JP2006322379A - Axial flow impeller - Google Patents

Axial flow impeller Download PDF

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Publication number
JP2006322379A
JP2006322379A JP2005146263A JP2005146263A JP2006322379A JP 2006322379 A JP2006322379 A JP 2006322379A JP 2005146263 A JP2005146263 A JP 2005146263A JP 2005146263 A JP2005146263 A JP 2005146263A JP 2006322379 A JP2006322379 A JP 2006322379A
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impeller
blade
axial
axial flow
flow type
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JP2005146263A
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JP5011657B2 (en
Inventor
Kazuo Ogino
和郎 荻野
Atsushi Osada
篤 長田
Hitoshi Nozu
仁志 野津
Kazuhiro Muromachi
和弘 室町
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Panasonic Holdings Corp
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Matsushita Electric Industrial Co Ltd
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Abstract

<P>PROBLEM TO BE SOLVED: To provide an axial flow impeller which generates low noise under condition where the same is installed in an apparatus by reducing blade generation noise. <P>SOLUTION: An impeller 6 has a rear end 4 of a side surface of a blade 1 on a delivery side more than an outer circumference 3 end A in series in a view in an axial direction between the outer circumference 3 end A and a hub 5 side B of the blade 1, and has mounting angle α of the outer circumference 3 of the blade 1 bigger than mounting angle β in an inner circumference angle and getting bigger as it goes to the outer circumference 3 side. Consequently, work can be efficiently done without generating swirl, generation of power and noise is small and the low noise axial flow impeller can be provided. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

本発明は、空気調和機器に使用される軸流型羽根車に関するものである。   The present invention relates to an axial flow type impeller used in an air conditioner.

従来、この種の軸流型羽根車は家庭や事務所で使用されているものがあった（例えば特許文献１参照）。   Conventionally, this type of axial flow type impeller has been used in homes and offices (see, for example, Patent Document 1).

以下、この種の軸流ファンについて、図７および図８を参照しながら説明する。   Hereinafter, this type of axial fan will be described with reference to FIGS.

図に示すように、軸流ファンのブレード１０１は、周方向断面が、前縁１０２から変曲点Ｐまでの間を吸込側へ凹とし、変曲点Ｐから後縁１０３までの間を、逆に凸とした形状となっている。   As shown in the figure, the blade 101 of the axial fan has a circumferential cross-section recessed from the leading edge 102 to the inflection point P toward the suction side, and from the inflection point P to the trailing edge 103, Conversely, it has a convex shape.

上記構成により、軸流ファンが回転すると、吸込側に障害物がある場合、ブレード１０１面では斜流の流れとなるが、ブレード１０１の曲率が変曲点を境に凹および凸になっているので、剥離が少なくなり、剥離渦が抑制され乱流騒音が小さくはなるが、周方向につけられた凹および凸形状なので、効果は小さい。
特開昭５６−４１４９４号公報 With the above configuration, when the axial fan rotates, if there is an obstacle on the suction side, the flow of the blade 101 is a diagonal flow, but the curvature of the blade 101 is concave and convex at the inflection point. Therefore, the separation is reduced, the separation vortex is suppressed and the turbulent noise is reduced, but the effect is small because of the concave and convex shapes attached in the circumferential direction.
JP 56-41494 A

このような従来の軸流型羽根車では、羽根車のブレードからの発生渦がまだ大きく、羽根車の発生騒音が大きく発生するという課題があり、上記従来例のブレード形状では、さらに騒音を低減することが要求されている。   In such a conventional axial flow type impeller, there is a problem that the generated vortex from the blade of the impeller is still large, and the generated noise of the impeller is greatly generated. The blade shape of the conventional example further reduces the noise. Is required to do.

本発明は、このような従来の課題を解決するものであり、ブレード発生騒音を低減し、機器に組み込んだ状態での低騒音の軸流型羽根車を提供することを目的としている。   The present invention solves such a conventional problem, and an object of the present invention is to provide a low-noise axial-flow impeller that reduces blade-generated noise and is incorporated in equipment.

