JP2009150621A - Heat exchanger and air-conditioner - Google Patents

Heat exchanger and air-conditioner Download PDF

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JP2009150621A
JP2009150621A JP2007330528A JP2007330528A JP2009150621A JP 2009150621 A JP2009150621 A JP 2009150621A JP 2007330528 A JP2007330528 A JP 2007330528A JP 2007330528 A JP2007330528 A JP 2007330528A JP 2009150621 A JP2009150621 A JP 2009150621A
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heat exchanger
flat tubes
heat exchange
flat
fins
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Masaaki Sato
全秋 佐藤
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Toshiba Carrier Corp
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Toshiba Carrier Corp
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Abstract

<P>PROBLEM TO BE SOLVED: To provide a heat exchanger having improved performance of draining condensed water deposited on fins and improved heat exchanging efficiency while preventing the one-side flow of refrigerant from split-flow headers into flat tubes. <P>SOLUTION: In the heat exchanger, the plurality of flat tubes 2 in which refrigerant flows are provided in parallel in the direction of opposing flat faces 2a in parallel to one another, the split-flow headers 3 are connected to the upper and lower sides of the flat tubes 2, and the fins 5, 6 which have a plurality of fin face portions 5a, 6a arrayed up and down at spaces where heat exchanging air flows are provided in a plurality of rows between the adjacent flat tubes 2 in the flowing direction of the heat exchanging air. The fin face portions 5a, 6a are inclined to the horizontal direction, and the fin face portions 5a, 6a of the fins 5, 6 in each row which are located adjacent to each other in the flowing direction of the heat exchanging air are inclined in the mutually opposite directions. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

本発明は、熱交換器及び空気調和機に関し、特に、冷媒が流れる複数の扁平管を鉛直方向に配列し、それらの扁平管の間に熱交換用のフィンを配置した熱交換器及びこの熱交換器を用いた空気調和機に関する。   The present invention relates to a heat exchanger and an air conditioner, and in particular, a heat exchanger in which a plurality of flat tubes through which a refrigerant flows are arranged in the vertical direction and fins for heat exchange are arranged between the flat tubes and the heat. The present invention relates to an air conditioner using an exchanger.

例えば、下記特許文献１に記載されているように、冷媒が流れる複数の扁平管を扁平面を平行に対向させて鉛直方向に配列し、扁平管の上下両端に冷媒が流れる分流用ヘッダを接続し、隣り合って位置する扁平管の間に熱交換用コルゲートフィンを配置した熱交換器が知られている。コルゲートフィンは、ろう付けや接着等により扁平管の扁平面に接合され又は密着されている。なお、特許文献１に記載された熱交換器では、コルゲートフィンは、熱交換空気の通風方向に沿った上流側から見た場合に山型形状となるように形成されている。   For example, as described in Patent Document 1 below, a plurality of flat tubes through which a refrigerant flows are arranged in a vertical direction with the flat surfaces facing each other in parallel, and a diversion header through which the refrigerant flows is connected to the upper and lower ends of the flat tube And the heat exchanger which has arrange | positioned the corrugated fin for heat exchange between the flat tubes located adjacently is known. The corrugated fin is joined or closely adhered to the flat surface of the flat tube by brazing, bonding, or the like. In the heat exchanger described in Patent Document 1, the corrugated fin is formed in a mountain shape when viewed from the upstream side along the ventilation direction of the heat exchange air.

扁平管を鉛直方向に配列するとともに扁平管の上下両端に分流用ヘッダを接続することにより、分流用ヘッダから各扁平管に流入する冷媒の片寄りを防止することができる。   By arranging the flat tubes in the vertical direction and connecting the diversion headers to the upper and lower ends of the flat tubes, it is possible to prevent the refrigerant from flowing into the flat tubes from the diversion headers.

また、コルゲートフィンを山型形状に形成することにより、コルゲートフィンに付着した凝縮水はコルゲートフィンの傾斜に沿って流れ落ちるようになり、コルゲートフィンの水捌け性を向上させることができる。
特開２００４−１７７０３９号公報 In addition, by forming the corrugated fins in a mountain shape, the condensed water adhering to the corrugated fins flows down along the inclination of the corrugated fins, and the water drainage of the corrugated fins can be improved.
JP 2004-177039 A

しかしながら、前述の熱交換器においては、以下の点について配慮がなされていない。   However, in the above-described heat exchanger, the following points are not considered.

コルゲートフィンを山型形状に形成した場合、コルゲートフィンの上端側又は下端側において、コルゲートフィンが存在しない空間部分が発生する。すると、熱交換器に向けて流れる熱交換空気は、コルゲートフィンが存在せずに通風抵抗が少ない空間部分を大量に通過するようになり、扁平管やコルゲートフィンに当たる空気量が減り、熱交換器の熱交換効率が低下する。   When the corrugated fin is formed in a mountain shape, a space portion where the corrugated fin does not exist is generated on the upper end side or the lower end side of the corrugated fin. Then, the heat exchange air flowing toward the heat exchanger passes through a large amount of space where there is no corrugated fin and low ventilation resistance, reducing the amount of air hitting the flat tube and corrugated fin, and the heat exchanger The heat exchange efficiency is reduced.

