014329A (en) * 2008-07-03 2010-01-21 Daikin Ind Ltd Heat exchanger
JP2010139115A (en) * 2008-12-10 2010-06-24 Sharp Corp Heat exchanger and heat exchanger unit
JP5336914B2 (en) * 2009-04-15 2013-11-06 シャープ株式会社 Heat exchanger and air conditioner equipped with the same
JP2012026615A (en) * 2010-07-21 2012-02-09 Mitsubishi Electric Corp Outdoor unit, and refrigeration cycle apparatus with the same
JP5538503B2 (en) * 2012-10-05 2014-07-02 三菱電機株式会社 Outdoor unit and refrigeration cycle apparatus

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