JP2019219139A - Corrugated fin for heat exchanger - Google Patents

Corrugated fin for heat exchanger Download PDF

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JP2019219139A
JP2019219139A JP2018118911A JP2018118911A JP2019219139A JP 2019219139 A JP2019219139 A JP 2019219139A JP 2018118911 A JP2018118911 A JP 2018118911A JP 2018118911 A JP2018118911 A JP 2018118911A JP 2019219139 A JP2019219139 A JP 2019219139A
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wave
corrugated fin
flat surface
upstream
fin
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雅也 鵜野
Masaya Uno
雅也 鵜野
卓也 文後
Takuya Bungo
卓也 文後
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T Rad Co Ltd
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Abstract

To prevent clogging in a circulation direction of air flow, and to enhance heat exchange by reducing air resistance, in a fin having fine wave-shaped irregularity on a rising surface and a falling sure of each wave of a corrugated fin, in a heat exchanger in which the corrugated fins and flat tubes are alternately arranged.SOLUTION: Irregular waves 2 are formed on a rising surface and a falling surface of each wave in a thickness direction of a metallic plate, an upstream flat face 3 free from the irregular wave 2 is formed on an upstream end portion of air current 1 of each wave, and a width t1 in a circulation direction of the air flow 1, of the upstream flat face 3 is 0.5 mm-2.5 mm.SELECTED DRAWING: Figure 1

Description

本発明は、ラジエータやオイルクーラ、チャージエアクーラ、ＥＧＲクーラ等の熱交換器に使用されるコルゲートフィンに関するものである。   The present invention relates to a corrugated fin used for a heat exchanger such as a radiator, an oil cooler, a charge air cooler, an EGR cooler, and the like.

一例として、建設機械に用いられるラジエータは、偏平チューブとコルゲートフィンとを交互に並列し、各偏平チューブの両端が一対のタンクに挿通されている。そして、偏平チューブ内にはエンジン冷却水冷却用の熱媒体が流通し、偏平チューブの外面及びコルゲートフィンにはファンによって送風された気流がコルゲートフィンの稜線方向に流通する。そして、偏平チューブ内の熱媒体と気流との間に熱交換が行われるものである。   As an example, in a radiator used in construction machinery, flat tubes and corrugated fins are alternately arranged in parallel, and both ends of each flat tube are inserted into a pair of tanks. The heat medium for cooling the engine cooling water flows in the flat tube, and the airflow blown by the fan flows on the outer surface of the flat tube and the corrugated fin in the ridge direction of the corrugated fin. Then, heat exchange is performed between the heat medium and the airflow in the flat tube.

下記特許文献１には、コルゲートフィン及びそれを備える熱交換器が記載されている。このコルゲートフィンは、帯状金属板が波形に折返し曲折してなり、その各波の立上面および立下面に金属板の厚み方向に断面が凹凸する凹凸波が形成され、各波の稜線方向に気流が導かれる。
なお、立上面および立下面に形成される凹凸波は、平面が斜めに形成されたものや円弧状のものその他が存在する。 Patent Literature 1 below describes a corrugated fin and a heat exchanger including the same. This corrugated fin is formed by folding and bending a band-shaped metal plate into a wave form, and a corrugated wave whose cross section is uneven in the thickness direction of the metal plate is formed on the upper surface and the lower surface of each wave, and the air current flows in the ridgeline direction of each wave. Is led.
The uneven waves formed on the rising surface and the lower surface include those having a plane formed obliquely, those having an arc shape, and others.

