JP4895314B2 - Axial fan - Google Patents

Axial fan Download PDF

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JP4895314B2
JP4895314B2 JP2008553148A JP2008553148A JP4895314B2 JP 4895314 B2 JP4895314 B2 JP 4895314B2 JP 2008553148 A JP2008553148 A JP 2008553148A JP 2008553148 A JP2008553148 A JP 2008553148A JP 4895314 B2 JP4895314 B2 JP 4895314B2
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angle
blade
hub
axial fan
tip
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JP2009531578A (en
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ソク ゾ，キョン
ヨン パク，セ
ジュン キム，ウ
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ハラ クライメート コントロール コーポレーション
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/26—Rotors specially for elastic fluids
    • F04D29/32—Rotors specially for elastic fluids for axial flow pumps
    • F04D29/325—Rotors specially for elastic fluids for axial flow pumps for axial flow fans
    • F04D29/328—Rotors specially for elastic fluids for axial flow pumps for axial flow fans with unequal distribution of blades around the hub
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/26—Rotors specially for elastic fluids
    • F04D29/32—Rotors specially for elastic fluids for axial flow pumps
    • F04D29/38—Blades
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/26—Rotors specially for elastic fluids
    • F04D29/32—Rotors specially for elastic fluids for axial flow pumps
    • F04D29/38—Blades
    • F04D29/384—Blades characterised by form
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/26—Rotors specially for elastic fluids
    • F04D29/32—Rotors specially for elastic fluids for axial flow pumps
    • F04D29/38—Blades
    • F04D29/384—Blades characterised by form
    • F04D29/386—Skewed blades
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/52—Casings; Connections of working fluid for axial pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
    • F04D29/661—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps
    • F04D29/666—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps by means of rotor construction or layout, e.g. unequal distribution of blades or vanes

Description

本発明は、軸流ファンに関し、特に、翼の変形及びアンバランスを低減できる構造的な安定性を図ると共に、低騒音を達成できる軸流ファンに関する。   The present invention relates to an axial flow fan, and more particularly, to an axial flow fan capable of achieving structural stability capable of reducing blade deformation and imbalance and achieving low noise.

図１に示すように、軸流ファン１０は、自動車のラジエーター、コンデンサーなどの熱交換機内部を流れる熱交換媒体を冷却するために使用され、モーターなどの駆動源５０の軸５２に結合したハブ（ｈｕｂ）２０と、ハブ２０の外周に放射状に配置される多数の翼３０と、翼３０の先端に連結して翼３０の変形を防ぐファンバンド（Ｆａｎ Ｂａｎｄ）４０で構成されている。したがって、軸流ファン１０は、駆動源５０からハブ２０に伝達された回転力によって回転し、翼３０により軸方向に空気を流している。   As shown in FIG. 1, the axial fan 10 is used to cool a heat exchange medium flowing inside a heat exchanger such as a radiator or a condenser of an automobile, and is a hub coupled to a shaft 52 of a driving source 50 such as a motor ( hub 20, a large number of blades 30 arranged radially on the outer periphery of the hub 20, and a fan band 40 connected to the tip of the blade 30 to prevent the blade 30 from being deformed. Therefore, the axial fan 10 is rotated by the rotational force transmitted from the drive source 50 to the hub 20, and air is caused to flow in the axial direction by the blades 30.

熱交換器に固定されたシュラウド（Ｓｈｒｏｕｄ）６０は、軸流ファン１０により流された空気を効率よく導くために使用される。シュラウド６０は、軸流ファン１０が回転可能に挿入できる大きさの送風口を有し、且つ駆動源のモーター５０を保持できるように形成されている。   A shroud 60 fixed to the heat exchanger is used to efficiently guide the air flowed by the axial fan 10. The shroud 60 has a blower opening of a size that allows the axial fan 10 to be rotatably inserted therein, and is formed so as to hold the motor 50 as a driving source.

従来の軸流ファン１０の翼３０では、図２に示すように、回転方向側縁である前縁ＬＥ（Ｌｅａｄｉｎｇ Ｅｄｇｅ）と回転反対方向側縁である後縁ＴＥ（Ｔｒａｉｌｉｎｇ Ｅｄｇｅ）は、翼３０がハブ２０と連結する翼根（Ｒｏｏｔ ｏｆ Ｂｌａｄｅ）３２から、翼３０の中央部側にかけては回転と反対の方向に向いて湾曲する後向きスイープ角（Ｂａｃｋｗａｒｄ Ｓｗｅｅｐｉｎｇ Ａｎｇｌｅ）をもち、ファンバンド４０と連結する翼端３４（Ｔｉｐ ｏｆ Ｂｌａｄｅ）にかけて回転方向に向いて湾曲する前向きスイープ角（Ｆｏｒｗａｒｄ Ｓｗｅｅｐｉｎｇ Ａｎｇｌｅ）をもっている。このようなスイープ角が変わることは、軸流ファンの性能を決める重要な要因であるが、満足いく送風効率と騒音低減効果を得ることが難しいことが知られている。   In the blade 30 of the conventional axial flow fan 10, as shown in FIG. 2, the leading edge LE (Leading Edge) which is the rotation direction side edge and the trailing edge TE (Trailing Edge) which is the rotation opposite direction side edge are the blade 30. Has a backward sweeping angle (Backward Sweeping Angle) that curves in the direction opposite to the rotation from the root of blade 32 connected to the hub 20 toward the center of the blade 30, and is connected to the fan band 40. It has a forward sweeping angle (Forward Sweeping Angle) that curves in the direction of rotation toward the tip of blade 34 (Tip of Blade). Such a change in the sweep angle is an important factor that determines the performance of the axial fan, but it is known that it is difficult to obtain a satisfactory blowing efficiency and noise reduction effect.

