JP2011226448A - Centrifugal fan and air conditioner - Google Patents

Centrifugal fan and air conditioner Download PDF

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JP2011226448A
JP2011226448A JP2010099409A JP2010099409A JP2011226448A JP 2011226448 A JP2011226448 A JP 2011226448A JP 2010099409 A JP2010099409 A JP 2010099409A JP 2010099409 A JP2010099409 A JP 2010099409A JP 2011226448 A JP2011226448 A JP 2011226448A
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centrifugal fan
main plate
blade
shroud
trailing edge
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JP5444108B2 (en
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Mitsuyoshi Ishijima
満義 石嶋
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Toshiba Carrier Corp
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Toshiba Carrier Corp
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Abstract

PROBLEM TO BE SOLVED: To solve a problem wherein noise is generated at trailing edges of blades of a rotating centrifugal fan due to trailing vortex, and in particular, when a centrifugal fan having trailing edges of blades formed approximately linearly from a shroud side to a main plate side is used, noise caused by trailing vortex becomes pronounced.SOLUTION: In this centrifugal fan 1, a recess 7 recessed to a leading edge 5 direction is provided at the trailing edge 6 positioned on the outer peripheral side of a blade 4 of the centrifugal fan 1. A portion in the vicinity of the trailing edge 6 on the main plate 2 side of the blade 4 is bent to a counter-rotating direction of the centrifugal fan 1, and the end on the main plate 2 side of the trailing edge 6 is protruded to the counter-rotating direction of the centrifugal fan 1 with respect to the shroud 3 side end of the trailing edge 6.

Description

本開示は遠心ファンと空気調和機に関する。   The present disclosure relates to a centrifugal fan and an air conditioner.

従来の送風機の形態として種々のものがあるが、その中で、ファンの軸方向から吸込んだ空気を半径方向に吹出す遠心ファンがある。この遠心ファンを備えた送風機は、例えば、空気調和機の室内機に配され、室内熱交換器に空気を送風し、熱交換された空気を室内へ吐出する作用をなす。   There are various types of conventional blowers. Among them, there is a centrifugal fan that blows out air sucked in from the axial direction of the fan in the radial direction. The blower provided with this centrifugal fan is disposed, for example, in an indoor unit of an air conditioner, and blows air to the indoor heat exchanger and discharges the heat-exchanged air into the room.

上記送風機の構成は、駆動電動機と、この駆動電動機の回転軸に嵌着される遠心ファンとからなる。この遠心ファンを選択することにより、空気調和機の室内機の薄形化が促進され、かつ熱交換器に対する熱交換量を確保できる。   The configuration of the blower includes a drive motor and a centrifugal fan that is fitted to the rotating shaft of the drive motor. By selecting this centrifugal fan, it is possible to promote the thinning of the indoor unit of the air conditioner and to secure a heat exchange amount for the heat exchanger.

上記遠心ファンは例えば、特許文献１のように、主板とシュラウドとの間に回転半径方向に沿って複数の翼が設けられ、この翼の後縁がシュラウド側から主板側にかけて略直線状に形成されている。   In the centrifugal fan, for example, as in Patent Document 1, a plurality of blades are provided between the main plate and the shroud along the rotational radius direction, and the trailing edge of the blade is formed substantially linearly from the shroud side to the main plate side. Has been.

国際公開特許ＷＯ２００７／１１９５３２号International Patent Publication No. WO2007 / 119532

遠心ファンを用いた送風機を運転する場合、回転する遠心ファンの翼の後縁部において翼後流渦による騒音が発生する。特に、上記特許文献１のように翼の後縁がシュラウド側から主板側にかけて略直線状に形成された遠心ファンを用いる場合、翼後流渦による騒音が顕著となる。   When operating a blower using a centrifugal fan, noise is generated by the wake vortex at the trailing edge of the rotating centrifugal fan blade. In particular, when a centrifugal fan in which the trailing edge of the blade is formed in a substantially linear shape from the shroud side to the main plate side as in Patent Document 1 above, noise due to the blade wake vortex becomes significant.

