JP2016160905A - Centrifugal fan - Google Patents

Centrifugal fan Download PDF

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Publication number
JP2016160905A
JP2016160905A JP2015043352A JP2015043352A JP2016160905A JP 2016160905 A JP2016160905 A JP 2016160905A JP 2015043352 A JP2015043352 A JP 2015043352A JP 2015043352 A JP2015043352 A JP 2015043352A JP 2016160905 A JP2016160905 A JP 2016160905A
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Prior art keywords
centrifugal fan
airflow
negative pressure
main plate
shroud
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JP2015043352A
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Inventor
明広 重田
Akihiro Shigeta
明広 重田
欣公 田積
Yoshitaka Tazumi
欣公 田積
遼 黒田
Ryo Kuroda
遼 黒田
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Panasonic Intellectual Property Management Co Ltd
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Panasonic Intellectual Property Management Co Ltd
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Priority to JP2015043352A priority Critical patent/JP2016160905A/en
Priority to CN201610124294.8A priority patent/CN105937500A/en
Publication of JP2016160905A publication Critical patent/JP2016160905A/en
Pending legal-status Critical Current

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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
    • F04D25/00—Pumping installations or systems
    • F04D25/02—Units comprising pumps and their driving means
    • F04D25/08—Units comprising pumps and their driving means the working fluid being air, e.g. for ventilation
    • F04D25/088—Ceiling fans
    • 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
    • F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
    • F04D29/281—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for fans or blowers
    • 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
    • F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
    • F04D29/30—Vanes
    • 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
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/4206—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for elastic fluid 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
    • F04D29/68—Combating cavitation, whirls, noise, vibration or the like; Balancing by influencing boundary layers
    • F04D29/681—Combating cavitation, whirls, noise, vibration or the like; Balancing by influencing boundary layers especially adapted for elastic fluid 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
    • F04D29/70—Suction grids; Strainers; Dust separation; Cleaning
    • F04D29/701—Suction grids; Strainers; Dust separation; Cleaning especially adapted for elastic fluid pumps
    • F04D29/703—Suction grids; Strainers; Dust separation; Cleaning especially adapted for elastic fluid pumps specially for fans, e.g. fan guards

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Air-Conditioning Room Units, And Self-Contained Units In General (AREA)

Abstract

PROBLEM TO BE SOLVED: To provide a centrifugal fan which reduces air blowing noise caused by peeling of an airflow on a negative pressure surface side of a blade and also which can suppress increase in fan power.SOLUTION: A centrifugal fan comprises: a main plate 12 whose center is a rotation center; a shroud 14 arranged opposing to the main plate 12; and a plurality of blades 13 disposed radially between the main plate 12 and the shroud 14. The blade 13 is formed by a positive pressure surface 13a which becomes a front surface with respect to the rotation direction, and a negative pressure surface 13b which becomes a rear surface with respect to the rotation direction. The negative pressure surface 13b includes: a first curve surface 13c extending from a front edge side; a discontinuous second curve surface 13d different from the first curve surface 13c, on the rear edge side of the negative pressure surface 13b; and a step part 13e formed at a boundary between the first curve surface 13c and the second curve surface 13d.SELECTED DRAWING: Figure 3

Description

本発明は、特に低騒音化に優れた遠心ファンに関するものである。   The present invention relates to a centrifugal fan particularly excellent in noise reduction.

従来から、天井吊下型や天井埋込型の空気調和装置においては、遠心ファンが多く用いられている。
一般に、この種の遠心ファンは、主板と、主板の外周に放射状に配設された複数のブレードと、主板の反対側に配置されブレードの相互間を結合するシュラウドとで構成され、モータで回転駆動されるものである。
このような遠心ファンにおいては、ブレードとシュラウドとの結合部の付近で、ブレードの負圧面に気流の剥離が発生するため騒音が大きくなるという問題があった。 Conventionally, centrifugal fans are often used in ceiling-suspended and ceiling-embedded air conditioners.
In general, this type of centrifugal fan is composed of a main plate, a plurality of blades arranged radially on the outer periphery of the main plate, and a shroud that is arranged on the opposite side of the main plate and connects the blades, and is rotated by a motor. It is driven.
In such a centrifugal fan, there is a problem in that noise is increased because air current separation occurs on the suction surface of the blade in the vicinity of the joint between the blade and the shroud.

このような問題を解決する技術として、従来、例えば、ブレードを前縁側が最大肉厚を有する翼形状に形成するとともに、ブレードの外周部の負圧面に略半翼形状の突起を形成し、この突起を、突起の断面において最大翼厚点が突起の中央より後縁側に近い位置に配置するとともに、シュラウドの側からハブの側の方向に形成するようにした技術が開示されている（例えば、特許文献１を参照。）。   As a technique for solving such a problem, conventionally, for example, the blade is formed into a blade shape having a maximum thickness on the leading edge side, and a substantially half blade-shaped protrusion is formed on the suction surface of the outer peripheral portion of the blade. A technique is disclosed in which the protrusion is disposed at a position where the maximum blade thickness point is closer to the trailing edge side than the center of the protrusion in the cross section of the protrusion and is formed in the direction from the shroud side to the hub side (for example, (See Patent Document 1).

