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JP2014214894A - Heat exchanger plate fin - Google Patents

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Publication number
JP2014214894A
JP2014214894A JP2013089928A JP2013089928A JP2014214894A JP 2014214894 A JP2014214894 A JP 2014214894A JP 2013089928 A JP2013089928 A JP 2013089928A JP 2013089928 A JP2013089928 A JP 2013089928A JP 2014214894 A JP2014214894 A JP 2014214894A
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Prior art keywords
plate fin
heat exchanger
hole edge
collar
corrugated
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端　聖一
Seiichi Hata
聖一 端
正隆 福澤
Masataka Fukuzawa
正隆 福澤
雅志 竹内
Masashi Takeuchi
雅志 竹内
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T Rad Co Ltd
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T Rad Co Ltd
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/24—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely
    • F28F1/32—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely the means having portions engaging further tubular elements

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

Abstract

【課題】 プレートフィン４のチューブ挿通孔２に設けられたカラー部３の風下側に空気の滞留域が生じることを解消する。
【解決手段】 カラー部３の周りに孔縁波形部６を形成し、隣合うカラー部３間の中間に中間波形部５を形成する。そして、中間波形部５と孔縁波形部６とを半ピッチずらした横断面波形に曲折し、中間波形部５と孔縁波形部６の境界を斜面７で接続する。
【選択図】 図６PROBLEM TO BE SOLVED: To eliminate an air staying area on the leeward side of a collar portion 3 provided in a tube insertion hole 2 of a plate fin 4.
A hole edge corrugated portion is formed around a collar portion, and an intermediate corrugated portion is formed in the middle between adjacent collar portions. Then, the intermediate corrugated portion 5 and the hole edge corrugated portion 6 are bent into a cross-sectional waveform shifted by a half pitch, and the boundary between the intermediate corrugated portion 5 and the hole edge corrugated portion 6 is connected by the slope 7.
[Selection] Figure 6

Description

本発明は主として、空調用の熱交換器に用いるプレートフィンに関し、より詳しくは、プレートフィンを波形に曲折したものに関する。   The present invention mainly relates to a plate fin used in a heat exchanger for air conditioning, and more particularly to a plate fin bent into a waveform.

空調用熱交換器のプレートフィン４で波形に曲折されたものは、図８に示すごとく、平面方形の金属板を幅方向に断面波形に曲折し、その長手方向に定間隔に多数のチューブ挿通孔を形成するとともに、その孔縁部をそれぞれ立ち上げてカラー部３を形成する。そして、各カラー部３を整合させ、多数のプレートフィン４を積層するとともに、そのカラー部３にチューブ９を挿通し、そのチューブ９の内部を拡開して、チューブ９外周とカラー部３内周とを密着させる。そして、チューブ９内に冷媒12を流通させるとともに、プレートフィン４の幅方向に空気流13を流通させ、冷媒12と空気流13との間に熱交換を行なうものである。   As shown in FIG. 8, the plate fin 4 of the heat exchanger for air conditioning is bent into a waveform, and a flat rectangular metal plate is bent into a sectional waveform in the width direction, and a number of tubes are inserted at regular intervals in the longitudinal direction. While forming a hole, the edge part of each hole is raised and the collar part 3 is formed. Then, the collar portions 3 are aligned, a large number of plate fins 4 are stacked, the tube 9 is inserted into the collar portion 3, the inside of the tube 9 is expanded, and the tube 9 outer periphery and the collar portion 3 Close contact with the circumference. And while circulating the refrigerant | coolant 12 in the tube 9, the air flow 13 is distribute | circulated in the width direction of the plate fin 4, and heat exchange is performed between the refrigerant | coolant 12 and the air flow 13. As shown in FIG.

図８の例は、一列あたり二山の山10が形成され、それらの間に谷11が設けられている。山10の頂部は、稜線10ａが長手方向に形成され、谷11の底部には谷線11ｂが、同様に長手方向に形成されている。各プレートフィン４のフィンピッチｆは、1.4〜1.8ｍｍ程度であり、山10の高さｈは、1.0〜1.5ｍｍ程度である。   In the example of FIG. 8, two peaks 10 are formed per row, and a valley 11 is provided between them. At the top of the mountain 10, a ridge line 10a is formed in the longitudinal direction, and at the bottom of the valley 11, a valley line 11b is similarly formed in the longitudinal direction. The fin pitch f of each plate fin 4 is about 1.4 to 1.8 mm, and the height h of the peak 10 is about 1.0 to 1.5 mm.