本発明は、このような課題を解決するためになされたもので、その目的は、分流用ヘッダから各扁平管に流入する冷媒の片寄りを防止できるとともにフィンに付着した凝縮水の水捌け性を向上させることができ、しかも、熱交換効率を向上させることができる熱交換器及びこの熱交換器を用いた空気調和機を提供することである。   The present invention has been made in order to solve such a problem. The purpose of the present invention is to prevent misalignment of the refrigerant flowing into each flat tube from the diversion header and to prevent the condensed water from adhering to the fins from draining. An object of the present invention is to provide a heat exchanger capable of improving the heat exchange efficiency and an air conditioner using the heat exchanger.

本発明の実施の形態に係る第１の特徴は、冷媒が流れる複数の扁平管を扁平面が互いに平行に対向する向きに並設し、これらの扁平管の上下に分流用ヘッダを接続し、複数のフィン面部を熱交換空気が通風可能な間隔をもって上下に配列したフィンを隣り合う前記扁平管の間に熱交換空気の通風方向に複数列設けた熱交換器において、前記フィン面部を水平方向に対して傾斜させ、前記フィン面部の傾斜方向を熱交換空気の通風方向に隣り合って位置する各列間の前記フィンにおいて互いに逆方向としたことである。   The first feature according to the embodiment of the present invention is that a plurality of flat tubes through which refrigerant flows are arranged in parallel so that the flat surfaces face each other in parallel, and a shunt header is connected above and below these flat tubes, In a heat exchanger in which a plurality of fin surface portions are arranged in rows above and below adjacent flat tubes with a plurality of fin surface portions arranged vertically at intervals allowing heat exchange air to flow, the fin surface portions are arranged in a horizontal direction. And the direction of inclination of the fin surface portion is opposite to each other in the fins between the rows located adjacent to each other in the ventilation direction of the heat exchange air.

本発明の実施の形態に係る第２の特徴は、圧縮機と室外熱交換器と膨張装置と室内熱交換器とを順次接続した空気調和機において、前記室外熱交換器と前記室内熱交換器との少なくとも一方は本発明の実施の形態に係る第１の特徴の熱交換器である。   According to a second aspect of the present invention, there is provided an air conditioner in which a compressor, an outdoor heat exchanger, an expansion device, and an indoor heat exchanger are sequentially connected, the outdoor heat exchanger and the indoor heat exchanger. And at least one of them is a heat exchanger having the first feature according to the embodiment of the present invention.

本発明によれば、分流用ヘッダから各扁平管に流入する冷媒の片寄りを防止できるとともにフィンに付着した凝縮水の水捌け性を向上させることができ、しかも、熱交換効率を向上させることができる。   According to the present invention, it is possible to prevent the refrigerant from flowing into each flat tube from the diversion header, to improve the drainage of the condensed water attached to the fins, and to improve the heat exchange efficiency. it can.

以下、本発明の実施の形態を図面を用いて説明する。   Hereinafter, embodiments of the present invention will be described with reference to the drawings.

（第１の実施の形態）
本発明の第１の実施の形態に係る熱交換器１は、図１に示すように、複数の扁平管２と、扁平管２の両端側に接続された分流用ヘッダ３、４と、隣り合う扁平管２の間に固定されたフィンであるコルゲートフィン５、６とを備えている。なお、コルゲートフィン５、６は、熱交換器１に向けて通風される熱交換空気の通風方向である上流側と下流側とに配置されている。熱交換空気の通風方向は図２に示す矢印Ａ方向であり、図１においては、熱交換空気の通風方向の上流側に位置するコルゲートフィン５のみが見えている。 (First embodiment)
As shown in FIG. 1, the heat exchanger 1 according to the first embodiment of the present invention is adjacent to a plurality of flat tubes 2 and diversion headers 3 and 4 connected to both ends of the flat tubes 2. Corrugated fins 5 and 6 which are fins fixed between the matching flat tubes 2 are provided. In addition, the corrugated fins 5 and 6 are arrange | positioned at the upstream and downstream which are the ventilation direction of the heat exchange air ventilated toward the heat exchanger 1. FIG. The ventilation direction of the heat exchange air is the direction of arrow A shown in FIG. 2, and in FIG. 1, only the corrugated fins 5 located on the upstream side of the ventilation direction of the heat exchange air are visible.

複数の扁平管２は、長手方向が鉛直方向となる上下方向向きに配列され、隣り合う扁平管２は、扁平管２における扁平方向の面である扁平面２ａが互いに平行に対向する向きに並設されている。扁平管２は冷媒が流れる管であり、冷媒が流れる複数の孔２ｂを有する多孔管構造とされている。   The plurality of flat tubes 2 are arranged in the vertical direction in which the longitudinal direction is the vertical direction, and the adjacent flat tubes 2 are arranged in such a manner that the flat surfaces 2a that are flat surfaces of the flat tubes 2 face each other in parallel. It is installed. The flat tube 2 is a tube through which a refrigerant flows, and has a porous tube structure having a plurality of holes 2b through which the refrigerant flows.