特許第４８７３８６５号公報Japanese Patent No. 4873865

しかしながら、前記従来の技術においては、ブレードの負圧面側の出口幅が正圧面側の出口幅と同じ場合に比べて、遠心ファンの吹出部の開口面積が狭くなるので、同一風量を送風する場合に遠心ファンの回転数を上げることとなり、ファン動力の増加によってシステム性能が悪化するという問題を有している。
本発明は、前記した点に鑑みてなされたものであり、ブレードの負圧面側の気流の剥離による送風騒音を低減するとともに、ファン動力の増加を抑制することのできる遠心ファンを提供することを目的とするものである。 However, in the conventional technique, the opening area of the blowout portion of the centrifugal fan is narrower than when the outlet width on the suction surface side of the blade is the same as the outlet width on the pressure surface side, so that the same air volume is blown In addition, the rotational speed of the centrifugal fan is increased, and there is a problem that system performance deteriorates due to an increase in fan power.
The present invention has been made in view of the foregoing points, and provides a centrifugal fan that can reduce blowing noise due to airflow separation on the suction surface side of a blade and can suppress an increase in fan power. It is the purpose.

前記目的を達成するため、本発明は、中心を回転中心とする主板と、前記主板と対向して配置されたシュラウドと、前記主板と前記シュラウドとの間に放射状に配設した複数のブレードと、を備えてなる遠心ファンにおいて、前記ブレードは、回転方向に対して前面となる正圧面と、回転方向に対して後面となる負圧面とから形成され、前記負圧面は前縁側から延びる第１曲面と、前記負圧面の後縁側に、前記第１曲面とは異なる不連続な第２曲面と、前記第１曲面と前記第２曲面との境界に形成される段差部とを備えていることを特徴とする。
この構成によれば、気流が段差部を通過する際に、負圧を発生させて、ブレードの負圧面に再付着することで、気流の剥離を抑制することができ、遠心ファン出口の開口面積が狭くなることなく、気流の剥離による送風騒音を低減することができる。 To achieve the above object, the present invention comprises a main plate having a center of rotation, a shroud disposed opposite to the main plate, and a plurality of blades radially disposed between the main plate and the shroud. The blade is formed of a pressure surface that is a front surface with respect to the rotation direction and a suction surface that is a rear surface with respect to the rotation direction, and the suction surface extends from the front edge side. Provided with a curved surface, a discontinuous second curved surface different from the first curved surface, and a step formed at the boundary between the first curved surface and the second curved surface on the trailing edge side of the suction surface. It is characterized by.
According to this configuration, when the airflow passes through the stepped portion, negative pressure is generated and reattached to the negative pressure surface of the blade, so that separation of the airflow can be suppressed and the opening area of the centrifugal fan outlet The air blowing noise due to the separation of the airflow can be reduced without narrowing.

また、前記構成において、前記段差部は、前記負圧面に複数形成されていることを特徴とする。
この構成によれば、空調負荷が低く、ファンの回転速度が遅くて気流の速度が遅い場合でも、遠心ファン出口の開口面積が狭くなることなく、気流の剥離による送風騒音を低減することができる。 Moreover, the said structure WHEREIN: The said level | step-difference part is formed in multiple numbers on the said negative pressure surface, It is characterized by the above-mentioned.
According to this configuration, even when the air-conditioning load is low, the fan rotation speed is slow, and the airflow speed is slow, the blowing noise due to airflow separation can be reduced without reducing the opening area of the centrifugal fan outlet. .

また、前記構成において、前記段差部は、前記シュラウドの側から前記主板の側に向かう中途部まで形成されていることを特徴とする。
この構成によれば、空調負荷が高く、ファンの回転速度が速くて気流の速度が速い場合でも、遠心ファン出口の開口面積が狭くなることなく、気流の剥離による送風騒音をより低減することができる。 Moreover, the said structure WHEREIN: The said level | step-difference part is formed from the said shroud side to the midway part which goes to the said main plate side, It is characterized by the above-mentioned.
According to this configuration, even when the air conditioning load is high, the fan rotation speed is high, and the airflow speed is high, the blowing noise due to the separation of the airflow can be further reduced without reducing the opening area of the centrifugal fan outlet. it can.

本発明によれば、気流の剥離を抑制することができ、遠心ファン出口の開口面積が狭くなることなく、気流の剥離による送風騒音を低減することができるので、ブレードの負圧面側の気流の剥離による送風騒音を低減しつつ、ファン動力を増加させない遠心ファンを提供できる。   According to the present invention, airflow separation can be suppressed, and air blowing noise due to airflow separation can be reduced without reducing the opening area of the centrifugal fan outlet, so the airflow on the suction surface side of the blade can be reduced. A centrifugal fan that does not increase fan power while reducing blowing noise due to peeling can be provided.

本発明の第１実施形態における遠心ファンを搭載した空気調和装置を示す断面図である。It is sectional drawing which shows the air conditioning apparatus carrying the centrifugal fan in 1st Embodiment of this invention. 第１実施形態における遠心ファンを示す斜視図である。It is a perspective view which shows the centrifugal fan in 1st Embodiment. 第１実施形態における遠心ファンのブレードを示す断面図である。It is sectional drawing which shows the blade of the centrifugal fan in 1st Embodiment. 第１実施形態におけるオリフィスおよび遠心ファン内を通過する気流の流れを示す説明図である。It is explanatory drawing which shows the flow of the airflow which passes the inside of the orifice and centrifugal fan in 1st Embodiment. 本発明の遠心ファンと従来の遠心ファンとの風量と騒音との関係を示すグラフである。It is a graph which shows the relationship between the air volume and noise of the centrifugal fan of this invention and the conventional centrifugal fan. 本発明の第２実施形態における遠心ファンのブレードを示す断面図である。It is sectional drawing which shows the blade of the centrifugal fan in 2nd Embodiment of this invention. 本発明の第３実施形態におけるオリフィスおよび遠心ファンを示す部分断面図である。It is a fragmentary sectional view showing an orifice and a centrifugal fan in a 3rd embodiment of the present invention.