この山10の数を一列につき三つとした提案が下記特許文献１に記載されている。
これは、その平面が図７（Ａ）に示すごとく形成され、その断面は（Ｂ）のごとく形成されている。このようにチューブ列の一列ごとに山10の数を三つ山とすることにより、図８の例に比べて、熱交換性能を向上させる、と記載されている。 A proposal in which the number of peaks 10 is three per row is described in Patent Document 1 below.
The plane is formed as shown in FIG. 7A, and the cross section is formed as shown in FIG. As described above, it is described that the heat exchange performance is improved as compared with the example of FIG.

特開平９−７９６９５号公報JP-A-9-79695

本発明者の実験によれば、従来の波形に曲折されたプレートフィンは、いずれも図７（Ａ）に示す如く、カラー部３の空気流13の下流側に空気の滞留部８（死水域）が大きく形成される。滞留部８が形成されると、その部分の熱交換性能が低下する。
また、近年のエアコンの省エネルギー化の要求により、各プレートフィンのフィンピッチが従来の1.4〜1.8ｍｍに替えて、1.2〜1.5ｍｍへと高密度化されている。そのため、空気抵抗が増大し、送風動力を増す必要があった。
そこで、本発明はカラー部３の下流側に生じる空気の滞留域を可能な限り小さくし、熱交換を促進するとともに、空気抵抗を低下させるフィンを提案することを課題とする。 According to the inventor's experiment, as shown in FIG. 7A, the plate fins bent in the conventional corrugation are all located on the downstream side of the air flow 13 of the collar portion 3 in the air retention portion 8 (dead water area). ) Is formed greatly. If the retention part 8 is formed, the heat exchange performance of the part will fall.
Further, due to the recent demand for energy saving of air conditioners, the fin pitch of each plate fin is increased to 1.2 to 1.5 mm instead of the conventional 1.4 to 1.8 mm. For this reason, the air resistance is increased, and it is necessary to increase the blowing power.
Accordingly, an object of the present invention is to propose a fin for reducing the air resistance while reducing the air retention area generated on the downstream side of the collar portion 3 as much as possible to promote heat exchange.

請求項１に記載の本発明は、プレート本体(1)の長手方向に定間隔に離間して、多数の円形のチューブ挿通孔(2)が並列され、その挿通孔(2)の孔縁にカラー部(3)が立ち上げ形成されてプレートフィン(4)を構成し、そのカラー部(3)で多数のプレートフィンが積層され、各カラー部(3)にチューブが挿通されてコアを形成し、チューブ内に冷媒が流通すると共に、プレートフィン(4)の幅方向に空気流が流通する熱交換器のプレートフィンにおいて、
プレート本体(1)の長手方向に隣接するカラー部(3)(3)の中間部に、その幅方向に断面波形に曲折された中間波形部(5)を有し、
各カラー部(3)の孔縁部近傍には前記幅方向に断面波形に曲折された孔縁波形部(6)を有し、その孔縁波形部(6)と前記中間波形部(5)は、前記幅方向に半ピッチ分、波の位相がずれ且つ、その孔縁波形部(6)の各波の稜線(6a)および谷線(6b)の両端と、中間波形部(5)の各波の稜線(5a)および谷線(5b)の両端とは互いに離間され、その離間して隣り合う稜線(5a)(6a)と谷線(5b)(6b)との間が斜面(7)で連結されていることを特徴とする熱交換器のプレートフィンである。 The present invention according to claim 1 has a large number of circular tube insertion holes (2) arranged in parallel at a regular interval in the longitudinal direction of the plate body (1), and is arranged at the edge of the insertion hole (2). A collar part (3) is raised and formed to form a plate fin (4). A large number of plate fins are stacked on the collar part (3), and a tube is inserted into each collar part (3) to form a core. In the plate fin of the heat exchanger in which the refrigerant flows in the tube and the air flow flows in the width direction of the plate fin (4),
In the intermediate part of the collar part (3) (3) adjacent in the longitudinal direction of the plate body (1), it has an intermediate corrugated part (5) bent in a cross-sectional corrugation in its width direction,
In the vicinity of the hole edge portion of each collar portion (3), there is a hole edge corrugated portion (6) bent in a cross-sectional waveform in the width direction, the hole edge corrugated portion (6) and the intermediate corrugated portion (5) The phase of the wave is shifted by a half pitch in the width direction, and both ends of the ridge line (6a) and valley line (6b) of each wave of the hole edge waveform part (6), and the intermediate waveform part (5) The ridgeline (5a) and valley line (5b) of each wave are separated from each other, and the slope (7a) between the ridgeline (5a) (6a) and the valley line (5b) (6b) that are adjacent to each other is separated. ) Are connected to each other with a plate fin of a heat exchanger.

