JP2006097953A - Heat exchanger with fin - Google Patents

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JP2006097953A
JP2006097953A JP2004283872A JP2004283872A JP2006097953A JP 2006097953 A JP2006097953 A JP 2006097953A JP 2004283872 A JP2004283872 A JP 2004283872A JP 2004283872 A JP2004283872 A JP 2004283872A JP 2006097953 A JP2006097953 A JP 2006097953A
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heat exchanger
heat transfer
fin
transfer tube
fins
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Shigeto Yamaguchi
成人 山口
Shoichi Yokoyama
昭一 横山
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Panasonic Holdings Corp
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Matsushita Electric Industrial Co Ltd
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Abstract

<P>PROBLEM TO BE SOLVED: To house a heat exchanger with a fin inserted with as many heat exchanger tubes as possible, and having heat exchanger tubes with at least two types of outer diameters in a space with a small depth so as to prevent dripping of condensed water attached to the heat exchanger in an indoor unit of an air conditioner, to extensively improve a heat exchange capacity, and to efficiently and inexpensively manufacture the heat exchanger with the fin. <P>SOLUTION: Fins of a substantially rectangular back face side heat exchanger, and fins of a substantially doglegged front face side heat exchanger wherein a shortest distance between an outer diameter center of a heat exchanger tube most nearest to each straight parts of an upwind front rim and an upwind rear rim of a fin, and the upwind front rim or the upwind rear rim is not constant in the same heat exchanger tube row is composed to allow easy flowing of the condensed water along the fins. The fins are connected, and combined with fin collars with different diameters to form them as one fin by continuous press working. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

本発明は、空気調和機の室内ユニットに搭載されるフィン付き熱交換器に関する。   The present invention relates to a finned heat exchanger mounted on an indoor unit of an air conditioner.

一般に空気調和機の室内ユニットは、図７に示すように、筐体６１に、前面の吸込み口６２ａおよび上面の吸込み口６２ｂなど一箇所以上の吸込み口と、下面の吹出し口６３など一箇所以上の吹出し口とが設けられ、この筐体６１内に貫流送風機６５とフィン付き熱交換器６４とが収納されている。   In general, an indoor unit of an air conditioner includes, as shown in FIG. 7, at least one suction port such as a front suction port 62a and an upper suction port 62b, and one or more suction ports 63 such as a lower suction port 63. And a once-through fan 65 and a heat exchanger 64 with fins are accommodated in the casing 61.

この従来のフィン付き熱交換器６４は、筐体６１内の前面側に配置され、上下方向中央部近辺で折り曲げ加工された主たる前面側熱交換器６４Ａと、筐体６１内の背面側に配置された背面側熱交換器６４Ｂと、前面側熱交換器６４Ａの前面にそれぞれ補助的に取り付けられた補助熱交換器６４Ｃとから構成されている。そして、前面側熱交換器６４Ａおよび背面側熱交換器６４Ｂにより貫流送風機６５を風上側から取り囲むような形態に配置して、限られた空間にできるだけ大きいフィン付き熱交換器を収納している。なお、補助熱交換器６４Ｃは熱交換能力を向上させるために設けているものだが、主たる前面側熱交換器６４Ａや背面側熱交換器６４Ｂとは別の工程で製造した後、主たる前面側熱交換器６４Ａや背面側熱交換器６４Ｂに追加接続されて取り付けられるもので、図７では、主たる前面側熱交換器６４Ａに追加接続されている場合を示している。また、前面側熱交換器６４Ａの折り曲げ部近辺には、単に前面側熱交換器６４Ａを折り曲げてフィンがない空間があいてしまうと、殆ど熱交換しないで気流がフィン付き熱交換器を通過してしまうおそれがあるため、このようなことがないように、スペーサ６６が配設されている。   This conventional finned heat exchanger 64 is arranged on the front side in the casing 61, and is arranged on the main front side heat exchanger 64 </ b> A bent near the center in the vertical direction and on the back side in the casing 61. The rear-side heat exchanger 64B and the auxiliary heat exchanger 64C attached to the front surface of the front-side heat exchanger 64A, respectively. And it arrange | positions in the form which surrounds the once-through fan 65 from the windward side by 64 A of front side heat exchangers, and the back side heat exchanger 64B, and accommodates the heat exchanger with a fin as large as possible in the limited space. The auxiliary heat exchanger 64C is provided to improve the heat exchanging capacity. However, after the auxiliary heat exchanger 64C is manufactured in a separate process from the main front side heat exchanger 64A and the rear side heat exchanger 64B, the main front side heat is supplied. It is attached by being additionally connected to the exchanger 64A and the back side heat exchanger 64B, and FIG. 7 shows a case where it is additionally connected to the main front side heat exchanger 64A. Also, if there is a space without fins in the vicinity of the bent portion of the front side heat exchanger 64A by simply bending the front side heat exchanger 64A, the airflow passes through the heat exchanger with fins with little heat exchange. Therefore, the spacer 66 is disposed so as not to cause such a situation.

これに対して、前面側熱交換器６４Ａの折り曲げ加工を不要にし、このスペーサ６６をなくしながら、熱交換しないで気流がフィン付き熱交換器を通過してしまうようなことを防止する構造として、前面側熱交換器を円弧状に形成した構成が開示されている（例えば、特許文献１参照）。   On the other hand, as a structure that eliminates the need to bend the front-side heat exchanger 64A and eliminates the spacer 66 and prevents the airflow from passing through the finned heat exchanger without heat exchange, The structure which formed the front side heat exchanger in circular arc shape is disclosed (for example, refer patent document 1).

この特許文献１には、図８および図９に示すように、前面側熱交換器７１Ａのフィン７２の形状を貫流送風機７３の周面の一部を囲むように円弧状に形成した空気調和機の室内ユニットが開示されている。この前面側熱交換器７１Ａに略直角に挿通された伝熱管７４は、複数列設けられており、これらの伝熱管７４の風上側列と風下側列とで互いに二等辺三角形を描くように配置されている。したがって結果的に、円弧形状部分の内側に配置されている風下側の伝熱管７４の段ピッチＡは、円弧形状部分の外側に配置されている風上側列の伝熱管７４の段ピッチＢよりも小さくなって形成されている。   In this Patent Document 1, as shown in FIGS. 8 and 9, an air conditioner in which the shape of the fin 72 of the front side heat exchanger 71 </ b> A is formed in an arc shape so as to surround a part of the peripheral surface of the once-through fan 73. Indoor units are disclosed. A plurality of rows of heat transfer tubes 74 inserted through the front side heat exchanger 71A at a substantially right angle are provided, and the windward row and the leeward row of these heat transfer tubes 74 are arranged so as to draw an isosceles triangle. Has been. Therefore, as a result, the step pitch A of the leeward heat transfer tubes 74 arranged inside the arc-shaped portion is larger than the step pitch B of the heat-transfer tubes 74 arranged in the outside of the arc-shaped portion. It is formed smaller.

この構成によれば、スペーサ６６が不要になるとともに、製造時のフィン７２の材料においてスペーサ６６に対応する箇所で廃材を生じないため、フィン７２の材料の廃材を少なくでき、また各伝熱管７４同士を連通させるヘアピンやリターンベンドの曲げピッチの種類が、Ａ、Ｂ、Ｃの３種類だけで済む利点がある。また、スペーサ６６を設けていないため、スペーサ６６に対応する箇所分だけフィン７２の面積が増加することとなり、熱交換能力が向上する。
特許第３０９１８３０号公報（第３−８頁、第１図） According to this configuration, the spacer 66 is not necessary, and the waste material is not generated at the location corresponding to the spacer 66 in the material of the fin 72 at the time of manufacture. Therefore, the waste material of the material of the fin 72 can be reduced, and each heat transfer tube 74 is provided. There is an advantage that only three types of bending pitches A, B, and C are required for the hairpins and return bends that communicate with each other. Further, since the spacer 66 is not provided, the area of the fin 72 is increased by the portion corresponding to the spacer 66, and the heat exchange capability is improved.
Japanese Patent No. 3091830 (page 3-8, Fig. 1)

しかしながら、上記従来の構成のフィン付き熱交換器では、前面側熱交換器７１Ａが円弧状であり、フィン７２の上部の傾斜が緩くなるため、フィン付き熱交換器を蒸発器として用いている場合に、フィン７２の上部に凝縮する水が滞留したり、最悪の場合には、凝縮水がフィン７２に沿って流れずに、貫流送風機７３に水滴が落下して、吹出し口７５から水滴が飛散するおそれがある。   However, in the heat exchanger with fins of the above-described conventional configuration, the front-side heat exchanger 71A has an arc shape and the upper portion of the fins 72 has a gentle slope, and therefore the finned heat exchanger is used as an evaporator. In the worst case, the condensed water stays in the upper part of the fins 72. In the worst case, the condensed water does not flow along the fins 72, but the water drops fall on the once-through fan 73, and the water drops are scattered from the outlet 75. There is a risk.

本発明はこのような従来の課題を解決するものであり、フィン付き熱交換器の形態を改善し、空気調和機の室内ユニットの限られた空間、特に奥行きが狭い空間にできるだけ大きなフィン付き熱交換器を収納し、熱交換能力の大幅な向上をはかるとともに、蒸発器として使用したときフィン表面に凝縮する水をフィンに沿って円滑に流下させることができるフィン付き熱交換器を提供することを目的とするものである。   The present invention solves such a conventional problem, improves the configuration of the finned heat exchanger, and heats the finned heat as much as possible in a limited space of the indoor unit of the air conditioner, particularly in a narrow space. To provide a heat exchanger with fins that can store an exchanger, greatly improve the heat exchange capacity, and can smoothly flow down water condensed on the fin surface along the fin when used as an evaporator. It is intended.

本発明の請求項１に係るフィン付き熱交換器は、前面側に吸込み口がおよび下面側に吹出し口がそれぞれ設けられた筐体とこの筐体に収納される貫流送風機とから風回路を構成する空気調和機の室内ユニットに搭載されるフィン付き熱交換器であって、
前記吸込み口から貫流送風機までの風回路の途中または貫流送風機から吹出し口までの風回路の途中に配置される前面側熱交換器と背面側熱交換器とから構成され、
前記前面側熱交換器および前記背面側熱交換器はそれぞれ所定の間隔で平行に並べられてその間を気体が流動する多数のフィンと、このフィンに略直角に挿入されて内部を冷媒が流動する多数の伝熱管とから構成され、
前記前面側熱交換器におけるフィンを、その風上前縁および風下後縁がそれぞれが同じ鈍角をなす２本の直線部並びにこれら２本の直線の間を結ぶ１本の曲線部により、略くの字状に形成するとともに、
略くの字状に形成された前記フィンの直線状の風上前縁と直線状の風下後縁とで挟まれた二つの領域のうち、貫流送風機に近い側の領域における風上前縁と風下後縁との距離を１８〜２４ｍｍにすると共に当該フィン部に挿入される伝熱管、および当該フィンの曲線状の風上前縁と曲線状の風下後縁とで挟まれた領域の部分に挿入される伝熱管の外径を６．０〜８．５にして気体の主流方向に沿う方向となる列方向に２列配置し、また、貫流送風機から遠い側の領域および背面側熱交換器の領域における風上前縁と風下後縁との距離を２４〜３０ｍｍにすると共に、当該フィン部に挿入される伝熱管およびにおけるフィンの風上前縁の直線部と風下後縁の直線部とで挟まれた部分に挿入される伝熱管の外径を４．０〜７．５ｍｍにするとともに、気体の主流方向に沿う列方向に伝熱管を３列で配置したものである。 A finned heat exchanger according to a first aspect of the present invention comprises a wind circuit comprising a casing provided with a suction port on the front side and a blow-out port on the bottom side, and a cross-flow fan accommodated in the casing. A heat exchanger with fins mounted on an indoor unit of an air conditioner,
It is composed of a front side heat exchanger and a back side heat exchanger arranged in the middle of the wind circuit from the inlet to the once-through fan or in the middle of the wind circuit from the once-through fan to the outlet,
The front-side heat exchanger and the back-side heat exchanger are arranged in parallel at predetermined intervals, and a large number of fins through which gas flows, and the refrigerant flows through the fins inserted at substantially right angles. Consisting of a large number of heat transfer tubes,
The fins in the front-side heat exchanger are roughly defined by two straight portions where the windward leading edge and the leeward trailing edge form the same obtuse angle, and one curved portion connecting the two straight lines. While forming in the shape of
Of the two regions sandwiched between the linear windward leading edge and the linear leeward trailing edge of the fin formed in a substantially square shape, the windward leading edge in the region close to the cross-flow fan The distance from the leeward trailing edge is set to 18 to 24 mm, and the heat transfer tube inserted into the fin portion, and the portion of the region sandwiched between the curved leeward leading edge and the curved leeward trailing edge of the fin The outer diameter of the heat transfer tubes to be inserted is 6.0 to 8.5, and two rows are arranged in the row direction along the main flow direction of the gas, and the region far from the cross-flow blower and the rear side heat exchanger The distance between the windward leading edge and the windward trailing edge in the region is 24 to 30 mm, and the straight portion of the windward leading edge and the straight portion of the leeward trailing edge of the fin in the heat transfer tube inserted into the fin portion The outer diameter of the heat transfer tube inserted in the portion sandwiched between It is obtained by placing the heat transfer tube in three rows in the column direction along the main flow direction of the gas.

また、請求項２に係るフィン付き熱交換器は、請求項１記載の熱交換器において、前面側熱交換器におけるフィンの直線状の風上前縁と直線状の風下後縁とで挟まれた二つの領域のうち、貫流送風機から遠い側の領域および背面側熱交換器におけるフィンの風上前縁の直線部と風下後縁の直線部とで挟まれた部分に挿入される伝熱管を２種類の外径の伝熱管で構成し、
且つ大きい方の外径の伝熱管を、気体の流れの最も風上の列に配置するとともに、低循環量で小能力の熱交換器を必要とする場合は、当該フィン付き熱交換器を凝縮器またはガスクーラーとして使用する際の冷媒出口寄りの伝熱管として、または蒸発器として使用する際の冷媒入口寄りの伝熱管として、１パスを用い、小さい方の外径の伝熱管については、当該フィン付き熱交換器を凝縮器またはガスクーラーとして使用する際には、大きい方の外径の前記伝熱管より冷媒上流側の伝熱管として、または蒸発器として使用する際には、大きい方の外径の伝熱管より冷媒下流側の伝熱管として、４パスを用いて、それぞれ冷媒を流すようにしたものである。 The finned heat exchanger according to claim 2 is sandwiched between the straight upwind front edge and the straight downwind trailing edge of the fin in the front side heat exchanger according to claim 1. Of the two regions, a heat transfer tube inserted in a region sandwiched between a straight portion of the windward leading edge and a straight portion of the leeward trailing edge of the fin in the region far from the once-through fan and the rear heat exchanger Consists of two types of outer diameter heat transfer tubes,
In addition, when the heat exchanger tube with the larger outer diameter is placed in the furthest upstream row of the gas flow, and a heat exchanger with a small circulation capacity and a small capacity is required, the finned heat exchanger is condensed. As a heat transfer tube near the refrigerant outlet when used as an evaporator or gas cooler, or as a heat transfer tube near the refrigerant inlet when used as an evaporator, one pass is used for the heat transfer tube with the smaller outer diameter. When using a finned heat exchanger as a condenser or gas cooler, when using it as a heat transfer tube upstream of the refrigerant from the heat transfer tube with the larger outer diameter, or when using it as an evaporator, As the heat transfer tube on the downstream side of the refrigerant with respect to the heat transfer tube having the diameter, the refrigerant is caused to flow through four paths.

また、請求項３に係るフィン付き熱交換器は、請求項１に記載の熱交換器において、前面側熱交換器におけるフィンの直線状の風上前縁と直線状の風下後縁とで挟まれた二つの領域のうち、貫流送風機から遠い側の領域および背面側熱交換器におけるフィンの風上前縁の直線部と風下後縁の直線部とで挟まれた部分に挿入される伝熱管を２種類の外径の伝熱管で構成し、
且つ大きい方の外径の伝熱管を、気体の流れの最も風上の列に配置するとともに、高循環量で大能力の熱交換器を必要とする場合は、当該フィン付き熱交換器を凝縮器またはガスクーラーとして使用する際の冷媒出口寄りの伝熱管として、または蒸発器として使用する際の冷媒入口寄りの伝熱管として２パスを用い、小さい方の外径の伝熱管については、当該フィン付き熱交換器を凝縮器またはガスクーラーとして使用する際には、大きい方の外径の前記伝熱管より冷媒上流側の伝熱管として、または蒸発器として使用する際には、大きい方の外径の伝熱管より冷媒下流側の伝熱管として、５または６パスを用いて、それぞれ冷媒を流すようにしたものである。 The finned heat exchanger according to claim 3 is sandwiched between the linear upwind front edge and the straight downwind trailing edge of the fin in the front side heat exchanger in the heat exchanger according to claim 1. Heat transfer tube inserted into the region between the straight part of the windward leading edge and the straight part of the leeward trailing edge of the fins in the region far from the once-through fan and the rear heat exchanger Consists of two types of outer diameter heat transfer tubes,
In addition, when the heat exchanger tube with the larger outer diameter is placed in the most upwind row of the gas flow, and a high capacity heat exchanger with high circulation rate is required, the finned heat exchanger is condensed. As a heat transfer tube near the refrigerant outlet when used as an evaporator or a gas cooler, or as a heat transfer tube near the refrigerant inlet when used as an evaporator, a two-pass heat transfer tube is used. When the attached heat exchanger is used as a condenser or a gas cooler, the larger outer diameter is used as the heat transfer tube upstream of the refrigerant from the heat transfer tube having the larger outer diameter or as the evaporator. As the heat transfer tube on the downstream side of the refrigerant from the heat transfer tube, 5 or 6 passes are used to flow the refrigerant.

また、請求項４に係るフィン付き熱交換器は、請求２に記載の熱交換器において、前面側熱交換器におけるフィンの直線状の風上前縁と直線状の風下後縁とで挟まれた二つの領域のうち貫流送風機に近い側の領域のフィン部および当該フィンの曲線状の風上前縁と曲線状の風下後縁とで挟まれた領域の部分にそれぞれ挿入される伝熱管を２種類の外径の伝熱管で構成し、
且つ大きい方の外径の前記伝熱管を、気体の流れの最も風下の列に配置するとともに、当該フィン付き熱交換器を凝縮器若しくはガスクーラーとして使用する際の冷媒入口寄りの伝熱管、または蒸発器として使用する際の冷媒出口寄りの伝熱管として用い、
小さい方の外径の前記伝熱管については、当該フィン付き熱交換器を凝縮器若しくはガスクーラーとして使用する際には、大きい方の外径の前記伝熱管より冷媒下流側の伝熱管として、または蒸発器として使用する際には、大きい方の外径の前記伝熱管より冷媒上流側の伝熱管として、それぞれ２パスを用いて冷媒を流すようにしたものである。 A finned heat exchanger according to a fourth aspect is the heat exchanger according to the second aspect, wherein the fin is sandwiched between a straight windward leading edge and a straight leeward trailing edge of the front side heat exchanger. The heat transfer tubes inserted respectively into the fin portion of the region close to the once-through fan and the region of the fin sandwiched between the curved upwind leading edge and the curved downwind trailing edge of the fin. Consists of two types of outer diameter heat transfer tubes,
And the heat transfer tube having the larger outer diameter is arranged in the most leeward row of the gas flow, and the heat transfer tube near the refrigerant inlet when the finned heat exchanger is used as a condenser or a gas cooler, or Used as a heat transfer tube near the refrigerant outlet when used as an evaporator,
For the heat transfer tube having a smaller outer diameter, when the finned heat exchanger is used as a condenser or a gas cooler, as a heat transfer tube downstream of the refrigerant from the heat transfer tube having a larger outer diameter, or When used as an evaporator, the refrigerant is caused to flow using two paths each as a heat transfer tube upstream of the heat transfer tube having a larger outer diameter.

