JP2017078386A - Centrifugal fan - Google Patents

Centrifugal fan Download PDF

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Publication number
JP2017078386A
JP2017078386A JP2015207700A JP2015207700A JP2017078386A JP 2017078386 A JP2017078386 A JP 2017078386A JP 2015207700 A JP2015207700 A JP 2015207700A JP 2015207700 A JP2015207700 A JP 2015207700A JP 2017078386 A JP2017078386 A JP 2017078386A
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Japan
Prior art keywords
shroud
main plate
blade
centrifugal fan
trailing edge
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JP2015207700A
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Japanese (ja)
Inventor
遼 黒田
Ryo Kuroda
遼 黒田
欣公 田積
Yoshitaka Tazumi
欣公 田積
小川　修
Osamu Ogawa
修 小川
昭宏 近藤
Akihiro Kondo
昭宏 近藤
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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 JP2015207700A priority Critical patent/JP2017078386A/en
Priority to CN201610766236.5A priority patent/CN106609763B/en
Publication of JP2017078386A publication Critical patent/JP2017078386A/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
    • 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
    • F04D29/661—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps
    • F04D29/663—Sound attenuation

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Abstract

PROBLEM TO BE SOLVED: To reduce turbulence noise by allowing a main stream passing between blades to blow without being disturbed.SOLUTION: A centrifugal fan 100 is formed of a main plate 101, a shroud 102, and blades 103. A warp 109 is curved such that a distance from a rotation axis becomes small toward the direction of the main plate 101 and the distance between the warp 109 and the rotation axis becomes large from a predetermined portion, and a blade trailing edge 112 is brought close to the rotation direction side as going from the shroud to the main plate so that an exit angle 114 on the shroud 102 side of the blade trailing edge 112 becomes smaller than an exit angle 114 on the main plate 101 side. With this, since the warp 109 scrapes out a main stream 180, the main stream 180 increases in flow rate and flows on the surface of the blade 103 along the blade trailing edge 112 direction, the flow speed in the shroud 102 direction is increased by a lift action of the blade 103, and further, the main stream 180 passing between the blades 103 is sucked in the direction of the shroud 102 side and is blown out, so that turbulence noise can be reduced.SELECTED DRAWING: Figure 1

Description

本発明は、空気調和機の室内機などに幅広く用いられる遠心ファンを備えた送風装置に関するものである。   The present invention relates to an air blower including a centrifugal fan that is widely used in indoor units of air conditioners.

従来、この種の遠心ファンは、主板とシュラウドと翼とで構成されており、翼の前縁側から後縁側の全体に亘って死水域低減空間を形成している（例えば、特許文献１参照）。   Conventionally, this type of centrifugal fan is composed of a main plate, a shroud, and a blade, and forms a dead water area reduction space from the front edge side to the rear edge side of the blade (see, for example, Patent Document 1). .

図６は特許文献１に記載された従来遠心ファンの斜視図、図７は特許文献１に記載された従来遠心ファンの翼前縁側の断面図、図８は特許文献１に記載された従来遠心ファンの翼後縁側の断面図を示すものである。   6 is a perspective view of a conventional centrifugal fan described in Patent Document 1, FIG. 7 is a cross-sectional view of a blade leading edge side of the conventional centrifugal fan described in Patent Document 1, and FIG. 8 is a conventional centrifugal fan described in Patent Document 1. FIG. 3 is a cross-sectional view of the fan blade trailing edge side.

図６に示すように、主板１０１と、主板１０１に対向配置され略中空円錐台形状のシュラウド１０２と、主板１０１とシュラウド１０２との間に配置される翼３０３と、を有する遠心ファン３００で構成されている。   As shown in FIG. 6, a centrifugal fan 300 including a main plate 101, a substantially hollow frustoconical shroud 102 disposed opposite to the main plate 101, and a blade 303 disposed between the main plate 101 and the shroud 102. Has been.