分流用ヘッダ３、４は水平向きに配列されて冷媒が流れる管であり、下方に位置する一方の分流用ヘッダ３には扁平管２の下端側が接続され、上方に位置する他方の分流用ヘッダ４には扁平管２の上端側が接続されている。分流用ヘッダ３の一端には冷媒の流出入用の接続管７が接続され、分流用ヘッダ４の一端には冷媒の流出入用の接続管８が接続されている。接続管７、８は、熱交換器１が蒸発器として作動する場合には、下側の接続管７が冷媒流入用として用いられ、上側の接続管８が冷媒流出用として用いられる。そして、下側の分流用ヘッダ３に流入した液状冷媒は、各扁平管２内を流通して上側の分流用ヘッダ４へと至ったのち、接続管８から熱交換器１の外部へと流出する。   The diversion headers 3 and 4 are horizontally arranged pipes through which the refrigerant flows. One of the diversion headers 3 positioned below is connected to the lower end of the flat tube 2 and the other diversion header located above. 4 is connected to the upper end side of the flat tube 2. A connection pipe 7 for refrigerant inflow / outflow is connected to one end of the diversion header 3, and a connection pipe 8 for refrigerant inflow / outflow is connected to one end of the diversion header 4. When the heat exchanger 1 operates as an evaporator, the lower connection pipe 7 is used for refrigerant inflow and the upper connection pipe 8 is used for refrigerant outflow. The liquid refrigerant that has flowed into the lower diversion header 3 flows through the respective flat tubes 2 to reach the upper diversion header 4, and then flows out from the connection pipe 8 to the outside of the heat exchanger 1. To do.

図２は、熱交換器１の一部を示す水平断面図である。隣り合う扁平管２の間には、コルゲートフィン５、６が固定されている。図２において示す矢印Ａ方向が、熱交換器１に向かう熱交換空気の通風方向であり、コルゲートフィン５、６は熱交換空気の通風方向と交差する向きに配置され、一方のコルゲートフィン５が熱交換空気の通風方向の上流側に配置され、他方のコルゲートフィン６が熱交換空気の通風方向の下流側に配置されている。   FIG. 2 is a horizontal sectional view showing a part of the heat exchanger 1. Corrugated fins 5 and 6 are fixed between adjacent flat tubes 2. The arrow A direction shown in FIG. 2 is the ventilation direction of the heat exchange air toward the heat exchanger 1, and the corrugated fins 5 and 6 are arranged in a direction intersecting with the ventilation direction of the heat exchange air. It arrange | positions in the upstream of the ventilation direction of heat exchange air, and the other corrugated fin 6 is arrange | positioned in the downstream of the ventilation direction of heat exchange air.

コルゲートフィン５は、図３及び図４（ａ）に示すように、アルミニウム製の板状部材を波形に折り曲げることにより形成され、互いに平行に対向して熱交換が行なわれる複数のフィン面部５ａと、扁平管２の扁平面２ａに固定される複数の固定面部５ｂとを有している。フィン５を隣り合う扁平管２の間に固定した場合に、フィン面部５ａは上下方向に配列され、各フィン面部５ａは水平方向に対して傾斜している。この傾斜角度“θ”は、４５°前後（例えば、４５±５°）とされている。また、上下方向で隣り合うフィン面部５ａの間隔は、熱交換空気が通風可能な間隔とされている。固定面部５ｂの扁平管２への固定は、ろう付けや接着等により行なわれている。   As shown in FIGS. 3 and 4A, the corrugated fin 5 is formed by bending a plate-like member made of aluminum into a corrugated shape, and a plurality of fin face portions 5a that are opposed to each other in parallel and perform heat exchange. And a plurality of fixed surface portions 5b fixed to the flat surface 2a of the flat tube 2. When the fins 5 are fixed between the adjacent flat tubes 2, the fin surface portions 5a are arranged in the vertical direction, and each fin surface portion 5a is inclined with respect to the horizontal direction. The inclination angle “θ” is about 45 ° (for example, 45 ± 5 °). Moreover, the space | interval of the fin surface part 5a adjacent in an up-down direction is made into the space | interval which can ventilate heat exchange air. The fixing surface portion 5b is fixed to the flat tube 2 by brazing, bonding, or the like.

