JP5717620B2 - Automotive heat exchanger fan - Google Patents

Automotive heat exchanger fan Download PDF

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JP5717620B2
JP5717620B2 JP2011279278A JP2011279278A JP5717620B2 JP 5717620 B2 JP5717620 B2 JP 5717620B2 JP 2011279278 A JP2011279278 A JP 2011279278A JP 2011279278 A JP2011279278 A JP 2011279278A JP 5717620 B2 JP5717620 B2 JP 5717620B2
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健太郎 木村
健太郎 木村
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T.RAD CO., L T D.
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Description

本発明は、自動車用熱交換器のコアに対向して配置される冷却ファンに関する。   The present invention relates to a cooling fan disposed to face a core of an automotive heat exchanger.

従来の自動車用熱交換器のファンは、熱交換器コアの背面に対向して配置され、電気モータやエンジンの回転軸等によって駆動され、熱交換器コアの前面側から背面側に起風するものである。この冷却ファンは、ボス部の外周に複数の翼部が一体に形成されている。
図９は、従来型冷却ファンの一例（下記特許文献１に記載）を示し、ボス部１の外周に多数の翼部２が放射状に突設されている。そして、矢印の回転方向の前縁３は、その付根Ａとボス部１の中心とを結ぶ直線Ｅと、前縁３の先端Ｂとボス部１の先端とを結ぶ直線Ｄとのなす角αが１°程度であり、略両直線Ｅ，Ｄは一致するといえる。なお、より厳密には前縁の先端には、小さな円弧（図１参照）が形成されているので、前縁の先端Ｂとは翼部２の先端の延長線と前縁の延長線との交点をいう（以下同じ）。 A fan for a conventional automotive heat exchanger is disposed opposite to the back surface of the heat exchanger core, driven by an electric motor, a rotating shaft of an engine, or the like, and wakes up from the front side of the heat exchanger core to the back side. Is. In this cooling fan, a plurality of blade portions are integrally formed on the outer periphery of the boss portion.
FIG. 9 shows an example of a conventional cooling fan (described in Patent Document 1 below), in which a large number of blade portions 2 are radially projected on the outer periphery of the boss portion 1. The leading edge 3 in the rotational direction of the arrow is an angle α formed by a straight line E connecting the root A and the center of the boss part 1 and a straight line D connecting the tip B of the front edge 3 and the tip of the boss part 1. Is about 1 °, and it can be said that both straight lines E and D coincide. More precisely, since a small arc (see FIG. 1) is formed at the leading edge of the leading edge, the leading edge B is defined by the extension line of the leading edge of the wing 2 and the extending line of the leading edge. An intersection (hereinafter the same).

特開２００３−２３９８９４号公報JP 2003-239894 A

このような自動車用熱交換器のファンは、省エネルギーの観点から風量を維持しつつ、消費電力のより少ないものが望まれている。
そこで、本発明はコンピュータシミュレーションから、翼部の前縁の最適形状を見出し、課題を解決する。 From the viewpoint of energy saving, it is desired that the fan of such a heat exchanger for automobiles has less power consumption while maintaining the air volume.
Therefore, the present invention finds the optimum shape of the leading edge of the wing from computer simulation and solves the problem.

請求項１に記載の本発明は、ボス部(1)の外周に複数の翼部(2)が放射状に突出された熱交換器用冷却ファンにおいて、
そのファンの消費動力を減少させるため、各翼部(2)の回転方向の前縁(3)が次の条件を有する熱交換器用冷却ファン。
(1)その前縁(3)の半径方向の先端（Ｂ）と、その前縁(3)の付根（Ａ）とを結ぶ直線（Ｄ）が、その付根（Ａ）とボス部(1)の中心Ｏとを結ぶ直線（Ｅ）より回転方向の前方にあり、その両直線（Ｄ）（Ｅ）のなす角αが10度〜25度の範囲にある。
(2)その前縁(3)は、その半径方向の中間部が回転方向前方に凸となる弧状に形成され、その弧状の曲率半径Ｒとファンの直径であるファン径Ｄ０との比、Ｒ/Ｄ０が0.18〜0.42である。 The present invention according to claim 1 is a cooling fan for a heat exchanger in which a plurality of blade parts (2) project radially from the outer periphery of a boss part (1).
A cooling fan for a heat exchanger in which the leading edge (3) in the rotational direction of each blade (2) has the following conditions in order to reduce the power consumption of the fan.
(1) A straight line (D) connecting the tip (B) of the front edge (3) in the radial direction and the root (A) of the front edge (3) is connected to the root (A) and the boss (1). The straight line (E) connecting with the center O of the straight line is ahead in the rotational direction, and the angle α formed by both straight lines (D) and (E) is in the range of 10 to 25 degrees.
(2) the ratio of the front edge (3) has its intermediate portion in the radial direction is formed in an arc shape that protrudes forward in the rotational direction, and the fan diameter D 0 is a radius of curvature R and fan diameter of the arc, R / D 0 is 0.18 to 0.42.