このような点を考慮して、本出願の発明者は、特許文献１及び特許文献２で軸流ファンを提案した。
特許文献１の軸流ファン１０ａは、図３及び図４に示すように、波形構造の翼３０ａをもち、前縁ＬＥ及び後縁ＴＥのスイープ角が、翼根３２ａから翼端３４ａにかけて、後向きから前向きに、前向きから後向きにと、交互に変化している。さらに、翼弦長ＣＬ（Ｃｈｏｒｄ Ｌｅｎｇｔｈ）は、翼根３２ａから翼端３４ａにかけて徐々に大きくなっている。符号αは、水平線Ｈに対する翼３０ａの角度であり、符号２０ａと４０ａは、それぞれハブとファンバンドを表している。 In consideration of such points, the inventors of the present application proposed an axial fan in Patent Document 1 and Patent Document 2.
As shown in FIGS. 3 and 4, the axial fan 10a of Patent Document 1 has a corrugated blade 30a, and the sweep angle of the leading edge LE and the trailing edge TE is directed backward from the blade root 32a to the blade tip 34a. It changes alternately from forward to forward and from forward to backward. Further, the chord length CL (Cord Length) gradually increases from the blade root 32a to the blade tip 34a. Symbol α is the angle of the blade 30a with respect to the horizontal line H, and symbols 20a and 40a represent the hub and the fan band, respectively.

特許文献２の軸流ファン１０ｂは、図５及び図６に示すように、特許文献１と同様に、波形構造の翼３０ｂであり、翼弦長ＣＬ（図４参照）が、翼根３２ｂから翼端３４ｂにかけて徐々に大きくなっている。さらに、翼根３２ｂは最大後向きスイープ角を、翼端３４ｂは最大前向きスイープ角を有している。符号２０ｂと４０ｂは、それぞれハブ、ファンバンドを示している。   As shown in FIGS. 5 and 6, the axial fan 10b of Patent Document 2 is a corrugated blade 30b as in Patent Document 1, and the chord length CL (see FIG. 4) is from the blade root 32b. It gradually increases toward the blade tip 34b. Further, the blade root 32b has a maximum backward sweep angle, and the blade tip 34b has a maximum forward sweep angle. Reference numerals 20b and 40b denote a hub and a fan band, respectively.

上記の波形構造の翼３０ａ、３０ｂを有する軸流ファン１０ａ、１０ｂによると、前縁ＬＥと後縁ＴＥの中央を繋いだ線である中央弦線ＭＬ（Ｍｉｄ−ｃｈｏｒｄ Ｌｉｎｅ）にある変曲点Ｐ１、Ｐ２間の領域は、空気の流動を分散させる領域として作用し、空気の流れが集中しないようにして、これにより図１及び図２に示した軸流ファン１０に比べて、送風効率が高められると共に、騒音も低減できる。例えば、図７に示すように、上記の波形構造の翼を有する軸流ファンにおいては、ハブ２０ｂの中心Ｃと、隣り合う二つの翼３０ｂ、３０ｂとハブ２０ｂとが接するそれぞれの翼根３２ｂの中心Ｃ１、Ｃ２とを通る二つの線Ｌ１、Ｌ２がなす角度を翼分布角Ａ１、翼３０ｂの数がｎとすると、等分布角は、３６０／ｎとなる。   According to the axial fans 10a and 10b having the corrugated blades 30a and 30b described above, the inflection point is in a central chord line ML (Mid-Chord Line) which is a line connecting the centers of the leading edge LE and the trailing edge TE. The region between P1 and P2 acts as a region for dispersing the air flow, so that the air flow is not concentrated, so that the blowing efficiency is higher than that of the axial fan 10 shown in FIGS. In addition to being increased, noise can also be reduced. For example, as shown in FIG. 7, in the axial flow fan having the above-described corrugated blades, the center C of the hub 20 b and the blade roots 32 b of the two adjacent blades 30 b and 30 b and the hub 20 b are in contact with each other. If the angle between two lines L1 and L2 passing through the centers C1 and C2 is the blade distribution angle A1 and the number of blades 30b is n, the uniform distribution angle is 360 / n.