コルゲートフィン６の基本的な構造はコルゲートフィン５と同じであり、板状部材を波形に折り曲げることにより形成され、図４（ｂ）に示すように、互いに平行に対向して熱交換が行なわれる複数のフィン面部６ａと、扁平管２の扁平面２ａに固定される複数の固定面部６ｂとを有している。コルゲートフィン６を隣り合う扁平管２の間に固定した場合に、フィン面部６ａは上下方向に配列され、各フィン面部６ａは水平方向に対して傾斜している。この傾斜角度“θ”は、４５°前後（例えば、４５±５°）とされている。また、上下方向で隣り合うフィン面部６ａの間隔は、熱交換空気が通風可能な間隔とされている。固定面部６ｂの扁平管２への固定は、ろう付けや接着等により行なわれている。なお、コルゲートフィン６のフィン面部６ａの傾斜方向と、コルゲートフィン５のフィン面部５ａの傾斜方向とが逆方向となっている。このため、２つのコルゲートフィン５、６を隣り合う扁平管２の間に熱交換空気の通風方向に沿った上流側と下流側とに配列した場合、図４（ｃ）に示すように、フィン面部５ａとフィン面部６ａとが交差した配置状態となる。   The basic structure of the corrugated fins 6 is the same as that of the corrugated fins 5 and is formed by bending a plate-like member into a corrugated shape. As shown in FIG. A plurality of fin surface portions 6a and a plurality of fixed surface portions 6b fixed to the flat surface 2a of the flat tube 2 are provided. When the corrugated fins 6 are fixed between the adjacent flat tubes 2, the fin surface portions 6a are arranged in the vertical direction, and each fin surface portion 6a is inclined with respect to the horizontal direction. The inclination angle “θ” is about 45 ° (for example, 45 ± 5 °). Moreover, the space | interval of the fin surface part 6a adjacent to an up-down direction is made into the space | interval which can ventilate heat exchange air. The fixing surface portion 6b is fixed to the flat tube 2 by brazing, bonding, or the like. The inclination direction of the fin surface portion 6a of the corrugated fin 6 and the inclination direction of the fin surface portion 5a of the corrugated fin 5 are opposite to each other. Therefore, when the two corrugated fins 5 and 6 are arranged between the adjacent flat tubes 2 on the upstream side and the downstream side along the ventilation direction of the heat exchange air, as shown in FIG. It will be in the arrangement state where surface part 5a and fin surface part 6a crossed.

図３に示すように、フィン面部５ａ、６ａの表面には、葉脈状の凹溝９が形成されている。この凹溝９は、フィン面部５ａ、６ａの表面に付着した凝縮水が凹溝９内に入り込んだ場合、その凝縮水をフィン面部５ａ、６ａの傾斜に沿って下向きに導く向きに形成されている。この凹溝９が形成されることにより、フィン面部５ａ、６ａの表面に付着した凝縮水が凹溝９内を流れ落ち、凝縮水の水捌け性が向上する。   As shown in FIG. 3, a leaf-shaped concave groove 9 is formed on the surfaces of the fin surface portions 5a and 6a. The concave groove 9 is formed in a direction to guide the condensed water downward along the inclination of the fin surface portions 5a and 6a when condensed water adhering to the surfaces of the fin surface portions 5a and 6a enters the concave groove 9. Yes. By forming the concave groove 9, the condensed water adhering to the surfaces of the fin surface portions 5a and 6a flows down in the concave groove 9, and the drainage of the condensed water is improved.

扁平管２の扁平面２ａには、上下方向に延びる凹溝１０が形成されている。この凹溝１０が形成されることにより、扁平面２ａ上を流れ落ちた凝縮水が扁平面２ａに到着した後、その一部が凹溝１０内を流れ落ちるようになる。   On the flat surface 2a of the flat tube 2, a concave groove 10 extending in the vertical direction is formed. By forming the concave groove 10, after the condensed water flowing down on the flat surface 2 a arrives at the flat surface 2 a, a part of the condensed water flows down in the concave groove 10.

このような構成において、この熱交換器１においては、複数の扁平管２が鉛直方向に配列され、これらの扁平管２の上下両端に水平向きに配列された分流用ヘッダ３、４が接続されている。このため、分流用ヘッダ３、４から扁平管２に流入する冷媒の片寄りが防止され、全ての扁平管２と全てのコルゲートフィン５、６とが熱交換のために有効に利用され、熱交換器１の熱交換効率が向上する。   In such a configuration, in this heat exchanger 1, a plurality of flat tubes 2 are arranged in the vertical direction, and the diversion headers 3, 4 arranged in the horizontal direction are connected to the upper and lower ends of these flat tubes 2. ing. For this reason, the deviation of the refrigerant flowing into the flat tube 2 from the diversion headers 3 and 4 is prevented, and all the flat tubes 2 and all the corrugated fins 5 and 6 are effectively used for heat exchange. The heat exchange efficiency of the exchanger 1 is improved.