以下、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。なお、この実施形態によって本発明が限定されるものではない。   Hereinafter, embodiments of the present invention will be described with reference to the drawings. In addition, this invention is not limited by this embodiment.

（第１実施形態）
図１は本発明の第１実施形態における遠心ファンを搭載した空気調和装置を示す断面図である。
図１に示すように、空気調和装置１は、天井５０に形成された凹部５１に埋め込まれ、凹部５１の上面である取り付け壁５２に、ボルト５３およびナット５４によって、吊り下げられている。 (First embodiment)
FIG. 1 is a cross-sectional view showing an air conditioner equipped with a centrifugal fan according to a first embodiment of the present invention.
As shown in FIG. 1, the air conditioner 1 is embedded in a recess 51 formed in a ceiling 50, and is suspended by a bolt 53 and a nut 54 on a mounting wall 52 that is an upper surface of the recess 51.

空気調和装置１は、一面が開口した直方体の筐体２と、筐体２の上面３に固定されたモータ取り付け用部材４と、モータ取り付け用部材４に取り付けられたモータ５と、モータ５の回転軸に取り付けられた遠心ファン６と、筐体２の開口部中央にグリル７ａおよびフィルター７ｂから構成されている空気の吸込口７と、吸込口７の周囲に形成された吹出口８と、吹出口８から流出する気流の方向を変更するためのフラップ９と、吸込口７から吸い込まれた空気を遠心ファン６に導くため、略ラッパ状に除々に縮径するオリフィス１０と、遠心ファン６の周囲に配設された、熱交換器１１とを備えている。   The air conditioner 1 includes a rectangular parallelepiped housing 2 whose one surface is open, a motor attachment member 4 fixed to the upper surface 3 of the housing 2, a motor 5 attached to the motor attachment member 4, A centrifugal fan 6 attached to the rotary shaft, an air inlet 7 composed of a grill 7a and a filter 7b at the center of the opening of the housing 2, and an outlet 8 formed around the inlet 7; A flap 9 for changing the direction of the airflow flowing out from the air outlet 8, an orifice 10 that gradually decreases in diameter in a substantially trumpet shape to guide the air sucked from the air inlet 7 to the centrifugal fan 6, and the centrifugal fan 6 , And a heat exchanger 11 disposed around the periphery.

図２は本発明の第１実施形態における遠心ファン６を示す斜視図である。
図２に示すように、遠心ファン６は、主板１２と、主板１２の外周付近に放射状に配設された複数のブレード１３と、主板１２の反対側に配置されブレード１３の相互間を結合するシュラウド１４と、から構成されている。
主板１２は、外周の平坦部１２ａと、中央のすり鉢上に盛り上がった第１凸部１２ｂと、第１凸部１２ｂの上部を覆うように形成された第２凸部１２ｃと、から構成されている。 FIG. 2 is a perspective view showing the centrifugal fan 6 in the first embodiment of the present invention.
As shown in FIG. 2, the centrifugal fan 6 is connected to the main plate 12, a plurality of blades 13 arranged radially near the outer periphery of the main plate 12, and the blades 13 arranged on the opposite side of the main plate 12. And a shroud 14.
The main plate 12 is composed of an outer peripheral flat portion 12a, a first convex portion 12b raised on a central mortar, and a second convex portion 12c formed so as to cover the upper portion of the first convex portion 12b. Yes.

第１凸部１２ｂの内側は空洞になっており、第１凸部１２ｂの内側には、モータ５が配設されている。第１凸部１２ｂの上部には、モータ５の冷却に必要な気流が流れるように、複数の孔１２ｄが形成されている。また、第２凸部１２ｃの略中心には、モータ５の回転軸が固定されるボス１２ｅが形成されている。   The inside of the 1st convex part 12b is a cavity, and the motor 5 is arrange | positioned inside the 1st convex part 12b. A plurality of holes 12d are formed in the upper portion of the first convex portion 12b so that an air flow necessary for cooling the motor 5 flows. A boss 12e to which the rotation shaft of the motor 5 is fixed is formed at the approximate center of the second convex portion 12c.

シュラウド１４は、シュラウド端縁１４ａとシュラウド外形１４ｂと、シュラウド端縁１４ａとシュラウド外形１４ｂとをつなぐシュラウド曲面１４ｃと、から構成されている。シュラウド端縁１４ａの内径は、オリフィス１０の最も内径の小さい端縁より大きく、遠心ファン６はシュラウド端縁１４ａが、オリフィス１０にオーバーラップするよう配設されている。   The shroud 14 includes a shroud end edge 14a and a shroud outer shape 14b, and a shroud curved surface 14c that connects the shroud end edge 14a and the shroud outer shape 14b. The inner diameter of the shroud edge 14 a is larger than the edge having the smallest inner diameter of the orifice 10, and the centrifugal fan 6 is arranged so that the shroud edge 14 a overlaps the orifice 10.