本開示は上述した課題を解決するためなされたもので、円盤状の主板と、前記主板に対向して設けられたシュラウドと、前記主板と前記シュラウド間に跨って設けられた複数枚の翼を有する遠心ファンにおいて、前記翼の外周側に位置する後縁は翼の内周側に位置する前縁方向に凹陥した凹状部を有し、翼の主板側の後縁近傍が遠心ファンの反回転方向に湾曲し、後縁の主板側端部が後縁のシュラウド側端部に対し遠心ファンの反回転方向に突出して設けられた遠心ファンとする。   The present disclosure has been made to solve the above-described problem, and includes a disk-shaped main plate, a shroud provided to face the main plate, and a plurality of wings provided between the main plate and the shroud. In the centrifugal fan, the trailing edge located on the outer peripheral side of the blade has a concave portion recessed in the direction of the leading edge located on the inner peripheral side of the blade, and the vicinity of the trailing edge on the main plate side of the blade is counter-rotating of the centrifugal fan. The centrifugal fan is provided in such a manner that the main plate side end portion of the rear edge protrudes in the anti-rotation direction of the centrifugal fan with respect to the shroud side end portion of the rear edge.

本発明の第１の実施の形態に係る遠心ファンの斜視図。The perspective view of the centrifugal fan which concerns on the 1st Embodiment of this invention. 本発明の第１の実施の形態に係る遠心ファンの翼拡大図。The blade | wing enlarged view of the centrifugal fan which concerns on the 1st Embodiment of this invention. 凹状部端点高さに対する騒音値の特性図。The characteristic figure of the noise value with respect to the concave part end point height. 遠心ファンの翼後縁での翼後流渦の発生の様子を示す概略図。Schematic which shows the mode of generation | occurrence | production of the blade | wing wake vortex in the blade trailing edge of a centrifugal fan. 翼吐出整流部の水平断面形状図。The horizontal cross-section figure of a blade discharge rectification | straightening part. 翼吐出整流部の正圧面と負圧面の曲率半径に対する電動機負荷と風量の関係図。The relationship figure of the motor load and the air volume with respect to the curvature radius of the pressure surface and suction surface of a blade discharge rectification | straightening part. 本発明の遠心ファンを備える空気調和機の室内機の断面図。Sectional drawing of the indoor unit of an air conditioner provided with the centrifugal fan of this invention.

以下、図１乃至図７を用いて説明を行う。
（第１の実施の形態）
図１は本発明の第１の実施の形態に係る遠心ファン１の全体斜視図である。
本遠心ファン１は円盤状の主板２と、主板２と同一の外径を有する環状のシュラウド３と、主板２とシュラウド３間に跨った複数枚の翼４からなる。この翼４は内周側に位置する前縁５方向に凹陥した凹状部７を外周側に位置する後縁６に有している。主板２の内周側にはシュラウド３側に膨出し、駆動電動機２２（図７参照）の回転軸が係合するハブ２ａが一体に形成されている。
主板２と対向してシュラウド３が設けられており、この主板２とシュラウド３の間に翼４が内周側の前縁５から、外周側の後縁６にかけてを反回転方向に傾斜して設けられている。また、翼４の回転方向側の面が正圧面８であり、反回転方向側の面が負圧面９である。
遠心ファン１は図中実線矢印の方向へ回転する。 Hereinafter, description will be made with reference to FIGS.
(First embodiment)
FIG. 1 is an overall perspective view of a centrifugal fan 1 according to a first embodiment of the present invention.
The centrifugal fan 1 includes a disk-shaped main plate 2, an annular shroud 3 having the same outer diameter as the main plate 2, and a plurality of blades 4 straddling the main plate 2 and the shroud 3. The blade 4 has a concave portion 7 recessed in the direction of the front edge 5 located on the inner peripheral side at the rear edge 6 located on the outer peripheral side. A hub 2a that bulges toward the shroud 3 and engages with the rotating shaft of the drive motor 22 (see FIG. 7) is integrally formed on the inner peripheral side of the main plate 2.
A shroud 3 is provided opposite to the main plate 2, and the blade 4 is inclined between the main plate 2 and the shroud 3 in the counter-rotating direction from the inner peripheral front edge 5 to the outer peripheral rear edge 6. Is provided. The surface on the rotational direction side of the blade 4 is the pressure surface 8, and the surface on the counter-rotation direction side is the suction surface 9.
The centrifugal fan 1 rotates in the direction of the solid arrow in the figure.