また、コルゲートフィン５、６のフィン面部５ａ、６ａが水平方向に対して傾斜しているため、フィン面部５ａ、６ａに付着した凝縮水がフィン面部５ａ、６ａの傾斜に沿って流れ落ち易くなり、コルゲートフィン５、６に付着した凝縮水の水捌け性を向上させることができる。フィン面部５ａ、６ａの傾斜角度が小さくなるにつれて凝縮水の流れ落ち性が低下するが、フィン面部５ａ、６ａの傾斜角度“θ”を水平面に対して４５°前後とすることにより凝縮水の流れ落ち性を十分に確保することができる。一方、この傾斜角度が大きくなるにつれて隣り合う扁平管２の間におけるコルゲートフィン５、６が存在しない空間（図４（ａ）に示す“Ｘ”、図４（ｂ）に示す“Ｙ”の領域）が増大して熱交換有効面積が減少するので、フィン面部５ａ、６ａの傾斜角度“θ”を水平面に対して４５°前後とすることが好適である。   Further, since the fin surface portions 5a, 6a of the corrugated fins 5, 6 are inclined with respect to the horizontal direction, the condensed water attached to the fin surface portions 5a, 6a is likely to flow down along the inclination of the fin surface portions 5a, 6a. It is possible to improve the drainage of the condensed water adhering to the corrugated fins 5 and 6. As the inclination angle of the fin surface portions 5a and 6a decreases, the flowability of the condensed water decreases. However, by setting the inclination angle “θ” of the fin surface portions 5a and 6a to approximately 45 ° with respect to the horizontal plane, the flowability of the condensed water is reduced. Can be secured sufficiently. On the other hand, as this inclination angle increases, the space where the corrugated fins 5 and 6 do not exist between the adjacent flat tubes 2 ("X" shown in FIG. 4 (a), "Y" shown in FIG. 4 (b)). ) Increases and the heat exchange effective area decreases, it is preferable that the inclination angle “θ” of the fin surface portions 5a and 6a is about 45 ° with respect to the horizontal plane.

さらに、フィン面部５ａ、６ａの上面側に葉脈状の凹溝９が形成されており、フィン面部５ａ、６ａに付着した凝縮水が凹溝9に触れると、凝縮水は速やかに凹溝9内に流れ込む。このため、コルゲートフィン５、６に付着した凝縮水の水捌け性をより一層向上させることができる。   Further, a leaf-shaped concave groove 9 is formed on the upper surface side of the fin surface portions 5a and 6a, and when condensed water adhering to the fin surface portions 5a and 6a touches the concave groove 9, the condensed water is promptly contained in the concave groove 9. Flow into. For this reason, the drainage property of the condensed water adhering to the corrugated fins 5 and 6 can be further improved.

さらに、扁平管２の扁平面２ａに凹溝１０が形成されているため、コルゲートフィン５、６のフィン面部５ａ、６ａを流れ落ちた凝縮水が扁平面２ａに到着した後、その凝縮水の一部が凹溝１０内を速やかに流れ落ちる。このため、扁平面２ａに付着した凝縮水が熱交換空気の通風の妨げになるということが低減され、熱交換器１の熱交換効率の向上を図ることができる。   Furthermore, since the concave groove 10 is formed in the flat surface 2a of the flat tube 2, after the condensed water that has flowed down the fin surface portions 5a and 6a of the corrugated fins 5 and 6 arrives at the flat surface 2a, The part immediately flows down in the groove 10. For this reason, it is reduced that the condensed water adhering to the flat surface 2a obstructs ventilation of the heat exchange air, and the heat exchange efficiency of the heat exchanger 1 can be improved.

２つのコルゲートフィン５、６は、図４に示すように、フィン面部５ａ、６ａの傾斜方向が逆方向に形成され、熱交換空気の通風方向に沿った上流側と下流側とに前後して配置されている。このため、隣り合う扁平管２の間の空間におけるフィン５、６による熱交換空気の通風抵抗を考えた場合、その空間において略均等になる。このため、コルゲートフィン５、６の全体が熱交換のために有効に利用され、熱交換器１の熱交換効率が向上する。なお、隣り合う扁平管２の間の空間に図４（ａ）に示すようなコルゲートフィン５のみが存在する場合には、コルゲートフィン５が存在しない空間“Ｘ”に熱交換空気の流れが集中し、熱交換効率が低下する。また、隣り合う扁平管２の間の空間に図４（ｂ）に示すようなコルゲートフィン６のみが存在する場合には、コルゲートフィン６が存在しない空間“Ｙ”に熱交換空気の流れが集中し、熱交換効率が低下する。   As shown in FIG. 4, the two corrugated fins 5, 6 are formed so that the inclined directions of the fin surface portions 5 a, 6 a are reversed, and the upstream and downstream sides along the ventilation direction of the heat exchange air are moved back and forth. Has been placed. For this reason, when the ventilation resistance of the heat exchange air by the fins 5 and 6 in the space between the adjacent flat tubes 2 is considered, it becomes substantially equal in the space. Therefore, the entire corrugated fins 5 and 6 are effectively used for heat exchange, and the heat exchange efficiency of the heat exchanger 1 is improved. When only the corrugated fins 5 as shown in FIG. 4A exist in the space between the adjacent flat tubes 2, the flow of heat exchange air is concentrated in the space “X” where the corrugated fins 5 do not exist. As a result, the heat exchange efficiency decreases. When only the corrugated fins 6 as shown in FIG. 4B exist in the space between the adjacent flat tubes 2, the flow of heat exchange air is concentrated in the space “Y” where the corrugated fins 6 do not exist. As a result, the heat exchange efficiency decreases.