次に、ブレード１３の形状について説明する。
図３は本発明の第１実施形態における遠心ファン６のブレード１３を示す断面図である。
図３に示すように、ブレード１３は、遠心ファン６の回転方向に対して前面となる正圧面１３ａと、回転方向に対して後面となる負圧面１３ｂとから形成されている。負圧面１３ｂは、遠心ファン６の中心に近い前縁側から延びる第１曲面１３ｃと、第１曲面１３ｃとは異なる曲面で、遠心ファン６の外周に近い後縁側の第２曲面１３ｄと、第１曲面１３ｃと第２曲面１３ｄとの境界部分に形成された段差部１３ｅと、を備えている。 Next, the shape of the blade 13 will be described.
FIG. 3 is a sectional view showing the blade 13 of the centrifugal fan 6 in the first embodiment of the present invention.
As shown in FIG. 3, the blade 13 is formed of a positive pressure surface 13 a that is the front surface with respect to the rotation direction of the centrifugal fan 6 and a negative pressure surface 13 b that is the rear surface with respect to the rotation direction. The negative pressure surface 13b is a first curved surface 13c extending from the front edge side near the center of the centrifugal fan 6, a curved surface different from the first curved surface 13c, a second curved surface 13d on the rear edge side near the outer periphery of the centrifugal fan 6, and a first And a step 13e formed at the boundary between the curved surface 13c and the second curved surface 13d.

仮想線１５は、従来の遠心ファンのブレード位置であり、各ブレード１３の間の距離が狭くならないように、第２曲面１３ｄは、従来の遠心ファンのブレード位置よりも内側に凹む形で形成される。
また、ブレード１３は軽量化のため中空で構成されている。段差部１３ｅの位置は、負圧面１３ｂの壁近傍を流れる気流が失速して剥離する点（剥離点）の直前がよく、段差部１３ｅの高さｈ１を代表長さとしたレイノルズ数で６０００程度（一般的な空気調和装置１の遠心ファン６の気流の速度程度）では、剥離点から４ｈ１から６ｈ１手前が望ましい。また、高さｈ１は１ｍｍから２ｍｍ程度が望ましい。 The imaginary line 15 is the blade position of the conventional centrifugal fan, and the second curved surface 13d is formed in a shape recessed inward from the blade position of the conventional centrifugal fan so that the distance between the blades 13 is not narrowed. The
The blade 13 is hollow to reduce the weight. The position of the stepped portion 13e is preferably immediately before the point where the airflow flowing in the vicinity of the negative pressure surface 13b stalls and peels off (peeling point), and the Reynolds number with the height h1 of the stepped portion 13e as the representative length is about 6000 ( In the general air conditioner 1, the speed of the air flow of the centrifugal fan 6 is preferably 4h1 to 6h1 before the separation point. The height h1 is preferably about 1 mm to 2 mm.

次に、本実施形態における遠心ファンの作用について説明する。
まず、空気調和装置１の動作について説明する。
図１において、遠心ファン６がＣ方向に回転すると、気流Ｗ１はグリル７ａおよびフィルター７ｂから空気調和装置１に流入し、オリフィス１０で整流されて遠心ファン６に導かれる。そして、遠心ファン６の外周より放射状に吹き出されて、熱交換器１１を通過する際に所定の温度に冷却または加熱され、吹出口８からフラップ９によって所定の方向に向けられて流出される。 Next, the operation of the centrifugal fan in this embodiment will be described.
First, the operation of the air conditioner 1 will be described.
In FIG. 1, when the centrifugal fan 6 rotates in the C direction, the airflow W1 flows into the air conditioner 1 from the grill 7a and the filter 7b, is rectified by the orifice 10, and is guided to the centrifugal fan 6. And it blows off radially from the outer periphery of the centrifugal fan 6, is cooled or heated to a predetermined temperature when passing through the heat exchanger 11, and flows out from the outlet 8 in a predetermined direction by the flap 9.

気流Ｗ１の一部は、熱交換器１１を通過せずに、モータ５の熱を奪う冷却気流Ｗ２と、オリフィス１０の外周からショートサーキットして再び遠心ファン６に流入する循環気流Ｗ３となって、遠心ファン６内で気流Ｗ１と合流する。   A part of the air flow W1 becomes a cooling air flow W2 that takes the heat of the motor 5 without passing through the heat exchanger 11, and a circulation air flow W3 that short-circuits from the outer periphery of the orifice 10 and flows into the centrifugal fan 6 again. In the centrifugal fan 6, the airflow W1 is merged.

次に、遠心ファン６内を通過する気流Ｗ１の流れについて説明する。
図４は、オリフィス１０および遠心ファン６内を通過する気流Ｗ１の流れを示す説明図である。
図４に示すように、気流Ｗ１はシュラウド１４に近い気流Ｗ１ａと、シュラウド１４と主板１２との略中央を通る気流Ｗ１ｂと、主板１２に近い気流Ｗ１ｃとがあり、気流の速度はＷ１ａ＜Ｗ１ｂ＜Ｗ１ｃとなっている。
また、図３に示すように、負圧面１３ｂでは、遠心ファン６がＢ方向に回転することから気流Ｗ１が離れようとするために、正圧面１３ａを流れる気流Ｗ１に比べて剥離が起こりやすい。特に、負圧面１３ｂの後縁側では、気流Ｗ１の境界層が発達することによる壁面近傍での失速が起こりやすくなる。 Next, the flow of the airflow W1 that passes through the centrifugal fan 6 will be described.
FIG. 4 is an explanatory diagram showing the flow of the airflow W1 passing through the orifice 10 and the centrifugal fan 6. As shown in FIG.
As shown in FIG. 4, the airflow W1 includes an airflow W1a close to the shroud 14, an airflow W1b passing through the approximate center of the shroud 14 and the main plate 12, and an airflow W1c close to the main plate 12, and the velocity of the airflow is W1a <W1b. <W1c.
Also, as shown in FIG. 3, the negative pressure surface 13b tends to separate from the air flow W1 flowing on the positive pressure surface 13a because the air flow W1 tends to be separated because the centrifugal fan 6 rotates in the B direction. In particular, on the trailing edge side of the negative pressure surface 13b, a stall near the wall surface is likely to occur due to the development of the boundary layer of the air flow W1.