特開２０１１−１１２３３１号公報JP 2011-112331 A

上記特許文献１に記載のフィンには、その気流方向の端面にも凹凸波が形成されている。すると、気流の上流側のフィン端部では、この凹凸形状が流体抵抗を増加させると共に、気流に含まれる塵埃等による目詰まりの原因となっている。
また、気流の下流側のフィン端部においては、気体とコルゲートフィンとの温度差が減少しており熱交換への寄与は少ないにもかかわらず、圧力損失は上流部と同程度であり、無用な圧力損失が生じている。
そこで本発明は、その流体抵抗を低減させるとともに、気流の流入側端部におけるフィンの目詰まりを抑制することを目的とする。 The fin described in Patent Document 1 also has an uneven wave on the end face in the airflow direction. Then, at the fin end on the upstream side of the airflow, the uneven shape increases the fluid resistance and causes clogging due to dust and the like included in the airflow.
At the end of the fin on the downstream side of the air flow, the temperature difference between the gas and the corrugated fin is reduced and the contribution to heat exchange is small. Pressure loss has occurred.
Accordingly, it is an object of the present invention to reduce the fluid resistance and to suppress clogging of fins at an inflow side end of an airflow.

請求項１に記載の本発明は、帯状金属板が波形に折返し曲折されてなり、各波の稜線５の方向に気流１が導かれるコルゲートフィンにおいて、
前記各波の立上面および立下面に、金属板の厚み方向に凹凸波２が形成され、前記各波の前記気流１の上流端部には、前記凹凸波２の存在しない上流平坦面３が形成され、その上流平坦面３の前記気流１の流通方向の幅ｔ１が０．５ｍｍ〜２．５ｍｍであることを特徴とする熱交換器用コルゲートフィンである。 The corrugated fin according to the first aspect of the present invention is a corrugated fin in which the strip-shaped metal plate is folded and bent into a waveform, and the air flow 1 is guided in the direction of the ridgeline 5 of each wave.
An uneven wave 2 is formed in the thickness direction of the metal plate on the rising surface and the lower surface of each wave, and an upstream flat surface 3 free of the uneven wave 2 is formed at the upstream end of the air current 1 of each wave. A corrugated fin for a heat exchanger, wherein the width t1 of the formed upstream flat surface 3 in the flow direction of the air flow 1 is 0.5 mm to 2.5 mm.

請求項２に記載の本発明は、帯状金属板が波形に折返し曲折されてなり、各波の稜線５の方向に気流１が導かれるコルゲートフィンにおいて、
前記各波の立上面および立下面に、金属板の厚み方向に凹凸波２が形成され、前記各波の前記気流１の下流端部には、前記凹凸波２の存在しない下流平坦面４が形成され、その下流平坦面４の前記気流１の流通方向の幅ｔ２が０．９ｍｍ〜４．６ｍｍであることを特徴とする熱交換器用コルゲートフィンである。 According to a second aspect of the present invention, there is provided a corrugated fin in which a strip-shaped metal plate is folded and bent into a waveform, and the airflow 1 is guided in a direction of a ridgeline 5 of each wave.
An uneven wave 2 is formed in the thickness direction of the metal plate on the upper and lower surfaces of each wave, and a downstream flat surface 4 free of the uneven wave 2 is formed at the downstream end of the airflow 1 of each wave. A corrugated fin for a heat exchanger, wherein the width t2 of the formed flat surface 4 in the flow direction of the air flow 1 is 0.9 mm to 4.6 mm.

請求項１に記載の発明は、気流の流通方向の上流側のコルゲートフィンの端部には、凹凸波が形成されていない、幅ｔ１が０．５ｍｍ〜２．５ｍｍの上流平坦面３を設けたので、コルゲートフィンの目詰まりが防止される。即ち、殊にフィンの上流端縁に集中しがちな塵埃の目詰まりが抑制されて、空気の流通が維持される。
また、図２の特性曲線から明らかなように、平坦面の存在しない従来型フィン点Ａに比べて、交換熱量（ファンマッチング放熱量）が増大する。これは、上流平坦面３による伝熱面積の低下等の悪影響よりも、平坦面の圧力損失が低下したことによって流量が増加したことによる効果が上回り、冷却ファンの能力を考慮した交換熱量（ファンマッチング放熱量）が増加するからである。 According to the first aspect of the present invention, an upstream flat surface 3 having a width t1 of 0.5 mm to 2.5 mm, on which an uneven wave is not formed, is provided at an end of the corrugated fin on the upstream side in the airflow direction. Therefore, clogging of the corrugated fin is prevented. That is, the clogging of dust, which tends to concentrate on the upstream edge of the fin, is suppressed, and the flow of air is maintained.
Further, as is clear from the characteristic curve of FIG. 2, the exchange heat amount (fan matching heat radiation amount) increases as compared with the conventional fin point A having no flat surface. This is because the effect of the increase in the flow rate due to the decrease in the pressure loss of the flat surface is greater than the adverse effect of the decrease in the heat transfer area due to the upstream flat surface 3. This is because the amount of matching heat radiation increases.