さらに、翼分布角Ａ１は、等分布角にある軸流ファンから、所定の角度だけ軸流ファンの回転方向（＋）または回転反対方向（−）に移動され得るが、このとき、増加または減少できる角度の範囲をクリアランス角Ｂ（Ｃｌｅａｒａｎｃｅ Ａｎｇｌｅ）と定義される。即ち、“翼分布角Ａ１＝等分布角±クリアランス角Ｂ”で表わせる。 Further, the blade distribution angle A1 can be moved from the axial flow fan having the uniform distribution angle by a predetermined angle in the rotational direction (+) or the reverse rotation direction (−) of the axial flow fan. The range of possible angles is defined as a clearance angle B (Clearance Angle). That is, “blade distribution angle A1 = equal distribution angle ± clearance angle B”.

一方、特許文献３には、均等でない構造をした軸流ファンを開示している。ここでは、翼根から翼端までの曲率が少なくとも二つの翼間で異なっていて、この軸流ファンは、翼の翼根部分の剛性を高めて、翼端部分における騒音を低減する目的であることが示唆されている。 On the other hand, Patent Document 3 discloses an axial fan having an uneven structure. Here, the curvature from the blade root to the blade tip is different between at least two blades, and this axial fan is intended to increase the rigidity of the blade root portion and reduce the noise at the blade tip portion. It has been suggested.

ところが、上記のような従来の波形構造の翼を有する軸流ファンにおいては、クリアランス角Ｂを過度に大きくすると、軸流ファンが回転した時にバランスを崩し、満足いく程に騒音低減効果が達成できない問題点がある。   However, in the axial fan having the conventional corrugated blade as described above, if the clearance angle B is excessively large, the balance is lost when the axial fan rotates, and the noise reduction effect cannot be achieved to a satisfactory degree. There is a problem.

韓国特許公開２００２−９４１８３号明細書Korean Patent Publication No. 2002-94183 韓国特許公開２００２−９４１８４号明細書Korean Patent Publication No. 2002-94184 Specification 米国特許５，０００，６６０号明細書US Patent 5,000,660 Specification

本発明は、上述の従来の問題点に鑑みてなされたもので、最適のクリアランス角を決め、構造安定性を高くして翼の変形とアンバランスの発生を少なくして、低騒音を達成できる軸流ファンを提供することを目的とする。 The present invention has been made in view of the conventional problems described above, Me determine the clearance angle of the optimal, and by increasing the structural stability and reduce the occurrence of deformation and imbalance of the blade, a low noise It aims at providing the axial fan which can be achieved.

上記目的を達成するために、本発明は、ハブ（Ｈｕｂ）（１１０）と、ハブの円周に放射状に配置され、翼根（１２２）と翼端（１２４）との間でスイープ角の方向が翼端（１２４）側の最大の前向角から後向角、前向角、そして、翼根（１２２）側の最大の後向角の順に交互に徐々に変化する流動分散領域（Ｄ）を有する複数の翼（１２０）と、各翼の翼端（１２４）を一体的に連結するファンバンド（Ｆａｎ Ｂａｎｄ）（１３０）と、からなり、
ハブ（１１０）の中心（Ｃ）から、隣り合う二つの翼（１２０）とハブ（１１０）とが接するそれぞれの翼根（１２２）の中心（Ｃ１、Ｃ２）とを通る二つの線（Ｌ１、Ｌ２）がなす角度を翼分布角（Ａ１）とし、翼（１２０）の数をｎとして等分布角を３６０／ｎとし、翼（１２０）を等分布角から回転方向（＋）または回転反対方向（−）に配置させて翼分布角（Ａ１）とする角ををクリアランス角（Ｂ）とするとき、
翼（１２０）は、“翼分布角（Ａ１）＝等分布角±クリアランス角（Ｂ）”の式を満たすと同時に、クリアランス角（Ｂ）が４〜９°の範囲に不均等となるように配置されることを特徴とする。 In order to achieve the above object, the present invention provides a hub (110), a radial arrangement around the circumference of the hub, and a sweep angle direction between the blade root (122) and the blade tip (124). Is a flow dispersion region (D) in which the angle gradually changes alternately from the maximum forward angle on the blade tip (124) side to the backward angle, the forward angle, and the maximum backward angle on the blade root (122) side. a plurality of blades (120) having a fan band integrally connected to the wing tip (124) of each wing (fan band) (130), Ri Tona,
Two lines (L 1, L 2) passing from the center (C) of the hub (110) through the centers (C 1, C 2) of the respective two blades (120) and the blade roots (122) where the hub (110) is in contact. The angle formed by L2) is the blade distribution angle (A1) , the number of blades (120) is n, the uniform distribution angle is 360 / n , and the blade (120) is rotated from the uniform distribution angle to the rotation direction (+) or the reverse rotation direction. (-) to thereby arranged wings distribution angle corners to (A1) when you the clearance angle (B),
The blade (120) satisfies the formula “blade distribution angle (A1) = equal distribution angle ± clearance angle (B)”, and at the same time, the clearance angle (B) is uneven within the range of 4 to 9 °. It is characterized by being arranged.