遠心ファン３００の回転軸方向の翼３０３のそり３０９を主板１０１側に至る途中部分から変形させることによって、翼３０３の正圧面側における翼３０３とシュラウド１０２とで構成されるコーナー角３１０が、図９に示す従来遠心ファンのように主板１０１からシュラウド１０２方向に立設された翼４０３とシュラウド１０２とで構成されるコーナー角よりも拡大し、翼３０３の前縁側から後縁側の全体に亘って死水域低減空間を形成している。   By deforming the sled 309 of the blade 303 in the direction of the rotation axis of the centrifugal fan 300 from the middle part to the main plate 101 side, a corner angle 310 constituted by the blade 303 and the shroud 102 on the pressure surface side of the blade 303 is shown in FIG. 9, which is larger than the corner angle formed by the blades 403 and the shroud 102 erected from the main plate 101 in the direction of the shroud 102 as in the conventional centrifugal fan shown in FIG. 9, and extends from the front edge side to the rear edge side of the blade 303. A dead water area reduction space is formed.

特開２００９−１７４５４１号公報JP 2009-174541 A

しかしながら、前記従来の構成では、所定の回転方向に遠心ファン３００を回転させると、翼３０３の昇圧作用によって、シュラウド１０２の小径側開口部から吸込まれた流体（以下、主流１８０と呼ぶ）を、翼全体に亘りコーナー角３１０を拡大にした翼３０３が主板１０１方向に向かって押しつけるため、遠心ファン３００から吹出される回転軸方向の主流分布が主板１０１側に偏る。その結果、シュラウド１０２の壁面近傍を通過する主流１８０の速度が低下するため、主板１０１側を通過する主流１８０とシュラウド１０２側を通過する主流１８０に速度差が生じるため、主流１８０に乱れ１８２が生じ、乱流騒音が増大する課題を有していた。   However, in the conventional configuration, when the centrifugal fan 300 is rotated in a predetermined rotation direction, the fluid sucked from the small-diameter side opening of the shroud 102 (hereinafter referred to as the main flow 180) by the pressure increasing action of the blades 303, Since the blade 303 with the corner angle 310 enlarged over the entire blade presses toward the main plate 101, the main flow distribution in the rotation axis direction blown out from the centrifugal fan 300 is biased toward the main plate 101. As a result, the speed of the main flow 180 passing through the vicinity of the wall surface of the shroud 102 decreases, and therefore a speed difference occurs between the main flow 180 passing through the main plate 101 side and the main flow 180 passing through the shroud 102 side. It has a problem of generating and increasing turbulent noise.

本発明は、前記従来の課題を解決するもので、シュラウド壁面の近傍を通過する流体の乱れを低減し、乱流騒音が低下する送風装置を提供することを目的とする。   The present invention solves the above-described conventional problems, and an object of the present invention is to provide a blower that reduces the turbulence of the fluid passing near the shroud wall surface and reduces the turbulent noise.

前記従来の課題を解決するために、本発明の遠心ファンは、主板と、シュラウドと、翼と、で構成されており、前記翼前縁における前記回転軸方向のそりが、前記シュラウドから前記主板方向に従って、前記そりと前記回転軸との距離が小さくなり、ある所定の箇所から前記そりと前記回転軸との距離が大きくなるように湾曲し、前記翼後縁において前記翼後縁がシュラウドから主板に向かうに従って、回転方向側に寄らしたものである。   In order to solve the conventional problem, the centrifugal fan of the present invention includes a main plate, a shroud, and a wing, and the warp in the rotational axis direction at the blade leading edge is from the shroud to the main plate. According to the direction, the distance between the sled and the rotating shaft is reduced, the curved portion is curved so that the distance between the sled and the rotating shaft is increased from a predetermined position, and the blade trailing edge is separated from the shroud at the blade trailing edge. As it goes to the main plate, it is closer to the direction of rotation.