また、請求項５に係るフィン付き熱交換器は、請求項３に記載の熱交換器において、前面側熱交換器におけるフィンの直線状の風上前縁と直線状の風下後縁とで挟まれた二つの領域のうち貫流送風機に近い側の領域のフィン部および当該フィンの曲線状の風上前縁と曲線状の風下後縁とで挟まれた領域の部分にそれぞれ挿入される伝熱管を２種類の外径の伝熱管で構成し、
且つ大きい方の外径の前記伝熱管を、気体の流れの最も風下の列に配置するとともに、当該フィン付き熱交換器を凝縮器若しくはガスクーラーとして使用する際の冷媒入口寄りの伝熱管、または蒸発器として使用する際の冷媒出口寄りの伝熱管として用い、
小さい方の外径の前記伝熱管については、当該フィン付き熱交換器を凝縮器若しくはガスクーラーとして使用する際には、大きい方の外径の前記伝熱管より冷媒下流側の伝熱管として、または蒸発器として使用する際には、大きい方の外径の前記伝熱管より冷媒上流側の伝熱管として、それぞれ３パスを用いて冷媒を流すようにしたものである。 Further, the finned heat exchanger according to claim 5 is the heat exchanger according to claim 3, wherein the fin is sandwiched between the straight windward leading edge and the straight leeward trailing edge of the front-side heat exchanger. Heat transfer tubes inserted into the fin portion of the region close to the once-through fan and the region of the fin sandwiched between the curved upwind leading edge and the curved downwind trailing edge Consists of two types of outer diameter heat transfer tubes,
And the heat transfer tube having the larger outer diameter is arranged in the most leeward row of the gas flow, and the heat transfer tube near the refrigerant inlet when the finned heat exchanger is used as a condenser or a gas cooler, or Used as a heat transfer tube near the refrigerant outlet when used as an evaporator,
For the heat transfer tube having a smaller outer diameter, when the finned heat exchanger is used as a condenser or a gas cooler, as a heat transfer tube downstream of the refrigerant from the heat transfer tube having a larger outer diameter, or When used as an evaporator, the refrigerant is caused to flow using three passes each as a heat transfer tube upstream of the heat transfer tube having a larger outer diameter.

また、請求項６に係るフィン付き熱交換器は、請求項１から５のいずれか一項に記載の熱交換器において、前面側熱交換器におけるフィンの直線状の風上前縁と直線状の風下後縁とで挟まれた二つの領域のうち、貫流送風機から遠い側の領域のフィン部に挿入される伝熱管および背面側熱交換器におけるフィンの風上前縁の直線部と風下後縁の直線部とで挟まれた部分の伝熱管３列の配置ピッチを、１４．５〜１６ｍｍにしたものである。   Moreover, the heat exchanger with a fin which concerns on Claim 6 is a heat exchanger as described in any one of Claim 1 to 5. WHEREIN: The linear upwind front edge of the fin in a front side heat exchanger, and linear form Out of the two areas sandwiched by the leeward trailing edge of the heat exchanger tube inserted into the fin part in the area far from the once-through fan, and the straight part of the fin's windward leading edge and the leeward rear in the rear heat exchanger The arrangement pitch of the three rows of the heat transfer tubes sandwiched between the edge straight portions is 14.5 to 16 mm.

また、請求項７に係るフィン付き熱交換器は、請求項１から５のいずれか一項に記載の熱交換器において、前面側熱交換器におけるフィンの直線状の風上前縁と直線状の風下後縁とで挟まれた二つの領域のうち貫流送風機に近い側の領域のフィン部に挿入される伝熱管を気体の主流方向に沿う方向となる列方向に２列配置し、前記気体の主流方向に直角方向となる段方向に前記伝熱管の配置ピッチを１６〜２２ｍｍとしたものである。   Moreover, the heat exchanger with a fin which concerns on Claim 7 is a heat exchanger as described in any one of Claim 1 to 5. WHEREIN: The linear upwind front edge and linear form of the fin in a front side heat exchanger are used. Of the two regions sandwiched between the leeward trailing edges of the two heat transfer tubes inserted in the fin portion of the region close to the once-through fan and arranged in two rows in the row direction along the main flow direction of the gas, The arrangement pitch of the heat transfer tubes is 16 to 22 mm in a step direction perpendicular to the main flow direction.

また、請求項８に係るフィン付き熱交換器は、請求項１から７のいずれか一項に記載の熱交換器において、伝熱管とフィンの風上前縁または風下後縁との最短距離を、１．０ｍｍ以上としたものである。   Moreover, the heat exchanger with a fin according to claim 8 is the heat exchanger according to any one of claims 1 to 7, wherein the shortest distance between the heat transfer tube and the windward leading edge or leeward trailing edge of the fin is set. 1.0 mm or more.

また、請求項９に係るフィン付き熱交換器は、請求項１〜８に記載の熱交換器において、段方向に隣接する伝熱管の間のフィン表面に気体の主流方向に開口する複数の切り起こしを設け、
これら各切り起こしの伝熱管寄りの立ち上がり部を伝熱管の円周に概略沿う方向で形成するとともに、前記各切り起こしの列方向の幅に対する前記列方向に隣接する切り起こし間の幅の比を約２〜約２．５とし、更には切り起こしの高さを、隣接するフィン同士のピッチの３／８〜８／８にしたものである。 A heat exchanger with fins according to claim 9 is the heat exchanger according to any one of claims 1 to 8, wherein a plurality of slits opened in a gas main flow direction on a fin surface between adjacent heat transfer tubes in the step direction. Set up a wake,
The rising portion of each cut and raised near the heat transfer tube is formed in a direction substantially along the circumference of the heat transfer tube, and the ratio of the width between the cut and raised adjacent to the row direction to the width in the row direction of each cut and raised The height is about 2 to about 2.5, and the height of the cut and raised is 3/8 to 8/8 of the pitch between adjacent fins.

また、請求項１０に係るフィン付き熱交換器は、請求項９に記載の熱交換器において、前面側熱交換器におけるフィン部の切り起こしの高さを、貫流送風機に近い側の領域については、隣接するフィン同士のピッチの３／８〜５／８にして、他方の領域については隣接するフィン同士のピッチの５／８〜７／８とし、更には背面熱交換器においては７／８〜８／８としたものである。   Further, the finned heat exchanger according to claim 10 is the heat exchanger according to claim 9, wherein the height of the fin portion in the front side heat exchanger is set to a height close to the cross-flow fan. The pitch between adjacent fins is set to 3/8 to 5/8, the other region is set to 5/8 to 7/8 of the pitch between adjacent fins, and 7/8 in the rear heat exchanger. ~ 8/8.

また、請求項１１に係るフィン付き熱交換器は、請求項１から１０のいずれか一項に記載の熱交換器において、前面側熱交換器におけるフィン部の切り起こしの数を、貫流送風機に近い側の領域および他方の領域ともに気体の主流方向に沿う列方向に６個以上、更には背面熱交換器においては５個以下としたものである。   A finned heat exchanger according to claim 11 is the heat exchanger according to any one of claims 1 to 10, wherein the number of fins raised in the front side heat exchanger is set to the once-through fan. Both the near side region and the other region are 6 or more in the column direction along the main gas flow direction, and further 5 or less in the rear heat exchanger.

また、請求項１２に係るフィン付き熱交換器は、請求１から１０のいずれか一項に記載の熱交換器において、前面側熱交換器におけるフィン部の切り起こしの数を、貫流送風機に近い側の領域では、気体の主流方向に沿う列方向に６個以上、他方の領域では５個または４個、更には背面熱交換器においては３個以下としたものである。   A finned heat exchanger according to claim 12 is the heat exchanger according to any one of claims 1 to 10, wherein the number of fins raised in the front side heat exchanger is close to that of a once-through fan. In the region on the side, the number is 6 or more in the column direction along the gas main flow direction, 5 or 4 in the other region, and further 3 or less in the rear heat exchanger.

また、請求項１３に係るフィン付き熱交換器は、請求項１から１２のいずれか一項に記載の熱交換器において、列方向に隣接する２つの伝熱管の間において、内部を流れる冷媒同士に温度差がある場合、前記２つの伝熱管の列間中央部のフィンに、段方向に概略沿う方向で切り込みを設けたものである。   A finned heat exchanger according to claim 13 is the heat exchanger according to any one of claims 1 to 12, wherein the refrigerant flowing between the two heat transfer tubes adjacent to each other in the column direction. When there is a temperature difference, the fins at the center between the rows of the two heat transfer tubes are provided with cuts in a direction substantially along the step direction.

また、請求項１４に係るフィン付き熱交換器は、請求項１から１３に記載のいずれか一項に記載の熱交換器において伝熱管の内部を流動する冷媒として、ＨＦＣ冷媒、ＨＣ冷媒および二酸化炭素のいずれか一つを用いたものである。   A finned heat exchanger according to claim 14 is an HFC refrigerant, HC refrigerant, and carbon dioxide as a refrigerant that flows inside the heat transfer tube in the heat exchanger according to any one of claims 1 to 13. Any one of carbon is used.

本発明のフィン付き熱交換器は、フィン付き熱交換器の形態を改善し、空気調和機の室内ユニットの限られた空間、特に奥行きが狭い空間にできるだけ大きなフィン付き熱交換器を収納し、熱交換能力の大幅な向上をはかるとともに、蒸発器として使用したときフィン表面に凝縮する水をフィンに沿って円滑に流下させることができる。   The heat exchanger with fins of the present invention improves the form of the heat exchanger with fins, and houses the heat exchanger with fins as large as possible in a limited space of the indoor unit of the air conditioner, particularly a space with a small depth, In addition to greatly improving the heat exchange capacity, water condensed on the fin surface when used as an evaporator can smoothly flow down along the fin.

第１の発明は、前面側熱交換器におけるフィンの風上前縁および風下後縁はそれぞれが、同じ鈍角をなす２本の直線部およびこれら２本の直線の間を結ぶ１本の曲線部からなる略くの字状に形成され、前面側熱交換器におけるフィンの直線状の風上前縁と直線状の風下後縁とで挟まれた二つの領域のうち、貫流送風機から遠い側の領域および背面側熱交換器の風上側前縁の直線部と風下側後縁の直線部とで挟まれた領域について、外径４〜７．５ｍｍの伝熱管を３列配置するとともに段方向ピッチを１４．５〜１６ｍｍとしたことにより、通風抵抗をあまり上げることなく、高い空気側熱伝達率を得ることができ、したがって同一騒音時の風量を向上させて高い熱交換能力を発揮することができ、また、貫流送風機に近い側の領域および前面側熱交換器の曲線状の風上前縁と曲線状の風下後縁とで挟まれた領域については、外径が６．０〜８．５ｍｍの伝熱管を２列配置するとともに段方向ピッチを１６〜２２ｍｍとしたことにより、２列構成での通風抵抗としては若干高いが、高い空気側熱伝達率を得ることができ、また熱交換器全体としての通風抵抗の差異を少なくして風速分布を改善することができるので、同一騒音時の風量を向上させて優れた能力を発揮することができる。よって、限られた空間、特に奥行きが狭い空間により大きなフィン付き熱交換器を収納して、より大きな熱交換能力を発揮することができる。また、前面側熱交換器は後で折り曲げ加工する必要がなく、折り曲げたとき必要になるスペーサも当然要らない。また、このフィン付き熱交換器を蒸発器として使用する場合、前面側熱交換器および背面側熱交換器のそれぞれにおけるフィンに凝縮する水滴は連続した両フィンを伝い滑らかに流下することができる。さらに、前面側熱交換器におけるフィンの上側は風上前縁の直線と風下後縁の直線とに囲まれた鉛直に近い一定の角度で傾斜しているので、蒸発時にフィンの表面に凝縮する水滴が滞留することがない。   In the first aspect of the invention, the windward leading edge and the leeward trailing edge of the fin in the front-side heat exchanger each have two straight portions having the same obtuse angle, and one curved portion connecting the two straight lines. Of the two regions sandwiched between the straight upwind front edge and the straight downwind trailing edge of the fin in the front side heat exchanger, the far side from the once-through fan is formed. For the region sandwiched between the straight portion of the windward front edge and the straight portion of the leeward rear edge of the region and the rear side heat exchanger, three rows of heat transfer tubes having an outer diameter of 4 to 7.5 mm are arranged and the stepwise pitch 14.5 to 16 mm, it is possible to obtain a high air-side heat transfer coefficient without increasing the ventilation resistance so much, and thus to improve the air volume at the same noise and to exhibit a high heat exchange capability. And the area near the cross-flow fan and the front For the region sandwiched between the curved upwind leading edge and the curved downwind trailing edge of the heat exchanger, two rows of heat transfer tubes having an outer diameter of 6.0 to 8.5 mm are arranged and the stepwise pitch is set. Although the airflow resistance in the two-row configuration is slightly high due to 16 to 22 mm, a high air-side heat transfer coefficient can be obtained, and the difference in the airflow resistance as a whole heat exchanger is reduced to reduce the wind speed distribution. Therefore, it is possible to improve the air volume at the time of the same noise and to exhibit an excellent ability. Therefore, a larger finned heat exchanger can be accommodated in a limited space, particularly a space with a narrow depth, and a greater heat exchange capability can be exhibited. Further, the front-side heat exchanger does not need to be bent later, and a spacer that is necessary when bent is naturally not required. Further, when this finned heat exchanger is used as an evaporator, water droplets condensed on the fins in each of the front side heat exchanger and the back side heat exchanger can flow smoothly through both the continuous fins. Further, the upper side of the fin in the front heat exchanger is inclined at a certain angle close to the vertical surrounded by the straight line of the windward leading edge and the straight line of the leeward trailing edge, so it condenses on the fin surface during evaporation. Water droplets do not stay.

第２の発明は、当該フィン付き熱交換器を凝縮器若しくはガスクーラーとして使用する際の冷媒出口寄りの伝熱管または蒸発器として使用する際の冷媒入口寄りの外径が４〜７．５ｍｍの伝熱管を、３列構成の気体の流れの最も風上の列に配置して１パスで用いることにより、管内の熱伝達率を向上させ得るとともに空気と冷媒の温度差に関し対向流的な配置となるので、熱交換能力を増大させることができる。また、低能力で冷媒の循環量が小さく、さらには、この領域の冷媒は密度が大きいので冷媒流通抵抗をあまり増大させることがなく、したがって熱交換能力の増大を妨げることはない。さらに、外径が４〜７．５ｍｍの範囲で、当該フィン付き熱交換器を凝縮器若しくはガスクーラーとして使用する際の冷媒出口寄りの伝熱管または蒸発器として使用する際の冷媒入口寄りの伝熱管より、小さい方の外径の伝熱管を、当該フィン付き熱交換器を凝縮器若しくはガスクーラーとして使用する際に冷媒出口寄りの１パスで用いる伝熱管より冷媒上流側の伝熱管として、または当該フィン付き熱交換器を蒸発器として使用する際に冷媒入口寄りの１パスで用いる伝熱管より冷媒下流側の伝熱管として４パスで用いることにより、高い管内熱伝達率と低い冷媒流通抵抗を両立させて、熱交換能力を増大させることができる。   In the second invention, when the finned heat exchanger is used as a condenser or a gas cooler, the outer diameter near the refrigerant inlet when used as a heat transfer tube or an evaporator near the refrigerant outlet is 4 to 7.5 mm. By arranging the heat transfer tubes in the most upwind row of the gas flow in a three-row configuration and using it in one pass, the heat transfer coefficient in the tubes can be improved and the counter flow arrangement with respect to the temperature difference between the air and the refrigerant Therefore, the heat exchange capability can be increased. Moreover, the refrigerant capacity is low and the circulation amount of the refrigerant is small. Further, since the refrigerant in this region has a high density, it does not increase the refrigerant flow resistance so much, and therefore does not hinder the increase in heat exchange capacity. Further, when the heat exchanger with fins is used as a condenser or a gas cooler with an outer diameter in the range of 4 to 7.5 mm, the heat transfer tube near the refrigerant outlet when used as a condenser or a gas cooler or the transmission near the refrigerant inlet when used as an evaporator. A heat transfer tube having a smaller outer diameter than the heat tube, as a heat transfer tube upstream of the refrigerant from the heat transfer tube used in one pass near the refrigerant outlet when the finned heat exchanger is used as a condenser or a gas cooler, or When the finned heat exchanger is used as an evaporator, it is used in four passes as a heat transfer tube on the downstream side of the refrigerant from the heat transfer tube used in one pass near the refrigerant inlet, so that a high heat transfer coefficient in the tube and a low refrigerant flow resistance are obtained. It is possible to increase the heat exchange capacity in a compatible manner.

第３の発明は、当該フィン付き熱交換器を凝縮器若しくはガスクーラーとして使用する際の冷媒出口寄りの伝熱管または蒸発器として使用する際の冷媒入口寄りの外径が４〜７．５ｍｍの伝熱管を、３列構成の気体の流れの最も風上の列に配置して２パスで用いることにより、管内の熱伝達率を向上させ得るとともに空気と冷媒の温度差に関し対向流的な配置となるので、熱交換能力を増大させることができる。また、高能力で冷媒の循環量が大きく、さらに、外径が４〜７．５ｍｍの範囲で、当該フィン付き熱交換器を凝縮器若しくはガスクーラーとして使用する際の冷媒出口寄りの伝熱管または蒸発器として使用する際の冷媒入口寄りの伝熱管より、小さい方の外径の伝熱管を、当該フィン付き熱交換器を凝縮器若しくはガスクーラーとして使用する際に冷媒出口寄りの２パスで用いる伝熱管より冷媒上流側の伝熱管として、または当該フィン付き熱交換器を蒸発器として使用する際に冷媒入口寄りの２パスで用いる伝熱管より冷媒下流側の伝熱管として５または６パスで用いることにより、循環量が大きい場合でも高い管内熱伝達率と低い冷媒流通抵抗を両立させて、熱交換能力を増大させることができる。   The third invention has an outer diameter of 4 to 7.5 mm near the refrigerant inlet when used as a heat transfer tube or evaporator near the refrigerant outlet when the finned heat exchanger is used as a condenser or a gas cooler. By arranging the heat transfer tubes in the most upwind row of the gas flow in the three-row configuration and using them in two passes, the heat transfer coefficient in the tubes can be improved and the counter flow arrangement with respect to the temperature difference between the air and the refrigerant Therefore, the heat exchange capability can be increased. Further, the heat transfer tube near the refrigerant outlet when the finned heat exchanger is used as a condenser or a gas cooler with a high capacity and a large amount of refrigerant circulation, and an outer diameter in the range of 4 to 7.5 mm, or When using the finned heat exchanger as a condenser or a gas cooler, a heat transfer tube having a smaller outer diameter than the heat transfer tube near the refrigerant inlet when used as an evaporator is used in two passes near the refrigerant outlet. Used as a heat transfer tube on the upstream side of the refrigerant from the heat transfer tube, or as a heat transfer tube on the downstream side of the refrigerant from the heat transfer tube used in two passes closer to the refrigerant inlet when the finned heat exchanger is used as an evaporator. As a result, even when the amount of circulation is large, it is possible to achieve both a high heat transfer coefficient in the pipe and a low refrigerant flow resistance, thereby increasing the heat exchange capacity.

第４の発明は、前面側熱交換器におけるフィンの直線状の風上前縁と直線状の風下後縁とで挟まれた二つの領域のうち、貫流送風機から遠い側の領域および背面側熱交換器の風上側前縁の直線部と風下側後縁の直線部とで挟まれた領域について、外径４〜７．５ｍｍの伝熱管を３列配置するとともに段方向ピッチを１４．５〜１６ｍｍとしたことにより、通風抵抗をあまり上げることなく、高い空気側熱伝達率を得ることができ、したがって同一騒音時の風量を向上させて高い熱交換能力を発揮することができる。   4th invention is the area | region far from a cross flow fan, and back side heat | fever among two area | regions pinched by the linear windward front edge and linear leeward trailing edge of the fin in a front side heat exchanger. About the area | region pinched | interposed by the linear part of the windward front edge of a exchanger, and the linear part of a leeward trailing edge, 3 rows of heat exchanger tubes with an outer diameter of 4 to 7.5 mm are arranged, and the stepwise pitch is 14.5 to By setting the thickness to 16 mm, a high air-side heat transfer coefficient can be obtained without significantly increasing the ventilation resistance. Therefore, the air volume at the same noise time can be improved and high heat exchange capability can be exhibited.