本発明によると、クリアランス角が６〜７°の範囲であるのがより好ましい。   According to the invention, the clearance angle is more preferably in the range of 6-7 °.

また、ハブの中心から、隣り合う二つの翼とハブとが接するそれぞれの翼根の中心を通る二つの線がなす角度をハブ側翼分布角、二つの翼の翼端の中心を通る二つの線がなす角度を翼端側翼分布角とすると、ハブ側翼分布角と翼端側翼分布角が等しいことが好ましい。   Also, the angle formed by the two lines passing from the center of the hub through the center of each blade root where two adjacent blades contact the hub is the hub-side blade distribution angle, and the two lines passing through the center of the tip of the two blades. If the angle formed by the blade tip side blade distribution angle is preferably the hub side blade distribution angle and the blade tip side blade distribution angle are equal.

この際、翼は、翼端から翼根まで延びる前縁ＬＥを有して、前縁ＬＥは、翼根の最大後向角から翼端の最大前向角まで、スイープ角方向が徐々に変わり翼根側の後向角から、前向き、次いで後向きに、また前向きとなり、最後に翼端側で前向角となることが好ましい。また、翼は、翼端から翼根まで延びる後縁ＴＥを有して、後縁ＴＥのスイープ角の変化パターンが、前縁ＬＥのスイープ角の変化パターンと同じであることが好ましい。   At this time, the wing has a leading edge LE extending from the blade tip to the blade root, and the leading edge LE gradually changes in sweep angle direction from the maximum backward angle of the blade root to the maximum forward angle of the blade tip. From the backward angle on the blade root side, it is preferable to be forward, then backward, and forward, and finally the forward angle on the blade tip side. Further, the wing preferably has a trailing edge TE extending from the blade tip to the blade root, and the change pattern of the sweep angle of the trailing edge TE is preferably the same as the change pattern of the sweep angle of the leading edge LE.

本発明の特徴及び利点は、添付の図面に基づいた詳細な説明によりさらに明確になる。本明細書及び請求の範囲に使用された用語や単語は、発明者が自らの発明を最も最善の方法で説明するために用語の概念を適宜定義できるという原則に即して、本発明の技術的思想に符合する意味や概念として解釈されるべきである。   The features and advantages of the present invention will become more apparent from the detailed description based on the accompanying drawings. The terms and words used in the specification and claims are based on the principle that the inventor can appropriately define the concept of terms to describe his invention in the best way. It should be interpreted as a meaning or concept that matches the ideal thought.

図８には、本発明による軸流ファンの例を示している。本発明による軸流ファン１００は、ハブ（Ｈｕｂ）１１０と、ハブの円周に放射状に配置され、翼根１２２と翼端１２４との間の領域でスイープ角の方向が交互に変わる複数の翼１２０と、それぞれの翼端を一体的に連結するファンバンド（Ｆａｎ Ｂａｎｄ）１３０とからなっている。ここに挙げた軸流ファンの実施の形態は、９枚の翼１２０を持っている。   FIG. 8 shows an example of an axial fan according to the present invention. The axial fan 100 according to the present invention includes a hub 110 and a plurality of blades that are arranged radially on the circumference of the hub and in which the direction of the sweep angle is alternately changed in a region between the blade root 122 and the blade tip 124. 120 and a fan band (Fan Band) 130 for integrally connecting the blade tips. The embodiment of the axial fan described here has nine blades 120.

本発明によると、ハブ１１０の中心Ｃから、隣り合う二つの翼１２０、１２０とハブ１００とが接するそれぞれの翼根１２２の中心Ｃ１、Ｃ２とを通る二つの線Ｌ１、Ｌ２がなす角度を翼分布角Ａ１としたとき、翼１２０を等分布から回転方向（＋）または回転反対方向（−）に配置させて翼分布角（Ａ１）とする角度をクリアランス角Ｂとする。ここで、翼１２０の数をｎとすると、翼１２０が並ぶ間隔を示す等分布角は、３６０／ｎと定義できる。言い換えると、翼１２０は、例えば４０゜間隔で並べることができ、翼１２０の実際の等分布角は、クリアランス角の範囲で所定の角度だけ軸流ファン１００の回転方向（＋）または回転反対方向（−）に配置できる。 According to the present invention, from the center C of the hub 110, the angle formed by the two lines L1 and L2 passing through the centers C1 and C2 of the respective blade roots 122 where the adjacent two blades 120 and 120 and the hub 100 contact each other is formed. When the distribution angle A1 is set, a clearance angle B is defined as an angle at which the blades 120 are arranged in the rotational direction (+) or the rotation opposite direction (−) from the equal distribution to obtain the blade distribution angle (A1) . Here, when the number of the blades 120 is n, the uniform distribution angle indicating the interval at which the blades 120 are arranged can be defined as 360 / n. In other words, the blades 120 can be arranged, for example, at intervals of 40 °, and the actual uniform distribution angle of the blades 120 is the rotation direction (+) or the rotation opposite direction of the axial fan 100 by a predetermined angle within the clearance angle range. (-) Can be arranged .