さらに、２つのコルゲートフィン５、６は、熱交換空気の通風方向に沿って重なる部分は、コルゲートフィン５、６が交差する一部分のみである。このため、熱交換空気の通風方向と交差するコルゲートフィン５の上流側縁部の全体と、熱交換空気の通風方向と交差するコルゲートフィン６の上流側縁部の大部分とが熱交換空気の流れの中に曝されるので、熱交換器１の熱交換効率がさらに高くなる。   Further, the two corrugated fins 5 and 6 overlap with each other along the ventilation direction of the heat exchange air only at a portion where the corrugated fins 5 and 6 intersect. For this reason, the entire upstream edge of the corrugated fin 5 that intersects the ventilation direction of the heat exchange air and the majority of the upstream edge of the corrugated fin 6 that intersects the ventilation direction of the heat exchange air are the heat exchange air. Since it is exposed to the flow, the heat exchange efficiency of the heat exchanger 1 is further increased.

（第２の実施の形態）
本発明の第２の実施の形態に係る熱交換器１Ａを、図５及び図６に基づいて説明する。なお、第１の実施の形態において説明した構成要素と同じ構成要素には同じ符号を付け、重複する説明は省略する。 (Second Embodiment)
A heat exchanger 1A according to a second embodiment of the present invention will be described with reference to FIGS. In addition, the same code | symbol is attached | subjected to the same component as the component demonstrated in 1st Embodiment, and the overlapping description is abbreviate | omitted.

第２の実施の形態に係る熱交換器１Ａの基本的構成は、第１の実施の形態に係る熱交換器１と同じである。第２の実施の形態に係る熱交換器１Ａと第１の実施の形態に係る熱交換器１との異なる点は、複数の扁平管２が、熱交換空気の通風方向に沿った上流側と下流側とに位置して２列設けられている点である。扁平面２ａを平行に対向させた一列目の複数の扁平管２と、扁平面２ａを平行に対向させた２列目の複数の扁平管２とは、図６に示すように、熱交換空気の通風方向（矢印Ａ方向）において重ならない位置に配置されている。言い換えると、一列目の複数の扁平管２と、二列目の複数の扁平管２とは、千鳥状に配列されている。   The basic configuration of the heat exchanger 1A according to the second embodiment is the same as that of the heat exchanger 1 according to the first embodiment. The difference between the heat exchanger 1A according to the second embodiment and the heat exchanger 1 according to the first embodiment is that a plurality of flat tubes 2 are arranged on the upstream side along the ventilation direction of the heat exchange air. Two rows are provided on the downstream side. The plurality of flat tubes 2 in the first row with the flat surfaces 2a facing in parallel and the plurality of flat tubes 2 in the second row with the flat surfaces 2a facing in parallel are, as shown in FIG. Are arranged at positions that do not overlap with each other in the ventilation direction (direction of arrow A). In other words, the plurality of flat tubes 2 in the first row and the plurality of flat tubes 2 in the second row are arranged in a staggered manner.

なお、一列目の複数の扁平管２における隣り合う扁平管２の間には、コルゲートフィン５、６が配置されている。同様に、二列目の複数の扁平管２における隣り合う扁平管２の間には、コルゲートフィン５、６が配置されている。   Corrugated fins 5 and 6 are disposed between adjacent flat tubes 2 in the plurality of flat tubes 2 in the first row. Similarly, corrugated fins 5 and 6 are disposed between adjacent flat tubes 2 in the plurality of flat tubes 2 in the second row.

また、一列目の複数の扁平管２の両端部には分流用ヘッダ３、４が設けられ、二列目の複数の扁平管２の両端部にも分流用ヘッダ３、４が設けられている。そして、一列目の複数の扁平管２の上側に接続された分流用ヘッダ４と、二列目の複数の扁平管２の下側に接続された分流用ヘッダ３とが接続管１１により接続されている。   In addition, flow dividing headers 3 and 4 are provided at both ends of the plurality of flat tubes 2 in the first row, and flow dividing headers 3 and 4 are provided at both ends of the plurality of flat tubes 2 in the second row. . Then, the diversion header 4 connected to the upper side of the plurality of flat tubes 2 in the first row and the diversion header 3 connected to the lower side of the plurality of flat tubes 2 in the second row are connected by the connection tube 11. ing.

このような構成において、熱交換空気が矢印Ａで示す方向に通風された場合、一列目の複数の扁平管２の間に設けられたコルゲートフィン５、６の周囲を通過した熱交換空気は、二列目の複数の扁平管２に当たる。このため、熱交換空気が二列目の扁平管２にほとんど当たらずに素通りするということがなく、二列目の複数の扁平管２に対する熱交換が効率良く行なわれ、熱交換器１Ａの熱交換効率が向上する。   In such a configuration, when the heat exchange air is ventilated in the direction indicated by the arrow A, the heat exchange air that has passed around the corrugated fins 5 and 6 provided between the plurality of flat tubes 2 in the first row is: It hits a plurality of flat tubes 2 in the second row. For this reason, heat exchange air does not almost pass through the second row of flat tubes 2 and does not pass through, and heat exchange with respect to the plurality of flat tubes 2 in the second row is performed efficiently, and the heat of the heat exchanger 1A Exchange efficiency is improved.