第５の発明は、前面側熱交換器におけるフィンの直線状の風上前縁と直線状の風下後縁とで挟まれた二つの領域のうち、貫流送風機に近い側の領域および前面側熱交換器の曲線状の風上前縁と曲線状の風下後縁とで挟まれた領域については、外径が６．０〜８．５ｍｍの伝熱管を２列配置するとともに段方向ピッチを１６〜２２ｍｍとしたことにより、２列構成での通風抵抗としては若干高いが、高い空気側熱伝達率を得ることができ、また熱交換器全体としての通風抵抗の差異を少なくして風速分布を改善することができるので、同一騒音時の風量を向上させて優れた能力を発揮することができる。   The fifth aspect of the invention relates to a region on the side close to the once-through fan and front side heat among the two regions sandwiched between the straight windward leading edge and the straight leeward trailing edge of the fin in the front side heat exchanger. In the region sandwiched between the curved upwind leading edge and the curved downwind trailing edge of the exchanger, two rows of heat transfer tubes having an outer diameter of 6.0 to 8.5 mm are arranged and the stepwise pitch is set to 16 Although the airflow resistance in the two-row configuration is slightly high due to ˜22 mm, a high air-side heat transfer coefficient can be obtained, and the difference in the airflow resistance as a whole heat exchanger is reduced to reduce the wind speed distribution. Since it can be improved, it is possible to improve the air volume at the same noise and to exhibit excellent performance.

第６の発明は、フィン付き熱交換器を凝縮器若しくはガスクーラーとして使用する際の冷媒入口寄りの伝熱管または蒸発器として使用する際の冷媒出口寄りの伝熱管の外径を６．０〜８．５ｍｍの範囲で且つ他のいずれの伝熱管よりも太くするとともに２列構成の気体の流れの風下側の列に配置して２パスで用いるので、空気と冷媒との温度差に関し対向流的な配置による性能向上が得られるとともに、管内の熱伝達率は若干低下するが、冷媒流通抵抗を大幅に低下させることができ、したがって熱交換能力を大幅に増大させることができる。さらに、外径が６．０〜８．５ｍｍの範囲で、フィン付き熱交換器を凝縮器若しくはガスクーラーとして使用する際の冷媒入口寄りの伝熱管または蒸発器として使用する際の冷媒出口寄りの伝熱管より、小さい方の外径の伝熱管を、当該フィン付き熱交換器を凝縮器若しくはガスクーラーとして使用する際に、冷媒出口寄りの最も大きい外径の２パスで用いる伝熱管より冷媒下流側の伝熱管として、または当該フィン付き熱交換器を蒸発器として使用する際に、低循環量で小能力の熱交換器の構成を必要とする場合は冷媒出口寄りの最も大きい外径の２パスで用いる伝熱管より冷媒上流側の伝熱管として、２パスで用いることにより、管内熱伝達率を向上させて熱交換能力を増大させることができる。   6th invention sets the outer diameter of the heat exchanger tube near the refrigerant | coolant inlet at the time of using a heat exchanger with a fin as a condenser or a gas cooler, or the heat exchanger tube near the refrigerant | coolant outlet at the time of using as an evaporator to 6.0-. It is in the range of 8.5 mm and thicker than any other heat transfer tubes, and is arranged in the leeward row of the gas flow in a two-row configuration and used in two passes, so that the counter flow is related to the temperature difference between air and refrigerant As a result, the heat transfer rate in the pipe is slightly reduced, but the refrigerant flow resistance can be greatly reduced, and thus the heat exchange capacity can be greatly increased. Furthermore, in the range of 6.0 to 8.5 mm in outer diameter, the heat exchanger tube near the refrigerant inlet when using the finned heat exchanger as a condenser or gas cooler or near the refrigerant outlet when using as an evaporator. When using a heat exchanger tube having a smaller outer diameter than the heat transfer tube, and using the finned heat exchanger as a condenser or a gas cooler, the refrigerant is downstream of the heat transfer tube used in the two outermost paths near the refrigerant outlet. When using a finned heat exchanger as an evaporator or a heat exchanger with a low capacity and a small capacity heat exchanger when using the finned heat exchanger as an evaporator, the largest outer diameter 2 near the refrigerant outlet By using two passes as the heat transfer tubes on the refrigerant upstream side of the heat transfer tubes used in the passes, it is possible to improve the heat transfer coefficient in the tubes and increase the heat exchange capacity.

第７の発明は、フィン付き熱交換器を凝縮器若しくはガスクーラーとして使用する際の冷媒入口寄りの伝熱管または蒸発器として使用する際の冷媒出口寄りの伝熱管の外径を６．０〜８．５ｍｍの範囲で且つ他のいずれの伝熱管よりも太くするとともに２列構成の気体の流れの風下側の列に配置して２パスで用いるので、空気と冷媒との温度差に関し対向流的な配置による性能向上が得られるとともに、管内の熱伝達率は若干低下するが、冷媒流通抵抗を大幅に低下させることができ、したがって熱交換能力を大幅に増大させることができる。さらに、外径が６．０〜８．５ｍｍの範囲で、フィン付き熱交換器を凝縮器若しくはガスクーラーとして使用する際の冷媒入口寄りの伝熱管または蒸発器として使用する際の冷媒出口寄りの伝熱管より、小さい方の外径の伝熱管を、当該フィン付き熱交換器を凝縮器若しくはガスクーラーとして使用する際に、高い循環量で高能力の熱交換器の構成を必要とする場合は冷媒出口寄りの最も大きい外径で用いる伝熱管より冷媒下流側の伝熱管として、または当該フィン付き熱交換器を蒸発器として使用する際に、冷媒出口寄りの最も大きい外径で用いる伝熱管より冷媒上流側の伝熱管として、３パス以上で用いることにより、管内熱伝達率を向上させて熱交換能力を増大させることができる。   7th invention sets the outer diameter of the heat exchanger tube near the refrigerant | coolant inlet at the time of using a heat exchanger with a fin as a condenser or a gas cooler, or the heat exchanger tube near the refrigerant | coolant outlet at the time of using as an evaporator to 6.0-. It is in the range of 8.5 mm and thicker than any other heat transfer tubes, and is arranged in the leeward row of the gas flow in a two-row configuration and used in two passes, so that the counter flow is related to the temperature difference between air and refrigerant As a result, the heat transfer rate in the pipe is slightly reduced, but the refrigerant flow resistance can be greatly reduced, and thus the heat exchange capacity can be greatly increased. Furthermore, in the range of 6.0 to 8.5 mm in outer diameter, the heat exchanger tube near the refrigerant inlet when using the finned heat exchanger as a condenser or gas cooler or near the refrigerant outlet when using as an evaporator. When using a heat exchanger tube with a smaller outer diameter than the heat exchanger tube, when using the finned heat exchanger as a condenser or gas cooler, a high capacity heat exchanger with a high circulation rate is required From the heat transfer tube used at the largest outer diameter near the refrigerant outlet, when the heat exchanger with fins is used as the evaporator downstream of the heat transfer tube used at the largest outer diameter near the refrigerant outlet or when the finned heat exchanger is used as an evaporator By using it as 3 or more passes as the heat transfer tube on the upstream side of the refrigerant, the heat transfer rate in the tube can be improved and the heat exchange capacity can be increased.

第８の発明は、伝熱管とフィンの風上前縁または風下後縁との距離を、最短でも１．０ｍｍとしたので、当該フィン付き熱交換器を蒸発器として用いた場合、フィンの表面に付着し流下する凝縮水が伝熱管に当って、フィンの風上前縁または風下後縁から飛び出してしまうという現象を抑制することができる。   In the eighth invention, the distance between the heat transfer tube and the windward leading edge or leeward trailing edge of the fin is 1.0 mm at the shortest. Therefore, when the heat exchanger with fins is used as an evaporator, the surface of the fin The phenomenon that the condensed water adhering to and flowing down hits the heat transfer tube and jumps out from the windward leading edge or the windward trailing edge of the fin can be suppressed.

第９の発明は、段方向に隣接する伝熱管の間のフィン表面に気体の主流方向に開口して複数設けた切り起こしの温度境界層前縁効果により、高い空気側熱伝達率が得られるとともに、これら切り起こしの伝熱管寄りの立ち上がり部を伝熱管の円周に概略沿う方向で形成したので、気流を伝熱管の後流部に誘導することができ、したがって有効伝熱面積が増加するので、熱交換性能を向上させることができる。切り起こしの列方向の幅に対する列方向に隣接する切り起こし同士間（フィン基板）の幅の比を約２〜約２．５としたことにより、従来の比が約３の場合より熱交換能力を向上させ、さらには切り起こしの高さを隣接するフィン同士のピッチの３／８〜８／８にしたことにより、同一騒音時の風量を増加させることができ、より大きな熱交換能力を発揮することができる。   In the ninth aspect of the present invention, a high air-side heat transfer coefficient is obtained by the effect of the leading edge of the temperature boundary layer formed by cutting and raising a plurality of openings on the fin surface between the heat transfer tubes adjacent in the step direction. At the same time, since the rising portion of the cut and raised heat exchanger tube is formed in a direction substantially along the circumference of the heat transfer tube, the air flow can be guided to the wake portion of the heat transfer tube, and thus the effective heat transfer area increases. Therefore, heat exchange performance can be improved. The ratio of the width between the cut and raised adjacent to each other in the row direction (fin substrate) to the width in the row direction of the cut and raised is about 2 to about 2.5, so that the heat exchange capacity is higher than when the conventional ratio is about 3. In addition, by making the height of the cut and raised 3/8 to 8/8 of the pitch between adjacent fins, the air volume at the same noise can be increased, and a greater heat exchange capability is demonstrated. can do.

第１０の発明は、切り起こしの高さを、当該フィン付き熱交換器が貫流送風機に近い側の領域については、隣接するフィン同士のピッチの３／８〜５／８として通風抵抗を比較的大きくするとともに、他の領域については隣接するフィン同士のピッチの５／８〜７／８、更には背面熱交換器においては７／８〜８／８として風速分布に合わせて通風抵抗を徐々に小さくしたことにより、当該フィン付き熱交換器の風速分布をより均一化することができ、したがってより大きな熱交換能力を発揮することができる。   In the tenth aspect of the invention, the height of the cut and raised is set to 3/8 to 5/8 of the pitch between adjacent fins in the region where the finned heat exchanger is close to the once-through fan. In the other region, the ventilation resistance is gradually adjusted to 5/8 to 7/8 of the pitch between adjacent fins, and 7/8 to 8/8 in the rear heat exchanger according to the wind speed distribution. By making it small, the wind speed distribution of the heat exchanger with fins can be made more uniform, and therefore a larger heat exchange capability can be exhibited.

第１１の発明は、切り起こしの数を、当該フィン付き熱交換器が貫流送風機に近い側の領域および他の領域については気体の主流方向に沿う列方向に６個以上、更には背面熱交換器においては５個以下として、それより通風抵抗を小さくしたことにより、より簡易的に当該フィン付き熱交換器の風速分布をより均一化することができ、大きな熱交換能力を発揮することができる。   In the eleventh aspect of the present invention, the number of cut and raised portions is six or more in the column direction along the main flow direction of the gas for the region on the side where the heat exchanger with fins is close to the once-through fan and the other regions, and further heat exchange on the back surface. By reducing the ventilation resistance to 5 or less in the heat exchanger, the air velocity distribution of the finned heat exchanger can be made more uniform more easily and a large heat exchange capability can be exhibited. .

第１２の発明は、切り起こしの数を、当該フィン付き熱交換器が貫流送風機に近い側の領域においては、気体の主流方向に沿う列方向に６個以上、他の領域については５個または４個、更には背面熱交換器においては３個以下として、それより通風抵抗を小さくしたことにより、簡易的に当該フィン付き熱交換器の風速分布をより一層均一化することができ、したがってより効率良く大きな熱交換能力を発揮することができる。   In a twelfth aspect of the present invention, the number of cut and raised portions is 6 or more in the row direction along the main flow direction of gas in the region where the heat exchanger with fins is close to the once-through fan, or 5 in other regions. By reducing the ventilation resistance to 4 or even 3 or less in the rear heat exchanger, the wind speed distribution of the finned heat exchanger can be made more uniform easily, and therefore more Efficiently large heat exchange capability can be demonstrated.

第１３の発明は、列方向に隣接する２つの伝熱管の間において、内部を流れる流体に温度差がある場合、２つの伝熱管の列間中央部のフィンに、段方向に概略沿う方向で切り込みを設けたことにより、フィンを通した熱伝導による熱交換ロスを防ぐことができるので、熱交換能力を低下させることがない。   In a thirteenth aspect of the present invention, when there is a temperature difference in the fluid flowing inside between two heat transfer tubes adjacent in the row direction, the fins at the center between the rows of the two heat transfer tubes are arranged in a direction along the step direction. By providing the cuts, heat exchange loss due to heat conduction through the fins can be prevented, so that the heat exchange capability is not reduced.

第１４の発明は、伝熱管の内部を流動する冷媒流体として、オゾン破壊係数の小さいＨＦＣ冷媒、ＨＣ冷媒および二酸化炭素のいずれか１つを用いることにより、地球環境の保護に貢献することができる。特に、ＨＣ冷媒や二酸化炭素は地球温暖化係数が小さい冷媒であるため、より地球環境の保護に貢献することができる。   The fourteenth invention can contribute to the protection of the global environment by using any one of an HFC refrigerant, an HC refrigerant, and carbon dioxide having a small ozone destruction coefficient as a refrigerant fluid flowing inside the heat transfer tube. . In particular, since HC refrigerant and carbon dioxide are refrigerants having a small global warming potential, they can further contribute to the protection of the global environment.

（実施の形態１）
以下、本発明の実施の形態１に係るフィン付き熱交換器について、図面を参照しながら説明する。 (Embodiment 1)
Hereinafter, the finned heat exchanger according to Embodiment 1 of the present invention will be described with reference to the drawings.

まず、本実施の形態１に係るフィン付き熱交換器が搭載される空気調和機の室内ユニットについて図１に基づき説明する。図１はこの室内ユニットの縦断面図である。   First, the indoor unit of the air conditioner in which the finned heat exchanger according to the first embodiment is mounted will be described with reference to FIG. FIG. 1 is a longitudinal sectional view of the indoor unit.

図１に示すように、この空気調和機の室内ユニット１の筐体２には、前面と上面とに吸込み口３ａ、３ｂが設けられ、また下面に吹出し口４が設けられ、筐体２内には、貫流送風機５とフィン付き熱交換器１０とが収納されている。   As shown in FIG. 1, the housing 2 of the indoor unit 1 of this air conditioner is provided with suction ports 3 a and 3 b on the front surface and the upper surface, and an outlet port 4 on the lower surface. Contains a once-through fan 5 and a heat exchanger 10 with fins.

このフィン付き熱交換器１０は、筐体２内の前面側に配置された前面側熱交換器２０と、筐体２内の背面側に配置された背面側熱交換器４０とから構成されており、またこれら前面側熱交換器２０および背面側熱交換器４０は、貫流送風機５を風上側から取り囲むように配置されている。   The finned heat exchanger 10 includes a front-side heat exchanger 20 disposed on the front side in the housing 2 and a back-side heat exchanger 40 disposed on the back side in the housing 2. The front side heat exchanger 20 and the back side heat exchanger 40 are arranged so as to surround the once-through fan 5 from the windward side.

前記各熱交換器２０、４０は、所定の間隔で平行に並べられてその間を空気が流動する多数のフィン２１、４１と、これらのフィン２１、４１に略直角に挿入されて内部を冷媒（冷媒流体）が流動する多数の伝熱管１１とを有し、また前面側熱交換器２０と背面側熱交換器４０とは、そのフィン２１、４１同士は分離されているが、伝熱管１１が連通されることにより一つの熱交換器として作用する。   Each of the heat exchangers 20 and 40 is arranged in parallel at a predetermined interval, and a large number of fins 21 and 41 through which air flows. A large number of heat transfer tubes 11 through which the refrigerant fluid flows, and the front side heat exchanger 20 and the back side heat exchanger 40 have their fins 21 and 41 separated from each other. By communicating, it acts as one heat exchanger.

次に、実施の形態に係るフィン付き熱交換器について、図１および図２〜４を用いて説明する。   Next, the finned heat exchanger according to the embodiment will be described with reference to FIG. 1 and FIGS.

図２は実施の形態に係るフィン付き熱交換器の前面側熱交換器２０のフィン２１と背面側熱交換器４０のフィン４１の側面図、図３はその前面側熱交換器２０のフィン２１の要部拡大側面図である。図４は、図２のフィン付き熱交換器の前面側熱交換器２０のフィン２１および背面側熱交換器４０のフィン４１の上端部同士が境界部で繋がった状態の１枚のフィン１３として連続的にプレス加工してできるフィンを２枚、プレスの送り方向に連続して並べたイメージを示す側面図である。   FIG. 2 is a side view of the fins 21 of the front-side heat exchanger 20 and the fins 41 of the rear-side heat exchanger 40 of the finned heat exchanger according to the embodiment, and FIG. 3 is the fins 21 of the front-side heat exchanger 20. FIG. 4 shows one fin 13 in a state where the upper ends of the fins 21 of the front heat exchanger 20 and the fins 41 of the rear heat exchanger 40 of the finned heat exchanger of FIG. It is a side view which shows the image which arranged two fins formed by carrying out a continuous press process continuously in the feed direction of a press.

図２および図３に示すように、前面側熱交換器２０のフィン２１の風上側前縁部および風下側後縁部とのそれぞれは、互いにその延長線の交差部分の角度θ１およびθ２が同じ鈍角をなす２本の直線部２２、２３および３２、３３と、これら２本の直線部２２、２３と３２、３３との間をそれぞれ結ぶ各１本の曲線部２４、３４とからなる略くの字形状に形成されている。ここで、直線部２２と３２および２３と３３は、それぞれ平行にされている。また、曲線部２４、３４としての形状は、楕円曲線、双曲線、スプラインなどがあるが、風上側縁部の曲線部２４と、風下側縁部の曲線部３４とは、同じ寸法形状にされている。なお、本実施の形態では、図１〜図４に示すように、風上側縁部の曲線部２４と、風下側縁部の曲線部３４とを円弧形状にするとともに、それらを同じ曲率半径で形成している。また、背面側熱交換器４０のフィン４１の風上側前縁部および風下側後縁部は平行な直線部４２、４３で構成されている。   As shown in FIGS. 2 and 3, the windward front edge and the leeward rear edge of the fin 21 of the front-side heat exchanger 20 have the same angle θ1 and θ2 at the intersection of their extension lines. Abbreviated two straight portions 22, 23 and 32, 33, and one curved portion 24, 34 connecting the two straight portions 22, 23 and 32, 33, respectively. It is formed in a letter shape. Here, the straight portions 22 and 32 and 23 and 33 are parallel to each other. The curved portions 24 and 34 may be elliptical curves, hyperbolic curves, splines, etc., but the curved portion 24 at the leeward edge and the curved portion 34 at the leeward edge are of the same size and shape. Yes. In the present embodiment, as shown in FIGS. 1 to 4, the curved portion 24 at the leeward edge and the curved portion 34 at the leeward edge are formed in an arc shape, and they have the same radius of curvature. Forming. Further, the windward front edge and the leeward rear edge of the fin 41 of the back side heat exchanger 40 are configured by parallel straight portions 42 and 43.

略くの字状の前面側熱交換器２０のフィン２１の直線状の風上前縁と直線状の風下後縁とで挟まれた二つの領域のうち、貫流送風機５に近い側の一方の領域の風上前縁と風下後縁との距離、すなわち風上前縁２３と風下後縁３３との距離Ｂは、貫流送風機５から遠い側の他方の領域の風上前縁と風下後縁との距離、すなわち風上前縁２２と風下後縁３２との距離Ａより短く形成されている。なお、一方の領域とは、略くの字状に形成された熱交換器２０の屈曲部より上方部分を示しており、また他方の領域とは、略くの字状に形成された熱交換器２０の屈曲部より下方部分を示している。   Of the two regions sandwiched between the straight upwind front edge and the straight downwind rear edge of the fin 21 of the substantially U-shaped front-side heat exchanger 20, one of the areas close to the cross-flow fan 5 is provided. The distance B between the windward leading edge and the windward trailing edge of the area, that is, the distance B between the windward leading edge 23 and the windward trailing edge 33 is the windward leading edge and the windward trailing edge of the other area on the side far from the once-through fan 5. , That is, shorter than the distance A between the windward leading edge 22 and the leeward trailing edge 32. In addition, one area | region has shown the upper part from the bending part of the heat exchanger 20 formed in the substantially square shape, and the other area | region is the heat exchange formed in the substantially square shape. The lower part of the container 20 is shown below the bent part.