請求項２に記載の発明は、気流の流通方向の下流側のコルゲートフィンの端部には、凹凸波が形成されていない、幅ｔ２が０．９ｍｍ〜４．６ｍｍの下流平坦面４を設けたので、図４に示す特性曲線から明らかな如く、平坦面のない従来型フィン点Ａに比べて、平坦面としたことによる伝熱面積の低下等の悪影響よりも、圧力損失が低下したことによって流量が増加したことによる効果が上回り、冷却ファンの能力を考慮した交換熱量（ファンマッチング放熱量）が増加する。   According to the second aspect of the present invention, a downstream flat surface 4 having a width t2 of 0.9 mm to 4.6 mm in which no corrugated wave is formed is provided at an end of the corrugated fin on the downstream side in the airflow direction. Therefore, as is clear from the characteristic curve shown in FIG. 4, the pressure loss was reduced more than the conventional fin point A having no flat surface due to the adverse effect such as the decrease in the heat transfer area due to the flat surface. As a result, the effect of the increase in the flow rate exceeds the effect, and the exchange heat amount (fan matching heat radiation amount) in consideration of the capacity of the cooling fan increases.

本発明の第１実施例の熱交換器用コルゲートフィン７の正面図（Ａ）及び斜視図（Ｂ）。The front view (A) and the perspective view (B) of the corrugated fin 7 for heat exchangers of the 1st Example of this invention. 同熱交換器用コルゲートフィン７における上流平坦面３の幅を横軸とし、ファンマッチング放熱量比を縦軸とした特性曲線。A characteristic curve in which the width of the upstream flat surface 3 in the corrugated fin 7 for the heat exchanger is set on the horizontal axis, and the fan matching heat radiation amount ratio is set on the vertical axis. 本発明の第２実施例の熱交換器用コルゲートフィン７の正面図。The front view of the corrugated fin 7 for heat exchangers of the 2nd Example of this invention. 同熱交換器用コルゲートフィン７における下流平坦面４の幅を横軸とし、ファンマッチング放熱量比を縦軸とした特性曲線。A characteristic curve in which the width of the downstream flat surface 4 in the corrugated fin 7 for the heat exchanger is set as the horizontal axis, and the fan matching heat radiation amount ratio is set as the vertical axis. 本発明の第３実施例の熱交換器用コルゲートフィン７の正面図。The front view of the corrugated fin 7 for heat exchangers of the 3rd Example of this invention. 本発明の熱交換器用コルゲートフィン７と偏平チューブ６とを並列して形成した熱交換器コアの斜視図。The perspective view of the heat exchanger core which formed the corrugated fin 7 for heat exchangers of this invention, and the flat tube 6 in parallel. 本発明の他の実施例の熱交換器用コルゲートフィン７の正面図（Ａ）及び斜視図（Ｂ）。The front view (A) and the perspective view (B) of the corrugated fin 7 for heat exchangers of another Example of this invention. 図７のＶＩＩＩ−ＶＩＩＩ矢視断面図。FIG. 8 is a sectional view taken along the line VIII-VIII in FIG. 7. 同実施例の変形例１。Modification 1 of the embodiment. 同実施例の変形例２。Modification 2 of the embodiment. 同実施例のコルゲートフィンを用いた熱交換器コアの斜視図。The perspective view of the heat exchanger core using the corrugated fin of the embodiment. 熱交換器の正面図。The front view of a heat exchanger.