本発明の軸流型羽根車は、上記目的を達成するために、吸込側に障害物がある場合に、吸込側の障害物による半径方向の渦の発生を防止する形状としたブレード曲率を有する形状としたものである。   In order to achieve the above object, the axial-flow impeller of the present invention has a blade curvature that prevents the generation of radial vortices due to the obstruction on the suction side when there is an obstruction on the suction side. It is a shape.

本発明によれば、課題となっているブレード発生騒音を低減し、機器に組み込んだ状態での軸流型羽根車の騒音を低減することができる。   ADVANTAGE OF THE INVENTION According to this invention, the blade generation noise used as a subject can be reduced and the noise of the axial-flow type impeller in the state integrated in the apparatus can be reduced.

本発明の軸流型羽根車は、上記目的を達成するために、ブレードの側面の後端が、羽根車外周からハブ側まで、軸方向にみて順次吐出側にあり、かつブレードの取付角度が外周側ほど大きい羽根車としたものである。   In the axial flow type impeller of the present invention, in order to achieve the above object, the rear end of the side surface of the blade is sequentially on the discharge side in the axial direction from the outer periphery of the impeller to the hub side, and the mounting angle of the blade is The impeller is larger on the outer peripheral side.

本発明によれば、課題となっているブレード発生騒音を低減し、機器に組み込んだ状態での軸流型羽根車の騒音を低減することができる。   ADVANTAGE OF THE INVENTION According to this invention, the blade generation noise used as a subject can be reduced and the noise of the axial-flow type impeller in the state integrated in the apparatus can be reduced.

また、他の手段は、上記目的を達成するために、本発明の軸流型羽根車は、上記目的を達成するために、ブレードの側面の後端が、羽根車外周からハブ側まで、軸方向にみて順次吐出側にあり、かつブレードの半径方向断面が吸込側に凸形状のそりを持つ軸流型羽根車としたものである。   In order to achieve the above-mentioned object, the axial flow type impeller according to the present invention is configured so that the rear end of the side surface of the blade has a shaft extending from the outer periphery of the impeller to the hub side. The axial flow type impeller has a sled that is sequentially on the discharge side as viewed in the direction and has a convex cross section in the radial direction of the blade on the suction side.

本発明によれば、課題となっているブレード発生騒音を低減し、機器に組み込んだ状態での軸流型羽根車の騒音を低減することができる。   ADVANTAGE OF THE INVENTION According to this invention, the blade generation noise used as a subject can be reduced and the noise of the axial-flow type impeller in the state integrated in the apparatus can be reduced.

また、他の手段は、上記目的を達成するために、羽根車を囲むベルマウスは、曲率部と円筒部を有し、円筒部の吐出側端面と羽根車の外周部の吐出側端面とが、側面断面で同じ軸方向位置にある軸流型羽根車としたものである。   In order to achieve the above object, the bell mouth surrounding the impeller has a curvature portion and a cylindrical portion, and the discharge side end surface of the cylindrical portion and the discharge side end surface of the outer peripheral portion of the impeller are provided. The axial flow type impeller is located at the same axial position in the side cross section.

本発明によれば、課題となっているブレード発生騒音を低減し、機器に組み込んだ状態での軸流型羽根車の騒音を低減することができる。   ADVANTAGE OF THE INVENTION According to this invention, the blade generation noise used as a subject can be reduced and the noise of the axial-flow type impeller in the state integrated in the apparatus can be reduced.

また、他の手段は、上記目的を達成するために、羽根車を囲むベルマウスは、曲率部と円筒部を有し、前記曲率部は対向する面である対面方向の中心断面では１／４円弧を形成し、前記対面方向と略直交し対向する面であるもう一つの対面方向の中心断面では、１／４から１／８の範囲の円弧となっている軸流型羽根車としたものである。   In order to achieve the above object, the bellmouth surrounding the impeller has a curvature portion and a cylindrical portion, and the curvature portion is ¼ in the central section in the facing direction, which is a facing surface. An axial flow type impeller that forms an arc and has an arc in the range of ¼ to で は in the center section in the other facing direction, which is a surface that is substantially orthogonal to and opposed to the facing direction. It is.