したがって、翼１２０の翼分布角Ａ１は、“翼分布角Ａ１＝等分布角±クリアランス角Ｂ”の式で表現でき、クリアランス角Ｂは、好ましくは４〜９°の範囲、より好ましくは、６〜７°の範囲である。 Thus, wing profile angle A1 of the blade 120 may be represented by the formula of "wings distribution angle A1 = equal distribution angle ± clearance angle B ', the clearance angle B is preferably in the range from 4 to 9 °, more preferably, It is in the range of 6-7 °.

さらに、ハブ１１０の中心Ｃから、隣り合う二つの翼１２０、１２０とハブ１１０とが接するそれぞれの翼根１２２の中心Ｃ１、Ｃ２とを通る二つの線Ｌ１、Ｌ２がなす角度をハブ側翼分布角Ａ１ｒとし、ハブ１１０の中心Ｃから、二つの翼１２０、１２０の翼端１２４の中心Ｃ３、Ｃ４とを通る二つの線Ｌ３、Ｌ４がなす角度を翼端側翼分布角Ａ１ｔとすると、ハブ側翼分布角Ａ１ｒと翼端側翼分布角Ａ１ｔは、等しいのが好ましい。   Further, from the center C of the hub 110, an angle formed by two lines L1 and L2 passing through the centers C1 and C2 of the respective blade roots 122 where the adjacent two blades 120 and 120 and the hub 110 are in contact with each other is set as a hub side blade distribution angle. Assuming that the angle formed by two lines L3 and L4 passing through the center C3 and C4 of the blade tip 124 of the two blades 120 and 120 from the center C of the hub 110 is a blade-side blade distribution angle A1t, The angle A1r and the blade tip side blade distribution angle A1t are preferably equal.

図９は、図８に示した本発明による軸流ファンにおける翼の構造を説明する部分正面図である。図９の翼１２０には、前縁ＬＥ（Ｌｅａｄｉｎｇ Ｅｄｇｅ）、後縁ＴＥ（Ｔｒａｉｌｉｎｇ Ｅｄｇｅ）、及び前縁と後縁との間の中央を半径方向に延びる線で限定される中央弦ＭＬ（Ｍｉｄ−ｃｈｏｒｄ Ｌｉｎｅ）が示されている。図示したように、本発明による軸流ファンでは、翼１２０の前縁ＬＥは、翼根１２２と翼端１２４の全体区間からみて、翼根１２２側の最大後向角から翼端１２４側の最大前向角まで徐々に方向が変わるスイープ角を有している。さらに、前縁ＬＥは、途中でスイープ角が後向きから前向きに変わる第１の変曲点ｒ１１から、スイープ角が前向きから後向きに変わる第２の変曲点ｒ１２を通り、スイープ角が後向きから前向きに変わる第３の変曲点ｒ１３に至る小区間の流動分散領域Ｄを有している。 FIG. 9 is a partial front view for explaining the structure of the blades in the axial fan according to the present invention shown in FIG. 9 includes a leading edge LE (Leading Edge), a trailing edge TE (Trailing Edge), and a central chord ML (Mid defined by a line extending radially between the leading edge and the trailing edge). -Chord Line). As shown in the drawing, in the axial fan according to the present invention, the leading edge LE of the blade 120 has a maximum backward angle on the blade root 122 side to a maximum on the blade tip 124 side as viewed from the entire section of the blade root 122 and the blade tip 124. It has a sweep angle that changes direction gradually to a forward angle. Furthermore, the leading edge LE from a first inflection point r 11 to replace the forward sweep angle from backward halfway through the second inflection point r 12 sweep angle changes rearward from forward sweep angle retrospective and a flow dispersion region D of small sections leading to the third inflection point r 13 alternative to forward from.

言い換えると、翼１２０の前縁ＬＥは、翼根１２２側の後向き領域と翼端１２４側の前向き領域との間で、スイープ角が翼根１２２側後向きから前向き、後向き、そして前向きの順に徐々に変わり、最後に翼端１２４側で前向きになっている   In other words, the leading edge LE of the wing 120 gradually increases in the order of the sweep angle between the rearward region on the blade root 122 side and the forward region on the blade tip 124 side in the order from the rearward toward the blade root 122 toward the front, the rearward, and the frontward. Changed, and finally turned forward on the wing tip 124 side

また、図示したように、翼１２０の後縁ＴＥも同様に、前縁ＬＥと同じパターンで形成され、即ち、翼根１２２側の後向き領域と翼端１２４側の前向き領域との間で、スイープ角が翼根１２２側後向きから、前向き、後向き、そして前向きの順に徐々に変わり、最後に翼端１２４側で前向きとなっている   Further, as illustrated, the trailing edge TE of the blade 120 is similarly formed in the same pattern as the leading edge LE, that is, sweeps between the backward region on the blade root 122 side and the forward region on the blade tip 124 side. The angle gradually changes from the rear side of the blade root 122 side toward the front side, the rear side, and the front side.