次に、図面に基づいて本発明の各実施の形態につき説明する。
図１および図２は本発明の第１実施例の熱交換器用コルゲートフィン７であって、図１（Ａ）はその正面図、図１（Ｂ）は斜視略図である。
この熱交換器用コルゲートフィンは、一例としてアルミニウムの帯状金属板を波形に折返し曲折してなり、気流１が各波の稜線５に平行に流通する。 Next, embodiments of the present invention will be described with reference to the drawings.
1 and 2 show a corrugated fin 7 for a heat exchanger according to a first embodiment of the present invention. FIG. 1 (A) is a front view thereof, and FIG. 1 (B) is a schematic perspective view.
The corrugated fins for a heat exchanger are formed by, for example, folding and bending an aluminum band-shaped metal plate into a waveform, and the air flow 1 flows parallel to the ridgeline 5 of each wave.

この熱交換器用コルゲートフィン７の各波の立上面および立下面には、夫々凹凸波２が形成されている。この凹凸波２は、金属板の厚み方向に横断面が浅い波形に形成されたものである。その各凹凸は、図１（Ａ）の正面図において、斜めの一方方向に傾斜している。そして、その熱交換器用コルゲートフィン７の気流１の上流端部に上流平坦面３が形成されている。その上流平坦面３の気流１の流通方向の幅ｔ１は、１．５ｍｍが最適である。なお、その幅ｔ１は、少なくとも０．５ｍｍ〜２．５ｍｍの範囲Ｌとすることができる。   The corrugated fins 7 for the heat exchanger are formed with the corrugated waves 2 on the rising surface and the rising surface of each wave, respectively. The uneven wave 2 is formed in a waveform whose cross section is shallow in the thickness direction of the metal plate. Each of the concavities and convexities is inclined in one oblique direction in the front view of FIG. An upstream flat surface 3 is formed at the upstream end of the airflow 1 of the heat exchanger corrugated fin 7. The optimum width t1 of the upstream flat surface 3 in the flow direction of the airflow 1 is 1.5 mm. Note that the width t1 can be at least in a range L of 0.5 mm to 2.5 mm.

このような熱交換器用コルゲートフィン７は、図６および図１２に示す如く、偏平チューブ６と熱交換器用コルゲートフィン７とが交互に並列されてコアを構成し、エンジン冷却水が一方のタンクから他方にタンクに、各偏平チューブ６を介して流通し、偏平チューブ６の外面側及び熱交換器用コルゲートフィン７にファンにより起風された気流１が流通する。そして、気流１と偏平チューブ６内の流体との間に熱交換が行われる。
なお、この実施例は、気流１の流入方向の端部のみに上流平坦面３が形成され、熱交換器用コルゲートフィン７の下流端にはそれが存在しない。 In such a heat exchanger corrugated fin 7, as shown in FIGS. 6 and 12, a flat tube 6 and a heat exchanger corrugated fin 7 are alternately arranged in parallel to form a core, and engine cooling water is supplied from one tank. On the other hand, the air flow 1 circulated through the flat tubes 6 through the tanks, and the air flow 1 generated by the fan flows to the outer surface side of the flat tubes 6 and the corrugated fins 7 for the heat exchanger. Then, heat exchange is performed between the air flow 1 and the fluid in the flat tube 6.
In this embodiment, the upstream flat surface 3 is formed only at the end of the airflow 1 in the inflow direction, and does not exist at the downstream end of the heat exchanger corrugated fin 7.