これによって、所定の回転方向に前記遠心ファンを回転させると、前記シュラウドの小径側開口部から流体が吸込まれ（以下、主流と呼ぶ）、前記主流を前記そりが効率よく掻き出すことで、前記翼と前記翼の間を通過する主流の流量が増加し、前記翼の表面を翼後縁方向に沿うように流れ、更に前記翼の揚力作用によって前記シュラウド方向の流速が増大するため、前記翼と前記翼との間を通過する前記主流が前記シュラウド側方向にも引き寄せられながら吹出される。   Accordingly, when the centrifugal fan is rotated in a predetermined rotation direction, fluid is sucked from the small-diameter side opening of the shroud (hereinafter referred to as main flow), and the sled efficiently scrapes the main flow, whereby the blade The flow rate of the main stream passing between the blade and the blade increases, flows along the surface of the blade along the trailing edge direction of the blade, and further increases the flow velocity in the shroud direction by the lift action of the blade. The main flow passing between the blades is blown out while being drawn also in the shroud side direction.

また、本発明の送風装置は、前記翼後縁において、前記翼と前記主板とで構成される傾斜角が、前記翼と前記シュラウドとの接合部と前記翼と前記主板との接合部とを結ぶ直線と前記主板とで構成される傾斜角よりも大きくなるように湾曲部を有している。   Further, in the air blower of the present invention, at the trailing edge of the blade, an inclination angle formed by the blade and the main plate includes a joint portion between the blade and the shroud, and a joint portion between the blade and the main plate. A curved portion is provided so as to be larger than an inclination angle formed by the connecting straight line and the main plate.

これによって、前記遠心ファンの動作点が、高静圧・低風量の場合、前記遠心ファンから吹出される風速分布の偏りが前記主板側に一層集中する傾向となるが、前記主流を前記そりで効率よく掻き出すことで、前記翼と前記翼の間を通過する前記主流が前記翼後縁方向に向かってスムーズに流れ、前記湾曲部によって前記シュラウド側に前記主流が吸引されるため、乱れることなく吹出される。   As a result, when the operating point of the centrifugal fan is high static pressure and low air volume, the deviation of the wind speed distribution blown out from the centrifugal fan tends to concentrate more on the main plate side. By scraping efficiently, the main flow passing between the blades flows smoothly toward the trailing edge of the blade, and the main flow is sucked to the shroud side by the curved portion, so that it is not disturbed. Be blown out.

本発明の送風装置は、翼と翼との間を通過する主流がシュラウド側方向に引き寄せられながら吹出されるため、乱流騒音を低減することができる。   In the air blower of the present invention, since the main flow passing between the blades is blown out while being drawn in the shroud side direction, turbulent noise can be reduced.

本発明の実施の形態１に係る遠心ファンの一例を示す断面図Sectional drawing which shows an example of the centrifugal fan which concerns on Embodiment 1 of this invention 本発明の実施の形態１に係る遠心ファンの一例を示す翼断面図Blade cross-sectional view showing an example of a centrifugal fan according to Embodiment 1 of the present invention 本発明の実施の形態１に係る遠心ファンの一例を示す翼前縁側の断面図Sectional drawing of the blade leading edge side which shows an example of the centrifugal fan which concerns on Embodiment 1 of this invention 本発明の実施の形態１に係る遠心ファンの一例を示す翼後縁側の断面図Sectional drawing of the blade trailing edge side which shows an example of the centrifugal fan which concerns on Embodiment 1 of this invention 本発明の実施の形態２に係る遠心ファンの一例を示す翼後縁側の断面図Sectional drawing on the blade trailing edge side showing an example of a centrifugal fan according to Embodiment 2 of the present invention 従来技術１記載の遠心ファンの一例を示す斜視図The perspective view which shows an example of the centrifugal fan of the prior art 1 description 従来技術１記載の遠心ファンの一例を示す翼前縁側断面図Blade front edge side sectional view showing an example of a centrifugal fan described in Prior Art 1 従来技術１記載の遠心ファンの一例を示す翼後縁側断面図Blade rear edge side sectional view showing an example of the centrifugal fan described in the prior art 1 従来技術の遠心ファンの一例を示す翼後縁側断面図Blade rear edge side sectional view showing an example of a conventional centrifugal fan