請求項２に記載の本発明は、請求項１に記載の熱交換器のプレートフィンにおいて、
前記斜面(7)が平面視で菱形に形成された熱交換器のプレートフィンである。 According to a second aspect of the present invention, in the plate fin of the heat exchanger according to the first aspect,
The inclined surface (7) is a plate fin of a heat exchanger formed in a diamond shape in plan view.

請求項３に記載の本発明は、請求項１または請求項２に記載の熱交換器のプレートフィンにおいて、
各プレートフィンのカラー部(3)の高さｆが1.2〜1.5mmであり、稜線の高さｈが0.4〜0.8mmである熱交換器のプレートフィンである。 According to a third aspect of the present invention, in the plate fin of the heat exchanger according to the first or second aspect,
The plate fins of the heat exchanger are such that the height f of the collar portion (3) of each plate fin is 1.2 to 1.5 mm and the height h of the ridgeline is 0.4 to 0.8 mm.

請求項４に記載の本発明は、請求項１〜請求項３のいずれかに記載の熱交換器のプレートフィンにおいて、
前記チューブ挿通孔(2)が幅方向に一列以上あり、各列に波形の稜線(5a)(6a)が３以上存在する熱交換器のプレートフィンである。 The present invention according to claim 4 is the plate fin of the heat exchanger according to any one of claims 1 to 3,
The tube insertion holes (2) are plate fins of a heat exchanger having one or more rows in the width direction and three or more corrugated ridges (5a) (6a) in each row.

本発明の熱交換器のプレートフィンは、隣合うカラー部３，３間の中間部に、中間波形部５を有し、各カラー部３の孔縁部近傍に孔縁波形部６を有し、その孔縁波形部６と中間波形部５は、フィンの幅方向に半ピッチ分、波の位相がずれている。さらに、孔縁波形部６の各波の稜線6aおよび谷線6bの両端と、中間波形部５の各波の稜線5aおよび谷線5bの両端とは互いに離間され、その離間して隣り合う稜線5a，6aと谷線5b，6bとの間が斜面７で連結されている。
それにより、各カラー部の風下側に形成される空気の滞留域を可及的に無くし、熱交換を促進する効果がある。これは、隣接するカラー部に衝突した空気流が、それを迂回しつつ、半ピッチずれて配置された、各波形部５，６の斜面および、それらを接続する斜面７に導かれる。そして、流入時に幅方向に進入した空気流は、斜めのベクトルを得て、平面視で斜めに流通する。そして、その空気流が隣接するカラー部３の風下側に斜めに導かれ、そこに存在した従来の滞留域を通過するからである。 The plate fin of the heat exchanger of the present invention has an intermediate corrugated portion 5 in the intermediate portion between the adjacent collar portions 3 and 3, and has a hole edge corrugated portion 6 in the vicinity of the hole edge portion of each collar portion 3. The hole edge corrugated portion 6 and the intermediate corrugated portion 5 are out of phase with each other by a half pitch in the fin width direction. Furthermore, both ends of the ridgeline 6a and valley line 6b of each wave of the hole edge corrugated portion 6 and both ends of the ridgeline 5a and valley line 5b of each wave of the intermediate corrugated portion 5 are separated from each other, and the ridgelines adjacent to each other are separated. A slope 7 connects the 5a, 6a and the valley lines 5b, 6b.
Thereby, there is an effect of accelerating heat exchange by eliminating as much as possible an air retention area formed on the leeward side of each collar portion. This is guided to the slopes of the corrugated parts 5 and 6 and the slopes 7 connecting them, which are arranged with a half-pitch shift while the air flow colliding with the adjacent collar part is bypassed. And the airflow which approached in the width direction at the time of inflow obtains a diagonal vector, and distribute | circulates diagonally by planar view. This is because the air flow is obliquely guided to the leeward side of the adjacent collar portion 3 and passes through the conventional staying area existing there.