本実施の形態に係るフィン付き熱交換器において、伝熱性能および通風抵抗の観点から推奨される平行な直線状の風上前縁２２と風下後縁３２との距離Ａ（一方の領域）は２４〜３０ｍｍ、平行な直線状の風上前縁２３と風下後縁３３との距離Ｂ（他方の領域）は１８〜２４ｍｍである。   In the heat exchanger with fins according to the present embodiment, a distance A (one region) between the parallel straight windward leading edge 22 and the windward trailing edge 32 that is recommended from the viewpoint of heat transfer performance and ventilation resistance. The distance B (the other region) between the 24-30 mm parallel straight upwind leading edge 23 and the downwind trailing edge 33 is 18-24 mm.

また、図２および図４に示すように、背面側熱交換器４０のフィン４１の風上前縁４２と風下後縁４３との距離は、略くの字状の前面側熱交換器２０のフィン２１の直線状の風上前縁と直線状の風下後縁とで挟まれた二つの領域のうち、貫流送風機５から遠い側の一方の領域の風上前縁２２と風下後縁３２との距離Ａに等しくされている。   As shown in FIGS. 2 and 4, the distance between the windward front edge 42 and the leeward rear edge 43 of the fin 41 of the back side heat exchanger 40 is the same as that of the front side heat exchanger 20 having a substantially square shape. Of the two regions sandwiched between the linear upwind front edge and the straight downwind trailing edge of the fin 21, the upwind front edge 22 and the downwind trailing edge 32 of one region far from the cross flow fan 5 Is equal to the distance A.

これら前面側熱交換器２０のフィン２１と背面側熱交換器４０のフィン４１とは、図４に示すように、上端部同士が境界部で繋がった状態の１枚のフィン１３として連続的にプレス加工して製造される。なお、前面側熱交換器２０のフィン２１の貫流送風機５から遠い側の直線状の風上前縁２２または風下後縁３２がフィンの送り方向となす角度をα、貫流送風機５に近い側の直線状の風上前縁２３または風下後縁３３がフィンプレスの送り方向となす角度をβ、フィン１枚のフィンプレス時の送り幅をＣとすると、α＋β＝θ１＝θ２、Ａ／ｓｉｎα＝Ｂ／ｓｉｎβ＝Ｃ、の関係式が成り立つので、既知のθ１＝θ２、Ａ、Ｂから、α、β、Ｃが一義的に決まる。   As shown in FIG. 4, the fins 21 of the front heat exchanger 20 and the fins 41 of the rear heat exchanger 40 are continuously formed as one fin 13 in which the upper ends are connected to each other at the boundary. Manufactured by pressing. In addition, the angle which the linear upwind front edge 22 or the downwind rear edge 32 of the fin 21 of the front side heat exchanger 20 on the side far from the crossflow fan 5 and the feed direction of the fin is α, Assuming that the angle formed by the straight windward leading edge 23 or the leeward trailing edge 33 with the fin press feed direction is β, and the feed width during fin press of one fin is C, α + β = θ1 = θ2, A / sin α = Since the relational expression B / sin β = C is established, α, β, and C are uniquely determined from the known θ1 = θ2, A, and B.

また、図４に示すように、フィン１３（２１、４１）が金属板から連続プレス加工されて製造される際に、フィン付き熱交換器１０の収納の都合上などから、その両端部や前面側熱交換器２０と背面側熱交換器４０との間となる箇所にはカットして捨てる部分ができるが、そのとき生じる廃材５１、５２、５３はわずかだけであり、他は無駄なく用いられ連続してフィン１３が造られる。   Further, as shown in FIG. 4, when the fins 13 (21, 41) are manufactured by continuous press processing from a metal plate, the both ends and the front surface thereof are used for convenience of storing the heat exchanger 10 with fins. A portion between the side heat exchanger 20 and the back side heat exchanger 40 can be cut and discarded, but the waste materials 51, 52, 53 generated at that time are only a few, and the others are used without waste. The fins 13 are continuously formed.

図３に示すように、各フィン１３にはフィンカラー１２が丸孔形状にバーリング加工されている。   As shown in FIG. 3, the fin collar 12 is burring processed into a round hole shape in each fin 13.

図４に示すように、前面側熱交換器２０のフィン２１と背面側熱交換器４０のフィン４１とが繋がった状態の１枚のフィンとして連続的にプレス加工して製造されたフィン１３が多数積層され、フィンカラー１２を通して伝熱管１１が挿入（挿通）され、その後、フィンカラー１２と伝熱管１１とを密着させるために、伝熱管１１を拡管し、そしてフィン１３を前面側熱交換器２０と背面側熱交換器４０との境界部で切断して、前面側熱交換器２０と背面側熱交換器４０とに分離する。   As shown in FIG. 4, the fin 13 manufactured by continuously pressing as a single fin in a state where the fins 21 of the front-side heat exchanger 20 and the fins 41 of the rear-side heat exchanger 40 are connected. A large number of layers are stacked, and the heat transfer tubes 11 are inserted (inserted) through the fin collars 12, and then the heat transfer tubes 11 are expanded and the fins 13 are connected to the front side heat exchanger in order to bring the fin collars 12 and the heat transfer tubes 11 into close contact with each other. It cut | disconnects in the boundary part of 20 and the back side heat exchanger 40, and isolate | separates into the front side heat exchanger 20 and the back side heat exchanger 40. FIG.

図１および図２に示すように、伝熱管１１の直径、伝熱管１１における気体（空気である）の主流方向（流れ方向）に対して直角方向となる、いわゆる段方向のピッチ、および気体の主流方向に沿う、いわゆる列方向の数、すなわち列数については、略くの字状の前面側熱交換器２０のフィン２１の直線状の風上前縁と直線状の風下後縁とで挟まれた二つの領域のうち、貫流送風機５から遠い側の領域と、背面側熱交換器４０のフィン４１の直線状の風上前縁４２および直線状の風下後縁４３で挟まれた領域とでは、異なるように形成されている。   As shown in FIG. 1 and FIG. 2, the diameter of the heat transfer tube 11, the so-called stepwise pitch that is perpendicular to the main flow direction (flow direction) of the gas (air) in the heat transfer tube 11, and the gas The number in the so-called row direction along the main flow direction, that is, the number of rows, is sandwiched between the straight upwind front edge and the straight downwind trailing edge of the fin 21 of the generally U-shaped front heat exchanger 20. Among the two regions, a region far from the once-through fan 5 and a region sandwiched between the straight windward leading edge 42 and the straight windward trailing edge 43 of the fin 41 of the rear heat exchanger 40 Then, they are formed differently.

すなわち、略くの字状の前面側熱交換器２０のフィン２１の直線状の風上前縁と直線状の風下後縁とで挟まれた二つの領域のうち、貫流送風機５から遠い側の領域、すなわち直線状の風上前縁２２と直線状の風下後縁３２とで挟まれた領域および背面側熱交換器４０のフィン４１の直線状の風上前縁４２と直線状の風下後縁４３とで挟まれた領域のフィン２１、４１にそれぞれ挿入される伝熱管１１としては、４〜７．５ｍｍの範囲の外径の大きい方の伝熱管１１ａと小さい方の伝熱管１１ｂの２種類の外径の伝熱管が用いられて（構成されて）、列方向には３列配置され、また段方向のピッチＤについては、１４．５〜１６ｍｍとして形成されている。また、略くの字状の前面側熱交換器２０のフィン２１の直線状の風上前縁と直線状の風下後縁とで挟まれた二つの領域のうち、貫流送風機５に近い側の領域、すなわち直線状の風上前縁２３と直線状の風下後縁３３とで挟まれた領域および前面側熱交換器２０における曲線状の風上前縁２４と曲線状の風下側後縁３４とで挟まれた領域のフィン２１にそれぞれ挿入される伝熱管１１としては、６．０〜８．５ｍｍの範囲の外径の小さい方の伝熱管１１ｃと大きい方の伝熱管１１ｄの２種類の外径の伝熱管が用いられて（構成されて）、列方向には２列配置され、また段方向のピッチＥについては、１６〜２２ｍｍとして形成されている。   That is, in the two regions sandwiched between the straight upwind front edge and the straight downwind rear edge of the fin 21 of the substantially U-shaped front side heat exchanger 20, the far side from the once-through fan 5 is located. A region, that is, a region sandwiched between the straight upwind leading edge 22 and the straight downwind trailing edge 32 and the straight upwind front edge 42 of the fin 41 of the back side heat exchanger 40 and the straight downwind rear. As the heat transfer tubes 11 inserted into the fins 21 and 41 in the region sandwiched between the edges 43, the heat transfer tube 11a having a larger outer diameter in the range of 4 to 7.5 mm and the heat transfer tube 11b having a smaller outer diameter are 2 pieces. Heat transfer tubes of various types of outer diameters are used (configured), arranged in three rows in the row direction, and the pitch D in the step direction is 14.5 to 16 mm. In addition, of the two regions sandwiched between the linear upwind front edge and the straight downwind trailing edge of the fin 21 of the substantially U-shaped front side heat exchanger 20, the side closer to the cross-flow fan 5 is provided. A region, that is, a region sandwiched between the straight leeward leading edge 23 and the linear leeward trailing edge 33 and the curved upwind leading edge 24 and the curved leeward trailing edge 34 in the front-side heat exchanger 20. As the heat transfer tubes 11 inserted into the fins 21 in the region sandwiched between the two, there are two types of heat transfer tubes 11c, the smaller outer heat transfer tube 11c and the larger heat transfer tube 11d in the range of 6.0 to 8.5 mm. Heat transfer tubes having an outer diameter are used (configured), two rows are arranged in the row direction, and the pitch E in the step direction is 16 to 22 mm.

また、図３に示すように、前面側熱交換器２０における曲線状の風上前縁と曲線状の風下側後縁とで挟まれた領域のフィン２１に挿入される伝熱管１１ｃ、１１ｄの段方向ピッチＥについては、気体の流れの風上側の列ピッチＥｕのほうが、気体の流れの風下側の列ピッチＥｄに比べて同等以下（同一またはそれより小さい）となるよう形成されている。   Further, as shown in FIG. 3, the heat transfer tubes 11 c and 11 d inserted into the fins 21 in the region sandwiched between the curved upwind front edge and the curved downwind rear edge of the front-side heat exchanger 20. Regarding the stepwise pitch E, the row pitch Eu on the leeward side of the gas flow is formed to be equal to or less than (equal or smaller) than the row pitch Ed on the leeward side of the gas flow.

また、例えば、冷房定格能力が４．０ｋＷ程度以下で最適な運転効率となる小能力のエアコンの室内機のパス構成を考えた場合に、図１に本実施の形態に係るフィン付き熱交換器１０を蒸発器として使用した際の冷媒の流れを示しているが、略くの字状の前面側熱交換器２０のフィン２１の直線状の風上前縁と直線状の風下後縁とで挟まれた二つの領域のうち、貫流送風機５から遠い側の領域、すなわち直線状の風上前縁２２と直線状の風下後縁３２とで挟まれた領域、および背面側熱交換器４０のフィン４１の直線状の風上前縁４２と直線状の風下後縁４３とで挟まれた領域のフィン２１、４１に挿入される４〜７．５ｍｍの範囲の２種類の外径の伝熱管１１のうち、大きい方の外径の６本の伝熱管１１ａを気体の流れの最も風上の列に配置し、蒸発器として使用する際の冷媒入口寄りの伝熱管として１パスで用いるとともに、小さい方の外径の前記伝熱管１１ｂを、大きい方の外径の伝熱管１１ａより冷媒下流側の伝熱管として４パスで用いて、冷媒が流される。   Further, for example, when considering a path configuration of an indoor unit of a small-capacity air conditioner having an optimum operating efficiency at a cooling rated capacity of about 4.0 kW or less, FIG. 1 shows a finned heat exchanger according to the present embodiment. 10 shows the flow of the refrigerant when the evaporator 10 is used as an evaporator, and the straight upwind front edge and the straight downwind trailing edge of the fin 21 of the substantially U-shaped front side heat exchanger 20 are shown. Of the two regions sandwiched, the region far from the once-through fan 5, that is, the region sandwiched between the straight upwind front edge 22 and the straight downwind trailing edge 32, and the rear heat exchanger 40 Two types of outer diameter heat transfer tubes in the range of 4 to 7.5 mm inserted into the fins 21 and 41 in a region sandwiched between the straight upwind front edge 42 and the straight downwind rear edge 43 of the fin 41. 11, the six heat transfer tubes 11a having the larger outer diameter are arranged in the most upstream side of the gas flow. The heat transfer tube near the refrigerant inlet when used as an evaporator is used in one pass, and the heat transfer tube 11b having a smaller outer diameter is used as a heat transfer tube on the downstream side of the refrigerant from the heat transfer tube 11a having a larger outer diameter. As shown in FIG.

この後、冷媒は除湿運転時以外は、全開状態にある除湿運転用の絞り手段８０を通過し、略くの字状の前面側熱交換器２０のフィン２１の直線状の風上前縁と直線状の風下後縁とで挟まれた二つの領域のうち、貫流送風機５に近い側の領域、すなわち直線状の風上前縁２３と直線状の風下後縁３３とで挟まれた領域、および前面側熱交換器２０の曲線状の風上前縁２４と曲線状の風下側後縁３４とで挟まれた領域のフィン（フィン部）２１に、挿入される６．０〜８．５ｍｍの範囲の２種類の外径の伝熱管１１のうち、外径の小さい方の伝熱管１１ｃを２パスにて流れ、そして最後に、冷媒は蒸発器として使用する際の冷媒出口寄りの外径の大きい方の４本の伝熱管１１ｄを２パスで流れて、フィン付き熱交換器から流出される。また、蒸発器として使用する際の冷媒出口寄りの外径の大きい方の４本の伝熱管１１ｄは、気体の流れの最も風下の列に配置することにより最適な熱交換器性能を実現するものである。ところが、冷房定格能力が４．０ｋＷ程度以上となる高能力で冷媒の流速が速く、伝熱管内での圧力損失が大きくなる場合には、圧力損失を低減させる為に、エアコンの室内機のパス構成を考えた場合は、小能力時の図１に示したパス構成に対して、図示はしない蒸発器として使用する際の冷媒入口寄りの伝熱管として２パスで用い、小さい方の外径の前記伝熱管１１ｂを、大きい方の外径の伝熱管１１ａより冷媒下流側の伝熱管として５または６パスで用いて冷媒が流され、最後に蒸発器として使用する際の冷媒出口寄りの外径の大きい方の４本を含んだ伝熱管１１ｄを利用して３パスで流れるように、パス数を全体的に増やす熱交換器の構成にして最適化を図る工夫が必要となる。   Thereafter, the refrigerant passes through the throttling means 80 for the dehumidifying operation in the fully opened state except during the dehumidifying operation, and the straight upwind front edge of the fin 21 of the generally U-shaped front side heat exchanger 20 Of the two regions sandwiched between the straight leeward trailing edges, the region closer to the once-through fan 5, that is, the region sandwiched between the linear leeward leading edge 23 and the linear leeward trailing edge 33, And 6.0 to 8.5 mm inserted into fins (fin portions) 21 in a region sandwiched between the curved upwind front edge 24 and the curved downwind rear edge 34 of the front side heat exchanger 20. Of the two types of heat transfer tubes 11 having the outer diameter in the range, the heat transfer tube 11c having the smaller outer diameter flows in two passes, and finally, the refrigerant has an outer diameter near the refrigerant outlet when used as an evaporator. The larger four heat transfer tubes 11d flow in two passes and are discharged from the finned heat exchanger. The four heat transfer tubes 11d having the larger outer diameter near the refrigerant outlet when used as an evaporator realize optimal heat exchanger performance by being arranged in the most leeward row of the gas flow. It is. However, if the cooling rated capacity is about 4.0 kW or higher and the refrigerant flow rate is high and the pressure loss in the heat transfer pipe increases, the path of the indoor unit of the air conditioner is reduced to reduce the pressure loss. When considering the configuration, in contrast to the path configuration shown in FIG. 1 for a small capacity, it is used in two passes as a heat transfer tube near the refrigerant inlet when used as an evaporator (not shown), and the smaller outer diameter is used. The heat transfer pipe 11b is used as a heat transfer pipe on the downstream side of the refrigerant from the heat transfer pipe 11a having the larger outer diameter, and the refrigerant is flowed in five or six passes, and finally the outer diameter near the refrigerant outlet when used as an evaporator. The heat exchanger tube 11d including the larger one of the four heat transfer tubes 11d is used so that the heat exchanger tube 11d can be flown in three passes.

なお、伝熱管１１は外径が４種類のものを用いているが、拡管前の外径でいえば、伝熱管１１ａは６〜６．３５ｍｍ、伝熱管１１ｂは約５ｍｍ、伝熱管１１ｃは約７ｍｍ、伝熱管１１ｄは７．９４〜８ｍｍを用いることが推奨される。   The heat transfer tube 11 has four types of outer diameters, but speaking of the outer diameter before tube expansion, the heat transfer tube 11a is 6 to 6.35 mm, the heat transfer tube 11b is about 5 mm, and the heat transfer tube 11c is about It is recommended to use 7.94-8 mm for 7 mm and heat transfer tube 11d.

また、上記パス構成は一例であり、他の組み合わせで実現しても同じ意味をなすものであり、場合によっては性能向上の為に、貫流送風機５より遠い側の領域における風上の１列目に外径の大きい前記伝熱管１１ａを配置した構成でもかまわないものとする。   Further, the above path configuration is an example, and even if realized by other combinations, it has the same meaning. In some cases, in order to improve the performance, the first row on the windward side in the region far from the once-through fan 5 A configuration in which the heat transfer tube 11a having a large outer diameter is disposed may be used.

一方、図１に基づき、本実施の形態のフィン付き熱交換器１０を蒸発器として使用する場合について説明をしたが、本実施の形態のフィン付き熱交換器を凝縮器またはガスクーラーとして使用する場合には、冷媒の流れ方向が逆になるが、他の構成は蒸発器として使用する場合と同じである。   On the other hand, although the case where the finned heat exchanger 10 of the present embodiment is used as an evaporator has been described based on FIG. 1, the finned heat exchanger of the present embodiment is used as a condenser or a gas cooler. In some cases, the flow direction of the refrigerant is reversed, but the other configuration is the same as when used as an evaporator.

また、本実施の形態のフィン付き熱交換器１０を段方向に再熱器と蒸発器に分けて使用し除湿運転を行う場合には、略くの字状の前面側熱交換器２０のフィン２１の直線状の風上前縁と直線状の風下後縁とで挟まれた二つの領域のうち、貫流送風機５から遠い側の領域、すなわち直線状の風上前縁２２と直線状の風下後縁３２とで挟まれた領域および背面側熱交換器４０を再熱器として用い、略くの字状の前面側熱交換器２０のフィン２１の直線状の風上前縁と直線状の風下後縁とで挟まれた二つの領域のうち、貫流送風機５に近い側の領域、すなわち直線状の風上前縁２３と直線状の風下後縁３３とで挟まれた領域および前面側熱交換器２０の曲線状の風上前縁２４と曲線状の風下側後縁３４とで挟まれた領域を蒸発器として用いる。この除湿運転のとき、冷媒は、図１に示すように、再熱器から、適切な絞り量が設定された絞り手段８０を経て、蒸発器に流入する。   Further, when the heat exchanger 10 with fins of the present embodiment is used in a regenerator and an evaporator separately in the stage direction and the dehumidifying operation is performed, the fins of the substantially U-shaped front heat exchanger 20 are used. Of the two regions sandwiched between the linear upwind front edge 21 and the straight downwind trailing edge, the region far from the cross-flow fan 5, that is, the straight upwind front edge 22 and the straight downwind Using the region sandwiched by the rear edge 32 and the rear heat exchanger 40 as a reheater, the straight upwind front edge of the fin 21 of the generally U-shaped front heat exchanger 20 and the straight Of the two regions sandwiched by the leeward trailing edge, the region closer to the once-through fan 5, that is, the region sandwiched by the linear windward leading edge 23 and the linear leeward trailing edge 33 and the front side heat A region sandwiched between the curved upwind front edge 24 and the curved downwind rear edge 34 of the exchanger 20 is used as an evaporator. At the time of this dehumidifying operation, as shown in FIG. 1, the refrigerant flows from the reheater through the throttle means 80 having an appropriate throttle amount set into the evaporator.