次に翼４について図２を用いて説明する。図２は翼４を正圧面８側から見た図であり、シュラウド３と翼４との境界線をＱ、翼４と主板２の境界線をＳとする。
後縁６は、シュラウド側の凹状部端点（シュラウド側端部）６ａと、凹状部７の最も前縁５側にある最凹点６ｂと、主板側の凹状部端点６ｃと主板２との接点（主板側端部）６ｄを繋ぐ線で構成されている。ここで、凹状部端点６ａはシュラウド３に接しており境界線Ｑの端点と一致している。凹状部端点６ｃは主板２外周から垂直方向（回転軸方向）に高さｌの位置に存在している。 Next, the blade 4 will be described with reference to FIG. FIG. 2 is a view of the blade 4 as seen from the pressure surface 8 side, where Q is the boundary line between the shroud 3 and the blade 4, and S is the boundary line between the blade 4 and the main plate 2.
The rear edge 6 is a contact point between the shroud-side concave portion end point (shroud side end portion) 6 a, the most concave point 6 b on the most front edge 5 side of the concave portion 7, the main plate-side concave portion end point 6 c and the main plate 2. (Main plate side end) It is composed of a line connecting 6d. Here, the concave end point 6 a is in contact with the shroud 3 and coincides with the end point of the boundary line Q. The concave end point 6c is present at a height l in the vertical direction (rotational axis direction) from the outer periphery of the main plate 2.

後縁６は凹状部端点６ａから最凹点６ｂに向かう曲線Ｍと、最凹点６ｂから凹状部端点６ｃに向い反回転方向に湾曲した曲線Ｎで構成され、凹状部端点６ｃから接点６ｄにかけて主板２に対する高さｌの垂線Ｏで構成されている。ここで、曲線Ｍと曲線Ｎは最凹点６ｂにおいて滑らかに接続されている。   The trailing edge 6 is composed of a curved line M from the concave part end point 6a to the most concave point 6b, and a curved line N curved in the counter-rotating direction from the concave part point 6b to the concave part end point 6c. It is composed of a vertical line O having a height 1 with respect to the main plate 2. Here, the curve M and the curve N are smoothly connected at the most concave point 6b.

ここで、主板２の外周とシュラウド３の外周間の回転軸方向の距離（高さ）をＬ１とする。また、凹状部端点６ａから主板へ下ろした垂線を垂線Ｈとする。
最凹点６ｂの主板２からの高さＬ２は０．５Ｌ１よりも小さく、例えば０．４Ｌ１の高さにされている。即ち、凹状部７の最も前縁方向に位置している最凹点６ｂの翼高さ方向位置が、シュラウド３より主板２に近くされている。 Here, the distance (height) in the rotation axis direction between the outer periphery of the main plate 2 and the outer periphery of the shroud 3 is L1. Further, a perpendicular line extending from the concave end point 6a to the main plate is defined as a perpendicular line H.
The height L2 of the most concave point 6b from the main plate 2 is smaller than 0.5L1, for example, 0.4L1. That is, the blade height direction position of the most concave point 6 b located in the most leading edge direction of the concave portion 7 is closer to the main plate 2 than the shroud 3.