上記構成に加えて、請求項２に記載のように、斜面７を平面視で菱形に形成した場合には、その斜面を介して、空気流をより円滑に斜めに各谷線5b，6b方向に導き、空気の滞留域を無くして、熱交換を促進できる。   In addition to the above configuration, when the slope 7 is formed in a diamond shape in plan view as described in claim 2, the air flow is more smoothly and obliquely inclined via the slope in the direction of each valley 5b, 6b. The heat exchange can be promoted by eliminating the air retention area.

上記いずれかの構成に加えて、請求項３に記載のように、各プレートフィンのカラー部３の高さｆを1.2〜1.5mmとし、稜線の高さｈを0.4〜0.8mmとした場合には、高密度のプレートフィン型熱交換器において、空気抵抗を低減し、空気の流通をよくして、熱交換を促進できる。
上記いずれかの構成に加えて、請求項４に記載のように、前記チューブ挿通孔(2)を幅方向に一列以上とし、各列に波形の稜線5a，6aを３以上形成した場合には、熱交換をさらに促進できる。 In addition to any of the above configurations, as described in claim 3, when the height f of the collar portion 3 of each plate fin is 1.2 to 1.5 mm and the height h of the ridgeline is 0.4 to 0.8 mm In a high density plate fin type heat exchanger, air resistance can be reduced, air circulation can be improved, and heat exchange can be promoted.
In addition to any of the above configurations, as described in claim 4, when the tube insertion holes (2) are arranged in one or more rows in the width direction and three or more corrugated ridges 5a, 6a are formed in each row , It can further promote heat exchange.

本発明の熱交換器のプレートフィンの平面図。The top view of the plate fin of the heat exchanger of this invention. 図１のII‐II矢視断面図。II-II arrow sectional drawing of FIG. 本発明の第２実施例のプレートフィン４の平面図。The top view of the plate fin 4 of 2nd Example of this invention. 図３のIV‐IV矢視断面図。FIG. 4 is a cross-sectional view taken along the line IV-IV in FIG. 3. 図３のＶ‐Ｖ矢視断面図。FIG. 5 is a cross-sectional view taken along line VV in FIG. 3. 本発明のプレートフィン４の作用を示す説明図。Explanatory drawing which shows the effect | action of the plate fin 4 of this invention. 従来型プレートフィンの平面図および断面図。The top view and sectional drawing of a conventional type plate fin. 同従来型フィンを用いた熱交換器の説明図。Explanatory drawing of the heat exchanger using the conventional fin.

次に、図面に基づいて本発明の実施の形態につき説明する。
図１および図２は、本発明のプレートフィン４であって、二列型のものであり、図３〜図５はその一列型のものである。したがって、両プレートフィン４は、基本的に同一の作用効果を有する。
図１および図２に示す第１実施例では、細長いプレート本体１に多数の円形のチューブ挿通孔２が二列に千鳥状に定間隔に穿設され、その孔縁にカラー部３が立上げ形成されている。このカラー部３の高さｆは、1.2〜1.5ｍｍ程である。 Next, embodiments of the present invention will be described with reference to the drawings.
1 and 2 show a plate fin 4 according to the present invention, which is of a two-row type, and FIGS. Therefore, both plate fins 4 have basically the same function and effect.
In the first embodiment shown in FIGS. 1 and 2, a large number of circular tube insertion holes 2 are formed in two rows in a staggered manner in a long and narrow plate body 1, and a collar portion 3 is raised at the hole edge. Is formed. The height f of the collar portion 3 is about 1.2 to 1.5 mm.