さらに、図４に示すように、前面側熱交換器２０のフィン２１と背面側熱交換器４０のフィン４１とを、これらの上端部同士が境界部で繋がった状態の１枚のフィン１３として連続的にプレス加工して製造するとき、前面側熱交換器２０と背面側熱交換器４０とのそれぞれのフィンカラー１２が段方向に隣接する部分の配置ピッチについては、その近隣の他の段方向のピッチＤよりも短いピッチＦとなるようにされている。   Furthermore, as shown in FIG. 4, the fins 21 of the front-side heat exchanger 20 and the fins 41 of the rear-side heat exchanger 40 are formed as one fin 13 in a state where these upper ends are connected to each other at the boundary. When manufacturing by continuously pressing, the arrangement pitch of the portions where the fin collars 12 of the front side heat exchanger 20 and the back side heat exchanger 40 are adjacent to each other in the step direction is set to other steps in the vicinity. The pitch F is shorter than the pitch D in the direction.

また、図２および図３に示すように、フィン１３（２１、４１）における段方向に隣接する伝熱管１１同士間の箇所には、気体の主流方向に開口する複数の切り起こし１４１、１５１、１６１、１７１、１８１、１９１、１４２、１５２、１６２、１７２、１８２、１９２が設けられるとともに、これら各切り起こし１４１、１５１、１６１、１７１、１８１、１９１、１４２、１５２、１６２、１７２、１８２、１９２のフィンカラー１２寄りの箇所、すなわち伝熱管１１寄りの箇所に設けられた切り起こし１４１、１５１、１６１、１７１、１８１、１９１、１４２、１５２、１６２、１７２、１８２、１９２の立ち上がり部１４１ａ、１５１ａ、１６１ａ、１４２ａ、１５２ａは、伝熱管１１の円周に概略沿う方向で形成されている。   As shown in FIGS. 2 and 3, a plurality of cuts 141, 151 that open in the mainstream direction of the gas are formed at locations between the heat transfer tubes 11 adjacent to each other in the step direction of the fins 13 (21, 41). 161, 171, 181, 191, 142, 152, 162, 172, 182, 192 are provided, and each of these cuts 141, 151, 161, 171, 181, 191, 142, 152, 162, 172, 182, 192 in the vicinity of the fin collar 12, that is, the cut-and-raised portions 141, 151, 161, 171, 181, 191, 142, 152, 162, 172, 182, 192 provided in the vicinity of the heat transfer tube 11, 151 a, 161 a, 142 a, 152 a are formed in a direction substantially along the circumference of the heat transfer tube 11.

ここで、図３に示すように、各切り起こし１４１、１５１、１６１、１７１、１８１、１９１の列方向の幅Ｗｓ１に対する、列方向に隣接する切り起こし１４１、１５１、１６１、１７１、１８１、１９１間のフィン部分における幅（列方向に隣接するフィン２１の平板部分の幅）Ｗｂ１の比Ｗｂ１／Ｗｓ１および切り起こし１４２、１５２の列方向の幅Ｗｓ２に対する、列方向に隣接する切り起こし１４２、１５２、１６２、１７２、１８２、１９２間のフィン部分の幅（列方向に隣接するフィン２１、４１の平板部分の幅）Ｗｂ２の比Ｗｂ２／Ｗｓ２が、約２〜約２．５となるようにされている。   Here, as shown in FIG. 3, the cuts 141, 151, 161, 171, 181, 191 adjacent to each other in the column direction with respect to the width Ws <b> 1 in the column direction of the cuts 141, 151, 161, 171, 181, 191. The width of the fin portion between them (the width of the flat plate portion of the fin 21 adjacent in the row direction) Wb1 ratio Wb1 / Ws1 and the cut-and-raised portions 142, 152 adjacent to each other in the row direction 142, 152 , 162, 172, 182, 192 (the width of the flat plate portion of the fins 21 and 41 adjacent in the row direction) Wb2 ratio Wb2 / Ws2 is set to be about 2 to about 2.5. ing.

また、フィン２１、４１の厚み方向に沿う切り起こし１４１、１５１、１６１、１７１、１８１、１９１、１４２、１５２、１６２、１７２、１８２、１９２の高さは、隣接するフィン１３（２１、４１）同士のピッチの３／８〜８／８となるようされている。   Further, the heights of the cuts 141, 151, 161, 171, 181, 191, 142, 152, 162, 172, 182, and 192 along the thickness direction of the fins 21 and 41 are set to the adjacent fins 13 (21 and 41). The pitch is 3/8 to 8/8 of the pitch between each other.

また、図１における領域Ｇ、Ｆ、Ｈは風速の異なる領域を示したものであり、各々の風速はＧ＞Ｆ＞Ｈの関係が成り立っている。   Further, regions G, F, and H in FIG. 1 show regions having different wind speeds, and the relationship between the wind speeds is G> F> H.

よって、高い熱交換性能を得るべく、切り起こし１４１、１５１、１６１、１７１、１８１、１９１の高さを、例えば図１における貫流送風機５に接近していて最も高風速となる領域Ｇについては、隣接するフィン１３（２１、４１）同士のピッチの３／８〜５／８とし、風速が次第に遅くなる領域Ｆ、Ｈについては隣接するフィン１３（２１、４１）同士のピッチの領域Ｆは３／８〜５／８、領域Ｈ、Ｇは５／８〜８／８として風速がより均一になるようにされている。   Therefore, in order to obtain high heat exchange performance, for the region G where the height of the cuts 141, 151, 161, 171, 181, 191 is close to the cross-flow fan 5 in FIG. For the regions F and H in which the wind speed is gradually reduced to 3/8 to 5/8 of the pitch between the adjacent fins 13 (21, 41), the region F of the pitch between the adjacent fins 13 (21, 41) is 3 / 8 to 5/8, and the regions H and G are set to 5/8 to 8/8 so that the wind speed becomes more uniform.

また、図３に示すように、伝熱管１１ａ、１１ｂ、１１ｃ、１１ｄとフィン２１、４１の風上前縁２２、２３、２４、４２または風下後縁３２、３３、３４、４３との最短距離Ｌｔ、および切り起こし１４１、１５１、１６１、１７１、１８１、１９１、１４２、１５２、１６２、１７２、１８２、１９２とフィン２１、４１の風上前縁２２、２３、２４、４２または風下後縁３２、３３、３４、４３との最短距離Ｌｓは、１．０ｍｍ以上となるようにされている。   Further, as shown in FIG. 3, the shortest distance between the heat transfer tubes 11a, 11b, 11c, 11d and the windward leading edges 22, 23, 24, 42 of the fins 21, 41 or the leeward trailing edges 32, 33, 34, 43. Lt, and cut and raised 141, 151, 161, 171, 181, 191, 142, 152, 162, 172, 182, 192 and fins 21, 41 leeward leading edge 22, 23, 24, 42 or leeward trailing edge 32 , 33, 34, and 43 are set to be 1.0 mm or longer.

また、図２および図３に示すように、列方向に隣接する２つの伝熱管１１同士間においては、内部を流れる冷媒同士に温度差がある場合に、これら２つの伝熱管１１（フィンカラー１２）の列間中央部のフィン部分に、概略段方向に沿う方向で切り込み１７が設けられている。   As shown in FIGS. 2 and 3, between the two heat transfer tubes 11 adjacent to each other in the column direction, when there is a temperature difference between the refrigerants flowing through the inside, these two heat transfer tubes 11 (fin collars 12). ) Is provided with a notch 17 in the direction along the approximate step direction.

また、空気調和機を除湿運転し、室内ユニット１のフィン付き熱交換器１０を段方向に再熱器と蒸発器とに分けて使用する場合には、図１に示す前面側熱交換器２０におけるフィン２１の曲線部２４、３４から下側部分を蒸発器として用いるとともに他の部分を再熱器として用いるが、この場合におけるフィン２１における再熱器の領域と蒸発器の領域との間の箇所に、切断しない部分１８をごくわずか残してほぼ完全に切断する切り込み１９が設けられている。   When the air conditioner is dehumidified and the finned heat exchanger 10 of the indoor unit 1 is divided into a reheater and an evaporator in the step direction, the front side heat exchanger 20 shown in FIG. The lower part from the curved portions 24 and 34 of the fin 21 is used as an evaporator and the other part is used as a reheater. In this case, between the region of the reheater and the region of the evaporator in the fin 21 A cut 19 is provided at the location which cuts almost completely, leaving only a small portion 18 that is not cut.

さらに、フィン付き熱交換器１０の伝熱管１１の内部を流れる（流動する）冷媒としては、ＨＦＣ冷媒、ＨＣ冷媒および二酸化炭素のいずれか一つが用いられる。   Further, any one of HFC refrigerant, HC refrigerant, and carbon dioxide is used as the refrigerant flowing (flowing) inside the heat transfer tube 11 of the finned heat exchanger 10.

これら前面側熱交換器２０および背面側熱交換器４０のフィン２１、４１は、上述したように、それぞれ上端部同士が境界部で繋がった状態の１枚のフィン１３として連続的にプレス加工して製造され、そしてこのフィン１３を多数積層させた後、フィンカラー１２に伝熱管１１を挿入（挿通）して拡管し、前面側熱交換器２０と前記背面側熱交換器４０とがフィン１３（２１、４１）で繋がった状態で製造し、次に前面側熱交換器２０と背面側熱交換器４０とをそのフィン２１、４１同士の境界部分で切断して、前面側熱交換器２０と背面側熱交換器４０とに分離して製造が行われる。   As described above, the fins 21 and 41 of the front-side heat exchanger 20 and the rear-side heat exchanger 40 are continuously pressed as one fin 13 in a state where the upper ends are connected to each other at the boundary portion. After a large number of the fins 13 are laminated, the heat transfer tube 11 is inserted (inserted) into the fin collar 12 to expand the tube, and the front side heat exchanger 20 and the back side heat exchanger 40 are connected to the fins 13. (21, 41), and the front side heat exchanger 20 and the back side heat exchanger 40 are cut at the boundary between the fins 21, 41, and the front side heat exchanger 20 is manufactured. And the rear side heat exchanger 40 are manufactured separately.

上述したように、この前面側熱交換器２０のフィン２１の風上前縁および風下後縁は、それぞれが同じ鈍角をなす２本の直線部およびこれら２本の直線の間を結ぶ１本の曲線部からなる略くの字状に形成され、略くの字状の前面側熱交換器２０のフィン２１の直線状の風上前縁と直線状の風下後縁とで挟まれた二つの領域のうち、貫流送風機５に近い側の一方の領域の風上前縁２３と風下後縁３３との距離を、貫流送風機５から遠い側の他方の領域の風上前縁２２と風下後縁３２との距離より短くすることにより、限られた空間、特に奥行きが狭い空間により大きなフィン付き熱交換器１０を収納して、より大きな熱交換能力を発揮することができる。また、前面側熱交換器２０は後で折り曲げ加工する必要がなく、折り曲げたとき必要になるスペーサも当然要らない。また、このフィン付き熱交換器１０を蒸発器として使用する場合、前面側熱交換器２０および背面側熱交換器４０のフィン２１、４１に凝縮する水滴は連続したそれぞれのフィン２１、４１を伝い滑らかに流下する。さらに、前面側熱交換器２０のフィン２１の上側は風上前縁２２の直線と風下後縁３２の直線とに囲まれた鉛直に近い一定の角度で傾斜しているので、蒸発時に前記フィンの表面に凝縮する水滴が滞留することがない。   As described above, the windward leading edge and the leeward trailing edge of the fin 21 of the front side heat exchanger 20 are each formed of two straight portions having the same obtuse angle and one straight line connecting these two straight lines. It is formed in a substantially square shape consisting of a curved portion, and is sandwiched between a straight upwind front edge and a straight downwind trailing edge of the fin 21 of the substantially square front heat exchanger 20. Among the areas, the distance between the windward leading edge 23 and the leeward trailing edge 33 in one area on the side close to the once-through fan 5 is the distance between the windward leading edge 22 and the leeward trailing edge in the other area far from the once-through fan 5. By making the distance shorter than 32, the larger finned heat exchanger 10 can be accommodated in a limited space, particularly in a space with a narrow depth, and a greater heat exchange capability can be exhibited. Further, the front-side heat exchanger 20 does not need to be bent later, and naturally a spacer that is required when bent is not required. In addition, when the finned heat exchanger 10 is used as an evaporator, water droplets condensed on the fins 21 and 41 of the front side heat exchanger 20 and the back side heat exchanger 40 travel through the continuous fins 21 and 41. It flows down smoothly. Further, the upper side of the fins 21 of the front side heat exchanger 20 is inclined at a constant angle close to the vertical surrounded by the straight line of the windward leading edge 22 and the straight line of the leeward trailing edge 32. Water droplets that condense on the surface of the water do not stay.

また、略くの字状の前面側熱交換器２０のフィン２１の直線状の風上前縁と直線状の風下後縁とで挟まれた二つの領域のうち、貫流送風機５から遠い側の領域の風上前縁２２と風下後縁３２との距離が２４〜３０ｍｍと薄型であると同時に、貫流送風機５に近い側の領域の風上前縁２３と風下後縁３３との距離をそれよりさらに薄い１８〜２４ｍｍとしたので、熱交換器を含む風回路に必要な奥行き幅がかなり小さくなり、したがって室内ユニット１を薄型化することができる。   Of the two regions sandwiched between the straight upwind front edge and the straight downwind rear edge of the fin 21 of the substantially U-shaped front side heat exchanger 20, The distance between the windward leading edge 22 and the windward trailing edge 32 in the area is as thin as 24 to 30 mm, and at the same time, the distance between the windward leading edge 23 and the windward trailing edge 33 in the area close to the cross-flow fan 5 Since the thickness is further reduced to 18 to 24 mm, the depth width required for the wind circuit including the heat exchanger is considerably reduced, and thus the indoor unit 1 can be thinned.

また、前面側熱交換器２０のフィン２１の風上前縁および風下後縁のそれぞれの曲線部２４、３４を同じ形状としたことにより、フィン１３を連続プレス加工する際、フィン１３の無駄な廃材５１、５２、５３をあまりつくることなく、効率的に生産することができる。   Further, since the curved portions 24 and 34 of the windward leading edge and the leeward trailing edge of the fin 21 of the front side heat exchanger 20 have the same shape, when the fin 13 is continuously pressed, the fin 13 is wasted. The waste materials 51, 52, and 53 can be efficiently produced without making much.

また、前面側熱交換器２０のフィン２１の風上前縁および風下後縁のそれぞれの曲線部２４、２５を円弧状としたことにより、フィン１３のプレス金型の加工およびメンテナンスが容易になる。   Further, the curved portions 24 and 25 of the windward leading edge and the leeward trailing edge of the fin 21 of the front side heat exchanger 20 are formed in an arc shape, thereby facilitating the processing and maintenance of the press mold of the fin 13. .

また、背面側熱交換器４０の風上前縁４２および風下後縁４３を平行な直線にすることにより、限られた空間により大きなフィン付き熱交換器１０を収納して、より大きな熱交換能力を発揮することができる。   In addition, by making the windward leading edge 42 and the leeward trailing edge 43 of the back side heat exchanger 40 parallel to each other, the large finned heat exchanger 10 can be accommodated in a limited space, and a larger heat exchange capacity can be obtained. Can be demonstrated.

また、フィン付き熱交換器１０のフィン１３は、背面側熱交換器４０のフィン４１の風上前縁４２と風下後縁４３との距離を、略くの字状の前面側熱交換器２０のフィン２１の直線状の風上前縁と直線状の風下後縁とで挟まれた二つの領域のうち、貫流送風機５から遠い側の領域の風上前縁２３と風下後縁３３との距離に等しくしたので、前面側熱交換器２０のフィン２１の上端部と背面側熱交換器４１のフィン４１の上端部とが繋がった状態の１枚のフィンとすることができ、したがって高い生産性でもって連続プレス加工を行うことができる。   Further, the fin 13 of the finned heat exchanger 10 is configured so that the distance between the windward leading edge 42 and the leeward trailing edge 43 of the fin 41 of the back surface side heat exchanger 40 is approximately the shape of the front side heat exchanger 20. Of the two regions sandwiched between the straight upwind leading edge and the straight downwind trailing edge of the fin 21, the upwind front edge 23 and the downwind trailing edge 33 in the region far from the cross-flow fan 5 Since it is equal to the distance, the fin 21 of the front side heat exchanger 20 and the upper end of the fin 41 of the back side heat exchanger 41 can be connected to each other, so that a high production can be obtained. The continuous press working can be performed with the property.

また、前面側熱交換器２０のフィン２１の直線状の風上前縁と直線状の風下後縁とで挟まれた二つの領域のうち、貫流送風機５から遠い側の領域、すなわち風上前縁２２と風下後縁３２とで挟まれた領域、および背面側熱交換器４０の風上側前縁４２の直線部と風下側後縁４３の直線部とで挟まれた領域については、外径が４〜７．５ｍｍの範囲の伝熱管１１ａ、１１ｂを３列配置するとともに段ピッチを１４．５〜１６ｍｍとしたことにより、通風抵抗をあまり大きくすることなく高い空気側熱伝達率を得ることができるとともに、同一騒音時の風量を多くして、高い熱交換能力を発揮させることができる。   Of the two regions sandwiched between the straight upwind front edge and the straight downwind rear edge of the fin 21 of the front heat exchanger 20, the region far from the cross-flow fan 5, that is, the upwind front The outer diameter of the region sandwiched between the edge 22 and the leeward trailing edge 32 and the region sandwiched between the straight portion of the windward front edge 42 and the straight portion of the leeward rear edge 43 of the rear side heat exchanger 40 By arranging three rows of heat transfer tubes 11a and 11b in the range of 4 to 7.5 mm and setting the step pitch to 14.5 to 16 mm, a high air-side heat transfer coefficient can be obtained without increasing the ventilation resistance. It is possible to increase the air volume at the same noise and to exhibit a high heat exchange capability.

また、フィン付き熱交換器１０を凝縮器若しくはガスクーラーとして使用する際の冷媒出口寄りの伝熱管１１または蒸発器として使用する際の冷媒入口寄りの伝熱管１１として、４．０〜７．５ｍｍの範囲の外径にされた伝熱管１１ａ、１１ｂのうち、大きい方の外径の伝熱管１１ａを３列構成の気体の流れの最も風上の列に配置するとともに１パスで用いることにより、管内の熱伝達率を向上させ得るとともに空気と冷媒との温度差に関し対向流的な配置にすることができるので、熱交換能力を増大させることができる。また、この領域の冷媒は密度が大きいので冷媒流通抵抗はあまり増大させることがなく、熱交換能力の増大を妨げることはない。さらに、外径が４．０〜７．５ｍｍの範囲で、フィン付き熱交換器１０を凝縮器若しくはガスクーラーとして使用する際の冷媒出口寄りの伝熱管１１ａまたは蒸発器として使用する際の冷媒入口寄りの伝熱管１１ａより、小さい方の外径の伝熱管１１ｂを、当該フィン付き熱交換器１０を凝縮器若しくはガスクーラーとして使用する際に、低能力の低循環量となる場合は、冷媒出口寄りの１パスで用いる伝熱管１１ａより冷媒上流側の伝熱管として、４パスで用い、高能力の高循環量となる場合は、冷媒出口寄りの２パスで、伝熱管１１ａより冷媒上流側の伝熱管として５または６パスで用い、高い管内熱伝達率と低い冷媒流通抵抗を両立させて、熱交換能力を増大させることができる。   Moreover, 4.0-7.5 mm as the heat exchanger tube 11 near the refrigerant | coolant exit when using the heat exchanger 10 with a fin as a condenser or a gas cooler, or the heat exchanger tube 11 near the refrigerant | coolant inlet when using as an evaporator. Among the heat transfer tubes 11a and 11b having an outer diameter in the range, the heat transfer tube 11a having the larger outer diameter is arranged in the most upwind row of the gas flow in the three-row configuration and used in one pass. Since the heat transfer coefficient in the pipe can be improved and the counterflow arrangement can be made with respect to the temperature difference between the air and the refrigerant, the heat exchange capability can be increased. In addition, since the refrigerant in this region has a high density, the refrigerant flow resistance does not increase so much and the increase in heat exchange capacity is not hindered. Furthermore, in the range of 4.0-7.5 mm in outer diameter, the heat exchanger tube 11a near the refrigerant outlet when the finned heat exchanger 10 is used as a condenser or a gas cooler, or a refrigerant inlet when used as an evaporator When the heat exchanger tube 11b having a smaller outer diameter than the closer heat exchanger tube 11a is used as the condenser or gas cooler when the finned heat exchanger 10 is used as a condenser or a gas cooler, As a heat transfer tube on the upstream side of the refrigerant from the heat transfer tube 11a used in the first pass, if it is used in four passes and has a high capacity and a high circulation rate, it is two passes closer to the refrigerant outlet and on the refrigerant upstream side than the heat transfer tube 11a. It can be used in 5 or 6 passes as a heat transfer tube, and a high heat transfer coefficient and a low refrigerant flow resistance can both be achieved, thereby increasing the heat exchange capacity.