本発明によれば、課題となっているブレード発生騒音を低減し、機器に組み込んだ状態での軸流型羽根車の騒音を低減することができる。   ADVANTAGE OF THE INVENTION According to this invention, the blade generation noise used as a subject can be reduced and the noise of the axial-flow type impeller in the state integrated in the apparatus can be reduced.

また、他の手段は、上記目的を達成するために、ベルマウスと熱交換するための熱交換器とを長方体の本体に取り付け、前記本体の縦方向寸法は羽根車の直径の８〜１５％とした軸流型羽根車としたものである。   In order to achieve the above object, the other means attaches a heat exchanger for exchanging heat with a bell mouth to a rectangular main body, and the vertical dimension of the main body is 8 to 8 mm of the diameter of the impeller. This is an axial flow type impeller of 15%.

本発明によれば、課題となっているブレード発生騒音を低減し、機器に組み込んだ状態での軸流型羽根車の騒音を低減することができる。   ADVANTAGE OF THE INVENTION According to this invention, the blade generation noise used as a subject can be reduced and the noise of the axial-flow type impeller in the state integrated in the apparatus can be reduced.

また、他の手段は、上記目的を達成するために、羽根車の吸込口に熱交換するための熱交換器を有し、羽根車との距離は羽根車の直径の１０〜３０％である軸流型羽根車としたものである。   Moreover, in order to achieve the said objective, another means has the heat exchanger for heat-exchange to the inlet of an impeller, and the distance with an impeller is 10 to 30% of the diameter of an impeller. It is an axial flow type impeller.

本発明によれば、課題となっているブレード発生騒音を低減し、機器に組み込んだ状態での軸流型羽根車の騒音を低減することができる。   ADVANTAGE OF THE INVENTION According to this invention, the blade generation noise used as a subject can be reduced and the noise of the axial-flow type impeller in the state integrated in the apparatus can be reduced.

本発明によれば、ブレード発生騒音を低減し、機器に組み込んだ状態での騒音を低減することができる軸流型羽根車を提供することができる。   ADVANTAGE OF THE INVENTION According to this invention, the axial flow type impeller which can reduce blade generation noise and can reduce the noise in the state integrated in the apparatus can be provided.

本願発明は、ブレードの側面の後端が、羽根車外周からハブ側まで、軸方向にみて順次吐出側にあり、かつブレードの取付角度が外周側にほど大きい羽根車とし、機器に組み込まれている状態で発生する斜流の流れ方向に適したブレード形状とし、ブレードでの発生渦を低減し、騒音を減少させる軸流型羽根車を提供することができる。   In the present invention, the rear end of the side surface of the blade is on the discharge side as viewed in the axial direction from the outer periphery of the impeller to the hub side, and the impeller has a larger mounting angle toward the outer peripheral side. It is possible to provide an axial-flow impeller that has a blade shape suitable for the direction of the flow of the diagonal flow that occurs in a state where the vortex generated in the blade is reduced and noise is reduced.

以下に、本発明の実施の形態について、図面を参照しながら説明する。   Embodiments of the present invention will be described below with reference to the drawings.

（実施の形態１）
図１および図２は本発明の実施の形態１における軸流型羽根車の側断面図およびブレード取付角を示す図である。 (Embodiment 1)
FIGS. 1 and 2 are a side sectional view and a blade mounting angle of the axial-flow impeller according to the first embodiment of the present invention.