本実施形態においては、負圧面１３ｂの後縁側に段差部１３ｅを設けることで、気流Ｗ１の境界層が発達する前に剥離するとともに、段差部１３ｅ近傍で循環渦が発生することによって負圧を発生し、段差部１３ｅで剥離した気流Ｗ１を第２曲面１３ｄに再付着させるよう気流Ｗ１を誘引することが可能となる。
これにより、負圧面１３ｂでの気流Ｗ１の境界層の発達を防止することとなり、剥離を抑制することとなる。よって、遠心ファン出口の開口面積が狭くなることなく、気流の剥離による送風騒音を低減することができる。 In the present embodiment, by providing the step portion 13e on the trailing edge side of the negative pressure surface 13b, separation occurs before the boundary layer of the air flow W1 develops, and negative pressure is generated by generating a circulating vortex near the step portion 13e. It is possible to attract the air flow W1 so that the air flow W1 generated and separated at the step portion 13e is reattached to the second curved surface 13d.
Thereby, the development of the boundary layer of the air flow W1 on the suction surface 13b is prevented, and the peeling is suppressed. Therefore, the blowing noise due to the separation of the airflow can be reduced without reducing the opening area of the centrifugal fan outlet.

図５は、本発明の段差部を設けた遠心ファンと、従来の段差部を設けない遠心ファンとをそれぞれ動作させた場合における風量と騒音との関係を示すグラフである。
図５示すように、同じ風量で動作させた場合、本発明の遠心ファンは、従来の遠心ファンに比べて、騒音を低減させることができることがわかる。 FIG. 5 is a graph showing the relationship between the air volume and noise when a centrifugal fan provided with a step portion according to the present invention and a conventional centrifugal fan not provided with a step portion are operated.
As shown in FIG. 5, when operated with the same air volume, it can be seen that the centrifugal fan of the present invention can reduce noise compared to a conventional centrifugal fan.

以上述べたように、本実施形態においては、負圧面１３ｂの後縁側に段差部１３ｅを設けるようにしたので、負圧面１３ｂでの気流Ｗ１の境界層の発達を防止することができ、剥離を抑制することができる。そのため、遠心ファン６の出口の開口面積が狭くなることなく、気流の剥離による送風騒音を低減することができる。
その結果、ブレード１３の負圧面１３ｂ側の気流の剥離による送風騒音を低減しつつ、ファン動力を増加させない遠心ファン６を提供できる。 As described above, in this embodiment, since the step portion 13e is provided on the trailing edge side of the suction surface 13b, the development of the boundary layer of the air flow W1 on the suction surface 13b can be prevented, and the separation is performed. Can be suppressed. Therefore, the blowing noise due to the separation of the airflow can be reduced without reducing the opening area of the outlet of the centrifugal fan 6.
As a result, it is possible to provide the centrifugal fan 6 that does not increase the fan power while reducing the blowing noise due to the separation of the airflow on the suction surface 13b side of the blade 13.

なお、本実施形態においては、段差部１３ｅの高さｈ１を一定にしているが、気流Ｗ１の速度によって高さｈ１を変える（例えば、速度が速いほど高さｈ１を低くする）ようにしてもよい。このように構成することで、より剥離を抑制することができ、ブレード１３の負圧面１３ｂ側の気流の剥離による送風騒音を低減しつつ、ファン動力を増加させない遠心ファン６を提供できる。   In the present embodiment, the height h1 of the stepped portion 13e is constant, but the height h1 may be changed according to the velocity of the airflow W1 (for example, the height h1 is decreased as the velocity increases). Good. By configuring in this way, it is possible to further suppress the separation, and it is possible to provide the centrifugal fan 6 that does not increase the fan power while reducing the blowing noise due to the separation of the air flow on the suction surface 13b side of the blade 13.

また、本実施形態においては、負圧面１３ｂの最後縁からの段差部１３ｅの位置を一定にしているが、気流Ｗ１の速度によって位置を変える（例えば、速度が速いほど後縁側にする）ようにしてもよい。このように構成することで、さらに剥離を抑制することとなり、ブレード１３の負圧面１３ｂ側の気流の剥離による送風騒音を低減しつつ、ファン動力を増加させない遠心ファン６を提供できる。   In the present embodiment, the position of the stepped portion 13e from the last edge of the negative pressure surface 13b is constant, but the position is changed according to the velocity of the air flow W1 (for example, the higher the velocity, the closer to the trailing edge). May be. With such a configuration, the centrifugal fan 6 can be provided that further suppresses the separation, reduces the blowing noise due to the separation of the air flow on the negative pressure surface 13b side of the blade 13, and does not increase the fan power.