また、前面側熱交換器２０におけるフィン２１の直線状の風上前縁と直線状の風下後縁とで挟まれた二つの領域のうち、貫流送風機５に近い側の領域すなわち風上前縁２３と風下後縁３３とで挟まれた領域および前面側熱交換器２０の曲線状の風上前縁２４と曲線状の風下側後縁３４とで挟まれた領域については、外径が６．０〜８．５ｍｍの範囲の伝熱管１１ｃ、１１ｄを２列配置するとともに段方向ピッチを１６〜２２ｍｍとしたことにより、２列構成での通風抵抗としては若干高いが、高い空気側熱伝達率を得ることができ、また熱交換器全体としての通風抵抗の差異を少なくして風速分布を改善することができるので、同一騒音時の風量を向上させて優れた熱交換能力を発揮させることができる。   Of the two regions sandwiched between the linear upwind edge of the fin 21 and the straight downwind trailing edge of the front heat exchanger 20, the region near the cross-flow fan 5, that is, the upwind front edge. 23 and the area sandwiched between the curved upwind front edge 24 and the curved downwind rear edge 34 of the front side heat exchanger 20 have an outer diameter of 6. By arranging two rows of heat transfer tubes 11c and 11d in the range of 0.0 to 8.5 mm and setting the stepwise pitch to 16 to 22 mm, the air flow resistance in the two-row configuration is slightly high, but high air-side heat transfer The air velocity distribution can be improved by reducing the difference in ventilation resistance as a whole heat exchanger, so that the air volume at the same noise level is improved and the excellent heat exchange capability is exhibited. Can do.

また、前面側熱交換器２０におけるフィン２１の曲線状の風上前縁２４と曲線状の風下側後縁３４とで挟まれた領域の部分に挿入される伝熱管１１の段方向ピッチについては、気体の流れの風上側の列の方が、気体の流れの風下側の列に比べて同等以下となるようしたので、伝熱管１１の段方向での本数を可能な限り多くしてこの領域での通風抵抗を高くすることができ、したがってフィン付き熱交換器１０の風速分布をより均一化することができるので、より大きな熱交換能力を発揮することができる。   In addition, regarding the stepwise pitch of the heat transfer tubes 11 inserted in the region sandwiched between the curved upwind front edge 24 and the curved downwind rear edge 34 of the fin 21 in the front heat exchanger 20. Since the leeward row of the gas flow is less than or equal to the leeward row of the gas flow, the number of the heat transfer tubes 11 in the step direction is increased as much as possible. Thus, the air flow distribution of the finned heat exchanger 10 can be made more uniform, so that a larger heat exchange capability can be exhibited.

また、フィン付き熱交換器１０を凝縮器若しくはガスクーラーとして使用する際の冷媒入口寄りの伝熱管１１ｄまたは蒸発器として使用する際の冷媒出口寄りの伝熱管１１ｄの外径を６．０〜８．５ｍｍの範囲で且つ他のいずれの伝熱管１１ａ、１１ｂ、１１ｃよりも太くするとともに２列構成の気体の流れの風下側の列に配置して２パスで用いるので、空気と冷媒との温度差に関し対向流的な配置による性能向上が得られるとともに、管内の熱伝達率は若干低下するが、冷媒流通抵抗を大幅に低下させることができ、したがって熱交換能力を大幅に増大させることができる。さらに、外径が６．０〜８．５ｍｍの範囲で、フィン付き熱交換器１０を凝縮器若しくはガスクーラーとして使用する際の冷媒入口寄りの伝熱管１１ｄまたは蒸発器として使用する際の冷媒出口寄りの伝熱管１１ｄより、小さい方の外径の伝熱管１１ｃを、当該フィン付き熱交換器１０を凝縮器若しくはガスクーラーとして使用する際に、低能力の低循環量となる場合は冷媒出口寄りの最も大きい外径の２パスで用いる伝熱管１１ｄより冷媒下流側の伝熱管として、または当該フィン付き熱交換器１０を蒸発器として使用する際に、冷媒出口寄りの最も大きい外径の２パスで用いる伝熱管１１ｄより冷媒上流側の伝熱管として、２パスで用い、高能力の高循環量となる場合は、当該フィン付き熱交換器１０を蒸発器として使用する際に、冷媒出口寄りの最も大きい外径の伝熱管１１ｄより冷媒上流側の伝熱管として、図示しない３パスで用いて構成することにより、管内熱伝達率を向上させて熱交換能力を増大させることができる。   Further, the outer diameter of the heat transfer tube 11d near the refrigerant inlet when the finned heat exchanger 10 is used as a condenser or a gas cooler or the heat transfer tube 11d near the refrigerant outlet when used as an evaporator is 6.0 to 8. .5 mm and thicker than any of the other heat transfer tubes 11a, 11b, 11c, and arranged in the leeward row of the gas flow in a two-row configuration and used in two passes, so the temperature of air and refrigerant With respect to the difference, performance can be improved by counterflow arrangement, and the heat transfer coefficient in the pipe is slightly reduced, but the refrigerant flow resistance can be greatly reduced, and thus the heat exchange capacity can be greatly increased. . Furthermore, when the finned heat exchanger 10 is used as a condenser or a gas cooler with an outer diameter in the range of 6.0 to 8.5 mm, the refrigerant transfer outlet 11d near the refrigerant inlet or the refrigerant outlet when used as an evaporator. When using the heat exchanger tube 11c having a smaller outer diameter than the heat exchanger tube 11d closer to the fin, when the finned heat exchanger 10 is used as a condenser or a gas cooler, if the circulation capacity is low and the circulation amount is low, the heat exchanger tube 11c is closer to the refrigerant outlet. When the finned heat exchanger 10 is used as an evaporator as a heat transfer tube downstream of the heat transfer tube 11d used in two passes having the largest outer diameter, or two passes having the largest outer diameter near the refrigerant outlet. When the heat transfer tube 11d used in the above is used in two passes as the heat transfer tube on the upstream side of the refrigerant and has a high capacity and a high circulation rate, when the heat exchanger with fins 10 is used as an evaporator, As the heat transfer tubes of the refrigerant upstream of the heat transfer tube 11d of the largest outer diameter of the mouth closer, by constituting with 3 passes, not shown, can be increased heat exchange capacity to enhance the tube heat transfer coefficient.

また、伝熱管１１ａ、１１ｂ、１１ｃ、１１ｄとフィン２１、４１の風上前縁２２、２３、２４、４２または風下後縁３２、３３、３４、４３との距離を、最短でも１．０ｍｍとしたので、フィン付き熱交換器１０を蒸発器として用いた場合、フィン２１、４１の表面に付着し流下する凝縮水が伝熱管１１ａ、１１ｂ、１１ｃ、１１ｄに当って、フィン２１、４１の風上前縁２２、２３、２４、４２または風下後縁３２、３３、３４、４３から飛び出してしまうという現象を抑制することができる。   Further, the distance between the heat transfer tubes 11a, 11b, 11c, 11d and the windward front edges 22, 23, 24, 42 of the fins 21, 41 or the leeward trailing edges 32, 33, 34, 43 is 1.0 mm at the shortest. Therefore, when the heat exchanger 10 with fins is used as an evaporator, the condensed water that adheres to and flows down on the surfaces of the fins 21 and 41 hits the heat transfer tubes 11a, 11b, 11c, and 11d, and the wind of the fins 21, 41 The phenomenon of jumping out from the upper front edges 22, 23, 24, 42 or the leeward rear edges 32, 33, 34, 43 can be suppressed.

また、フィン付き熱交換器１０を段方向で再熱器と蒸発器に分けて使用して除湿運転を行う場合、略くの字状の前面側熱交換器２０におけるフィン２１の直線状の風上前縁と直線状の風下後縁とで挟まれた二つの領域のうち貫流送風機５から遠い側の領域すなわち風上前縁２２と風下後縁３２とで挟まれた領域および背面側熱交換器４０を再熱器として用い、略くの字状の前面側熱交換器２０におけるフィン２１の直線状の風上前縁と直線状の風下後縁とで挟まれた二つの領域のうち貫流送風機５に近い側の領域すなわち風上前縁２３と風下後縁３３とで挟まれた領域および前面側熱交換器２０におけるフィン２１の曲線状の風上前縁２４と曲線状の風下側後縁３４とに挟まれた領域を蒸発器として用いることにより、再熱器と蒸発器の熱負荷を適切にバランスさせて良好な除湿運転を行うことができる。また、再熱器は蒸発器の鉛直方向上側に配置しているので、蒸発器の領域のフィンに結露する凝縮水が、再熱器のフィンの表面に当って再蒸発して、部屋を加湿してしまうのを防止することができる。   When the finned heat exchanger 10 is divided into a reheater and an evaporator in the stage direction and the dehumidifying operation is performed, the linear wind of the fins 21 in the substantially square front heat exchanger 20 is performed. Of the two regions sandwiched between the upper front edge and the straight leeward trailing edge, the region far from the cross-flow fan 5, that is, the region sandwiched between the windward leading edge 22 and the leeward trailing edge 32, and the rear side heat exchange. The recirculation device 40 is used as a reheater, and the flow through the two regions sandwiched between the straight upwind front edge and the straight downwind rear edge of the fin 21 in the substantially square front heat exchanger 20 The region near the blower 5, that is, the region sandwiched between the windward leading edge 23 and the leeward trailing edge 33, and the curved upwind front edge 24 and the curved downwind rear of the fin 21 in the front-side heat exchanger 20. By using the area sandwiched between the edges 34 as an evaporator, the heat sink between the reheater and the evaporator It can be a properly by balancing perform good dehumidifying operation. Also, because the reheater is located vertically above the evaporator, the condensed water that condenses on the fins in the evaporator area hits the surface of the reheater fins and re-evaporates to humidify the room. Can be prevented.

また、段方向に隣接する伝熱管１１の間のフィン２１、４１の表面に気体の主流方向に開口して複数設けられた切り起こし１４１、１５１、１６１、１４２、１５２、の温度境界層前縁効果により、高い空気側熱伝達率が得られるとともに、これら切り起こし１４１、１５１、１６１、１４２、１５２の伝熱管１１寄りの立ち上がり部１４１ａ、１５１ａ、１６１ａ、１４２ａ、１５２ａを伝熱管１１の円周に概略沿う方向で形成したので、気流を伝熱管１１の後流部に誘導することができ、したがって有効伝熱面積が増加するので、熱交換性能を向上させることができる。さらに、切り起こし１４１、１５１、１６１、１７１、１８１、１９１、１４２、１５２、１６２、１７２、１８２、１９２の列方向の幅Ｗｓ１、Ｗｓ２に対する列方向に隣接する切り起こし同士間の幅Ｗｂ１、Ｗｂ２の比Ｗｂ１／Ｗｓ１、Ｗｂ２／Ｗｓ２を、約２〜約２．５としたことにより、従来の比が約３の場合より熱交換能力を向上させることができる。   In addition, a temperature boundary layer leading edge of a plurality of cuts and raised portions 141, 151, 161, 142, 152 provided on the surfaces of the fins 21, 41 between the heat transfer tubes 11 adjacent to each other in the step direction so as to open in the gas main flow direction. Due to the effect, a high air-side heat transfer coefficient can be obtained, and the rising portions 141a, 151a, 161a, 142a, 152a of these cut-ups 141, 151, 161, 142, 152 near the heat transfer tube 11 are connected to the circumference of the heat transfer tube 11. Therefore, the air flow can be guided to the downstream portion of the heat transfer tube 11, and the effective heat transfer area is increased, so that the heat exchange performance can be improved. Further, the widths Wb1 and Wb2 between the cuts and raises adjacent to each other in the column direction with respect to the widths Ws1 and Ws2 in the column direction of the cuts and rises 141, 151, 161, 171, 181, 191, 142, 152, 162, 172, 182, and 192. By setting the ratios Wb1 / Ws1 and Wb2 / Ws2 to about 2 to about 2.5, the heat exchange capacity can be improved as compared with the conventional ratio of about 3.

また、各切り起こし１４１、１５１、１６１、１７１、１８１、１９１、１４２、１５２、１６２、１７２、１８２、１９２の高さを、隣接するフィン１３（２１、４１）同士のピッチの３／８〜８／８にしたことにより、同一騒音時の風量を増加させることができ、より大きな熱交換能力を発揮することができる。   Moreover, the height of each cut-and-raised 141, 151, 161, 171, 181, 191, 142, 152, 162, 172, 182, 192 is set to 3/8 to the pitch between adjacent fins 13 (21, 41). By setting it to 8/8, the air volume at the time of the same noise can be increased, and a larger heat exchange capability can be exhibited.

また、各切り起こし１４１、１５１、１６１、１７１、１８１、１９１、１４２、１５２、１６２、１７２、１８２、１９２の高さを、フィン付き熱交換器１０が貫流送風機５に接近する風速が大きい領域Ｇについては、隣接するフィン１３（２１、４１）同士のピッチの３／８〜５／８として通風抵抗を比較的大きくするとともに、他の領域Ｈ、Ｆについては隣接するフィン１３（２１、４１）同士のピッチの５／８〜８／８として通風抵抗をそれより小さくしたことにより、フィン付き熱交換器１０の風速分布をより均一化することができ、したがってより大きな熱交換能力を発揮することができる。   Further, the height of each of the raised parts 141, 151, 161, 171, 181, 191, 142, 152, 162, 172, 182, 192 is a region where the finned heat exchanger 10 approaches the once-through fan 5 and the wind speed is high. For G, the ventilation resistance is relatively large as 3/8 to 5/8 of the pitch between adjacent fins 13 (21, 41), and for other regions H and F, adjacent fins 13 (21, 41). ) By reducing the ventilation resistance to 5/8 to 8/8 of the pitch between each other, the wind speed distribution of the finned heat exchanger 10 can be made more uniform, and therefore a larger heat exchange capability is exhibited. be able to.

また、各切り起こし１４１、１５１、１６１、１４２、１５２とフィン２１、４１の風上前縁２２、２３、２４、４２または風下後縁３２、３３、３４、４３との距離を、最短でも１．０ｍｍとしたので、フィン付き熱交換器１０を蒸発器として用いた場合、フィン２１、４１の表面に付着した凝縮水が切り起こし１４１、１５１、１６１、１７１、１８１、１９１、１４２、１５２、１６２、１７２、１８２、１９２に沿って流下しながら、フィン２１の風上前縁２２、２３、２４、４２または風下後縁３２、３３、３４、４３から飛び出してしまうという現象を抑制することができる。   Further, the distance between each cut-and-raised 141, 151, 161, 142, 152 and the windward leading edges 22, 23, 24, 42 of the fins 21, 41 or the leeward trailing edges 32, 33, 34, 43 is at least 1. When the finned heat exchanger 10 is used as an evaporator, the condensed water adhering to the surfaces of the fins 21 and 41 is cut and raised 141, 151, 161, 171, 181, 191, 142, 152, The phenomenon of jumping out from the windward leading edges 22, 23, 24, 42 or the leeward trailing edges 32, 33, 34, 43 of the fin 21 while flowing down along 162, 172, 182, 192 is suppressed. it can.

また、列方向に隣接する２つの伝熱管１１の間において、内部を流れる流体に温度差がある場合、２つの伝熱管１１の列間中央部のフィン２１、４１に段方向に概略沿う方向に切り込み１７を設けたことにより、フィン２１、４１を通した熱伝導による熱交換ロスを防ぐことができるので、熱交換能力を低下させることがない。   Moreover, when there is a temperature difference in the fluid flowing inside between the two heat transfer tubes 11 adjacent to each other in the row direction, the fins 21 and 41 in the middle portion between the rows of the two heat transfer tubes 11 are in a direction along the step direction. Since the cuts 17 are provided, heat exchange loss due to heat conduction through the fins 21 and 41 can be prevented, so that the heat exchange capability is not lowered.

また、フィン付き熱交換器１０を段方向で再熱器と蒸発器とに分けて使用し除湿運転を行う場合、再熱器の領域と蒸発器の領域との間のフィン２１、４１に、切断しない部分１８をごくわずか残してほぼ完全に切断する切り込み１９を設けたことにより、フィン２１、４１の熱伝導による大幅な能力の低下を防ぐことができる。さらに、フィン付き熱交換器１０全体を蒸発器として使用する場合、フィン２１、４１の表面に凝縮する水を切り込み１９に滞留させることなく、フィン２１、４１のごくわずかだが繋がっている部分１８を通って円滑に流下させることができる。   In addition, when the heat exchanger 10 with fins is used in the stage direction by dividing it into a reheater and an evaporator and performing a dehumidifying operation, the fins 21 and 41 between the reheater region and the evaporator region, By providing the notches 19 that cut almost completely, leaving only a portion 18 that is not cut, it is possible to prevent a significant decrease in capability due to heat conduction of the fins 21 and 41. Furthermore, when the finned heat exchanger 10 as a whole is used as an evaporator, the water 18 that condenses on the surfaces of the fins 21 and 41 is not retained in the cuts 19, and the portions 18 that are connected to the fins 21 and 41 are slightly connected. It can flow smoothly through.

また、伝熱管１１の内部を流動する冷媒流体として、オゾン破壊係数の小さいＨＦＣ冷媒、ＨＣ冷媒および二酸化炭素のいずれか１つを用いることにより、地球環境の保護に貢献することができる。特に、ＨＣ冷媒や二酸化炭素は地球温暖化係数が小さい冷媒であるため、より地球環境の保護に貢献することができる。   Moreover, it is possible to contribute to protection of the global environment by using any one of an HFC refrigerant, an HC refrigerant, and carbon dioxide having a small ozone depletion coefficient as the refrigerant fluid flowing inside the heat transfer tube 11. In particular, since HC refrigerant and carbon dioxide are refrigerants having a small global warming potential, they can further contribute to the protection of the global environment.

また、前面側熱交換器２０におけるフィン２１の上端部と背面側熱交換器４０におけるフィン４１の上端部とが繋がった状態の１枚のフィン１３として連続プレス加工する際、後で伝熱管１１を挿入するためのフィンカラー１２の、気体の主流方向に対して直角方向となる段方向に対するピッチについては、両フィン２１、４１同士の境界部で隣接する箇所のフィンカラーの段方向のピッチＦを、他の段方向のピッチＤよりも短くなるようにしたので、前面側熱交換器２０と背面側熱交換器４０との境界部で隣接する箇所のフィンカラーのピッチＦを、他の近傍の段方向のピッチＤと同等とした場合と比較して、フィン材の廃材５２を少なくすることができる。   Moreover, when continuously pressing as one fin 13 in a state where the upper end portion of the fin 21 in the front side heat exchanger 20 and the upper end portion of the fin 41 in the rear side heat exchanger 40 are connected, the heat transfer tube 11 is later processed. As for the pitch of the fin collar 12 for inserting the fins with respect to the step direction perpendicular to the main gas flow direction, the pitch F of the fin collar in the step direction adjacent to the boundary between the fins 21 and 41 is F. Since the pitch D is shorter than the pitch D in the other stage direction, the pitch F of the fin collars adjacent to each other at the boundary between the front side heat exchanger 20 and the back side heat exchanger 40 is set to other neighborhoods. The waste material 52 of the fin material can be reduced as compared with the case where the pitch D is equal to the pitch D.