図１および図２において、吸い込み側に熱交換器などの空気抵抗体を有する場合、空気の流れは、ブレード１の入口部２から周方向よりも、ややブレード１の外周３側へと流れる斜流となる。このとき、通常のブレードでは、適した仕事を行わず、渦発生や動力発生が大きくなる。しかし、ブレード１の側面の後端４のブレード１の外周３端Ａからハブ５側ＢのＡＢ間で、軸方向にみて順次Ａより吐出側にあり、かつブレード１の外周３の取付角αが内周側の取付角βより大きく外周３側へ行くほど大きい羽根車６としているので、吸込側に空気抵抗体があり、羽根車の吸込側のハブ５側から吐出口の外周３側に斜めに沿って流れる流れの場合、外周３側での大きな昇圧が必要となるが、外周３側の取付角が大きいので、仕事を渦発生なく効率的に行うことができる。これにより、動力の発生や騒音の発生が小さくて済む。   In FIG. 1 and FIG. 2, when an air resistor such as a heat exchanger is provided on the suction side, the air flow is slightly inclined from the inlet portion 2 of the blade 1 toward the outer periphery 3 side of the blade 1 in the circumferential direction. It becomes a flow. At this time, a normal blade does not perform suitable work, and vortex generation and power generation increase. However, between the outer periphery 3 end A of the blade 1 at the rear end 4 of the side surface of the blade 1 and the AB on the hub 5 side B, the mounting angle α of the outer periphery 3 of the blade 1 is sequentially on the discharge side from A in the axial direction. Is larger than the mounting angle β on the inner circumferential side and larger toward the outer circumferential side 3, so that there is an air resistor on the suction side, from the hub 5 side on the suction side of the impeller to the outer circumferential side 3 side of the discharge port. In the case of a flow flowing along an oblique direction, a large pressure increase on the outer periphery 3 side is required, but since the mounting angle on the outer periphery 3 side is large, work can be efficiently performed without generating vortices. Thereby, generation | occurrence | production of motive power and noise generation can be small.

（実施の形態２）
図３は本発明の実施の形態２における軸流型羽根車の側断面図である。 (Embodiment 2)
FIG. 3 is a side sectional view of the axial-flow impeller in Embodiment 2 of the present invention.

なお、実施の形態１と同一部分については同一番号を付し、詳細な説明を省略する。図３に示すように、吸い込み側に熱交換器などの空気抵抗体を有する場合、空気の流れは、ブレード１の入口部２から周方向よりも、ややブレード１の外周３側へと流れる斜流となる。このとき、通常のブレードでは、最適な仕事を行わず、渦発生や動力発生が大きくなる。しかし、ブレード１の側面の後端４のブレード１の外周３端Ａからハブ５側ＢのＡＢ間で、軸方向にみて順次Ａより吐出側にあり、かつブレード１の外周３の取付角αが内周側の取付角βより大きく外周３側へ行くほど大きく、かつブレード１の半径方向断面が吸込側に凸形状のそり７を持つ羽根車６としているので、吸込側に空気抵抗体があり、羽根車の吸込側のハブ５側から吐出口の外周３側に斜めに沿って流れる流れの場合、外周３側での大きな昇圧が必要となるが、吸込側に凸形状のそり７を持つ外周３側の取付角が大きいので、仕事を渦発生なく効率的に行うことができる。また、外周３側での昇圧などの仕事を、渦発生なく効率的に行うことができる。これにより、動力の発生や騒音の発生が小さくて済む。   The same parts as those in the first embodiment are denoted by the same reference numerals, and detailed description thereof is omitted. As shown in FIG. 3, when an air resistor such as a heat exchanger is provided on the suction side, the air flow is inclined from the inlet portion 2 of the blade 1 to the outer periphery 3 side of the blade 1 slightly in the circumferential direction. It becomes a flow. At this time, an ordinary blade does not perform optimum work, and vortex generation and power generation increase. However, between the outer periphery 3 end A of the blade 1 at the rear end 4 of the side surface of the blade 1 and the AB on the hub 5 side B, the mounting angle α of the outer periphery 3 of the blade 1 is sequentially on the discharge side from A in the axial direction. Is larger than the mounting angle β on the inner peripheral side and increases toward the outer peripheral 3 side, and the radial cross section of the blade 1 is an impeller 6 having a convex sled 7 on the suction side, so that an air resistor is provided on the suction side. Yes, in the case of a flow that flows obliquely from the hub 5 side on the suction side of the impeller to the outer periphery 3 side of the discharge port, a large pressure increase on the outer periphery 3 side is required, but a convex sled 7 is provided on the suction side. Since the mounting angle on the outer periphery 3 side is large, work can be performed efficiently without generating vortices. In addition, work such as boosting on the outer periphery 3 side can be performed efficiently without generating vortices. Thereby, generation | occurrence | production of motive power and noise generation can be small.