第１の発明は、主板と、前記主板に対向配置される略中空円錐台形状のシュラウドと、
前記主板と前記シュラウドとの間に配置される翼と、前記翼前縁の前記回転軸方向のそりが、前記シュラウドから前記主板方向に従って、前記そりと前記回転軸との距離が小さくなり、ある所定の箇所から前記そりと前記回転軸との距離が大きくなるように湾曲し、前記翼後縁において前記翼後縁がシュラウドから主板に向かうに従って、回転方向側に寄らしたものである。 The first invention includes a main plate, a substantially hollow frustoconical shroud disposed opposite to the main plate,
The blade disposed between the main plate and the shroud, and the warp in the rotation axis direction of the blade leading edge, the distance between the sled and the rotation shaft is reduced according to the main plate direction from the shroud, The blade is curved so that the distance between the sled and the rotation shaft is increased from a predetermined position, and the blade trailing edge is shifted toward the rotation direction side from the shroud toward the main plate at the blade trailing edge.

所定の回転方向に前記遠心ファンを回転させると、前記翼の昇圧作用によって、前記シュラウド小径側開口部から流体が吸い込まれ（以下、主流と呼ぶ）、前記遠心ファンの回転軸方向の断面で見たときに、前記主流は前記シュラウドと前記主板で形成される略並行な２円弧の流体流路で曲げられ略遠心方向に吹出される。   When the centrifugal fan is rotated in a predetermined rotational direction, fluid is sucked from the shroud small-diameter side opening due to the pressure increasing action of the blades (hereinafter referred to as mainstream), and is seen in a section in the rotational axis direction of the centrifugal fan. When this occurs, the main flow is bent in a substantially parallel two-circular fluid flow path formed by the shroud and the main plate, and is blown out in a substantially centrifugal direction.

ここで、前記そりが前記主流を掻き出す作用によって、前記翼と前記翼の間を通過する主流の流量が増加する。更に、前記主流が前記翼の表面を翼後縁方向に向かって沿うように流れ、略遠心方向へ吹き出される（以下、吹出流と呼ぶ）。前記吹出流は前記翼の揚力作用によって前記シュラウド方向の流速が増大するため、前記シュラウド側方向に引き寄
せられながら略遠心方向へ前記遠心ファンの回転軸方向の風速分布に偏りが生じることなく、吹き出される。 Here, the flow rate of the main flow passing between the blades is increased by the action of the sled scraping the main flow. Further, the main flow flows along the surface of the blade toward the trailing edge of the blade and is blown out in a substantially centrifugal direction (hereinafter referred to as a blow-out flow). Since the flow velocity in the shroud direction is increased by the lifting action of the blades, the blowout flow is blown out without being biased in the wind speed distribution in the rotational axis direction of the centrifugal fan in the substantially centrifugal direction while being drawn in the shroud side direction. Is done.

これによって、前記シュラウド壁面近傍の流速が低下することなく吹出されるため、乱流騒音が低減できる。   As a result, the flow velocity in the vicinity of the shroud wall surface is blown out without decreasing, so that turbulent noise can be reduced.

第２の発明は、特に第１の発明の前記翼後縁を、前記翼と前記主板とで構成される傾斜角が、前記翼と前記シュラウドとの接合部と前記翼と前記主板との接合部とを結ぶ直線と前記主板とで構成される傾斜角よりも大きくなるように湾曲部を有している。   According to a second aspect of the present invention, in particular, the blade trailing edge of the first aspect of the invention has an inclination angle formed by the wing and the main plate, and a connection portion between the wing and the shroud and a connection between the wing and the main plate. A curved portion is provided so as to be larger than an inclination angle formed by a straight line connecting the portions and the main plate.