以上のように、流動分散領域Ｄは、二つの流動集中部Ｓ１、Ｓ２を形成し、その流動集中部Ｓ１、Ｓ２で、空気の流れが後縁ＴＥ側に集中し、流れの集中を次第に弱めて、これにより、消費電力に対して送風効率を高めるだけではなく、騒音発生量を大きく低減している。   As described above, the flow dispersion region D forms two flow concentration portions S1 and S2, and the flow concentration portions S1 and S2 cause the air flow to concentrate on the trailing edge TE side and gradually weaken the flow concentration. Thus, not only the air blowing efficiency is increased with respect to the power consumption, but also the noise generation amount is greatly reduced.

図１０〜図１５には、クリアランス角が本発明による４〜９°であるときに、各周波数での騒音レベルを比較したグラフを示している。図１０〜図１５に示すように、本発明の軸流ファン（実施例１及び実施例２）と従来の軸流ファンを同じ電圧条件下で試験した結果、本発明による軸流ファンが、従来のものに比べて騒音レベルが低いことが分かる。本発明による軸流ファンは、低い回転数でも風量が多く、また同じ風量の条件で、本発明の軸流ファンは、従来の軸流ファンと比べると、騒音が低く、回転数及び電圧が低いことが分かった。   10 to 15 show graphs comparing noise levels at each frequency when the clearance angle is 4 to 9 ° according to the present invention. As shown in FIGS. 10 to 15, the axial fan according to the present invention (Examples 1 and 2) and the conventional axial fan were tested under the same voltage condition. It can be seen that the noise level is low compared to the above. The axial fan according to the present invention has a large air volume even at a low rotational speed, and the axial fan of the present invention has lower noise, lower rotational speed and voltage than the conventional axial fan under the same air volume conditions. I understood that.

図１０〜図１５は、均等翼ファンの騒音レベルを黒色で示し、均等でないファンの騒音レベルを灰色で示している。図１０〜図１５において、均等でないファンの騒音ピーク値は、均等翼ファンにおける騒音ピーク値より著しく低いことが確認できる。   10 to 15 show the noise level of the uniform blade fan in black and the noise level of the non-uniform fan in gray. 10 to 15, it can be confirmed that the noise peak value of the non-uniform fan is significantly lower than the noise peak value of the uniform blade fan.

表１は、クリアランス角による全体騒音発生量（Ｏｖｅｒａｌｌ ｎｏｉｓｅ）の変化データを示したもので、図１６は、表１のデータをグラフで示したものである。   Table 1 shows change data of the total noise generation amount (Overall noise) according to the clearance angle, and FIG. 16 shows the data of Table 1 in a graph.

Figure 0004895314
Figure 0004895314

上記表１及び図１６において、クリアランス角が０°は、均等翼ファン、即ち、翼が正確に均等に分布されている場合（翼分布角＝等分布角）を意味している。図１６は、翼の分布角が等分布角であるとき、即ち、クリアランス角が０°であるときに、騒音発生が非常に高く、クリアランス角が大きくなるにつれて、騒音発生が次第に低くなるが、クリアランス角がある量を超えると、再び騒音発生が増加する傾向を明らかに示している。クリアランス角が４〜９°であると、均等なファンより騒音発生が明らかに低減して、特にクリアランス角が６〜７°のとき、騒音低減効果が最大になることが分かる。   In Table 1 and FIG. 16, a clearance angle of 0 ° means a uniform blade fan, that is, a case where blades are accurately and evenly distributed (blade distribution angle = equal distribution angle). FIG. 16 shows that when the distribution angle of the blades is a uniform distribution angle, that is, when the clearance angle is 0 °, the noise generation is very high, and the noise generation gradually decreases as the clearance angle increases. It clearly shows a tendency for noise generation to increase again when the clearance angle exceeds a certain amount. It can be seen that when the clearance angle is 4 to 9 °, the noise generation is clearly reduced by the uniform fan, and the noise reduction effect is maximized especially when the clearance angle is 6 to 7 °.

上記のように構成された本発明による軸流ファンを用いると、翼１２０の翼分布角を最適のクリアランス角にすることにより、従来の軸流ファンに比べ、騒音を大幅に低減することができ静かな運転を行うことが可能になる。さらに、クリアランス角を調節するだけではなく、翼に流動分散領域を作ることにより、送風効率増加と騒音低減の効果をさらに高めることができる。   When the axial fan according to the present invention configured as described above is used, the blade distribution angle of the blade 120 is set to an optimum clearance angle, so that noise can be greatly reduced as compared with the conventional axial fan. It becomes possible to perform quiet driving. Furthermore, not only by adjusting the clearance angle, but also by creating a flow dispersion region in the blade, it is possible to further enhance the effect of increasing the blowing efficiency and reducing noise.

また、本発明による軸流ファンは、従来の軸流ファンに比べ、低い回転数でも多い風量が得られ、構造の安定性を高めることができ、これにより、軸流ファンの耐久性を上げることができる。   In addition, the axial fan according to the present invention can obtain a larger air volume even at a lower rotational speed than the conventional axial fan, and can improve the stability of the structure, thereby improving the durability of the axial fan. Can do.