これは、遠心ファン１の回転時に、シュラウド３側を流れる空気の風速と風量が主板２側を流れる空気の風速と風量に対して大きいため、シュラウド３側の翼面積を小さくすると流量が大きく低下してしまうためである。
即ち、上述のようにＬ２の値を設定することで、シュラウド３側の翼面積を確保し風量が低下するのを抑えつつ凹状部７を設けるためである。
また最凹点６ｂの前記垂線Ｈからの距離（深さ）Ｌ３は０．３Ｌ１程度である。 This is because when the centrifugal fan 1 rotates, the air speed and air volume of the air flowing on the shroud 3 side are larger than the air speed and air volume of the air flowing on the main plate 2 side. It is because it will do.
That is, by setting the value of L2 as described above, the wing area on the shroud 3 side is ensured, and the concave portion 7 is provided while suppressing a decrease in the air volume.
The distance (depth) L3 of the most concave point 6b from the perpendicular H is about 0.3L1.

図３に上記実施の形態の遠心ファン１を風量が６５０ｍ３／ｈになる回転数で回転させたときに発生する騒音値と、凹状部端点６ｃの高さｌの主板２外周とシュラウド３外周間の距離Ｌ１に対する割合（ｌ／Ｌ１）との関係を測定した結果を実線で示す。
また、後縁６に凹状部７を有さない従来の遠心ファンを同様に風量が６５０ｍ３／ｈになる回転数で回転させたときの騒音値を図３に一点鎖線で示す。
ここで使用した遠心ファン１は主板２とシュラウド３の外径が３９０ｍｍ、Ｌ１が５０ｍｍ、Ｌ２が２０ｍｍ（０．４Ｌ１）、Ｌ３が１５ｍｍである。 FIG. 3 shows the noise value generated when the centrifugal fan 1 of the above embodiment is rotated at a rotational speed at which the air volume is 650 m <3> / h, and between the outer periphery of the main plate 2 and the outer periphery of the shroud 3 at the height l of the concave end 6c. The result of measuring the relationship with the ratio (l / L1) to the distance L1 is indicated by a solid line.
Further, the noise value when a conventional centrifugal fan having no concave portion 7 on the rear edge 6 is similarly rotated at a rotational speed at which the air volume becomes 650 m <3> / h is shown by a one-dot chain line in FIG.
The centrifugal fan 1 used here has an outer diameter of the main plate 2 and the shroud 3 of 390 mm, L1 of 50 mm, L2 of 20 mm (0.4L1), and L3 of 15 mm.

騒音値の特性は図３に実線で示すように、凹状部端点の高さｌが主板２外周とシュラウド３外周間の距離Ｌ１の１７％の場合に極小値をとることが実験により確認された。尚、後述する本実施の形態の凹状部端点６ｃの高さｌは特に断らないかぎり０．１７Ｌ１であるとする。   As shown by the solid line in FIG. 3, it has been experimentally confirmed that the noise value has a minimum value when the height l of the concave portion end point is 17% of the distance L1 between the outer periphery of the main plate 2 and the outer periphery of the shroud 3. . It is assumed that the height l of the concave end point 6c of this embodiment to be described later is 0.17L1 unless otherwise specified.

翼４の後縁６に凹状部７を設けた本実施の形態の翼後流渦Ｕの様子を図４（Ａ）に示し、翼４の後縁６が直線状に形成された従来の翼形状の翼後流渦Ｕの様子を図４（Ｂ）に示す。
図４（Ｂ）の従来の遠心ファンにおいては、前縁から導かれた空気が後縁から吐出する際に、後縁全体に分布して発生する翼後流渦Ｕが、後縁から離れるに従って合成され、大きな翼後流渦Ｕとなり騒音の原因となる。これに対し、図４（Ａ）に示すように後縁に凹状部７を設けた本実施の形態のものは、翼後流渦Ｕの発生位置を翼４の高さ方向においてずらすことができ、翼後流渦Ｕの合成を抑え騒音の発生を抑制することができる。 FIG. 4A shows the state of the wake vortex U of the present embodiment in which the concave portion 7 is provided on the trailing edge 6 of the blade 4, and the conventional blade in which the trailing edge 6 of the blade 4 is formed in a straight line. A state of the wing wake vortex U having a shape is shown in FIG.
In the conventional centrifugal fan of FIG. 4 (B), when the air guided from the leading edge is discharged from the trailing edge, the blade wake vortex U generated and distributed over the entire trailing edge is separated from the trailing edge. It is synthesized and becomes a large wake vortex U, which causes noise. On the other hand, as shown in FIG. 4A, in the present embodiment in which the concave portion 7 is provided at the trailing edge, the generation position of the blade wake vortex U can be shifted in the height direction of the blade 4. The generation of noise can be suppressed by suppressing the synthesis of the blade wake vortex U.