請求項２に記載の発明は、請求項１に記載の自動車用熱交換器のファンにおいて、
前記翼部(2)の後縁は、その半径方向の中間部が回転方向前方に凸となる曲線状に形成され且つ、その半径方向の先端部が回転方向の後方に突出され、
その半径方向の先端部の突出端とボス部(1)の中心Ｏとの半径ｒ１、中間位置と中心Ｏとの半径ｒ２、付根と中心Ｏとの半径ｒ３おける各翼幅ａ，ｂ，ｃが、中心Ｏに対する中心角で、次の比率にある。
ａ：ｂ：ｃ＝1：0.92：1.31 The invention according to claim 2 is the fan of the heat exchanger for automobiles according to claim 1,
The rear edge of the wing part (2) is formed in a curved shape in which the intermediate part in the radial direction is convex forward in the rotational direction, and the distal end part in the radial direction protrudes rearward in the rotational direction,
Each blade width a, b, c at the radius r1 between the projecting end of the tip portion in the radial direction and the center O of the boss portion (1), the radius r2 between the intermediate position and the center O, and the radius r3 between the root and the center O Is a central angle with respect to the center O and is in the following ratio.
a: b: c = 1: 0.92: 1.31

ここに、曲率半径とは、図１において、翼部２の前縁の付根の変曲部の点ｃ２とその前縁３の先端の変曲点ａ２とを共に通る半径Ｒをいう。
前縁(3)の付根（Ａ）とは、図１において、曲率半径Ｒの延長線と、ボス部１の外周との交点をいう。
前縁(3)の半径方向の先端（Ｂ）とは、図１において、曲率半径Ｒの延長線と翼部先端の直径Ｄ０の延長線との交点をいう。 Here, the radius of curvature refers to a radius R that passes through the inflection point a2 at the root of the leading edge of the wing 2 and the inflection point a2 at the tip of the leading edge 3 in FIG.
The root (A) of the front edge (3) refers to the intersection of the extension line of the radius of curvature R and the outer periphery of the boss portion 1 in FIG.
Before the radial direction of the tip of the edge (3) (B), in FIG. 1, refer to the intersection of an extension and Tsubasabu tip of the extension line of the diameter D 0 of the radius of curvature R.

直線ＤとＥのなす角αを10度〜25度とし、その前縁３の弧状の曲率半径Ｒとファン直径Ｄ０との比、Ｒ/Ｄ０を0.18〜0.42としたので、ファンの風量、静圧を維持して、消費動力を低減できる。
さらに、その前縁３は、その半径方向の中間部が回転方向前方に凸となる曲率半径Ｒの 弧状に形成され、その前縁３と翼部先端縁とのなす角が鈍角になるから、この自動車用熱交換器のファンは、冠水した道路の走行中に、水中で回転するファンの翼部の変形を可及的に防止できる。そのため、従来型ファンのように、それが水の存在で変形して、翼部先端が熱交換器コア表面に突き刺さり、コアを損傷することを確実に防止できる効果がある。 Since the angle α formed by the straight lines D and E is 10 to 25 degrees, the ratio of the arcuate radius of curvature R of the leading edge 3 to the fan diameter D 0 and R / D 0 is 0.18 to 0.42, The power consumption can be reduced by maintaining the static pressure.
Further, the leading edge 3 is formed in an arc shape with a radius of curvature R in which the radial intermediate portion is convex forward in the rotation direction, and the angle formed by the leading edge 3 and the blade tip edge becomes an obtuse angle. The fan of this automobile heat exchanger can prevent the deformation of the wing part of the fan rotating underwater as much as possible while traveling on a flooded road. Therefore, like a conventional fan, there is an effect that it can be surely prevented that the core is deformed by the presence of water and the blade tip is stuck into the surface of the heat exchanger core to damage the core.