そして、各カラー部３の周縁部には、それを平面略円形に取り囲むように孔縁波形部６が形成されている。そして、隣合う孔縁波形部６の間に中間波形部５が配置され、その中間波形部５の全体の平面形状は中間がくびれた鼓形に形成されている。各中間波形部５、孔縁波形部６は、横断面波形に形成され、その波形は孔縁波形部６と中間波形部５とで、プレートフィン４の幅方向に半ピッチずれている。そして、中間波形部５の波の頂部には稜線5aが、谷部には谷線5bがプレートフィン４の長手方向に形成されている。また、孔縁波形部６の頂部には稜線6aが、谷部には谷線6bが形成されている。その中間波形部５の稜線5aの両端は、平面菱形の斜面７を介して孔縁波形部６の谷線6bに接続され、その中間波形部５の谷線5bの両端は斜面７を介して孔縁波形部６の稜線6aに連結されている。この状態が、図４，図５に示されている。   The peripheral edge portion of each collar portion 3 is formed with a hole edge corrugated portion 6 so as to surround the collar portion 3 in a substantially circular plane. An intermediate corrugated portion 5 is disposed between adjacent hole edge corrugated portions 6, and the entire planar shape of the intermediate corrugated portion 5 is formed in a drum shape with a narrowed middle. Each of the intermediate corrugated portions 5 and the hole edge corrugated portion 6 are formed in a cross-sectional corrugated shape, and the corrugation is shifted by a half pitch in the width direction of the plate fin 4 between the hole edge corrugated portion 6 and the intermediate corrugated portion 5. A ridge line 5 a is formed at the top of the wave of the intermediate corrugated portion 5, and a valley line 5 b is formed at the trough portion in the longitudinal direction of the plate fin 4. A ridge line 6a is formed at the top of the hole edge corrugated portion 6, and a valley line 6b is formed at the valley. Both ends of the ridge line 5a of the intermediate corrugated part 5 are connected to the valley line 6b of the hole edge corrugated part 6 via the plane rhombus slope 7 and both ends of the valley line 5b of the intermediate corrugated part 5 via the slope 7 The hole edge corrugated portion 6 is connected to the ridge line 6a. This state is shown in FIGS.

さらに、図１に示す二列形では、孔縁波形部６、中間波形部５は千鳥に配置されている。また、一列形では図３のごとく長手方向に孔縁波形部６と中間波形部５とが交互に配置されている。そして、図２に示すごとく、稜線5aおよび稜線6aの高さｈは、0.4〜0.8ｍｍ程度である。この高さは、従来のそれに比べて半分程度である。これにより、プレートフィン４の空気抵抗を低減している。
なお、図１および図３において、各稜線5a、稜線6aは細線で表現し、各谷線5b、谷線6bは太線で表現している。 Further, in the two-row shape shown in FIG. 1, the hole edge corrugated portion 6 and the intermediate corrugated portion 5 are arranged in a staggered manner. In the single-row shape, the hole edge corrugated portions 6 and the intermediate corrugated portions 5 are alternately arranged in the longitudinal direction as shown in FIG. And as shown in FIG. 2, the height h of the ridgeline 5a and the ridgeline 6a is about 0.4-0.8 mm. This height is about half that of the prior art. Thereby, the air resistance of the plate fin 4 is reduced.
1 and 3, each ridge line 5a and ridge line 6a are represented by thin lines, and each valley line 5b and valley line 6b are represented by thick lines.