ここで、凹状部端点６ｃの高さｌを小さくし過ぎると風量が低下してしまう。また、凹状部端点６ｃは、最凹点６ｂよりも低い位置でなければならない。そのため高さｌはＬ１の５〜３０％の範囲であることが好ましい。   Here, if the height l of the recessed portion end point 6c is made too small, the air volume is reduced. Further, the concave end point 6c must be lower than the most concave point 6b. Therefore, the height l is preferably in the range of 5 to 30% of L1.

また、図５に凹状部端点６ｃと接点６ｄ間を通る翼吐出整流部１１の主板２に平行な断面形状を実線で示し、翼４の後縁６付近のシュラウド側断面形状を破線で示す。   5 shows a cross-sectional shape parallel to the main plate 2 of the blade discharge rectifying unit 11 passing between the concave end point 6c and the contact 6d by a solid line, and a shroud side cross-sectional shape near the trailing edge 6 of the blade 4 by a broken line.

凹状部端点６ｃと接点６ｄは垂線Ｈよりも反回転方向に位置している。そのため、翼４の主板２に平行な断面において接点６ｄから点ｅを含む主板側後縁近傍が反回転方向に湾曲し、接点６ｄが凹状部端点６ａより反回転方向に突出した形状となっている。   The concave end point 6c and the contact point 6d are located in the counter-rotating direction with respect to the perpendicular H. Therefore, in the cross section parallel to the main plate 2 of the wing 4, the vicinity of the main plate side rear edge including the point e from the contact 6d is curved in the anti-rotation direction, and the contact 6d protrudes in the anti-rotation direction from the concave end point 6a. Yes.

最凹点６ｂと境界線Ｓ上の点ｅを結んだシュラウド３側に凸の曲線を境界線Ｐとする。そして、境界線Ｑから境界線Ｐと境界線Ｓにかけての翼面を主翼面部１０とし、境界線Ｐから主板２と翼４との境界線にかけての翼面、即ち境界線Ｐよりも後縁側の翼面を翼吐出整流部１１とする。このとき、翼４の主板２に平行な断面において主翼面部１０は負圧面９側に凸の曲面で構成されており、翼吐出整流部１１は正圧面８側に凸の曲面で構成されている。翼吐出整流部１１において、負圧面９側の曲率半径Ｒ１と正圧面８側の曲率半径Ｒ２の関係がＲ１≧Ｒ２となっている。   A curved line convex toward the shroud 3 connecting the most concave point 6b and the point e on the boundary line S is defined as a boundary line P. The blade surface from the boundary line Q to the boundary line P and the boundary line S is the main blade surface portion 10, and the blade surface from the boundary line P to the boundary line between the main plate 2 and the blade 4, that is, the rear edge side of the boundary line P. The blade surface is a blade discharge rectification unit 11. At this time, in the cross section parallel to the main plate 2 of the blade 4, the main blade surface portion 10 is configured with a convex curved surface toward the suction surface 9, and the blade discharge rectifying portion 11 is configured with a convex curved surface toward the pressure surface 8. . In the blade discharge rectification unit 11, the relationship between the radius of curvature R1 on the suction surface 9 side and the radius of curvature R2 on the pressure surface 8 side is R1 ≧ R2.

さらに、翼吐出整流部１１の正圧面８側の曲率半径Ｒ２は後縁６との接点６ｄにおいて主板２の外周と正圧面８で接するように設定されている。   Further, the radius of curvature R2 on the pressure surface 8 side of the blade discharge rectifying unit 11 is set to contact the outer periphery of the main plate 2 at the pressure surface 8 at a contact point 6d with the trailing edge 6.