図２は、この熱交換器用コルゲートフィン７の上流平坦面３の幅ｔ１を横軸にとり、ファンマッチング放熱量比を縦軸にとった特性曲線である。
縦軸において、点Ａは上流平坦面３が存在しない従来型フィンの場合のファンマッチング放熱量であり、平坦面の幅の変化対して、従来型の放熱量に比較した値が図示されている。この特性曲線から次のことが明らかとなった
上流平坦面３の存在しない熱交換器用コルゲートフィン７に対して、上流平坦面３の幅ｔ１が１．５ｍｍのとき、特性曲線は最大値（ｍａｘ）を示し、上流平坦面３が少なくとも０．５ｍｍ〜２．５ｍｍの範囲Ｌで、従来型コルゲートフィンに比べて放熱量が増大した。 FIG. 2 is a characteristic curve in which the width t1 of the upstream flat surface 3 of the heat exchanger corrugated fin 7 is plotted on the horizontal axis, and the fan matching heat radiation amount ratio is plotted on the vertical axis.
On the vertical axis, point A is a fan matching heat radiation amount in the case of the conventional fin having no upstream flat surface 3, and shows a value in comparison with the conventional heat radiation amount with respect to a change in the width of the flat surface. . The following is clear from this characteristic curve. When the width t1 of the upstream flat surface 3 is 1.5 mm with respect to the heat exchanger corrugated fin 7 having no upstream flat surface 3, the characteristic curve has the maximum value (max). ), The amount of heat dissipation increased as compared with the conventional corrugated fin when the upstream flat surface 3 was at least in the range L of 0.5 mm to 2.5 mm.

これは、上流平坦面３を設けることによる長所が、それを設けないことによる短所を上回った結果である。即ち、上流平坦面３の気流１の方向の幅ｔ１が０．５ｍｍ〜２．５ｍｍの範囲Ｌでは、上流平坦面３のない従来型のフィンに比べて交換熱量（ファンマッチング放熱量）が増大する。これは、上流平坦面３による伝熱面積の低下等の悪影響よりも、平坦面の存在による圧力損失の低下によって流量が増加したことによる効果が上回り、冷却ファンの能力を考慮した交換熱量（ファンマッチング放熱量）が増加するからである。   This is a result of the advantage of providing the upstream flat surface 3 exceeding the disadvantage of not providing it. That is, when the width t1 of the upstream flat surface 3 in the direction of the airflow 1 is in the range L of 0.5 mm to 2.5 mm, the heat exchange amount (fan matching heat radiation amount) increases as compared with the conventional fin having no upstream flat surface 3. I do. This is because the effect of the increase in the flow rate due to the decrease in the pressure loss due to the presence of the flat surface exceeds the adverse effect of the decrease in the heat transfer area due to the upstream flat surface 3. This is because the amount of matching heat radiation increases.

次に、図３および図４は本発明の第２実施例であり、この例は気流１の下流端部に下流平坦面４が設けられている。
この下流平坦面４の気流１の流通方向の幅ｔ２は、２ｍｍが最適である。
なお、その幅ｔ２は少なくとも０．９ｍｍ〜４．６ｍｍの範囲Ｌで下流平坦面４が存在しない従来型フィン点Ａの場合の放熱量を十分に上回る。
なお、図２および図４の各特性曲線は、気流１が熱交換器コアに流入する風速を４ｍ／ｓ（２０℃）とし、偏平チューブに流入するエンジン冷却値水の温度を８０℃とし、コアの厚み（フィン高さ）を５．３ｍｍとし、コルゲートフィンのフィンピッチを２．５ｍｍとし、コルゲートフィンの波の立上面、立下面に平面に対し斜めの一方方向に傾斜している凹凸波を形成した条件のもとである。 Next, FIGS. 3 and 4 show a second embodiment of the present invention. In this embodiment, a downstream flat surface 4 is provided at the downstream end of the air flow 1.
The width t2 of the downstream flat surface 4 in the flow direction of the airflow 1 is optimally 2 mm.
Note that the width t2 is at least in the range L of 0.9 mm to 4.6 mm and sufficiently exceeds the heat radiation amount in the case of the conventional fin point A where the downstream flat surface 4 does not exist.
The characteristic curves in FIGS. 2 and 4 indicate that the wind speed at which the airflow 1 flows into the heat exchanger core is 4 m / s (20 ° C.), the temperature of the engine cooling water flowing into the flat tube is 80 ° C. The corrugated fin has a fin height of 5.3 mm, a fin pitch of the corrugated fin of 2.5 mm, and corrugated fins having a corrugated fin having an uneven surface inclined in one direction obliquely to a plane on the upper and lower surfaces. Under the conditions that formed.