（作用）
次に、図６に基づき本発明のプレートフィンの作用につき、説明する。
先ず、図６において、孔縁波形部６の稜線6aは細線で表現され、その谷線6bは太線で表現されている。同様に半ピッチずれた中間波形部５の稜線5aは細線で表現され、その谷線5bは太線で表現されている。
そして、孔縁波形部６の稜線6aの両端は、中間波形部５の谷線5bの両端に平面菱形の斜面７を介して連結され、孔縁波形部６の谷線6bは中間波形部５の稜線5aに斜面７を介して連結されている。そして、谷線6bと谷線5bとは図上太線によって連結され、稜線6aと稜線5aとは細線によって連結されている。 (Function)
Next, the action of the plate fin of the present invention will be described with reference to FIG.
First, in FIG. 6, the ridge line 6a of the hole edge corrugated portion 6 is expressed by a thin line, and the valley line 6b is expressed by a thick line. Similarly, the ridge line 5a of the intermediate waveform portion 5 shifted by a half pitch is expressed by a thin line, and the valley line 5b is expressed by a thick line.
Then, both ends of the ridge line 6a of the hole edge corrugated portion 6 are connected to both ends of the valley line 5b of the intermediate corrugated portion 5 via the plane rhombus slope 7 and the valley line 6b of the hole edge corrugated portion 6 is connected to the intermediate corrugated portion 5. Is connected to the ridge line 5a via the slope 7. The valley line 6b and the valley line 5b are connected by a thick line in the figure, and the ridge line 6a and the ridge line 5a are connected by a thin line.

ここで、中間波形部５には空気流れb0がプレートフィン４の風上側から流入し、孔縁波形部６には流れa0と、流れc0が流通したとする。
空気の流れa0、流れc0はそれぞれその正面にカラー部３が存在するため、それを迂回する。このとき、カラー部３の近傍ではそれに沿った流れa5、流れc5が存在する。カラー部３から比較的離れた位置では、流れa0は流れa1〜流れa4として斜めに流通する。これは空気流が通風抵抗の、より小さな位置を流通するからである。即ち、流れa1はその入口側の斜面７と、それに隣接する谷線5bとに導かれ、斜めのベクトルをもって、斜めの流れa1方向へ流通する。 Here, it is assumed that the air flow b 0 flows into the intermediate corrugated portion 5 from the windward side of the plate fin 4, and the flow a 0 and the flow c 0 flow through the hole edge corrugated portion 6.
Since the collar part 3 exists in front of the air flow a 0 and the flow c 0 , respectively, they are detoured. At this time, a flow a 5 and a flow c 5 are present in the vicinity of the collar portion 3. The relatively remote position from the collar 3, the flow a 0 is circulated obliquely as stream a 1 ~ flow a 4. This is because the air flow flows through a smaller position of the draft resistance. That is, the flow a 1 is guided to the slope 7 on the inlet side and the valley line 5b adjacent thereto, and flows in the direction of the oblique flow a 1 with an oblique vector.

同様に流れc0は、その正面のカラー部３を迂回し、流れc1方向の斜めに流通する。これは、中間波形部５と孔縁波形部６の稜線どうしおよび、谷線どうしが千鳥に配置され、それらが斜面７で連結された結果である。そして、流れa0は流れa1〜流れa4の斜め方向、流れc0は流れc1〜流れc4の斜め方向に流通する。その結果、流れa1〜流れa4は左隣のカラー部３の裏側に回り込み、そこに乱流を起こすとともに、空気の滞留域を可及的に減少させる。
同様に流れc1〜流れc4の空気流は右側のカラー部３の裏側に回り込み、そこの滞留域を解消させる。次に、中間波形部５に流入した流れb0は、カラー部３が存在しないため、そのまま直進方向に多くのベクトルを有する。 Similarly, the flow c 0 bypasses the collar portion 3 in front of the flow c and flows obliquely in the direction of the flow c 1 . This is a result of the ridge lines and valley lines of the intermediate corrugated portion 5 and the hole edge corrugated portion 6 being arranged in a staggered manner and connected by the slope 7. Then, the flow a 0 is an oblique direction of flow a 1 ~ flow a 4, flow c 0 is distributed to the diagonal direction of flow c 1 ~ flow c 4. As a result, the flow a 1 to the flow a 4 wrap around the back side of the collar portion 3 on the left side, causing turbulence there and reducing the air retention area as much as possible.
Similarly, the air flow of the flow c 1 to the flow c 4 goes around to the back side of the right collar portion 3 to eliminate the staying area there. Next, the flow b 0 flowing into the intermediate waveform portion 5 has many vectors in the straight direction as it is because the collar portion 3 does not exist.