上述した構成とすることで翼後流渦Ｕが小さくなって、駆動電動機に与える負荷を小さく抑えることができる。   By setting it as the structure mentioned above, the wing | wake vortex U becomes small and the load given to a drive motor can be restrained small.

図６に、負圧面９の曲率半径Ｒ１と正圧面８の曲率半径Ｒ２の関係が異なる遠心ファンを同一の駆動電動機で回転させた場合の駆動電動機の負荷（入力電力）と風量の関係を示す。ここで、曲線αはＲ１＝４５、Ｒ２＝５５（Ｒ１＜Ｒ２）、曲線βはＲ１＝Ｒ２＝４７ｍｍ、曲線γはＲ１＝４７ｍｍ、Ｒ２＝３６．５ｍｍ（Ｒ１＞Ｒ２）で有る。   FIG. 6 shows the relationship between the drive motor load (input power) and the air volume when centrifugal fans having different relationships between the curvature radius R1 of the suction surface 9 and the curvature radius R2 of the pressure surface 8 are rotated by the same drive motor. . Here, the curve α is R1 = 45, R2 = 55 (R1 <R2), the curve β is R1 = R2 = 47 mm, the curve γ is R1 = 47 mm, and R2 = 36.5 mm (R1> R2).

試験結果から、Ｒ１＜Ｒ２の遠心ファンに比較して、Ｒ１＝Ｒ２及びＲ１＞Ｒ２の遠心ファンは、後縁６から発生する翼後流渦Ｕが小さく、駆動電動機に掛かる負荷を小さく抑えることができる。このため、Ｒ１＜Ｒ２の遠心ファンに対して、Ｒ１≧Ｒ２の遠心ファンは、同一風量の場合において遠心ファン１の回転に必要な入力電流を低減することができる。   From the test results, compared with the centrifugal fan of R1 <R2, the centrifugal fan of R1 = R2 and R1> R2 has a small blade trailing vortex U generated from the trailing edge 6 and suppresses the load applied to the drive motor. Can do. For this reason, the centrifugal fan of R1 <R2 can reduce the input current required for rotation of the centrifugal fan 1 in the case of the same air volume, compared with the centrifugal fan of R1 <R2.

上述の構成とする遠心ファン１を各種送風機器に使用することで、送風量を低下することなく、入力電力と騒音を低減することが可能である。   By using the centrifugal fan 1 having the above-described configuration for various blower devices, it is possible to reduce input power and noise without reducing the blown amount.

図７に上記実施の形態の遠心ファン１を組込んだ空気調和機の室内機２０の縦断面図を示す。室内機２０は、筐体２０ａ内に室内熱交換器２３と遠心ファン１を収納して構成され、空気吸込口２５及び空気吐出口２４を有している。室内熱交換器２３は筐体２０ａの前面側に配置され、遠心ファンは筐体２０ａの背面側に設けられた架台２１に取付け固定された駆動電動機２２の回転軸に嵌着され、室内熱交換器２３と筐体２０ａの間に配置されている。そして空気調和機の運転時において、駆動電動機２２の駆動に伴い遠心ファン１が回転し、空気吸込口２５から室内熱交換器２３を介して室内機２０内部に空気を取り込み、室内熱交換器２３により熱交換された空気を空気吐出口２４から室内機２０外部へと送風する。   FIG. 7 shows a longitudinal sectional view of an indoor unit 20 of an air conditioner incorporating the centrifugal fan 1 of the above embodiment. The indoor unit 20 is configured by housing the indoor heat exchanger 23 and the centrifugal fan 1 in a housing 20a, and has an air suction port 25 and an air discharge port 24. The indoor heat exchanger 23 is disposed on the front surface side of the housing 20a, and the centrifugal fan is fitted on the rotating shaft of the drive motor 22 attached and fixed to the gantry 21 provided on the back surface side of the housing 20a. It is arrange | positioned between the container 23 and the housing | casing 20a. During the operation of the air conditioner, the centrifugal fan 1 rotates as the drive motor 22 is driven, and air is taken into the indoor unit 20 from the air suction port 25 via the indoor heat exchanger 23, and the indoor heat exchanger 23. The air exchanged by the air is blown from the air outlet 24 to the outside of the indoor unit 20.