（実施の形態３）
図４は本発明の実施の形態３における軸流型羽根車の断面図である。なお、実施の形態１または２と同一部分については同一番号を付し、詳細な説明を省略する。 (Embodiment 3)
FIG. 4 is a cross-sectional view of an axial-flow impeller in Embodiment 3 of the present invention. The same parts as those in the first or second embodiment are denoted by the same reference numerals, and detailed description thereof is omitted.

図４に示すように、吸い込み側に熱交換器などの空気抵抗体を有する場合、空気の流れは、ブレード１の入口部２から周方向よりも、ややブレード１の外周３側へと流れる斜流となる。このとき、通常のブレードでは、最適な仕事を行わず、渦発生や動力発生が大きくなる。しかし、羽根車６を囲むベルマウス８は、曲率部９と円筒部１０を有し、円筒部１０の吐出側端面Ｃと羽根車６の外周３部の吐出側端面Ａとが、側面断面形状で同じ軸方向位置にしているので、吐出部での流れは、ベルマウスの円筒部１０に衝突することなく、スムーズに流れる。円筒部１０が短く円筒部１０端面Ｃが羽根車６の外周３の吐出側端面Ａより、吸い込み側にある場合には、側面騒音が大きくなるし、逆に円筒部１０端面が長く円筒部１０端面Ｃが羽根車６の外周３部の吐出側端面Ａより、吐き出し側にある場合には、斜めの流れが円筒部に衝突し圧力損失が大きくなる。   As shown in FIG. 4, when an air resistor such as a heat exchanger is provided on the suction side, the air flow is inclined from the inlet portion 2 of the blade 1 to the outer periphery 3 side of the blade 1 slightly from the circumferential direction. It becomes a flow. At this time, an ordinary blade does not perform optimum work, and vortex generation and power generation increase. However, the bell mouth 8 surrounding the impeller 6 has a curvature portion 9 and a cylindrical portion 10, and the discharge-side end surface C of the cylindrical portion 10 and the discharge-side end surface A of the outer peripheral portion 3 of the impeller 6 have a side sectional shape. Therefore, the flow at the discharge portion smoothly flows without colliding with the cylindrical portion 10 of the bell mouth. When the cylindrical portion 10 is short and the end surface C of the cylindrical portion 10 is closer to the suction side than the discharge side end surface A of the outer periphery 3 of the impeller 6, the side noise increases, and conversely, the end surface of the cylindrical portion 10 is longer. When the end face C is on the discharge side from the discharge side end face A of the outer periphery 3 part of the impeller 6, the oblique flow collides with the cylindrical part and the pressure loss increases.

これにより、ブレード１での発生渦のみでなく、吐出部でのベルマウス８との衝突渦も低減することができ、発生騒音を抑えることができる。   Thereby, not only the generated vortex in the blade 1 but also the collision vortex with the bell mouth 8 in the discharge portion can be reduced, and the generated noise can be suppressed.

（実施の形態４）
図５は本発明の実施の形態４における軸流型羽根車の側断面と平面を示す図である。図５（ａ）は本発明の実施の形態４における軸流型羽根車の平面図を示し、図５（ｂ）は同羽根車の側面断面図を示す。 (Embodiment 4)
FIG. 5 is a view showing a side section and a plane of an axial-flow impeller according to Embodiment 4 of the present invention. Fig.5 (a) shows the top view of the axial flow type impeller in Embodiment 4 of this invention, FIG.5 (b) shows the side sectional drawing of the same impeller.

なお、実施の形態１乃至３のいずれかと同一部分については同一番号を付し、詳細な説明を省略する。   The same parts as those in any of Embodiments 1 to 3 are denoted by the same reference numerals, and detailed description thereof is omitted.