（第２実施形態）
次に、本発明の第２実施形態について説明する。
図６は、本発明の第２実施形態における遠心ファン６のブレード１３を示す断面図である。なお、前記第１実施形態と同一部分または相当する部分には同一符号を付し、その説明を省略する。 (Second Embodiment)
Next, a second embodiment of the present invention will be described.
FIG. 6 is a cross-sectional view showing the blade 13 of the centrifugal fan 6 in the second embodiment of the present invention. In addition, the same code | symbol is attached | subjected to the part which is the same as the said 1st Embodiment, or an equivalent part, and the description is abbreviate | omitted.

図６に示すように、負圧面１３ｂは、第１曲面１３ｃと、第２曲面１３ｄと、第１曲面１３ｃと第２曲面１３ｄとの境界部分に形成された第１段差部１３ｇと、第１曲面１３ｃおよび第２曲面１３ｃとは異なる曲面で、第２曲面１３ｃよりも遠心ファン６の外周に近い後縁側の第３曲面１３ｆと、第２曲面１３ｄと第２曲面１３ｆとの境界部分に形成された第２段差部１３ｈとを備えている。   As shown in FIG. 6, the negative pressure surface 13b includes a first curved surface 13c, a second curved surface 13d, a first step portion 13g formed at a boundary portion between the first curved surface 13c and the second curved surface 13d, and a first The curved surface is different from the curved surface 13c and the second curved surface 13c, and is formed at the boundary between the third curved surface 13f on the trailing edge side closer to the outer periphery of the centrifugal fan 6 than the second curved surface 13c, and the boundary between the second curved surface 13d and the second curved surface 13f. Second stepped portion 13h.

第１段差部１３ｇと第２段差部１３ｈとの位置は、負圧面１３ｂの壁近傍を流れる気流が失速して剥離する点（剥離点）の直前がよく、第１段差部１３ｇと第２段差部１３ｈの高さｈ２、ｈ３を代表長さとしたレイノルズ数で６０００程度（一般的な空気調和装置１の遠心ファン６の流速程度）では、剥離点から４ｈ２から６ｈ２および４ｈ３から６ｈ３手前が望ましい。また、高さｈ２およびｈ３はいずれも１ｍｍから２ｍｍ程度が望ましく、高さｈ２およびｈ３は必ずしも同じ高さでなくてもよい。   The positions of the first step portion 13g and the second step portion 13h are preferably just before the point (peeling point) where the airflow flowing in the vicinity of the negative pressure surface 13b stalls and peels off, and the first step portion 13g and the second step portion 13h. When the Reynolds number is about 6000 with the heights h2 and h3 of the portion 13h as representative lengths (about the flow rate of the centrifugal fan 6 of the general air conditioner 1), 4h2 to 6h2 and 4h3 to 6h3 before the separation point are desirable. The heights h2 and h3 are preferably about 1 mm to 2 mm, and the heights h2 and h3 are not necessarily the same height.

次に、本実施形態の作用について説明する。
本実施形態においては、図５に示すように、負圧面１３ｂでは、遠心ファン６がＢ方向に回転することから気流Ｗ１が離れようとするために、正圧面１３ａを流れる気流Ｗ１に比べて剥離が起こりやすい。特に、負圧面１３ｂの後縁側で気流Ｗ１の境界層が発達することによる壁面近傍での失速が起こりやすくなる。さらに、遠心ファン６の回転が遅く、気流の速度が比較的遅い場合には、気流の剥離点が前縁側で起こりやすくなる。 Next, the operation of this embodiment will be described.
In this embodiment, as shown in FIG. 5, the negative pressure surface 13b is separated from the air flow W1 flowing through the positive pressure surface 13a because the air flow W1 tends to be separated because the centrifugal fan 6 rotates in the B direction. Is likely to occur. In particular, the stall near the wall surface is likely to occur due to the development of the boundary layer of the airflow W1 on the trailing edge side of the suction surface 13b. Further, when the rotation of the centrifugal fan 6 is slow and the speed of the airflow is relatively slow, the separation point of the airflow tends to occur on the leading edge side.

そのため、負圧面１３ｂの後縁側に第２段差部１３ｈを設けることで、第２曲面１３ｄで再び気流Ｗ１の境界層が発達する前に剥離するとともに、第２段差部１３ｈ近傍で循環渦が発生することによって負圧を発生し、第２段差部１３ｈで剥離した気流Ｗ１を第３曲面１３ｆに再付着させるよう気流Ｗ１を誘引することになる。
これにより、負圧面１３ｂでの気流Ｗ１の境界層の発達を防止することとなり、剥離を抑制することとなる。よって、遠心ファン出口の開口面積が狭くなることなく、気流の剥離による送風騒音を低減することができる。 Therefore, by providing the second step portion 13h on the trailing edge side of the negative pressure surface 13b, the second curved surface 13d peels off before the boundary layer of the air flow W1 develops again, and a circulating vortex is generated in the vicinity of the second step portion 13h. As a result, a negative pressure is generated, and the air flow W1 is attracted so that the air flow W1 separated at the second step portion 13h is reattached to the third curved surface 13f.
Thereby, the development of the boundary layer of the air flow W1 on the suction surface 13b is prevented, and the peeling is suppressed. Therefore, the blowing noise due to the separation of the airflow can be reduced without reducing the opening area of the centrifugal fan outlet.