次に、図５は発明の第３実施例であり、この例が上記各実施例と異なる点は、気流１の上流端部に上流平坦面３が設けられ、下流端部に下流平坦面４が設けられていることである。
このようにすることにより、図５の実施例では、図２の効果と図４効果との両者を合わせ持つことになる。即ち、上流平坦面３においてコルゲートフィンの目詰まりが防止され、下流平坦面４により冷却ファンの能力を考慮した交換熱量（ファンマッチング放熱量）がさらに増加する。 Next, FIG. 5 shows a third embodiment of the invention. This embodiment is different from the above embodiments in that an upstream flat surface 3 is provided at the upstream end of the airflow 1 and a downstream flat surface 4 is provided at the downstream end. Is provided.
By doing so, the embodiment of FIG. 5 has both the effect of FIG. 2 and the effect of FIG. That is, the upstream flat surface 3 prevents corrugated fins from being clogged, and the downstream flat surface 4 further increases the amount of exchanged heat (fan matching heat radiation) in consideration of the capacity of the cooling fan.

次に、図７〜図１１は、本発明の他の実施例であって、図７の（Ａ）はその正面図、（Ｂ）は同斜視図、図８は図７のＶＩＩＩ−ＶＩＩＩ矢視断面図、図９はその第１変形例、図１０は同第２変形例、図１１はそのコアの斜視図である。これら各図が前記の各実施例と異なる点は、コルゲートフィンの各波の立上面および立下面に形成された凹凸波２の平面形状である。前記の各実施例では、凹凸波２が斜めの一方方向に傾斜して形成されていたが、図７〜図１１の各例は、それがＶ字状に形成されている。   7 to 11 show another embodiment of the present invention. FIG. 7A is a front view, FIG. 7B is a perspective view of the same, and FIG. 8 is a VIII-VIII arrow in FIG. 9 is a first modified example thereof, FIG. 10 is a second modified example thereof, and FIG. 11 is a perspective view of the core thereof. These drawings are different from the above-described embodiments in the planar shape of the corrugated waves 2 formed on the rising surface and the rising surface of each wave of the corrugated fin. In each of the above-described embodiments, the uneven wave 2 is formed to be inclined in one oblique direction, but in each of FIGS. 7 to 11, it is formed in a V-shape.

図７は、その基本形であり、上流平坦面３を気流１の上流端部に有し、図９はその第１変形例で、気流１の下流端部に下流平坦面４を有し、図１０は同第２変形例で、気流１の流通方向の両端部に、上流平坦面３、下流平坦面４を有するものである。
なお、本発明は上記各実施例に限らず、凹凸波２の形状を各種のものに変形できる。 FIG. 7 shows the basic form thereof, having an upstream flat surface 3 at the upstream end of the airflow 1, and FIG. 9 shows a first modification thereof having a downstream flat surface 4 at the downstream end of the airflow 1. Reference numeral 10 denotes a second modified example, which has an upstream flat surface 3 and a downstream flat surface 4 at both ends in the flow direction of the air flow 1.
The present invention is not limited to the above embodiments, and the shape of the uneven wave 2 can be modified into various shapes.

本発明のコルゲートフィンは、ラジエータやオイルクーラ、チャージエアクーラ、ＥＧＲクーラ等の各種熱交換器に利用できる。   The corrugated fin of the present invention can be used for various heat exchangers such as radiators, oil coolers, charge air coolers, and EGR coolers.