図５に示すように、吸い込み側に熱交換器などの空気抵抗体を有する場合、空気の流れは、ブレード１の入口部２から周方向よりも、ややブレード１の外周３側へと流れる斜流となる。このとき、通常のブレードでは、最適な仕事を行わず、渦発生や動力発生が大きくなる。しかし、羽根車６を囲むベルマウス８は、曲率部９と円筒部１０を有し、曲率部９は対向する面である対面方向１１の中心断面では１／４円弧を形成し、対面方向１１と略直交し対向する面であるもう一つの対面方向１２の中心断面では、１／４から１／８の範囲の円弧となっているので、本体の一方の寸法を大きくすることなく、高性能を発揮することができる。性能上、吸い込み空気抵抗は、曲率半径を１／８円弧以下の小さいものとすると、羽根車６外周３とベルマウス８の曲率部９の端面との間隔が狭くなり、その結果、空気抵抗が大きくなり、１／４円弧以上の大きなものとしても損失が変化ない。１／４円弧以上では、空気抵抗による損失が同じだが、１／４以下の円弧に比べて寸法が大きくなるため、１／４から１／８の範囲の円弧が、吸い込み空気抵抗と寸法を小さくすることができる。   As shown in FIG. 5, when an air resistor such as a heat exchanger is provided on the suction side, the air flow is inclined from the inlet portion 2 of the blade 1 to the outer periphery 3 side of the blade 1 slightly in the circumferential direction. It becomes a flow. At this time, an ordinary blade does not perform optimum work, and vortex generation and power generation increase. However, the bell mouth 8 surrounding the impeller 6 has a curvature portion 9 and a cylindrical portion 10, and the curvature portion 9 forms a ¼ arc in the central cross section of the facing direction 11 which is a facing surface. In the center section of the other facing direction 12, which is a surface that is substantially orthogonal to and opposite to each other, the arc is in the range of ¼ to 高性能, so that the high performance can be achieved without increasing one dimension of the main body. Can be demonstrated. In terms of performance, if the radius of curvature of the suction air resistance is as small as 1/8 arc or less, the distance between the outer periphery 3 of the impeller 6 and the end face of the curvature portion 9 of the bell mouth 8 is narrowed, and as a result, the air resistance is reduced. The loss does not change even if it is larger than 1/4 arc. Above 1/4 arc, the loss due to air resistance is the same, but since the dimensions are larger than 1/4 arc, arcs in the range of 1/4 to 1/8 reduce the suction air resistance and dimensions. can do.

これにより、ブレード１での発生渦のみでなく、吐出部でのベルマウス８との衝突渦も低減することができ、発生騒音を抑えることができ、さらに本体の寸法を大きくすることがない。   Thereby, not only the generated vortex in the blade 1 but also the collision vortex with the bell mouth 8 in the discharge portion can be reduced, the generated noise can be suppressed, and the size of the main body is not increased.

（実施の形態５）
図６は本発明の実施の形態５における軸流型羽根車の断面図である。 (Embodiment 5)
FIG. 6 is a cross-sectional view of an axial-flow impeller in Embodiment 5 of the present invention.

なお、実施の形態１乃至４のいずれかと同一部分については同一番号を付し、詳細な説明を省略する。   The same parts as those in any of Embodiments 1 to 4 are denoted by the same reference numerals, and detailed description thereof is omitted.

図６に示すように、ベルマウス８と熱交換するための熱交換器１３とを長方体の本体１４に取り付け、前記本体１４の一方向の寸法ａは羽根車６の直径Ｄの８〜１５％としている。本体１４の寸法ａを８％以下の場合、吸い込み曲率の大きさが小さくなり吸い込み圧力損失が大きくなり、１５％以上にしても性能上の変化は少ない。   As shown in FIG. 6, a bell mouth 8 and a heat exchanger 13 for exchanging heat are attached to a rectangular main body 14, and a dimension a in one direction of the main body 14 is 8 to 8 of the diameter D of the impeller 6. 15%. When the dimension a of the main body 14 is 8% or less, the suction curvature is small and the suction pressure loss is large. Even if it is 15% or more, there is little change in performance.