以上述べたように、本実施形態においては、負圧面１３ｂの後縁側に第１段差部１３ｇおよび第２段差部１３ｈを設けることにより、遠心ファン６の回転が遅く、気流の速度が比較的遅い場合でも、負圧面１３ｂでの気流Ｗ１の境界層の発達を防止することとなり、剥離を抑制することができる。そのため、空調負荷が低く、ファンの回転速度が遅くて気流の搬送速度が遅い場合でも、遠心ファン６出口の開口面積が狭くなることなく、気流の剥離による送風騒音を低減することができる。   As described above, in the present embodiment, by providing the first step portion 13g and the second step portion 13h on the trailing edge side of the negative pressure surface 13b, the rotation of the centrifugal fan 6 is slow and the speed of the airflow is relatively slow. Even in this case, the boundary layer of the air flow W1 on the suction surface 13b is prevented from developing, and separation can be suppressed. Therefore, even when the air-conditioning load is low, the fan rotation speed is low, and the airflow conveyance speed is low, the air blowing noise due to airflow separation can be reduced without reducing the opening area of the centrifugal fan 6 outlet.

その結果、空調負荷が低く、ファンの回転速度が遅くて気流の速度が遅い場合でも、ブレード１３の負圧面１３ｂ側の気流の剥離による送風騒音を低減しつつ、ファン動力を増加させない遠心ファン６を提供できる。   As a result, the centrifugal fan 6 does not increase the fan power while reducing the blowing noise due to the separation of the airflow on the negative pressure surface 13b side of the blade 13 even when the air conditioning load is low, the fan rotation speed is slow, and the airflow speed is slow. Can provide.

また、本実施形態においては、第１段差部１３ｇおよび第２段差部１３ｈの二段構成としているが、気流の速度がさらに遅く、負圧面１３ｂの最後縁で気流の剥離がある場合には、より段差部を増やして多段階構成とすることで、さらに剥離を抑制することができ、ブレード１３の負圧面１３ｂ側の気流の剥離による送風騒音を低減しつつ、ファン動力を増加させない遠心ファン６を提供できる。   In the present embodiment, the first step portion 13g and the second step portion 13h have a two-stage configuration, but when the airflow speed is further slower and there is airflow separation at the last edge of the negative pressure surface 13b, The centrifugal fan 6 that does not increase the fan power while reducing the blowing noise due to the separation of the airflow on the negative pressure surface 13b side of the blade 13 can be further suppressed by further increasing the stepped portion to form a multi-stage configuration. Can provide.

（第３実施形態）
次に、本発明の第３実施形態について説明する。
図７は、本発明の第３実施形態における遠心ファン６を示す部分断面図である。なお、前記第１実施形態および第２実施形態と同一部分または相当する部分には同一符号を付し、その説明を省略する。
図７に示すように、段差部１３ｅは、ブレードの高さ方向において、シュラウド１４の側から主板１２の側に向かう中途部まで設けられている。 (Third embodiment)
Next, a third embodiment of the present invention will be described.
FIG. 7 is a partial cross-sectional view showing the centrifugal fan 6 in the third embodiment of the present invention. In addition, the same code | symbol is attached | subjected to the part which is the same as that of the said 1st Embodiment and 2nd Embodiment, or an equivalent part, and the description is abbreviate | omitted.
As shown in FIG. 7, the stepped portion 13 e is provided from the shroud 14 side to the midway portion toward the main plate 12 side in the blade height direction.

本実施形態においても、前記各実施形態と同様に、図７において、負圧面１３ｂでは、気流Ｗ１が離れようとするために、正圧面１３ａを流れる気流Ｗ１に比べて剥離が起こりやすい。
特に、負圧面１３ｂの後縁側では、気流Ｗ１の境界層が発達することによる壁面近傍での失速が起こりやすくなる。さらに、シュラウド曲面１４ｃで気流方向の変化が大きく剥離が起こりやすい。反対に、主板１２の側は気流が流入するシュラウド端縁１４ａの側から比較的距離があり、第１凸部１２ｂから平坦部１２ａへの傾斜もシュラウド側面１４ｃの曲面と比べて緩やかであることから、気流の剥離が起こりにくい。さらに、遠心ファン６の回転が速く、気流の速度が比較的速い場合には、気流の剥離点が後縁側で起こりやすくなるとともに、剥離も起こりにくくなる。 Also in the present embodiment, as in each of the embodiments described above, in FIG. 7, the airflow W1 tends to be separated on the negative pressure surface 13b, and therefore, separation is more likely to occur than the airflow W1 flowing on the positive pressure surface 13a.
In particular, on the trailing edge side of the negative pressure surface 13b, a stall near the wall surface is likely to occur due to the development of the boundary layer of the air flow W1. Furthermore, the shroud curved surface 14c has a large change in the airflow direction and is likely to peel off. On the contrary, the main plate 12 side is relatively far from the shroud edge 14a side into which the airflow flows, and the inclination from the first convex portion 12b to the flat portion 12a is gentler than the curved surface of the shroud side surface 14c. As a result, airflow is unlikely to peel off. Furthermore, when the centrifugal fan 6 rotates fast and the airflow speed is relatively high, the airflow separation point is likely to occur on the trailing edge side, and separation is less likely to occur.