本発明の自動車用熱交換器のファンの正面図。The front view of the fan of the heat exchanger for motor vehicles of this invention. 図１のII−II矢視断面図。II-II arrow sectional drawing of FIG. 図１のIII−III線矢視図。The III-III arrow directional view of FIG. 図１における直線Ｄと直線Ｅとのなす角αを各種変えたときのファン効率をそれぞれ示す。The fan efficiency when the angle α formed by the straight line D and the straight line E in FIG. 図１におけるＲ/Ｄ０を各種変えたときのファン効率を示す。It shows the fan efficiency when varying various the R / D 0 in FIG. 本発明の冷却ファンおよび従来型冷却ファンの風量に対する静圧、トルク、効率、並びに熱交換器の圧力損失Ｖを示す。The static pressure with respect to the air volume of the cooling fan of this invention and the conventional cooling fan, torque, efficiency, and the pressure loss V of a heat exchanger are shown. 本発明の翼部の翼端渦ｗの説明図。Explanatory drawing of the tip vortex w of the wing | blade part of this invention. 従来型冷却ファンの翼端渦ｗの説明図。Explanatory drawing of the tip vortex w of a conventional cooling fan. 従来型冷却ファンの正面図。The front view of a conventional cooling fan.

本発明の自動車用熱交換器のファンは、熱交換器コアの背面に対向して配置され、その回転によりコアの前面側から背面側に起風するものである。
このファンは図１に示すごとく、ボス部１の外周に複数の翼部２が放射状に突出されたものである。そして、各翼部２の回転方向の前縁３の形状、その他を特定し、コンピュータシミュレーション解析することにより、従来の風量を維持しつつ、ファンの消費電力を減少させたものである。 The fan of the heat exchanger for automobiles of the present invention is arranged to face the back surface of the heat exchanger core, and winds from the front side to the back side of the core by its rotation.
As shown in FIG. 1, the fan has a plurality of wing parts 2 projecting radially on the outer periphery of the boss part 1. Then, the shape of the leading edge 3 in the rotation direction of each wing portion 2 and the like are specified and analyzed by computer simulation, thereby reducing the power consumption of the fan while maintaining the conventional air volume.

（解析例１）
前縁３における半径方向の先端（Ｂ）と、その前縁３の付根（Ａ）とを結ぶ直線（Ｄ）と、その付根（Ａ）とボス部(1)の中心Ｏとを結ぶ直線（Ｅ）のなす角αを、＋30°〜−30°まで変化させて、そのファン効率ηｓを測定し、その結果を図４に示す。
このとき、直線Ｄが直線Ｅより回転方向前方にある場合を同図で前進と表示し、逆に直線Ｄが直線Ｅよりも後方にある場合を後進とする。そして、図９に示す従来型ファンを基準（０％）にして、それぞれの角度におけるファン効率ηｓの向上割合を図４において％で表す。その結果、角αが前進の10°〜25°の範囲において、従来形状のファンよりも1.7〜1.8％ポイント（1.7〜1.8ポイント）だけファン効率ηｓが向上した。他の角度においては、ファン効率ηｓが前進10°〜25°よりもいずれも劣るものとなっている。 (Analysis example 1)
A straight line (D) connecting the tip (B) in the radial direction of the front edge 3 and the root (A) of the front edge 3, and a straight line connecting the root (A) and the center O of the boss part (1) ( The fan efficiency ηs was measured by changing the angle α formed by E) from + 30 ° to −30 °, and the result is shown in FIG.
At this time, the case where the straight line D is ahead of the straight line E in the rotational direction is displayed as forward in the figure, and conversely, the case where the straight line D is behind the straight line E is reverse. Then, with the conventional fan shown in FIG. 9 as a reference (0%), the improvement rate of the fan efficiency ηs at each angle is represented by% in FIG. As a result, the fan efficiency ηs was improved by 1.7 to 1.8% points (1.7 to 1.8 points) over the conventional fan in the range where the angle α was 10 ° to 25 ° of forward movement. At other angles, the fan efficiency ηs is inferior to the forward 10 ° to 25 °.

（解析例２）
そこで、前進10°〜25°の中間値として、前進22.5°とし、図１における前縁３のＲを変化させ、そのＲとファンの直径であるファン径Ｄ０との比であるＲ/Ｄ０と、ファン効率の変化を図５に示す。このＲは、同図においてＡ点とＢ点を通る曲率半径を意味する。なお、Ｒの中心は、Ａ点とＢ点を結ぶ直線の直角二等分線上にある。そして、図１のように前縁３側が凸になったものを図５では逆と表示し、前縁３が凹曲線になったものを正と表示し、各Ｒ/Ｄ０の大きさを変化させたとき、従来型形状に比べて、ファン効率の向上を測定した。 (Analysis example 2)
Therefore, the intermediate value of the forward 10 ° to 25 ° is set to the forward 22.5 °, the R of the leading edge 3 in FIG. 1 is changed, and the ratio of the R to the fan diameter D 0 which is the fan diameter R / D. FIG. 5 shows 0 and the change in fan efficiency. This R means the radius of curvature passing through points A and B in the figure. The center of R is on a perpendicular bisector of a straight line connecting points A and B. Then, as shown in FIG. 1, when the leading edge 3 side is convex, the reverse is displayed in FIG. 5, and when the leading edge 3 is a concave curve, it is displayed as positive, and the size of each R / D 0 is indicated. When changed, the improvement in fan efficiency was measured compared to the conventional shape.