１ 気流
２ 凹凸波
３ 上流平坦面
４ 下流平坦面
５ 稜線
６ 偏平チューブ
７ 熱交換器用コルゲートフィン
点Ａ 従来型フィン
Ｌ 範囲
ｔ１ 幅
ｔ２ 幅 DESCRIPTION OF SYMBOLS 1 Airflow 2 Concavo-convex wave 3 Upstream flat surface 4 Downstream flat surface 5 Ridge line 6 Flat tube 7 Corrugated fin for heat exchanger Point A Conventional fin L Range t1 width t2 width

Claims (2)

帯状金属板が波形に折返し曲折されてなり、各波の稜線方向に気流（１）が導かれるコルゲートフィンにおいて、
前記各波の立上面および立下面に、金属板の厚み方向に凹凸波（２）が形成され、前記各波の前記気流（１）の上流端部には、前記凹凸波（２）の存在しない上流平坦面（３）が形成され、その上流平坦面（３）の前記気流（１）の流通方向の幅（ｔ１）が０．５ｍｍ〜２．５ｍｍであることを特徴とする熱交換器用コルゲートフィン。 In a corrugated fin in which a band-shaped metal plate is folded and bent into a waveform, and an air current (1) is guided in a ridgeline direction of each wave,
An uneven wave (2) is formed in the thickness direction of the metal plate on the upper surface and the lower surface of each wave, and the uneven wave (2) is present at the upstream end of the air current (1) of each wave. An upstream flat surface (3) is formed, and a width (t1) of the upstream flat surface (3) in the flow direction of the airflow (1) is 0.5 mm to 2.5 mm. Corrugated fin. 帯状金属板が波形に折返し曲折されてなり、各波の稜線方向に気流（１）が導かれるコルゲートフィンにおいて、
前記各波の立上面および立下面に、金属板の厚み方向に凹凸波（２）が形成され、前記各波の前記気流（１）の下流端部には、前記凹凸波（２）の存在しない下流平坦面（４）が形成され、その下流平坦面（４）の前記気流（１）の流通方向の幅（ｔ２）が０．９ｍｍ〜４．６ｍｍであることを特徴とする熱交換器用コルゲートフィン。 In a corrugated fin in which a band-shaped metal plate is folded and bent into a waveform, and an air current (1) is guided in a ridgeline direction of each wave,
An uneven wave (2) is formed in the thickness direction of the metal plate on the rising surface and the lower surface of each wave, and the uneven wave (2) is present at the downstream end of the airflow (1) of each wave. A downstream flat surface (4) that is not formed is formed, and a width (t2) of the downstream flat surface (4) in the flow direction of the airflow (1) is 0.9 mm to 4.6 mm. Corrugated fin.
JP2018118911A 2018-06-22 2018-06-22 Corrugated fin for heat exchanger Pending JP2019219139A (en)

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2022054963A1 (en) * 2020-09-14 2022-03-17 株式会社ティラド Heat exchanger

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS484649U (en) * 1971-06-16 1973-01-19
JP2006138503A (en) * 2004-11-10 2006-06-01 Denso Corp Heat exchanger
JP2006266628A (en) * 2005-03-25 2006-10-05 Valeo Thermal Systems Japan Corp Fin for heat exchanger, and heat exchanger using the same
JP2007212009A (en) * 2006-02-07 2007-08-23 Sanden Corp Heat exchanger
WO2013008464A1 (en) * 2011-07-14 2013-01-17 パナソニック株式会社 Outdoor heat exchanger, and air conditioning device for vehicle
WO2016043340A1 (en) * 2014-09-19 2016-03-24 株式会社ティラド Corrugated fins for heat exchanger

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS484649U (en) * 1971-06-16 1973-01-19
JP2006138503A (en) * 2004-11-10 2006-06-01 Denso Corp Heat exchanger
JP2006266628A (en) * 2005-03-25 2006-10-05 Valeo Thermal Systems Japan Corp Fin for heat exchanger, and heat exchanger using the same
JP2007212009A (en) * 2006-02-07 2007-08-23 Sanden Corp Heat exchanger
WO2013008464A1 (en) * 2011-07-14 2013-01-17 パナソニック株式会社 Outdoor heat exchanger, and air conditioning device for vehicle
WO2016043340A1 (en) * 2014-09-19 2016-03-24 株式会社ティラド Corrugated fins for heat exchanger

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2022054963A1 (en) * 2020-09-14 2022-03-17 株式会社ティラド Heat exchanger

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