これらの結果、各カラー部３の下流側に形成される空気の滞留域を可及的になくし、熱交換を促進する。これは隣接するカラー部に衝突した空気流がそれを迂回しつつ、半ピッチずれて千鳥に配置された各中間波形部５、孔縁波形部６の斜面およびそれらを接続する斜面７に導かれるからである。そして、流入時にプレートフィン４の幅方向に流入した空気流は、その一部が斜めのベクトルを持ち、平面視で斜めに流通する。そして、その空気流が隣接するカラーの風下側に斜めに導かれ、従来の滞留域を通過してそれを解消する。   As a result, an air retention area formed on the downstream side of each collar portion 3 is eliminated as much as possible to promote heat exchange. This is guided to the slopes of the intermediate corrugations 5, the hole corrugations 6 arranged in a staggered manner, and the slopes 7 connecting them while the air flow colliding with the adjacent collars is bypassed. Because. A part of the air flow that flows in the width direction of the plate fin 4 at the time of inflow has an oblique vector and circulates obliquely in plan view. Then, the air flow is guided obliquely to the leeward side of the adjacent collar and passes through the conventional staying area to eliminate it.

１ プレート本体
２ チューブ挿通孔
３ カラー部
４ プレートフィン
５ 中間波形部
5a 稜線
5b 谷線
６ 孔縁波形部
6a 稜線
6b 谷線 1 Plate body 2 Tube insertion hole 3 Collar portion 4 Plate fin 5 Intermediate corrugated portion
5a Ridge line
5b Valley line 6 Hole edge corrugation
6a Ridge line
6b valley line

７ 斜面
８ 滞留部
９ チューブ
10 山
10a 稜線
11 谷
11b 谷線
12 冷媒
13 空気流 7 Slope 8 Retaining part 9 Tube
10 mountains
10a Ridge line
11 valley
11b valley line
12 Refrigerant
13 Air flow

Claims (4)

プレート本体(1)の長手方向に定間隔に離間して、多数の円形のチューブ挿通孔(2)が並列され、その挿通孔の孔縁にカラー部(3)が立ち上げ形成されてプレートフィン(4)を構成し、
そのカラー部(3)で多数のプレートフィンが積層され、各カラー部(3)にチューブが挿通されてコアを形成し、チューブ内に冷媒が流通すると共に、プレートフィン(4)の幅方向に空気流が流通する熱交換器のプレートフィンにおいて、
プレート本体(1)の長手方向に隣接するカラー部(3)(3)の中間部に、その幅方向に断面波形に曲折された中間波形部(5)を有し、各カラー部(3)の孔縁部近傍には前記幅方向に断面波形に曲折された孔縁波形部(6)を有し、その孔縁波形部(6)と前記中間波形部(5)は、前記幅方向に半ピッチ分、波の位相がずれ且つ、その孔縁波形部(6)の各波の稜線(6a)および谷線(6b)の両端と、中間波形部(5)の各波の稜線(5a)および谷線(5b)の両端とは互いに離間され、その離間して隣り合う稜線(5a)(6a)と谷線(5b)(6b)との間が斜面(7)で連結されていることを特徴とする熱交換器のプレートフィン。 A large number of circular tube insertion holes (2) are spaced apart at regular intervals in the longitudinal direction of the plate body (1), and a collar portion (3) is raised and formed at the hole edge of the insertion hole. (4)
A large number of plate fins are laminated in the collar portion (3), and a tube is inserted into each collar portion (3) to form a core, in which refrigerant flows in the tube and in the width direction of the plate fin (4). In the plate fins of the heat exchanger through which the airflow flows,
In the middle part of the collar part (3) (3) adjacent to the longitudinal direction of the plate body (1), there is an intermediate corrugated part (5) bent in a cross-sectional corrugation in the width direction, and each collar part (3) A hole edge corrugated portion (6) bent in a cross-sectional corrugation in the width direction in the vicinity of the hole edge portion, the hole edge corrugated portion (6) and the intermediate corrugated portion (5) in the width direction Half-pitch, the phase of the wave is out of phase, and both edges of the ridgeline (6a) and valley line (6b) of each hole edge corrugated part (6), and the ridgeline (5a) of each wave of the intermediate corrugated part (5) ) And the valley line (5b) are spaced apart from each other, and the separated ridge lines (5a) (6a) and valley lines (5b) (6b) are connected by the slope (7). The plate fin of the heat exchanger characterized by the above-mentioned. 請求項１に記載の熱交換器のプレートフィンにおいて、
前記斜面(7)が平面視で菱形に形成された熱交換器のプレートフィン。 In the plate fin of the heat exchanger according to claim 1,
A plate fin of a heat exchanger in which the slope (7) is formed in a diamond shape in plan view. 請求項１または請求項２に記載の熱交換器のプレートフィンにおいて、
各プレートフィンのカラー部(3)の高さｆが1.2〜1.5mmであり、稜線の高さｈが0.4〜0.8mmである熱交換器のプレートフィン。 In the plate fin of the heat exchanger according to claim 1 or 2,
A plate fin for a heat exchanger in which the height f of the collar portion (3) of each plate fin is 1.2 to 1.5 mm and the height h of the ridgeline is 0.4 to 0.8 mm. 請求項１〜請求項３のいずれかに記載の熱交換器のプレートフィンにおいて、
前記チューブ挿通孔(2)が幅方向に一列以上あり、各列に波形の稜線(5a)(6a)が３以上存在する熱交換器のプレートフィン。 In the plate fin of the heat exchanger according to any one of claims 1 to 3,
A plate fin of a heat exchanger in which the tube insertion holes (2) have one or more rows in the width direction, and each row has three or more corrugated ridges (5a) and (6a).
JP2013089928A 2013-04-23 2013-04-23 Heat exchanger plate fin Pending JP2014214894A (en)