前記遠心ファンの動作点が、高静圧・低風量の場合、前記遠心ファンから吹出される風速分布の偏りが前記主板側に一層集中する傾向となるが、前記主流を前記そりで効率よく掻き出すことで、前記翼と前記翼の間を通過する前記主流が前記翼後縁方向に向かってスムーズに流れ、前記湾曲部によって、前記シュラウド側に前記主流が吸引され、乱れることなく吹出されるため、乱流騒音が低減できる。乱流騒音の低減によって、前記遠心ファンのコンパクト化と前記遠心ファンの壁面上の圧力変動を低減できるため、前記遠心ファンの動バランスが良化され、空気調和機の室内機に搭載した場合に周辺部品との距離が小さくでき、結果、空気調和機の室内機がコンパクト化できる。   When the operating point of the centrifugal fan is high static pressure and low air flow, the deviation of the wind speed distribution blown from the centrifugal fan tends to concentrate more on the main plate side, but the main flow is efficiently scraped with the sled. Thus, the main flow passing between the wings smoothly flows toward the wing trailing edge, and the main flow is sucked to the shroud side by the curved portion and blown out without being disturbed. , Turbulent noise can be reduced. By reducing the turbulent noise, the centrifugal fan can be made compact and pressure fluctuations on the wall surface of the centrifugal fan can be reduced, so that the dynamic balance of the centrifugal fan is improved and installed in an indoor unit of an air conditioner. The distance from the peripheral parts can be reduced, and as a result, the indoor unit of the air conditioner can be made compact.

以下、本発明の各実施形態について、送風装置を図面に基づき説明する。なお、以下に説明する各実施形態は一例であり、本発明は各実施形態により限定されるものではない。   Hereinafter, a blower will be described with reference to the drawings for each embodiment of the present invention. Each embodiment described below is an example, and the present invention is not limited to each embodiment.

（実施の形態１）
図１は本発明の第１の実施の形態における遠心ファンの斜視図を示し、図２は本発明の第１の実施の形態における遠心ファンの翼の水平方向断面を示し、図３は本発明の第１の実施の形態における遠心ファンの翼前側断面図を示し、図４は本発明の第１の実施の形態における遠心ファンの翼後側断面図を示すものである。 (Embodiment 1)
FIG. 1 is a perspective view of a centrifugal fan according to a first embodiment of the present invention, FIG. 2 is a horizontal sectional view of a blade of the centrifugal fan according to the first embodiment of the present invention, and FIG. FIG. 4 shows a blade front cross-sectional view of the centrifugal fan in the first embodiment, and FIG. 4 shows a blade rear cross-sectional view of the centrifugal fan in the first embodiment of the present invention.

なお本実施の形態においては、図３は断面図であるので、シュラウド１０２と翼１０３は接合されているように記載されているが、図１から把握できるように、翼１０３の前縁側においては、シュラウド１０２と翼１０３は接合されていない。   In this embodiment, since FIG. 3 is a cross-sectional view, the shroud 102 and the blade 103 are described as being joined, but as can be understood from FIG. The shroud 102 and the wing 103 are not joined.

図１において、ファンモータの回転軸と連結されており、ファンモータを格納するための一端が開口した略中空円錐台形状を有する主板１０１と、主板１０１に対向配置されるシュラウド１０２と、主板１０１とシュラウド１０２との間に配置される翼１０３とで構成された遠心ファン１００である。   In FIG. 1, a main plate 101 that is connected to a rotating shaft of a fan motor and has a substantially hollow frustum shape that is open at one end for storing the fan motor, a shroud 102 that is disposed to face the main plate 101, and a main plate 101. And a centrifugal fan 100 composed of a blade 103 arranged between the shroud 102 and the shroud 102.

以上のように構成された送風装置について、以下その動作、作用を説明する。   About the air blower comprised as mentioned above, the operation | movement and an effect | action are demonstrated below.

まず、遠心ファン１００を所定の回転方向に回転させると、翼１０３の昇圧作用によって、シュラウド１０２の小径側開口部から吸込まれた流体（以下、主流１８０と呼ぶ）は、遠心ファン１００の回転軸方向の断面で見たときに、主流１８０はシュラウド１０２と主板１０１で形成される略並行な２円弧の流体流路で曲げられ、略遠心方向に吹出される。   First, when the centrifugal fan 100 is rotated in a predetermined rotation direction, the fluid sucked from the small-diameter side opening of the shroud 102 (hereinafter referred to as the main flow 180) by the pressure-increasing action of the blades 103 is the rotation axis of the centrifugal fan 100. When viewed in a cross-section in the direction, the main flow 180 is bent in a substantially parallel two-circular fluid flow path formed by the shroud 102 and the main plate 101 and is blown out in a substantially centrifugal direction.