その結果、図５に示すとおり、Ｒとファン径Ｄ０との比、Ｒ/Ｄ０が0.18〜0.42の範囲で最大値を得た。その範囲は従来のファンに比べて2.1〜2.4％ポイント（2.1〜2.4ポイント）だけファン効率が上昇している。他の曲率半径では、それらよりも低い値となった。
そこで、本発明はその孤状の曲率半径を中央部が凸となる孤状であって、そのＲ/Ｄ０が0.18〜0.42を採用する。 As a result, as shown in FIG. 5, the maximum value was obtained when the ratio of R to the fan diameter D 0 and R / D 0 was in the range of 0.18 to 0.42. In that range, fan efficiency has increased by 2.1 to 2.4 percentage points (2.1 to 2.4 points) compared to conventional fans. Other curvature radii were lower than those.
Accordingly, the present invention is the arc-shaped curvature radius central portion a arc shape protruding, the R / D 0 is adopted from 0.18 to 0.42.

次に図６は、αが22.5°で、Ｒが100mmの本発明のファンと、図９に示す従来型ファンの風量に対する静圧Ｐｓ、トルクＴ、効率ηｓを示すとともに、風量に対する熱交換器の圧力損失曲線Ｖを示したものである。この圧力損失曲線Ｖと、静圧曲線との交点が動作点である。同図で本発明のファンは×で示し、従来型のファンは■で示す。
動作点において、効率ηｓは、本願発明のほうが2.4％ポイント（2.4ポイント）改善され、消費電力は3.7％ポイント（3.7ポイント）低減した。 Next, FIG. 6 shows the static pressure Ps, the torque T, and the efficiency ηs with respect to the air volume of the fan of the present invention in which α is 22.5 ° and R is 100 mm, and the conventional fan shown in FIG. The pressure loss curve V is shown. The intersection of this pressure loss curve V and the static pressure curve is the operating point. In the figure, the fan of the present invention is indicated by x, and the conventional fan is indicated by ■.
In the operating point, the efficiency ηs was improved by 2.4% points (2.4 points) in the present invention, and the power consumption was reduced by 3.7% points (3.7 points).

（解析例３）
そこで、ファン周りの空気の流れを可視化（シミュレーション解析によるヘリシティ分布）した。その結果、図７のごとく本発明の場合は翼部２の翼端から生じる渦ｗが隣接する翼部２の翼端にぶつからず、その内側を通過することがわかった。
これに対して、図９の従来型ファンでは、図８に示すごとく、翼部２の翼端から生じる渦ｗが隣接する翼部２の翼端に衝突するように流れていることがわかった。 (Analysis example 3)
Therefore, the air flow around the fan was visualized (helicity distribution by simulation analysis). As a result, as shown in FIG. 7, in the case of the present invention, it has been found that the vortex w generated from the blade tip of the blade portion 2 does not hit the blade tip of the adjacent blade portion 2 but passes through the inside thereof.
On the other hand, in the conventional fan of FIG. 9, it was found that the vortex w generated from the blade tip of the blade portion 2 flows so as to collide with the blade tip of the adjacent blade portion 2 as shown in FIG. .