従来の軸流ファンとシュラウド組立て体の一例を示す分解斜視図である。It is a disassembled perspective view which shows an example of the conventional axial fan and shroud assembly. 従来の軸流ファンの部分正面図である。It is a partial front view of the conventional axial fan. 従来の軸流ファンの別の例を示す正面図である。It is a front view which shows another example of the conventional axial fan. 弦（Ｃｈｏｒｄ）を定義するための翼の断面図である。It is sectional drawing of the wing | blade for defining a chord (Chord). 従来の軸流ファンのまた別の例を示す斜視図である。It is a perspective view which shows another example of the conventional axial fan. 図５に示された軸流ファンの部分正面図である。FIG. 6 is a partial front view of the axial fan shown in FIG. 5. 図５に示した軸流ファンにおける翼分布角を説明する部分正面図である。FIG. 6 is a partial front view illustrating blade distribution angles in the axial fan shown in FIG. 5. 本発明による軸流ファンの実施の形態を示す正面図である。It is a front view which shows embodiment of the axial fan by this invention. 図８に示した本発明の軸流ファンにおける翼の構造を説明する部分正面図である。It is a partial front view explaining the structure of the blade | wing in the axial-flow fan of this invention shown in FIG. 本発明第１の実施形態の軸流ファンと従来の均等翼の軸流ファンにおける周波数による騒音レベルを比較したグラフである。It is the graph which compared the noise level by the frequency in the axial fan of the 1st Embodiment of this invention, and the conventional axial fan of a uniform blade. 本発明第２の実施形態の軸流ファンと従来の均等翼の軸流ファンにおける周波数による騒音レベルを比較したグラフである。It is the graph which compared the noise level by the frequency in the axial fan of the 2nd Embodiment of this invention, and the axial fan of the conventional uniform blade. 本発明第３の実施形態の軸流ファンと従来の均等翼の軸流ファンにおける周波数による騒音レベルを比較したグラフである。It is the graph which compared the noise level by the frequency in the axial fan of the 3rd Embodiment of this invention, and the conventional axial fan of a uniform blade. 本発明第４の実施形態の軸流ファンと従来の均等翼の軸流ファンにおける周波数による騒音レベルを比較したグラフである。It is the graph which compared the noise level by the frequency in the axial fan of the 4th Embodiment of this invention, and the conventional axial fan of a uniform blade. 本発明第５の実施形態の軸流ファンと従来の均等翼の軸流ファンにおける周波数と騒音レベルの関係を示す比較グラフである。It is a comparative graph which shows the relationship between the frequency and noise level in the axial fan of the 5th Embodiment of this invention, and the conventional axial fan of a uniform blade. 本発明第６の実施形態の軸流ファンと従来の均等翼の軸流ファンにおける周波数と騒音レベルの関係を示す比較グラフである。It is a comparative graph which shows the relationship between the frequency and noise level in the axial fan of the 6th Embodiment of this invention, and the conventional axial fan of a uniform blade. クリアランス角による全体騒音発生量（Ｏｖｅｒａｌｌ ｎｏｉｓｅ）の変化パターンを示したグラフである。It is the graph which showed the change pattern of the total noise generation amount (Overall noise) by clearance angle.

符号の説明Explanation of symbols

１１０； ハブ（Ｈｕｂ）
１２０； 翼
１２２； 翼根
１２４； 翼端
１３０； ファンバンド（Ｆａｎ Ｂａｎｄ）
Ａ１； 翼分布角
Ｃ； ハブの中心
Ｃ１、Ｃ２； ハブに接する翼根の中心
Ｌ１、Ｌ２； ハブの中心と翼根の中心とを通る線
Ｄ； 流動分散領域
Ｓ１、Ｓ２； 流動集中部
ｒ１１、ｒ１２、ｒ１３； 第１の変曲点、第２の変曲点、第３の変曲点 110; Hub
120; Wing 122; Wing root 124; Wing tip 130; Fan Band
A1; blade distribution angle C; hub center C1, C2; blade root center in contact with hub L1, L2; line passing through hub center and blade root center D; flow dispersion region S1, S2; flow concentration portion r 11 , r 12 , r 13 ; first inflection point, second inflection point, third inflection point

Claims (5)