空気調和機の室内機２０に上記遠心ファン１を組込ことで、運転時に遠心ファンから発生する騒音が少なく、低い入力電力でも必要な送風量を確保することができる。   By incorporating the centrifugal fan 1 into the indoor unit 20 of the air conditioner, noise generated from the centrifugal fan during operation is small, and a necessary air blowing amount can be ensured even with low input power.

1…遠心ファン、2…主板、3…シュラウド、4…翼、5…前縁、6…後縁、7…凹状部、8…正圧面、9…負圧面、10…翼面部、11…翼吐出整流部、20…室内機、21…架台、22…駆動電動機、23…室内熱交換器、24…空気吹出口、25…空気吸込口、6a…凹状部端点、6b…最凹点、6c…凹状部端点、6d…接点、e…点、Ｈ…垂線、Ｍ…曲線、Ｎ…曲線、Ｏ…垂線、Ｐ…境界線、Ｑ…境界線、Ｓ…境界線 1 ... centrifugal fan, 2 ... main plate, 3 ... shroud, 4 ... blade, 5 ... front edge, 6 ... rear edge, 7 ... concave, 8 ... pressure surface, 9 ... vacuum surface, 10 ... blade surface, 11 ... blade Discharge rectification unit, 20 ... indoor unit, 21 ... pedestal, 22 ... drive motor, 23 ... indoor heat exchanger, 24 ... air outlet, 25 ... air inlet, 6a ... end of concave part, 6b ... most concave point, 6c ... concave end point, 6d ... contact, e ... point, H ... perpendicular, M ... curve, N ... curve, O ... perpendicular, P ... boundary line, Q ... boundary line, S ... boundary line

Claims (4)

円盤状の主板と、
前記主板に対向して設けられたシュラウドと、
前記主板と前記シュラウド間に跨って設けられた複数枚の翼を有する遠心ファンにおいて、
前記翼の外周側に位置する後縁は翼の内周側に位置する前縁方向に凹陥した凹状部を有し、
翼の主板側の後縁近傍が遠心ファンの反回転方向に湾曲し、後縁の主板側端部が後縁のシュラウド側端部に対し遠心ファンの反回転方向に突出して設けられたことを特徴とする遠心ファン。 A disc-shaped main plate;
A shroud provided facing the main plate;
In the centrifugal fan having a plurality of blades provided between the main plate and the shroud,
The rear edge located on the outer peripheral side of the wing has a concave portion recessed in the front edge direction located on the inner peripheral side of the wing,
The vicinity of the trailing edge of the blade on the main plate side is curved in the counter-rotating direction of the centrifugal fan, and the main plate-side end portion of the trailing edge is provided to protrude in the counter-rotating direction of the centrifugal fan with respect to the shroud side end portion of the trailing edge. Features a centrifugal fan. 前記凹状部の最も前縁方向に位置する点の翼高さ方向位置が、シュラウドより主板に近く設けられたことを特徴とする請求項１に記載の遠心ファン。   2. The centrifugal fan according to claim 1, wherein a blade height direction position of a point positioned in the most front edge direction of the concave portion is provided closer to the main plate than the shroud. 前記翼の主板に平行な断面において、主板側後縁近傍の負圧面側の曲率半径が正圧面側の曲率半径より大又は同一であることを特徴とする請求項１乃至２に記載の遠心ファン。   3. The centrifugal fan according to claim 1, wherein, in a cross section parallel to the main plate of the blade, the radius of curvature on the suction surface side in the vicinity of the trailing edge on the main plate side is greater than or equal to the radius of curvature on the pressure surface side. . 請求項１乃至３のいずれか一項に記載の遠心ファンと熱交換器を備えたことを特徴とする空気調和機。   An air conditioner comprising the centrifugal fan according to any one of claims 1 to 3 and a heat exchanger.
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