このように翼端渦が隣接する翼に干渉する程度が低下すると、消費動力が低減すると推測できる。なお、実験では、ファン径Ｄ０は320mmであり、ボス直径は120mmである。また、各翼部２の捩れ角は、図１のa1−a2（半径ｒ１）の位置で12°、ｂ1−ｂ2（半径ｒ２）の中間位置で16°、ｃ1−ｃ2（半径ｒ３）の根元位置で20°である。各部における捩れ角βを図３に図示する。基準直線はファンの軸線に直交する面である。
その翼部の半径方向の先端部の突出端とボス部1の中心Ｏとの半径ｒ１、中間位置と中心Ｏとの半径ｒ２、付根と中心Ｏとの半径ｒ３おける各翼幅ａ，ｂ，ｃが、中心Ｏに対する中心角で、次の範囲比率ある。ａ：ｂ：ｃ＝1：0.92：1.31 Thus, it can be estimated that the power consumption decreases when the degree of interference between the blade tip vortex and the adjacent blade decreases. In the experiments, the fan diameter D 0 is 320 mm, the boss diameter is 120 mm. Further, the twist angle of each wing part 2 is 12 ° at the position of a1−a2 (radius r1) in FIG. 1, 16 ° at the intermediate position of b1−b2 (radius r2), and the root of c1−c2 (radius r3). The position is 20 °. The torsion angle β in each part is shown in FIG. The reference straight line is a plane orthogonal to the fan axis.
Each blade width a, b, radius r1 between the projecting end of the tip of the blade in the radial direction and the center O of the boss portion 1, radius r2 between the intermediate position and the center O, and radius r3 between the root and the center O, c is a central angle with respect to the center O, and has the following range ratio. a: b: c = 1: 0.92: 1.31

なお、本発明は四輪の自動車用熱交換器のファンを主に開発したものであるが、自動二輪車用熱交換器のファン、建設機械等の車両用熱交換器のファンにも使用可能である。   Although the present invention was developed mainly for fans of automobile heat exchangers for automobiles, it can also be used for fans of heat exchangers for motorcycles and heat exchangers for vehicles such as construction machinery. is there.

１ ボス部
２ 翼部
３ 前縁
４ 冷却ファン
Ｄ０ ファン径
Ｒ 曲率半径 1 Boss part 2 Wing part 3 Leading edge 4 Cooling fan D 0 Fan diameter R Curvature radius

Claims (2)

ボス部(1)の外周に複数の翼部(2)が放射状に突出された熱交換器用冷却ファンにおいて、
そのファンの消費動力を減少させるため、各翼部(2)の回転方向の前縁(3)が次の条件を有する熱交換器用冷却ファン。
(1)その前縁(3)の半径方向の先端（Ｂ）と、その前縁(3)の付根（Ａ）とを結ぶ直線（Ｄ）が、その付根（Ａ）とボス部(1)の中心Ｏとを結ぶ直線（Ｅ）より回転方向の前方にあり、その両直線（Ｄ）（Ｅ）のなす角αが10度〜25度の範囲にある。
(2)その前縁(3)は、その半径方向の中間部が回転方向前方に凸となる弧状に形成され、その弧状の曲率半径Ｒとファンの直径であるファン径Ｄ０との比、Ｒ/Ｄ０が0.18〜0.42である。 In the heat exchanger cooling fan in which a plurality of blades (2) project radially from the outer periphery of the boss (1),
A cooling fan for a heat exchanger in which the leading edge (3) in the rotational direction of each blade (2) has the following conditions in order to reduce the power consumption of the fan.
(1) A straight line (D) connecting the tip (B) of the front edge (3) in the radial direction and the root (A) of the front edge (3) is connected to the root (A) and the boss (1). The straight line (E) connecting with the center O of the straight line is ahead in the rotational direction, and the angle α formed by both straight lines (D) and (E) is in the range of 10 to 25 degrees.
(2) the ratio of the front edge (3) has its intermediate portion in the radial direction is formed in an arc shape that protrudes forward in the rotational direction, and the fan diameter D 0 is a radius of curvature R and fan diameter of the arc, R / D 0 is 0.18 to 0.42. 請求項１に記載の熱交換器用冷却ファンにおいて、
前記翼部(2)の後縁は、その半径方向の中間部が回転方向前方に凸となる曲線状に形成され且つ、その半径方向の先端部が回転方向の後方に突出され、
その半径方向の先端部の突出端とボス部(1)の中心Ｏとの半径ｒ１、中間位置と中心Ｏとの半径ｒ２、付根と中心Ｏとの半径ｒ３おける各翼幅ａ，ｂ，ｃが、中心Ｏに対する中心角で、次の比率にある。
ａ：ｂ：ｃ＝1：0.92：1.31 The cooling fan for a heat exchanger according to claim 1,
The rear edge of the wing part (2) is formed in a curved shape in which the intermediate part in the radial direction is convex forward in the rotational direction, and the distal end part in the radial direction protrudes rearward in the rotational direction,
Each blade width a, b, c at the radius r1 between the projecting end of the tip portion in the radial direction and the center O of the boss portion (1), the radius r2 between the intermediate position and the center O, and the radius r3 between the root and the center O Is a central angle with respect to the center O and is in the following ratio.
a: b: c = 1: 0.92: 1.31
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