ここで、図２に示す翼１０３の水平方向の断面において、翼前縁１１１は回転軸１２０と翼１０３との距離が最も小さくなる箇所を示し、翼後縁１１２は回転軸１２０と翼１０３との距離が最も大きくなる箇所を示している。また、出口角１１４は翼１０３のキャンバーライン１１３と接線とのなす角である。   Here, in the horizontal cross section of the wing 103 shown in FIG. 2, the wing leading edge 111 indicates a portion where the distance between the rotating shaft 120 and the wing 103 is the smallest, and the wing trailing edge 112 indicates the rotating shaft 120 and the wing 103. The part where the distance of is the largest is shown. The exit angle 114 is an angle formed by the camber line 113 of the wing 103 and a tangent line.

次に翼１０３の形状について説明する。図３は翼の前縁側を示している。翼前縁１１１のそり１０９が、シュラウド１０２から主板１０１の方向に従って、回転軸１２０との距離が小さくなり、ある所定の箇所からそり１０９と回転軸１２０との距離が大きくなるように湾曲している。図４は、翼の後縁側を示している。翼後縁１１２において、翼後縁１１２がシュラウドから主板に向かうに従って、回転方向側に寄っている。   Next, the shape of the wing 103 will be described. FIG. 3 shows the leading edge side of the wing. The sled 109 of the blade leading edge 111 is curved so that the distance from the rotating shaft 120 decreases and the distance between the sled 109 and the rotating shaft 120 increases from a predetermined position according to the direction from the shroud 102 to the main plate 101. Yes. FIG. 4 shows the trailing edge side of the wing. In the wing trailing edge 112, the wing trailing edge 112 is closer to the rotational direction side from the shroud toward the main plate.

遠心ファン１００を所定の回転方向に回転させると、翼１０３の昇圧作用によって、シュラウド１０２の小径側開口部から吸込まれた流体（以下、主流１８０と呼ぶ）は、遠心ファン１００の回転軸方向の断面で見たときに、主流１８０はシュラウド１０２と主板１０１で形成される略並行な２円弧の流体流路で曲げられ略遠心方向に吹出される。   When the centrifugal fan 100 is rotated in a predetermined rotation direction, the fluid sucked from the small-diameter side opening of the shroud 102 (hereinafter referred to as the main flow 180) by the pressure increasing action of the blades 103 is moved in the rotation axis direction of the centrifugal fan 100. When viewed in cross section, the main flow 180 is bent by a substantially parallel two-circular fluid flow path formed by the shroud 102 and the main plate 101 and is blown out in a substantially centrifugal direction.

ここで、そり１０９が主流１８０を掻き出す作用によって、翼１０３と翼１０３の間を通過する主流１８０の流量が増加する。更に、主流１８０が翼１０３の表面を翼後縁方向に向かって沿うように流れ、略遠心方向へ吹き出される（以下、吹出流１８１と呼ぶ）。吹出流１８１は翼１０３の揚力（１９０）作用によってシュラウド１０２方向の流速が増大するため、シュラウド１０２側方向に引き寄せられながら略遠心方向へ遠心ファン１００の回転軸１２０方向の風速分布に偏りが生じることなく、吹き出される。   Here, the flow rate of the main stream 180 passing between the blades 103 and 103 is increased by the action of the sled 109 scraping the main stream 180. Further, the main flow 180 flows along the surface of the blade 103 along the blade trailing edge direction, and is blown out in a substantially centrifugal direction (hereinafter referred to as a blow-out flow 181). Since the airflow 181 increases the flow velocity in the direction of the shroud 102 due to the lift (190) action of the blades 103, the airflow distribution in the direction of the rotary shaft 120 of the centrifugal fan 100 is biased in the substantially centrifugal direction while being drawn toward the shroud 102 side. Without being blown out.