（第３の実施の形態）
本発明の第３の実施の形態に係る空気調和機１２を図７に基づいて説明する。この空気調和機１２は、圧縮機１３と、室外熱交換器１４と、膨張装置１５と、室内熱交換器１６とを順次接続して構成されている。圧縮機１３と室外熱交換器１４と室内熱交換器１６との間には、冷媒の流れ方向を逆向きに可変することができる四方切換弁１７が設けられている。この空気調和機１２においては、冷房運転時の冷媒の流れ方向が実線の矢印で示す方向となり、暖房運転時の冷媒の流れ方向が破線の矢印で示す方向となる。 (Third embodiment)
An air conditioner 12 according to a third embodiment of the present invention will be described with reference to FIG. The air conditioner 12 is configured by sequentially connecting a compressor 13, an outdoor heat exchanger 14, an expansion device 15, and an indoor heat exchanger 16. Between the compressor 13, the outdoor heat exchanger 14, and the indoor heat exchanger 16, a four-way switching valve 17 that can change the flow direction of the refrigerant in the reverse direction is provided. In the air conditioner 12, the refrigerant flow direction during the cooling operation is a direction indicated by a solid line arrow, and the refrigerant flow direction during the heating operation is a direction indicated by a broken line arrow.

また、この空気調和機１２においては、第１の実施の形態で説明した熱交換器１、又は、第２の実施の形態で説明した熱交換器１Ａが、室外熱交換器１４として用いられている。   In this air conditioner 12, the heat exchanger 1 described in the first embodiment or the heat exchanger 1A described in the second embodiment is used as the outdoor heat exchanger 14. Yes.

このような構成において、この空気調和機１２では暖房運転時には冷媒が破線で示す矢印方向に流れ、圧縮機１３により圧縮されて高温・高圧となった冷媒（気体）は、室内熱交換器１６に送られ、室内熱交換器１６内においてファンによる送風を受け、冷媒は放熱して液化する。この放熱により、室内が暖房される。液化した冷媒は膨張装置１５において低圧・低温の霧状の冷媒となる。この霧状の冷媒が室外熱交換器１４において気化し、室外から気化熱を奪い、この熱が室内の暖房のために用いられる。冷房運転時には、冷媒の流れ方向が暖房運転時と逆向きとなり、室内が冷房される。   In such a configuration, in the air conditioner 12, during the heating operation, the refrigerant flows in the arrow direction indicated by the broken line, and the refrigerant (gas) compressed by the compressor 13 and having a high temperature and a high pressure is transferred to the indoor heat exchanger 16. The air is sent by the fan in the indoor heat exchanger 16, and the refrigerant dissipates heat and liquefies. The room is heated by this heat radiation. The liquefied refrigerant becomes a low-pressure and low-temperature mist refrigerant in the expansion device 15. This mist-like refrigerant is vaporized in the outdoor heat exchanger 14, takes heat of vaporization from the outside, and this heat is used for indoor heating. During the cooling operation, the flow direction of the refrigerant is opposite to that during the heating operation, and the room is cooled.

この空気調和機１２においては、室外熱交換器１４として、第１の実施の形態で説明した熱交換器１、又は、第２の実施の形態で説明した熱交換器１Ａが用いられているため、熱交換効率を向上させることができ、冷房効果及び暖房効果の高い空気調和機１２を得ることができる。   In this air conditioner 12, the heat exchanger 1 described in the first embodiment or the heat exchanger 1A described in the second embodiment is used as the outdoor heat exchanger 14. Further, the heat exchange efficiency can be improved, and the air conditioner 12 having a high cooling effect and heating effect can be obtained.

なお、本実施の形態では、第１の実施形態に係る熱交換器１又は第２の実施の形態に係る熱交換器１Ａを室外熱交換器１４として使用した場合について説明したが、室内熱交換器１６において使用してもよい。   In the present embodiment, the case where the heat exchanger 1A according to the first embodiment or the heat exchanger 1A according to the second embodiment is used as the outdoor heat exchanger 14 has been described. It may be used in the vessel 16.

本発明の第１の実施の形態に係る熱交換器を示す斜視図である。It is a perspective view which shows the heat exchanger which concerns on the 1st Embodiment of this invention. その一部を示す水平断面図である。It is a horizontal sectional view showing a part thereof. コルゲートフィンの一部を示す斜視図である。It is a perspective view which shows a part of corrugated fin. コルゲートフィンの配置状態を示す説明図である。It is explanatory drawing which shows the arrangement | positioning state of a corrugated fin. 本発明の第２の実施の形態に係る熱交換器を示す斜視図である。It is a perspective view which shows the heat exchanger which concerns on the 2nd Embodiment of this invention. その一部を示す水平断面図である。It is a horizontal sectional view showing a part thereof. 本発明の第３の実施の形態に係る空気調和機の概略構造を示すブロック図である。It is a block diagram which shows schematic structure of the air conditioner which concerns on the 3rd Embodiment of this invention.