これにより、ブレード１での発生渦のみでなく、吐出部でのベルマウス８との衝突渦も低減することができ、発生騒音を抑えることができ、さらに本体１４の寸法を大きくすることがない。   Thereby, not only the generated vortex in the blade 1 but also the collision vortex with the bell mouth 8 in the discharge portion can be reduced, the generated noise can be suppressed, and the size of the main body 14 is not increased. .

（実施の形態６）
図６は本発明の実施の形態６における軸流型羽根車の断面図である。 (Embodiment 6)
FIG. 6 is a cross-sectional view of an axial-flow impeller in Embodiment 6 of the present invention.

なお、実施の形態１乃至５のいずれかと同一部分については同一番号を付し、詳細な説明を省略する。   The same parts as those in any of Embodiments 1 to 5 are denoted by the same reference numerals, and detailed description thereof is omitted.

図６に示すように、羽根車６の吸込口に熱交換するための熱交換器１３を有し、羽根車との距離ｂは羽根車の直径の１０〜３０％である。熱交換器１３と羽根車６が羽根車の直径の１０％以下に接近していると熱交換器１３のフィンの後流の乱れの影響を羽根車が受けるので、騒音発生が大きくなり、３０％以上となると乱流の影響を受けないので、１０〜３０％の距離が最適であり、騒音に対する影響は小さい。   As shown in FIG. 6, it has the heat exchanger 13 for exchanging heat at the suction port of the impeller 6, and the distance b with the impeller is 10 to 30% of the diameter of the impeller. If the heat exchanger 13 and the impeller 6 are close to 10% or less of the diameter of the impeller, the impeller is affected by the turbulence of the wake of the fins of the heat exchanger 13, so that noise generation increases, and 30 Since the influence of turbulent flow will not be affected if the ratio is more than 10%, the distance of 10 to 30% is optimal and the influence on noise is small.

これにより、これにより、ブレード１での発生渦のみでなく、吐出部でのベルマウス８との衝突渦も低減することができ、発生騒音を抑えることができ、さらに本体１４の寸法を大きくすることがない。   Thereby, not only the generated vortex in the blade 1 but also the collision vortex with the bell mouth 8 in the discharge portion can be reduced, the generated noise can be suppressed, and the size of the main body 14 is increased. There is nothing.

本発明の軸流型羽根車は、ブレード発生騒音を低減し、機器に組み込んだ状態での騒音を低減することができ、本体も小さくできる軸流型羽根車を提供することができる。   The axial flow type impeller of the present invention can provide an axial flow type impeller that can reduce blade generation noise, can reduce noise in a state where the blade is incorporated in equipment, and can have a smaller main body.

本発明の実施の形態１の軸流型羽根車の側断面図Side sectional view of the axial flow type impeller of Embodiment 1 of the present invention 同実施の形態１の軸流型羽根車のブレード取付角を示す図The figure which shows the braid | blade mounting angle of the axial flow type impeller of Embodiment 1 同実施の形態２の軸流型羽根車の側断面図Side sectional view of the axial flow type impeller of the second embodiment 同実施の形態３の軸流型羽根車の側断面図Side sectional view of the axial flow type impeller of Embodiment 3 同実施の形態４の軸流型羽根車の側断面図と平面図を示す図The figure which shows the sectional side view and top view of an axial-flow-type impeller of Embodiment 4 同実施の形態５、６の軸流型羽根車の側断面図Side sectional view of axial flow type impeller of Embodiments 5 and 6 従来の軸流型ファンの正面図Front view of a conventional axial fan 従来の軸流型ファンのブレード断面図Cross section of a conventional axial fan blade