また、フィン付き熱交換器１０の製造方法は、筐体２内の前面側に配置されている前面側熱交換器２０と、筐体２内の背面側に配置されている背面側熱交換器４０とから構成されたフィン付き熱交換器１０を製造する製造方法であって、前面側熱交換器２０におけるフィン２１の上端部と背面側熱交換器４０におけるフィン４１の上端部とが境界部で繋がった状態の１枚のフィン１３として連続的にプレス加工し、そしてこれらフィン１３を多数積層して伝熱管１１を挿入、拡管した後、フィン１３を前面側熱交換器２０と背面側熱交換器４０との境界部で切断して、前面側熱交換器２０と背面側熱交換器４０に分離するもので、前面側熱交換器２０と背面側熱交換器４０とを個別に製造する場合に比べて、効率的にフィン付き熱交換器１０を製造することができる。また、１枚のフィン１３に挿入する伝熱管１１ａ、１１ｂ、１１ｃ、１１ｄの直径の異なるものや列数の異なるものや列方向ピッチや段方向ピッチの異なるものを混在させたり、１枚のフィン１３に形成される切り起こし１４１、１５１、１６１、１７１、１８１、１９１、１４２、１５２、１６２、１７２、１８２、１９２については、その形状や高さが異なるものを混在させることができる。   Further, the manufacturing method of the finned heat exchanger 10 includes a front-side heat exchanger 20 disposed on the front side in the housing 2 and a back-side heat exchanger disposed on the back side in the housing 2. 40 is a manufacturing method for manufacturing the finned heat exchanger 10, wherein the upper end portion of the fin 21 in the front side heat exchanger 20 and the upper end portion of the fin 41 in the rear side heat exchanger 40 are boundary portions. The fins 13 are continuously pressed as a single fin 13 connected to each other, and a large number of these fins 13 are stacked and the heat transfer tubes 11 are inserted and expanded, and then the fins 13 are connected to the front heat exchanger 20 and the rear heat. It cut | disconnects in the boundary part with the exchanger 40, and it isolate | separates into the front side heat exchanger 20 and the back side heat exchanger 40, and manufactures the front side heat exchanger 20 and the back side heat exchanger 40 separately. Compared to the case, the finned heat exchanger 10 is more efficient. It can be produced. Also, heat transfer tubes 11a, 11b, 11c, and 11d inserted into one fin 13 may have different diameters, different numbers of rows, different pitches in the row direction and stepwise pitch, or a single fin. As for the cut-and-raised portions 141, 151, 161, 171, 181, 191, 142, 152, 162, 172, 182, and 192 formed in the shape 13, those having different shapes and heights can be mixed.

また、前面側熱交換器２０と背面側熱交換器４０との境界部で隣接する箇所のフィンカラー１２のピッチＦを、他の近隣の段方向のピッチＤよりも短くなるように構成されているフィン付き熱交換器１０の製造方法については、前面側熱交換器２０におけるフィン２１の上端部と背面側熱交換器４０におけるフィン４１の上端部とが繋がった状態のフィン１３における、後で伝熱管１１を挿入するためのフィンカラー１２の気体の主流方向に対して直角方向となる段方向に対するピッチについては、前面側熱交換器２０と背面側熱交換器４０との境界部で隣接する箇所のフィンカラー１２のピッチＦを、他の近隣の段方向のピッチＤよりも短く形成し、そしてこれらフィン１３を多数積層して伝熱管１１を挿入、拡管した後、フィン１３を前面側熱交換器２０と背面側熱交換器４０との境界部で切断して、前面側熱交換器２０と背面側熱交換器４０に分離するようにしているので、前面側熱交換器２０と背面側熱交換器４０との境界部で隣接する箇所のフィンカラー１２の段方向のピッチＦを、他の近傍の段方向のピッチＤと同等とした場合と比較して、フィン材の廃材５２を少なくすることができる。   Further, the pitch F of the fin collars 12 adjacent to each other at the boundary between the front-side heat exchanger 20 and the rear-side heat exchanger 40 is configured to be shorter than the pitch D in the other adjacent step directions. As for the manufacturing method of the finned heat exchanger 10, the fin 13 in the state where the upper end of the fin 21 in the front-side heat exchanger 20 and the upper end of the fin 41 in the rear-side heat exchanger 40 are connected to each other later. About the pitch with respect to the step direction which becomes a right angle direction with respect to the main flow direction of the gas of the fin collar 12 for inserting the heat exchanger tube 11, it adjoins in the boundary part of the front side heat exchanger 20 and the back side heat exchanger 40. The pitch F of the fin collar 12 at a location is formed shorter than the pitch D in the other neighboring step directions, and after a large number of these fins 13 are stacked and the heat transfer tube 11 is inserted and expanded, the fin 13 is moved forward. Since it is cut at the boundary between the side heat exchanger 20 and the back side heat exchanger 40 and separated into the front side heat exchanger 20 and the back side heat exchanger 40, the front side heat exchanger 20 and Compared to the case where the pitch F in the step direction of the fin collar 12 at the adjacent portion at the boundary with the rear side heat exchanger 40 is made equal to the pitch D in the other step direction, the waste material 52 of the fin material is used. Can be reduced.

なお、上記実施の形態においては、吸込み口３ａ、３ｂが前面や上面などに設けている場合について説明したが、これに限るものではない。また、吹出し口４としては下面側に設けられている場合について説明したが、これに限るものではなく、前面などに設けられているものにも上記構成を適用することができる。   In addition, in the said embodiment, although the case where the suction inlets 3a and 3b were provided in the front surface, the upper surface, etc. was demonstrated, it does not restrict to this. Moreover, although the case where it provided in the lower surface side as the blower outlet 4 was demonstrated, it is not restricted to this, The said structure is applicable also to what is provided in the front surface etc.

また、上記実施の形態においては、前面側熱交換器２０および背面側熱交換器４０が吸込み口３ａ、３ｂから貫流送風機５までの風回路の途中に配設された場合について説明したが、これに限るものではなく、例えば貫流送風機５から吹出し口４までの風回路の途中に配設された熱交換器にも上記構成を適用することができる。さらに、熱交換器が室内ユニット内に３つ以上設けられるものや、１つしか設けられないものにも適用可能である。   Moreover, in the said embodiment, although the front side heat exchanger 20 and the back side heat exchanger 40 demonstrated the case where it was arrange | positioned in the middle of the wind circuit from the inlets 3a and 3b to the once-through fan 5, For example, the above configuration can also be applied to a heat exchanger disposed in the middle of the wind circuit from the once-through fan 5 to the outlet 4. Furthermore, the present invention can be applied to a case where three or more heat exchangers are provided in the indoor unit or a case where only one heat exchanger is provided.

上述した本実施の形態に係るフィン付き熱交換器によると、空気調和機の室内ユニットに搭載される前面側熱交換器と背面側熱交換器とから構成されるフィン付き熱交換器の形態およびその製造方法を改善し、前面側熱交換器のフィンの風上前縁および風下後縁は、それぞれが同じ鈍角をなす２本の直線部およびこの２本の直線の間を結ぶ１本の曲線部からなる略くの字状に形成され、この略くの字状の前面側熱交換器におけるフィンの直線状の風上前縁と直線状の風下後縁とで挟まれた二つの領域のうち、貫流送風機に近い側の領域の風上前縁と風下後縁との距離を、貫流送風機から遠い側の領域の風上前縁と風下後縁との距離より短くし、前面側熱交換器におけるフィンの風上前縁および風下後縁のそれぞれの曲線部を同じ形状とし、背面側熱交換器におけるフィンの風上前縁および風下後縁が平行な直線で構成され、背面側熱交換器におけるフィンの風上前縁と風下後縁との距離を、略くの字状の前面側熱交換器におけるフィンの直線状の風上前縁と直線状の風下後縁とで挟まれた二つの領域のうち、貫流送風機から遠い側の領域の風上前縁と風下後縁との距離に等しくすることにより、空気調和機の室内ユニットの限られた空間、特に奥行きが狭い空間にできるだけ大きなフィン付き熱交換器を収納し、熱交換能力の大幅な向上を図るとともに、蒸発器として使用した際に、フィン表面に凝縮する水を当該フィンに沿って円滑に流下させることができる。また、フィン付き熱交換器の製造方法によると、前面側熱交換器におけるフィンと背面側熱交換器におけるフィンとが繋がった１枚のフィンとして連続プレス加工するので、あまりフィン材の廃材を出さず、効率的に安価に製造することができる。   According to the heat exchanger with fins according to the present embodiment described above, the form of the heat exchanger with fins configured by the front side heat exchanger and the rear side heat exchanger mounted on the indoor unit of the air conditioner and The manufacturing method is improved, and the windward leading edge and the leeward trailing edge of the fins of the front side heat exchanger have two straight portions each having the same obtuse angle and one curve connecting the two straight lines. Of the two regions sandwiched between the straight windward leading edge and the straight leeward trailing edge of the fin in this generally square front heat exchanger. Among them, the distance between the windward leading edge and the leeward trailing edge in the area close to the once-through fan is shorter than the distance between the windward leading edge and the leeward trailing edge in the area far from the once-through fan, and heat exchange on the front side The curved part of the windward leading edge and the leeward trailing edge of the fin in the vessel should have the same shape and The windward leading edge and leeward trailing edge of the fin in the side heat exchanger are configured by straight lines, and the distance between the fins leading edge and leeward trailing edge of the rear side heat exchanger Of the two regions sandwiched between the straight windward leading edge and the linear leeward trailing edge of the fin in the front side heat exchanger, the windward leading edge and leeward trailing edge of the region far from the once-through fan The heat exchanger with a fin as large as possible is housed in a limited space of the indoor unit of the air conditioner, especially in a space with a narrow depth, thereby greatly improving the heat exchange capacity and the evaporator. When used as, water condensed on the fin surface can flow smoothly along the fin. Moreover, according to the manufacturing method of the heat exchanger with fins, since the fins in the front side heat exchanger and the fins in the back side heat exchanger are continuously pressed as one fin, the waste material of the fin material is not much generated. Therefore, it can be manufactured efficiently and inexpensively.

（実施の形態２）
図５は本発明の実施の形態２に係るフィン付き熱交換器についての部分拡大図であり、また、上記実施の形態と重複する内容と原理は省き、同一機能を示すものであれば同一番号にて図面を参照しながら以下に説明する。 (Embodiment 2)
FIG. 5 is a partially enlarged view of the heat exchanger with fins according to the second embodiment of the present invention, and the same reference numerals are used as long as they omit the contents and principles overlapping with the above-described embodiments and show the same functions. Will be described below with reference to the drawings.

図５に示すように、略くの字状の前面側熱交換器２０のフィン２１の直線状の風上前縁と直線状の風下後縁とで挟まれた二つの領域のうち、貫流送風機５から遠い側の領域、すなわち直線状の風上前縁２２と直線状の風下後縁３２とで挟まれた領域、および背面側熱交換器４０のフィン４１の直線状の風上前縁４２と直線状の風下後縁４３とで挟まれた領域のフィン２１、４１の部分において、図５中に示す矢印線のように気体が主流方向に沿う列方向に対してフィン２１の領域では１４３、１５３、１６３、１７３、１８３、１９３となるように６個の切り起こし設け、フィン４１では１４４、１５４、１６４、１７４、１８４となるように５個の切り起こしを設けて、前面側より背面側熱交換器のフィンにおける切り起こしの数を少なくすることにより、風速の低い背面側の空気抵抗が減少し、熱交換器全体における風速分布が安定し、効率の高い熱交換を実現できる。   As shown in FIG. 5, a cross-flow blower out of two regions sandwiched between a straight upwind front edge and a straight downwind trailing edge of the fin 21 of the generally U-shaped front side heat exchanger 20. 5, a region far from 5, that is, a region sandwiched between the straight windward leading edge 22 and the straight windward trailing edge 32, and the straight windward leading edge 42 of the fin 41 of the rear side heat exchanger 40. In the region of the fins 21 and 41 in the region sandwiched between the straight leeward trailing edge 43 and the region of the fin 21 in the row direction along the main flow direction as indicated by the arrow line in FIG. , 153, 163, 173, 183, and 193, and six fins are provided on the fin 41, and five fins are provided on the fin 41 so as to be 144, 154, 164, 174, and 184. Reduce the number of cuts in the side heat exchanger fins Rukoto by decreased air resistance lower rear side of the wind speed, the wind speed distribution in the entire heat exchanger is stabilized, can be realized with high heat exchange efficiency.

また、本実施の形態においては、例として切り起こしの数を意図的に前面側を６個、背面側を５個としたが、特に数や切り起こしの形状を限定するものではなく、他の組み合わせでも同じ意味をなすものである。   Further, in the present embodiment, the number of cut-and-raised is intentionally set to 6 on the front side and 5 on the back-side, but the number and the shape of the cut-and-raised are not particularly limited. Combinations have the same meaning.

（実施の形態３）
図６は本発明の実施の形態３に係るフィン付き熱交換器についての部分拡大図であり、また、上記実施の形態と重複する内容と原理は省き、同一機能を示すものであれば同一番号にて図面を参照しながら以下に説明する。 (Embodiment 3)
FIG. 6 is a partially enlarged view of the heat exchanger with fins according to the third embodiment of the present invention, and the same reference numerals are used as long as they omit the contents and principles overlapping with the above-described embodiments and show the same functions. Will be described below with reference to the drawings.

図３に示すように、略くの字状の前面側熱交換器２０のフィン２１の直線状の風上前縁と直線状の風下後縁とで挟まれた二つの領域のうち、貫流送風機５から遠い側の領域、すなわち直線状の風上前縁２２と直線状の風下後縁３２とで挟まれた領域、および背面側熱交換器４０のフィン４１の直線状の風上前縁４２と直線状の風下後縁４３とで挟まれた領域のフィン２１、４１の部分において、図６中に示す矢印線のように気体が主流方向に沿う列方向に対してフィン２１の領域では１４５、１５５、１６５、１７５となるように４個の切り起こし設け、フィン４１では１４６、１５６、１６６となるように３個の切り起こしを設けて、前面側より背面側熱交換器のフィンにおける切り起こしの数を少なくし、更には、図示しない前面側熱交換器における貫流送風機に近い側の切り起こし６個よりも風速分布に合わせて、次第に切り起こし数を少なくすることにより、風速の低い背面側の空気抵抗が減少し、熱交換器全体における風速分布が更に安定し、効率の高い熱交換を実現できる。   As shown in FIG. 3, the cross-flow blower out of the two regions sandwiched between the straight upwind front edge and the straight downwind trailing edge of the fin 21 of the generally U-shaped front side heat exchanger 20. 5, a region far from 5, that is, a region sandwiched between the straight windward leading edge 22 and the straight windward trailing edge 32, and the straight windward leading edge 42 of the fin 41 of the rear side heat exchanger 40. In the region of the fins 21 and 41 in the region sandwiched between the straight leeward trailing edge 43 and the region of the fin 21 in the row direction along the main flow direction as indicated by the arrow line shown in FIG. Four cuts are provided to be 155, 165 and 175, and three cuts are provided on the fin 41 so as to be 146, 156 and 166. Reduce the number of wakes, and further, heat exchange on the front side (not shown) The air resistance on the back side with low wind speed is reduced by gradually reducing the number of raised parts to match the wind speed distribution rather than the six raised parts on the side close to the once-through fan in the heat exchanger, and the wind speed distribution in the entire heat exchanger is reduced. Furthermore, stable and highly efficient heat exchange can be realized.

また、本実施の形態においては特に数や切り起こしの形状を限定するものではなく、他の組み合わせでも同じ意味をなすものである。   Further, in the present embodiment, the number and the shape of the cut and raised are not particularly limited, and other combinations have the same meaning.

このように、熱交換器におけるフィンの形状、寸法の改善、伝熱管の配置の改善に関するもので、特に空気調和機の室内ユニットに適用することができる他、伝熱管内を流れる冷媒と外部を流れる空気との間で熱交換を行う機器にも適用することができる。   In this way, it relates to the improvement of the shape and size of the fins in the heat exchanger and the improvement of the arrangement of the heat transfer tubes, and in particular, it can be applied to the indoor unit of the air conditioner, and the refrigerant flowing in the heat transfer tubes and the outside The present invention can also be applied to a device that exchanges heat with flowing air.

本発明の実施の形態１に係るフィン付き熱交換器を収納した空気調和機の室内ユニットの断面図Sectional drawing of the indoor unit of the air conditioner which accommodated the heat exchanger with a fin concerning Embodiment 1 of this invention 同フィン付き熱交換器のフィンの側面図Side view of fin of heat exchanger with fin 同フィン付き熱交換器のフィンの要部拡大側面図Fin side enlarged side view of the fins of the heat exchanger with fins 同フィン付き熱交換器のフィンを２枚プレスの送り方向に連続して並べたイメージを示す側面図Side view showing an image in which the fins of the finned heat exchanger are continuously arranged in the feed direction of the two-sheet press 本発明の実施の形態２におけるフィン付き熱交換器のフィンの要部拡大側面図The principal part expanded side view of the fin of the heat exchanger with a fin in Embodiment 2 of this invention 本発明の実施の形態３におけるフィン付き熱交換器のフィンの要部拡大側面図The principal part expanded side view of the fin of the heat exchanger with a fin in Embodiment 3 of this invention 従来のフィン付き熱交換器を収納した空気調和機の室内ユニットの断面図Sectional drawing of the indoor unit of an air conditioner that houses a conventional heat exchanger with fins 従来のフィンの概略側面図および従来のフィン付き熱交換器を収納した空気調和機の室内ユニットの概略断面図Schematic side view of a conventional fin and schematic cross-sectional view of an indoor unit of an air conditioner that houses a conventional heat exchanger with fins 従来のフィン付き熱交換器のフィンにおける伝熱管の配置ピッチの関係を示す模式図Schematic diagram showing the relationship between the arrangement pitch of heat transfer tubes in the fins of a conventional heat exchanger with fins

符号の説明Explanation of symbols

１ 室内ユニット
２ 筐体
３ａ、３ｂ 吸込み口
４ 吹出し口
５ 貫流送風機
１０ フィン付き熱交換器
１１、１１ａ、１１ｂ、１１ｃ、１１ｄ 伝熱管
１２ フィンカラー
１３、２１、４１ フィン
１７、１９ 切り込み
１８ 切断しない部分
２０ 前面側熱交換器
２２、２３、４２ 直線状の風上前縁
３２、３３、４３ 直線状の風下後縁
２４ 曲線状の風上前縁
３４ 曲線状の風下後縁
４０ 背面側熱交換器
１４１、１５１、１６１、１７１、１８１、１９１、１４２、１５２、１６２、１７２、１８２、１９２ 切り起こし
１４１ａ、１５１ａ、１６１ａ、１４２ａ、１５２ａ 立ち上がり部 DESCRIPTION OF SYMBOLS 1 Indoor unit 2 Housing | casing 3a, 3b Inlet 4 Outlet 5 Cross-flow fan 10 Heat exchanger with fin 11, 11a, 11b, 11c, 11d Heat transfer tube 12 Fin collar 13, 21, 41 Fin 17, 19 Not cut 18 Not cut Portion 20 Front heat exchanger 22, 23, 42 Straight upwind leading edge 32, 33, 43 Straight downwind trailing edge 24 Curved upwind leading edge 34 Curved downwind trailing edge 40 Backside heat exchange 141, 151, 161, 171, 181, 191, 142, 152, 162, 172, 182, 192 Cut and raise 141a, 151a, 161a, 142a, 152a Rising part

Claims (14)