本実施形態においては、段差部１３ｅをシュラウド１４の側から主板１２の側に向かう中途部まで設けることで、気流の剥離が起こりやすいシュラウド１４に近い気流Ｗ１ａは、負圧面１３ｂで境界層が発達する前に剥離するとともに、段差部１３ｅ近傍で循環渦が発生することによって負圧を発生させる。これにより、段差部１３ｅで剥離した気流Ｗ１ａを第２曲面１３ｄに再付着させるよう気流Ｗ１ａを誘引するとともに、気流の比較的速い主板１２に近い気流Ｗ１ｃは、剥離が起こりにくいことから、段差部１３ｅでの剥離によって逆に気流を乱さないようにすることになる。
その結果、空調負荷が高く、ファンの回転速度が速くて気流の速度が速い場合でも、遠心ファン出口の開口面積が狭くなることなく、気流の剥離による送風騒音をより低減することができる。 In the present embodiment, the step portion 13e is provided from the shroud 14 side to the midway portion toward the main plate 12, so that the air flow W1a near the shroud 14 where the air flow is likely to be separated develops a boundary layer on the negative pressure surface 13b. In addition, the negative pressure is generated by peeling off and generating a circulating vortex in the vicinity of the stepped portion 13e. Accordingly, the airflow W1a is attracted so as to reattach the airflow W1a separated at the stepped portion 13e to the second curved surface 13d, and the airflow W1c close to the main plate 12 having a relatively fast airflow is unlikely to peel off. On the contrary, the air flow is not disturbed by the separation at 13e.
As a result, even when the air conditioning load is high, the fan rotation speed is high, and the airflow speed is high, the air blowing noise due to the separation of the airflow can be further reduced without reducing the opening area of the centrifugal fan outlet.

以上述べたように、本実施形態においては、段差部１３ｅはシュラウド１４の側から主板１２の側に向かって途中まで設けるようにしたので、遠心ファン６の回転が速く、気流の速度が比較的速い場合でも、負圧面１３ｂでの気流Ｗ１の境界層の発達を防止することとなり、剥離を抑制することができる。これにより、空調負荷が低く、ファンの回転速度が遅くて気流の速度が遅い場合でも、遠心ファン６出口の開口面積が狭くなることなく、気流の剥離による送風騒音を低減することができる。   As described above, in the present embodiment, the step portion 13e is provided partway from the shroud 14 side toward the main plate 12 side, so that the centrifugal fan 6 rotates fast and the air velocity is relatively high. Even in the case of high speed, the boundary layer of the air flow W1 on the suction surface 13b is prevented from developing, and separation can be suppressed. Thereby, even when the air conditioning load is low, the fan rotation speed is low, and the airflow speed is low, the air blowing noise due to the separation of the airflow can be reduced without reducing the opening area of the outlet of the centrifugal fan 6.

その結果、空調負荷が高く、ファンの回転速度が速くて気流の速度が速い場合でも、ブレード１３の負圧面１３ｂ側の気流の剥離による送風騒音を低減しつつ、ファン動力を増加させない遠心ファン６を提供できる。   As a result, even when the air conditioning load is high, the fan rotation speed is high, and the airflow speed is high, the centrifugal fan 6 does not increase the fan power while reducing the blowing noise due to the separation of the airflow on the negative pressure surface 13b side of the blade 13. Can provide.

以上のように、本発明に係る遠心ファンは、ブレードの負圧面側の気流の剥離による送風騒音を低減しつつ、ファン動力を増加させないもので、天井吊下型や天井埋込型の空気調和機や各種の換気装置などの用途に適用することができる。   As described above, the centrifugal fan according to the present invention reduces the blowing noise due to the separation of the airflow on the suction surface side of the blade, and does not increase the fan power. It can be applied to applications such as machines and various ventilation devices.

１２ 主板
１３ ブレード
１３ａ 正圧面
１３ｂ 負圧面
１３ｃ 第１曲面
１３ｄ 第２曲面
１３ｅ 段差部
１３ｆ 第３曲面
１３ｇ 第１段差部
１３ｈ 第２段差部
１４ シュラウド 12 main plate 13 blade 13a positive pressure surface 13b negative pressure surface 13c first curved surface 13d second curved surface 13e stepped portion 13f third curved surface 13g first stepped portion 13h second stepped portion 14 shroud

Claims (3)

中心を回転中心とする主板と、前記主板と対向して配置されたシュラウドと、前記主板と前記シュラウドとの間に放射状に配設した複数のブレードと、を備えてなる遠心ファンにおいて、
前記ブレードは、回転方向に対して前面となる正圧面と、回転方向に対して後面となる負圧面とから形成され、
前記負圧面は前縁側から延びる第１曲面と、前記負圧面の後縁側に、前記第１曲面とは異なる不連続な第２曲面と、前記第１曲面と前記第２曲面との境界に形成される段差部とを備えていることを特徴とする遠心ファン。 In a centrifugal fan comprising: a main plate whose center is a rotation center; a shroud disposed opposite to the main plate; and a plurality of blades arranged radially between the main plate and the shroud.
The blade is formed of a pressure surface that is the front surface with respect to the rotation direction and a suction surface that is the rear surface with respect to the rotation direction,
The suction surface is formed on a boundary between the first curved surface extending from the front edge side, a discontinuous second curved surface different from the first curved surface on the rear edge side of the suction surface, and the first curved surface and the second curved surface. A centrifugal fan comprising a stepped portion. 前記段差部は、前記負圧面に複数形成されていることを特徴とする請求項１に記載の遠心ファン。   The centrifugal fan according to claim 1, wherein a plurality of the stepped portions are formed on the suction surface. 前記段差部は、前記シュラウドの側から前記主板の側に向かう中途部まで形成されていることを特徴とする請求項１または請求項２に記載の遠心ファン。   3. The centrifugal fan according to claim 1, wherein the stepped portion is formed from the shroud side to a midway portion toward the main plate side. 4.
JP2015043352A 2015-03-05 2015-03-05 Centrifugal fan Pending JP2016160905A (en)

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