ハブ（Ｈｕｂ）（１１０）と、
前記ハブの円周に放射状に配置され、翼根（１２２）と翼端（１２４）との間でスイープ角の方向が前記翼端（１２４）側の最大の前向角から後向角、前向角、そして、前記翼根（１２２）側の最大の後向角の順に交互に徐々に変化する流動分散領域（Ｄ）を有する複数の翼（１２０）と、
各翼の前記翼端（１２４）を一体的に連結するファンバンド（Ｆａｎ Ｂａｎｄ）（１３０）と、からなり、
前記ハブ（１１０）の中心（Ｃ）から、隣り合う二つの翼（１２０）と前記ハブ（１１０）とが接するそれぞれの前記翼根（１２２）の中心（Ｃ１、Ｃ２）とを通る二つの線（Ｌ１、Ｌ２）がなす角度を翼分布角（Ａ１）とし、前記翼（１２０）の数をｎとして等分布角を３６０／ｎとし、前記翼（１２０）を等分布角から回転方向（＋）または回転反対方向（−）に配置させて等分布角（Ａ１）とする角をクリアランス角（Ｂ）とするとき、
前記翼（１２０）は、“翼分布角（Ａ１）＝等分布角±クリアランス角（Ｂ）”の式を満たすと同時に、前記クリアランス角（Ｂ）が４〜９°の範囲に不均等となるように配置されることを特徴とする軸流ファン。A hub (110),
The hub is arranged radially on the circumference of the hub, and the direction of the sweep angle between the blade root (122) and the blade tip (124) is from the maximum forward angle on the blade tip (124) side to the backward angle, forward A plurality of blades (120) having a flow dispersion region (D) that gradually and alternately changes in the direction of the direction and the maximum backward angle on the blade root (122) side ;
A fan band integrally connected to said blade tip of each blade (124) (Fan Band) ( 130), Ri Tona,
Two lines passing from the center (C) of the hub (110) through two adjacent blades (120) and the center (C1, C2) of each blade root (122) where the hub (110) contacts. The angle formed by (L1, L2) is the blade distribution angle (A1) , the number of the blades (120) is n, the uniform distribution angle is 360 / n , and the blade (120) is rotated from the uniform distribution angle to the rotational direction (+ ) or rotating the opposite direction (-) to is arranged when you corners to an equal distribution angle (A1) clearance angle and (B) and,
The blade (120) satisfies the formula “blade distribution angle (A1) = equal distribution angle ± clearance angle (B)”, and at the same time, the clearance angle (B) is uneven within a range of 4 to 9 °. An axial fan characterized by being arranged as described above. 前記クリアランス角（Ｂ）が６〜７°の範囲であることを特徴とする請求項１に記載の軸流ファン。The axial fan according to claim 1, wherein the clearance angle (B) is in a range of 6 to 7 °. 前記ハブ（１１０）の中心（Ｃ）から、隣り合う二つの翼（１２０）と前記ハブ（１１０）とが接するそれぞれの翼根（１２２）の中心（Ｃ１、Ｃ２）とを通る二つの線（Ｌ１、Ｌ２）がなす角度をハブ側翼分布角（Ａ１ｒ）とし、前記二つの翼（１２０）それぞれの翼端（１２４）の中心（Ｃ３、Ｃ４）を通る二つの線（Ｌ３、Ｌ４）がなす角度を翼端側翼分布角（Ａ１ｔ）とすると、前記ハブ側翼分布角（Ａ１ｒ）と前記翼端側翼分布角（Ａ１ｔ）とが等しいことを特徴とする請求項１または２に記載の軸流ファン。  Two lines (from the center (C) of the hub (110)) through two adjacent blades (120) and the center (C1, C2) of each blade root (122) where the hub (110) is in contact ( The angle formed by L1 and L2) is the hub side blade distribution angle (A1r), and two lines (L3 and L4) passing through the centers (C3 and C4) of the blade tips (124) of the two blades (120) are formed. 3. The axial fan according to claim 1, wherein when the angle is a blade tip side blade distribution angle (A1t), the hub side blade distribution angle (A1r) and the blade tip side blade distribution angle (A1t) are equal. . 前記翼（１２０）は、翼端（１２４）から翼根（１２２）に延びる前縁（ＬＥ）を有して、前記前縁（ＬＥ）は、翼根（１２２）の最大後向角から翼端（１２４）の最大前向角まで、スイープ角方向が徐々に変わり、前記翼根（１２２）側の後向角から、前向き、次いで後向き、そしてまた前向きとなり、最後に翼端（１２４）側で前向角となることを特徴とする請求項１に記載の軸流ファン。The wing (120) has a leading edge (LE) extending from a wing tip (124) to a blade root (122), the leading edge (LE) being a wing from a maximum backward angle of the blade root (122). The sweep angle direction gradually changes to the maximum forward angle of the end (124), from the backward angle on the blade root (122) side, forward, then backward, and also forward, and finally the blade tip (124) side The axial fan according to claim 1 , wherein the axial flow fan has a forward angle. 前記翼（１２０）は、翼端（１２４）から翼根（１２２）に延びる後縁（ＴＥ）を有して、前記後縁（ＴＥ）のスイープ角の変化パターンが、前記前縁（ＬＥ）のスイープ角変化パターンと同じであることを特徴とする請求項４に記載の軸流ファン。The wing (120) has a trailing edge (TE) extending from the wing tip (124) to the blade root (122), and the change pattern of the sweep angle of the trailing edge (TE) is the leading edge (LE). 5. The axial fan according to claim 4 , wherein the sweep angle change pattern is the same.
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