前面側に吸込み口がおよび下面側に吹出し口がそれぞれ設けられた筐体とこの筐体に収納される貫流送風機とから風回路を構成する空気調和機の室内ユニットに搭載されるフィン付き熱交換器であって、
前記吸込み口から貫流送風機までの風回路の途中または貫流送風機から吹出し口までの風回路の途中に配置される前面側熱交換器と背面側熱交換器とから構成され、前記前面側熱交換器および前記背面側熱交換器はそれぞれ所定の間隔で平行に並べられてその間を気体が流動する多数のフィンと、このフィンに略直角に挿入されて内部を冷媒が流動する多数の伝熱管とから構成され、
前記前面側熱交換器におけるフィンを、その風上前縁および風下後縁がそれぞれが同じ鈍角をなす２本の直線部並びにこれら２本の直線の間を結ぶ１本の曲線部により、略くの字状に形成するとともに、
略くの字状に形成された前記フィンの直線状の風上前縁と直線状の風下後縁とで挟まれた二つの領域のうち、貫流送風機に近い側の領域における風上前縁と風下後縁との距離を１８〜２４ｍｍにすると共に当該フィン部に挿入される伝熱管、および当該フィンの曲線状の風上前縁と曲線状の風下後縁とで挟まれた領域の部分に挿入される伝熱管の外径を６．０〜８．５にして気体の主流方向に沿う方向となる列方向に２列配置し、また、貫流送風機から遠い側の領域および背面側熱交換器の領域における風上前縁と風下後縁との距離を２４〜３０ｍｍにすると共に、当該フィン部に挿入される伝熱管およびにおけるフィンの風上前縁の直線部と風下後縁の直線部とで挟まれた部分に挿入される伝熱管の外径を４．０〜７．５ｍｍにするとともに、気体の主流方向に沿う列方向に伝熱管を３列で配置したことを特徴とするフィン付き熱交換器。 Heat exchange with fins mounted on an indoor unit of an air conditioner that constitutes a wind circuit from a housing provided with a suction port on the front side and a blow-off port on the lower surface side and a cross-flow fan housed in the housing A vessel,
The front-side heat exchanger is composed of a front-side heat exchanger and a rear-side heat exchanger arranged in the middle of the wind circuit from the suction port to the once-through fan or in the middle of the wind circuit from the once-through fan to the outlet. The back side heat exchangers are arranged in parallel at predetermined intervals, and a large number of fins through which gas flows, and a large number of heat transfer tubes inserted into the fins at substantially right angles and through which the refrigerant flows. Configured,
The fins in the front-side heat exchanger are roughly defined by two straight portions where the windward leading edge and the leeward trailing edge form the same obtuse angle, and one curved portion connecting the two straight lines. While forming in the shape of
Of the two regions sandwiched between the linear windward leading edge and the linear leeward trailing edge of the fin formed in a substantially square shape, the windward leading edge in the region close to the cross-flow fan The distance from the leeward trailing edge is set to 18 to 24 mm, and the heat transfer tube inserted into the fin portion, and the portion of the region sandwiched between the curved leeward leading edge and the curved leeward trailing edge of the fin The outer diameter of the heat transfer tubes to be inserted is 6.0 to 8.5, and two rows are arranged in the row direction along the main flow direction of the gas, and the region far from the cross-flow blower and the rear side heat exchanger The distance between the windward leading edge and the windward trailing edge in the region is 24 to 30 mm, and the straight portion of the windward leading edge and the straight portion of the leeward trailing edge of the fin in the heat transfer tube inserted into the fin portion The outer diameter of the heat transfer tube inserted in the portion sandwiched between , Finned heat exchanger, characterized in that a heat transfer tube in three rows in the column direction along the main flow direction of the gas. 前面側熱交換器におけるフィンの直線状の風上前縁と直線状の風下後縁とで挟まれた二つの領域のうち、貫流送風機から遠い側の領域および背面側熱交換器におけるフィンの風上前縁の直線部と風下後縁の直線部とで挟まれた部分に挿入される伝熱管を２種類の外径の伝熱管で構成し、
且つ大きい方の外径の伝熱管を、気体の流れの最も風上の列に配置するとともに、低循環量で小能力の熱交換器を必要とする場合は、当該フィン付き熱交換器を凝縮器またはガスクーラーとして使用する際の冷媒出口寄りの伝熱管として、または蒸発器として使用する際の冷媒入口寄りの伝熱管として、１パスを用い、小さい方の外径の伝熱管については、当該フィン付き熱交換器を凝縮器またはガスクーラーとして使用する際には、大きい方の外径の前記伝熱管より冷媒上流側の伝熱管として、または蒸発器として使用する際には、大きい方の外径の伝熱管より冷媒下流側の伝熱管として、４パスを用いて、それぞれ冷媒を流すようにしたことを特徴とする請求項１に記載のフィン付き熱交換器。 Of the two areas sandwiched between the straight windward leading edge and the straight leeward trailing edge of the fin in the front side heat exchanger, the area far from the cross-flow fan and the fin wind in the back side heat exchanger The heat transfer tube inserted into the portion sandwiched between the straight portion of the upper front edge and the straight portion of the leeward trailing edge is composed of two types of outer diameter heat transfer tubes,
In addition, when the heat exchanger tube with the larger outer diameter is placed in the furthest upstream row of the gas flow, and a heat exchanger with a small circulation capacity and a small capacity is required, the finned heat exchanger is condensed. As a heat transfer tube near the refrigerant outlet when used as an evaporator or gas cooler, or as a heat transfer tube near the refrigerant inlet when used as an evaporator, one pass is used for the heat transfer tube with the smaller outer diameter. When using a finned heat exchanger as a condenser or gas cooler, when using it as a heat transfer tube upstream of the refrigerant from the heat transfer tube with the larger outer diameter, or when using it as an evaporator, 2. The finned heat exchanger according to claim 1, wherein each of the refrigerant flows through four passes as a heat transfer tube on the downstream side of the refrigerant from the heat transfer tube having a diameter. 前面側熱交換器におけるフィンの直線状の風上前縁と直線状の風下後縁とで挟まれた二つの領域のうち、貫流送風機から遠い側の領域および背面側熱交換器におけるフィンの風上前縁の直線部と風下後縁の直線部とで挟まれた部分に挿入される伝熱管を２種類の外径の伝熱管で構成し、
且つ大きい方の外径の伝熱管を、気体の流れの最も風上の列に配置するとともに、高循環量で大能力の熱交換器を必要とする場合は、当該フィン付き熱交換器を凝縮器またはガスクーラーとして使用する際の冷媒出口寄りの伝熱管として、または蒸発器として使用する際の冷媒入口寄りの伝熱管として２パスを用い、小さい方の外径の伝熱管については、当該フィン付き熱交換器を凝縮器またはガスクーラーとして使用する際には、大きい方の外径の前記伝熱管より冷媒上流側の伝熱管として、または蒸発器として使用する際には、大きい方の外径の伝熱管より冷媒下流側の伝熱管として、５または６パスを用いて、それぞれ冷媒を流すようにしたことを特徴とする請求項１に記載のフィン付き熱交換器。 Of the two areas sandwiched between the straight windward leading edge and the straight leeward trailing edge of the fin in the front side heat exchanger, the area far from the cross-flow fan and the fin wind in the back side heat exchanger The heat transfer tube inserted into the portion sandwiched between the straight portion of the upper front edge and the straight portion of the leeward trailing edge is composed of two types of outer diameter heat transfer tubes,
In addition, when the heat exchanger tube with the larger outer diameter is placed in the most upwind row of the gas flow, and a high capacity heat exchanger with high circulation rate is required, the finned heat exchanger is condensed. As a heat transfer tube near the refrigerant outlet when used as an evaporator or a gas cooler, or as a heat transfer tube near the refrigerant inlet when used as an evaporator, a two-pass heat transfer tube is used. When the attached heat exchanger is used as a condenser or a gas cooler, the larger outer diameter is used as the heat transfer tube upstream of the refrigerant from the heat transfer tube having the larger outer diameter or as the evaporator. The finned heat exchanger according to claim 1, wherein the refrigerant is made to flow by using 5 or 6 paths as the heat transfer pipe downstream of the heat transfer pipe. 前面側熱交換器におけるフィンの直線状の風上前縁と直線状の風下後縁とで挟まれた二つの領域のうち貫流送風機に近い側の領域のフィン部および当該フィンの曲線状の風上前縁と曲線状の風下後縁とで挟まれた領域の部分にそれぞれ挿入される伝熱管を２種類の外径の伝熱管で構成し、
且つ大きい方の外径の前記伝熱管を、気体の流れの最も風下の列に配置するとともに、当該フィン付き熱交換器を凝縮器若しくはガスクーラーとして使用する際の冷媒入口寄りの伝熱管、または蒸発器として使用する際の冷媒出口寄りの伝熱管として用い、小さい方の外径の前記伝熱管については、当該フィン付き熱交換器を凝縮器若しくはガスクーラーとして使用する際には、大きい方の外径の前記伝熱管より冷媒下流側の伝熱管として、または蒸発器として使用する際には、大きい方の外径の前記伝熱管より冷媒上流側の伝熱管として用い、また、低循環量で小能力の熱交換器の構成を必要とする場合はそれぞれ２パスを用いて冷媒を流すようにしたことを特徴とする請求項２に記載のフィン付き熱交換器。 Of the two regions sandwiched between the straight upwind front edge and the straight downwind trailing edge of the fin in the front side heat exchanger, the fin portion in the region near the cross-flow fan and the curved wind of the fin The heat transfer tubes inserted respectively in the region sandwiched between the upper front edge and the curved leeward rear edge are composed of two types of heat transfer tubes with outer diameters,
And the heat transfer tube having the larger outer diameter is arranged in the most leeward row of the gas flow, and the heat transfer tube near the refrigerant inlet when the finned heat exchanger is used as a condenser or a gas cooler, or Used as a heat transfer tube near the refrigerant outlet when used as an evaporator, and for the heat transfer tube with a smaller outer diameter, when using the finned heat exchanger as a condenser or a gas cooler, the larger one When used as a heat transfer tube on the downstream side of the refrigerant from the heat transfer tube of the outer diameter or as an evaporator, it is used as a heat transfer tube on the refrigerant upstream side of the heat transfer tube of the larger outer diameter, and with a low circulation amount The finned heat exchanger according to claim 2, wherein when a configuration of a small capacity heat exchanger is required, the refrigerant is caused to flow using two passes. 前面側熱交換器におけるフィンの直線状の風上前縁と直線状の風下後縁とで挟まれた二つの領域のうち貫流送風機に近い側の領域のフィン部および当該フィンの曲線状の風上前縁と曲線状の風下後縁とで挟まれた領域の部分にそれぞれ挿入される伝熱管を２種類の外径の伝熱管で構成し、
且つ大きい方の外径の前記伝熱管を、気体の流れの最も風下の列に配置するとともに、当該フィン付き熱交換器を凝縮器若しくはガスクーラーとして使用する際の冷媒入口寄りの伝熱管、または蒸発器として使用する際の冷媒出口寄りの伝熱管として用い、小さい方の外径の前記伝熱管については、当該フィン付き熱交換器を凝縮器若しくはガスクーラーとして使用する際には、大きい方の外径の前記伝熱管より冷媒下流側の伝熱管として、または蒸発器として使用する際には、大きい方の外径の前記伝熱管より冷媒上流側の伝熱管として用い、また、高循環量で大能力の熱交換器の構成を必要とする場合はそれぞれ３パス以上を用いて冷媒を流すようにしたことを特徴とする請求項３に記載のフィン付き熱交換器。 Of the two regions sandwiched between the straight upwind front edge and the straight downwind trailing edge of the fin in the front side heat exchanger, the fin portion in the region near the cross-flow fan and the curved wind of the fin The heat transfer tubes inserted respectively in the region sandwiched between the upper front edge and the curved leeward rear edge are composed of two types of heat transfer tubes with outer diameters,
And the heat transfer tube having the larger outer diameter is arranged in the most leeward row of the gas flow, and the heat transfer tube near the refrigerant inlet when the finned heat exchanger is used as a condenser or a gas cooler, or Used as a heat transfer tube near the refrigerant outlet when used as an evaporator, and for the heat transfer tube with a smaller outer diameter, when using the finned heat exchanger as a condenser or a gas cooler, the larger one When used as a heat transfer tube on the downstream side of the refrigerant from the heat transfer tube of the outer diameter or as an evaporator, it is used as a heat transfer tube on the refrigerant upstream side of the heat transfer tube of the larger outer diameter, and has a high circulation rate. The finned heat exchanger according to claim 3, wherein when a configuration of a high-capacity heat exchanger is required, the refrigerant is caused to flow by using three or more passes. 前面側熱交換器におけるフィンの直線状の風上前縁と直線状の風下後縁とで挟まれた二つの領域のうち、貫流送風機から遠い側の領域のフィン部に挿入される伝熱管および背面側熱交換器におけるフィンの風上前縁の直線部と風下後縁の直線部とで挟まれた部分の伝熱管３列の配置ピッチを、１４．５〜１６ｍｍにしたことを特徴とする請求項１から５のいずれか一項に記載のフィン付き熱交換器。 Of the two regions sandwiched between the straight windward leading edge and the straight leeward trailing edge of the fin in the front side heat exchanger, the heat transfer tube inserted into the fin portion in the region far from the once-through fan, and The arrangement pitch of the three rows of heat transfer tubes in the portion sandwiched between the straight portion of the windward leading edge and the straight portion of the leeward trailing edge of the fin in the back side heat exchanger is 14.5 to 16 mm. The heat exchanger with fins according to any one of claims 1 to 5. 前面側熱交換器におけるフィンの直線状の風上前縁と直線状の風下後縁とで挟まれた二つの領域のうち貫流送風機に近い側の領域のフィン部に挿入される伝熱管を気体の主流方向に沿う方向となる列方向に２列配置し、前記気体の主流方向に直角方向となる段方向に前記伝熱管の配置ピッチを１６〜２２ｍｍとしたことを特徴とする請求項１から５のいずれか一項に記載のフィン付き熱交換器。 In the front heat exchanger, the heat transfer tubes inserted into the fins in the region close to the cross-flow fan are gasified between the two regions sandwiched between the straight windward leading edge and the straight leeward trailing edge of the fin. Two rows are arranged in a row direction which is a direction along the main flow direction of the gas, and the arrangement pitch of the heat transfer tubes is set to 16 to 22 mm in a step direction which is a direction perpendicular to the main flow direction of the gas. The heat exchanger with a fin according to any one of 5. 伝熱管とフィンの風上前縁または風下後縁との最短距離を、１．０ｍｍ以上としたことを特徴とする請求項１から７のいずれか一項に記載のフィン付き熱交換器。 The heat exchanger with fins according to any one of claims 1 to 7, wherein a shortest distance between the heat transfer tube and the windward leading edge or the leeward trailing edge of the fin is 1.0 mm or more. 段方向に隣接する伝熱管の間のフィン表面に気体の主流方向に開口する複数の切り起こしを設け、
これら各切り起こしの伝熱管寄りの立ち上がり部を伝熱管の円周に概略沿う方向で形成するとともに、前記各切り起こしの列方向の幅に対する前記列方向に隣接する切り起こし間の幅の比を約２〜約２．５とし、更には切り起こしの高さを、隣接するフィン同士のピッチの３／８〜８／８にしたことを特徴とする請求項１から８に記載のフィン付き熱交換器。 Provided with a plurality of cuts and raised in the main flow direction of the gas on the fin surface between the heat transfer tubes adjacent in the step direction,
The rising portion of each cut and raised near the heat transfer tube is formed in a direction substantially along the circumference of the heat transfer tube, and the ratio of the width between the cut and raised adjacent to the row direction to the width in the row direction of each cut and raised The heat with fins according to claim 1, wherein the height of cut and raised is about 3/8 to 8/8 of the pitch between adjacent fins. Exchanger. 前面側熱交換器におけるフィン部の切り起こしの高さを、貫流送風機に近い側の領域については、隣接するフィン同士のピッチの３／８〜５／８にして、他方の領域については隣接するフィン同士のピッチの５／８〜７／８とし、更には背面熱交換器においては７／８〜８／８としたことを特徴とする請求項９に記載のフィン付き熱交換器。 The height of the fins in the front heat exchanger is set to 3/8 to 5/8 of the pitch between adjacent fins for the region close to the once-through fan, and the other region is adjacent. The heat exchanger with fins according to claim 9, wherein the pitch between fins is set to 5/8 to 7/8, and further, 7/8 to 8/8 in the rear heat exchanger. 前面側熱交換器におけるフィン部の切り起こしの数を、貫流送風機に近い側の領域および他方の領域ともに気体の主流方向に沿う列方向に６個以上、更には背面熱交換器においては５個以下としたことを特徴とする請求項１から１０記載のフィン付き熱交換器。 The number of fins raised and raised in the front side heat exchanger is 6 or more in the row direction along the main flow direction of the gas in both the region close to the once-through fan and the other region, and further 5 in the rear heat exchanger. The finned heat exchanger according to claim 1, wherein the heat exchanger has fins. 前面側熱交換器におけるフィン部の切り起こしの数を、貫流送風機に近い側の領域では、気体の主流方向に沿う列方向に６個以上、他方の領域では５個または４個、更には背面熱交換器においては３個以下としたことを特徴とする請求項１から１０に記載のフィン付き熱交換器。 The number of fins raised in the front heat exchanger is 6 or more in the row direction along the main flow direction of the gas in the region close to the once-through fan, 5 or 4 in the other region, and the back surface. The heat exchanger with fins according to claim 1, wherein the number of heat exchangers is three or less. 列方向に隣接する２つの伝熱管の間において、内部を流れる冷媒同士に温度差がある場合、前記２つの伝熱管の列間中央部のフィンに、段方向に概略沿う方向で切り込みを設けたことを特徴とする請求項１から１２のいずれか一項に記載のフィン付き熱交換器。 In the case where there is a temperature difference between the refrigerants flowing inside between two heat transfer tubes adjacent in the row direction, the fins at the center between the rows of the two heat transfer tubes were provided with cuts in a direction roughly along the step direction. The finned heat exchanger according to any one of claims 1 to 12, wherein the heat exchanger has a fin. 伝熱管の内部を流動する冷媒として、ＨＦＣ冷媒、ＨＣ冷媒および二酸化炭素のいずれか一つを用いたことを特徴とする請求項１から１３のいずれか一項に記載のフィン付き熱交換器。 14. The finned heat exchanger according to claim 1, wherein any one of an HFC refrigerant, an HC refrigerant, and carbon dioxide is used as the refrigerant flowing inside the heat transfer tube.
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Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2007327707A (en) * 2006-06-09 2007-12-20 Hitachi Appliances Inc Air conditioner
JP2008039278A (en) * 2006-08-04 2008-02-21 Sharp Corp Heat exchanger and indoor unit of air conditioner
JP2008232448A (en) * 2007-03-16 2008-10-02 Daikin Ind Ltd Fin tube-type heat exchanger and air conditioner
JP2009156058A (en) * 2007-12-25 2009-07-16 Nissan Motor Co Ltd Exhaust gas control device of cylinder direct fuel injection spark ignition engine
JP2010096481A (en) * 2008-10-20 2010-04-30 Toshiba Carrier Corp Indoor unit for air conditioner
JP2015169387A (en) * 2014-03-07 2015-09-28 三菱重工業株式会社 Heat exchanger and air conditioner using same
CN105928260A (en) * 2016-04-22 2016-09-07 Tcl空调器(中山)有限公司 Evaporator end plates, evaporator assembly and cabinet-type air conditioner indoor unit

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2007327707A (en) * 2006-06-09 2007-12-20 Hitachi Appliances Inc Air conditioner
JP2008039278A (en) * 2006-08-04 2008-02-21 Sharp Corp Heat exchanger and indoor unit of air conditioner
JP2008232448A (en) * 2007-03-16 2008-10-02 Daikin Ind Ltd Fin tube-type heat exchanger and air conditioner
JP2009156058A (en) * 2007-12-25 2009-07-16 Nissan Motor Co Ltd Exhaust gas control device of cylinder direct fuel injection spark ignition engine
JP2010096481A (en) * 2008-10-20 2010-04-30 Toshiba Carrier Corp Indoor unit for air conditioner
JP2015169387A (en) * 2014-03-07 2015-09-28 三菱重工業株式会社 Heat exchanger and air conditioner using same
CN105928260A (en) * 2016-04-22 2016-09-07 Tcl空调器(中山)有限公司 Evaporator end plates, evaporator assembly and cabinet-type air conditioner indoor unit

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