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Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5761375U (en) * 1980-09-19 1982-04-12
JPS58128385U (en) * 1982-08-20 1983-08-31 ダイキン工業株式会社 Heat exchanger
JPH01179894A (en) * 1987-12-29 1989-07-17 Matsushita Electric Ind Co Ltd heat exchanger with fins
US4923002A (en) * 1986-10-22 1990-05-08 Thermal-Werke, Warme-Kalte-Klimatechnik GmbH Heat exchanger rib
JPH0979695A (en) * 1995-09-14 1997-03-28 Sanyo Electric Co Ltd Heat exchanger and air conditioner having heat exchanger
JPH09112942A (en) * 1995-10-11 1997-05-02 Sanyo Electric Co Ltd Heat exchanger and air conditioner having the heat exchanger
JP2008128569A (en) * 2006-11-21 2008-06-05 Mitsubishi Heavy Ind Ltd Fin and tube type heat exchanger
JP2010286133A (en) * 2009-06-09 2010-12-24 T Rad Co Ltd Plate fin heat exchanger
JP2011089656A (en) * 2009-10-20 2011-05-06 Panasonic Corp Heat exchanger, and article storage device including the same
JP2011163638A (en) * 2010-02-09 2011-08-25 Panasonic Corp Heat exchanger and article storage device with the same

Patent Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5761375U (en) * 1980-09-19 1982-04-12
JPS58128385U (en) * 1982-08-20 1983-08-31 ダイキン工業株式会社 Heat exchanger
US4923002A (en) * 1986-10-22 1990-05-08 Thermal-Werke, Warme-Kalte-Klimatechnik GmbH Heat exchanger rib
JPH01179894A (en) * 1987-12-29 1989-07-17 Matsushita Electric Ind Co Ltd heat exchanger with fins
JPH0979695A (en) * 1995-09-14 1997-03-28 Sanyo Electric Co Ltd Heat exchanger and air conditioner having heat exchanger
JPH09112942A (en) * 1995-10-11 1997-05-02 Sanyo Electric Co Ltd Heat exchanger and air conditioner having the heat exchanger
JP2008128569A (en) * 2006-11-21 2008-06-05 Mitsubishi Heavy Ind Ltd Fin and tube type heat exchanger
JP2010286133A (en) * 2009-06-09 2010-12-24 T Rad Co Ltd Plate fin heat exchanger
JP2011089656A (en) * 2009-10-20 2011-05-06 Panasonic Corp Heat exchanger, and article storage device including the same
JP2011163638A (en) * 2010-02-09 2011-08-25 Panasonic Corp Heat exchanger and article storage device with the same

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