符号の説明Explanation of symbols

１ ブレード
２ 入口部
３ 外周
４ 後端
５ ハブ
６ 羽根車
７ 凸形状のそり
８ ベルマウス
９ 曲率部
１０ 円筒部
１１ 対面方向
１２ もう一つの対面方向
１３ 熱交換器
１４ 本体
１０１ ブレード
１０２ 前縁
１０３ 後縁 DESCRIPTION OF SYMBOLS 1 Blade 2 Entrance part 3 Outer periphery 4 Rear end 5 Hub 6 Impeller 7 Convex sled 8 Bell mouth 9 Curvature part 10 Cylindrical part 11 Face-to-face direction 12 Another face-to-face direction 13 Heat exchanger 14 Main body 101 Blade 102 Front edge 103 Trailing edge

Claims (7)

吸込側の障害物による半径方向の渦を防止する形状としたブレード曲率を有する軸流型羽根車。 An axial-flow impeller having a blade curvature that prevents a vortex in the radial direction due to an obstruction on the suction side. ブレードの側面の後端が羽根車外周からハブ側まで軸方向にみて順次吐出側にあり、かつブレードの取付角度が外周側ほど大きい羽根車を有する軸流型羽根車。 An axial-flow impeller having a rear end of a side surface of a blade on the discharge side as viewed in the axial direction from the outer periphery of the impeller to the hub side, and an impeller having a larger blade mounting angle toward the outer peripheral side. ブレードの側面の後端が羽根車外周からハブ側まで軸方向にみて順次吐出側にあり、かつブレードの半径方向断面が吸込側に滑らかな凸形状のそりを持つ請求項１記載の軸流型羽根車。 2. An axial flow mold according to claim 1, wherein the rear end of the side surface of the blade is on the discharge side sequentially from the outer periphery of the impeller to the hub side, and the blade has a smooth convex warpage on the suction side in the radial direction. Impeller. 羽根車を囲むベルマウスは曲率部と円筒部を有し、円筒部の吐出側端面と羽根車の外周部の吐出側端面とが側面断面で同じ軸方向位置にあることを特徴とした請求項１または２記載の軸流型羽根車。 The bell mouth surrounding the impeller has a curvature portion and a cylindrical portion, and the discharge side end surface of the cylindrical portion and the discharge side end surface of the outer peripheral portion of the impeller are at the same axial position in a side cross section. The axial flow type impeller according to 1 or 2. 羽根車を囲むベルマウスは曲率部と円筒部を有し、前記曲率部は対面方向は１／４円弧を形成し、もう一つの対面方向は、１／４から１／８の範囲の円弧となっていることを特徴とする請求項１乃至３のいずれかに記載の軸流型羽根車。 The bell mouth surrounding the impeller has a curvature portion and a cylindrical portion, and the curvature portion forms a 1/4 arc in the facing direction, and the other facing direction has an arc in the range of 1/4 to 1/8. The axial flow type impeller according to any one of claims 1 to 3, wherein ベルマウスと熱交換するための熱交換器とを長方体の本体に取り付け、前記本体の縦方向寸法は羽根車の直径の８〜１５％としたことを特徴とした請求項１乃至４のいずれかに記載の軸流型羽根車。 A heat exchanger for exchanging heat with a bell mouth is attached to a rectangular main body, and the vertical dimension of the main body is 8 to 15% of the diameter of the impeller. An axial flow type impeller according to any one of the above. 羽根車の吸込口に熱交換するための熱交換器を有し、羽根車との距離は羽根車の直径の１０〜３０％であることを特徴とした請求項１乃至５のいずれかに記載の軸流型羽根車。 6. A heat exchanger for exchanging heat at the suction port of the impeller, wherein the distance from the impeller is 10 to 30% of the diameter of the impeller. Axial flow type impeller.
JP2005146263A 2005-05-19 2005-05-19 Axial type impeller Expired - Fee Related JP5011657B2 (en)

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WO2010026986A1 (en) * 2008-09-02 2010-03-11 日本電産株式会社 Axial fan
JP2010236372A (en) * 2009-03-30 2010-10-21 Daikin Ind Ltd Axial blower, air conditioner, and ventilation fan
US8348593B2 (en) 2008-09-02 2013-01-08 Nidec Corporation Serial axial fan
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