符号の説明Explanation of symbols

１…熱交換器、１Ａ…熱交換器、２…扁平管、２ａ…扁平面、３、４…分流用ヘッダ、５、６…コルゲートフィン（フィン）、５ａ、６ａ…フィン面部、９…葉脈状の凹溝、１０…凹溝、１２…空気調和機、１３…圧縮機、１４…室外熱交換器、１５…膨張装置、１６…室内熱交換器   DESCRIPTION OF SYMBOLS 1 ... Heat exchanger, 1A ... Heat exchanger, 2 ... Flat tube, 2a ... Flat surface, 3, 4 ... Header for diversion, 5, 6 ... Corrugated fin (fin), 5a, 6a ... Fin surface part, 9 ... Leaf vein Concave groove, 10 ... concave groove, 12 ... air conditioner, 13 ... compressor, 14 ... outdoor heat exchanger, 15 ... expansion device, 16 ... indoor heat exchanger

Claims (5)

冷媒が流れる複数の扁平管を扁平面が互いに平行に対向する向きに並設し、これらの扁平管の上下に分流用ヘッダを接続し、複数のフィン面部を熱交換空気が通風可能な間隔をもって上下に配列したフィンを隣り合う前記扁平管の間に熱交換空気の通風方向に複数列設けた熱交換器において、
前記フィン面部を水平方向に対して傾斜させ、前記フィン面部の傾斜方向を熱交換空気の通風方向に隣り合って位置する各列間の前記フィンにおいて互いに逆方向としたことを特徴とする熱交換器。 A plurality of flat tubes through which the refrigerant flows are arranged in parallel so that the flat surfaces face each other in parallel, and a shunt header is connected to the top and bottom of these flat tubes, and the plurality of fin surface portions are spaced at intervals through which heat exchange air can be ventilated. In the heat exchanger provided with a plurality of rows in the direction of ventilation of the heat exchange air between the flat tubes adjacent to the fins arranged vertically,
The fin surface portion is inclined with respect to the horizontal direction, and the inclined direction of the fin surface portion is opposite to each other in the fins between the rows located adjacent to the ventilation direction of heat exchange air. vessel. 前記フィン面部の表面に、葉脈状の凹溝が形成されていることを特徴とする請求項１記載の熱交換器。   The heat exchanger according to claim 1, wherein a leaf-shaped concave groove is formed on a surface of the fin surface portion. 前記扁平管の前記扁平面に、上下方向に延びる凹溝が形成されていることを特徴とする請求項１又は２記載の熱交換器。   The heat exchanger according to claim 1 or 2, wherein a concave groove extending in a vertical direction is formed in the flat surface of the flat tube. 前記扁平管が熱交換空気の通風方向に複数列設けられ、熱交換空気の通風方向に隣り合って位置する各列の前記扁平管は、熱交換空気の通風方向において重ならない位置に配置されていることを特徴とする請求項１ないし３のいずれか一に記載の熱交換器。   The flat tubes are provided in a plurality of rows in the direction of ventilation of the heat exchange air, and the flat tubes in each row located adjacent to the direction of ventilation of the heat exchange air are arranged at positions that do not overlap in the direction of ventilation of the heat exchange air. The heat exchanger according to any one of claims 1 to 3, wherein the heat exchanger is provided. 圧縮機と室外熱交換器と膨張装置と室内熱交換器とを順次接続した空気調和機において、
前記室外熱交換器と前記室内熱交換器との少なくとも一方は請求項１ないし４のいずれか一に記載の熱交換器であることを特徴とする空気調和機。 In an air conditioner in which a compressor, an outdoor heat exchanger, an expansion device, and an indoor heat exchanger are sequentially connected,
An air conditioner, wherein at least one of the outdoor heat exchanger and the indoor heat exchanger is the heat exchanger according to any one of claims 1 to 4.
JP2007330528A 2007-12-21 2007-12-21 Heat exchanger and air-conditioner Pending JP2009150621A (en)

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JP2015180852A (en) * 2015-07-24 2015-10-15 株式会社小松製作所 Corrugated fin and heat exchanger including the same
WO2017020666A1 (en) * 2015-08-05 2017-02-09 丹佛斯微通道换热器（嘉兴）有限公司 Heat exchanger
JP2019002588A (en) * 2017-06-12 2019-01-10 株式会社デンソー Heat exchanger and corrugated fin
US11187432B2 (en) 2017-06-12 2021-11-30 Denso Corporation Heat exchanger and corrugated fin
JP7305085B1 (en) * 2022-04-12 2023-07-07 三菱電機株式会社 Heat exchanger and refrigeration cycle equipment
WO2023199400A1 (en) * 2022-04-12 2023-10-19 三菱電機株式会社 Heat exchanger and refrigeration cycle device

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