これによって、シュラウド１０２壁面近傍の主流１８０の速度が低下することなく吹出されるため、乱流騒音が低減できる。   Thereby, since the speed of the main flow 180 in the vicinity of the shroud 102 wall surface is blown out, turbulent noise can be reduced.

（実施の形態２）
図５は、本発明の第２の実施の形態の遠心ファンの翼後側断面図を示すものである。全体の構成は、図１および図２に示すものと同様であり、同一構成要素には同一符号を付し、その説明を省略する。 (Embodiment 2)
FIG. 5 shows a blade rear cross-sectional view of a centrifugal fan according to a second embodiment of the present invention. The entire configuration is the same as that shown in FIGS. 1 and 2, and the same components are denoted by the same reference numerals and description thereof is omitted.

特に第１の発明の翼後縁１１２を、翼１０３と主板１０１とで構成される傾斜角２１１が、翼１０３とシュラウド１０２との接合部と翼１０３と主板１０１との接合部とを結ぶ直線と主板１０１とで構成される傾斜角２１０よりも大きくなるように湾曲部２０９を有する。   In particular, the blade trailing edge 112 according to the first aspect of the invention has an inclination angle 211 composed of the blade 103 and the main plate 101, and a straight line connecting the joint between the blade 103 and the shroud 102 and the joint between the blade 103 and the main plate 101. And the main plate 101 are provided with a curved portion 209 so as to be larger than an inclination angle 210.

ここで、主流１８０をそり１０９で効率よく掻き出すことで、翼１０３と翼１０３の間を通過する主流１８０が翼後縁１１２方向に向かってスムーズに流れ、翼後縁１１２がシュラウド１０２方向に向かって湾曲部２０９を有しているため、翼１０３の正圧面側から吹出される主流１８０の角度がより一層シュラウド１０２方向に吸引される。   Here, by efficiently scraping the main flow 180 with the sled 109, the main flow 180 passing between the blade 103 and the blade 103 flows smoothly toward the blade trailing edge 112, and the blade trailing edge 112 moves toward the shroud 102. Therefore, the angle of the main flow 180 blown out from the pressure surface side of the blade 103 is further sucked in the direction of the shroud 102.

これによって、遠心ファン１００の動作点が、高静圧・低風量の場合、遠心ファン１００から吹出される主流分布の偏りが主板１０１側に一層集中する傾向となるが、主流１８０をそり１０９で効率よく掻き出すことで、翼１０３と翼１０３の間を通過する主流１８０が翼後縁１１２方向に向かってスムーズに流れ、湾曲部２０９によってシュラウド１０２側に主流１８０が吸引されるため、乱れることなく吹出される。   As a result, when the operating point of the centrifugal fan 100 is high static pressure and low air flow, the bias of the main flow distribution blown out from the centrifugal fan 100 tends to be more concentrated on the main plate 101 side. By scraping efficiently, the main flow 180 passing between the blades 103 and 103 flows smoothly in the direction of the blade trailing edge 112, and the main flow 180 is sucked to the shroud 102 side by the curved portion 209. Be blown out.

これによって、一般的に遠心ファン１００の動作点が、高静圧・低風量の場合、遠心ファン１００から吹出される風速分布の偏りが主板１０１側に一層集中する傾向となるが、本発明では、湾曲部２０９から乱されることなくシュラウド１０２側に主流１８０が吸引されるため、乱流騒音が低減できる。乱流騒音の低減によって、遠心ファン１００のコンパクト化と遠心ファン１００の翼面上の圧力変動を低減できるため、遠心ファン１００の動バランスが良化され、空気調和機の室内機に搭載した場合に周辺部品との距離が小さくでき、結果、空気調和機の室内機がコンパクト化できる。   As a result, when the operating point of the centrifugal fan 100 is generally high static pressure and low air volume, the deviation of the wind speed distribution blown from the centrifugal fan 100 tends to be more concentrated on the main plate 101 side. Since the main flow 180 is attracted to the shroud 102 without being disturbed by the curved portion 209, turbulent noise can be reduced. When the centrifugal fan 100 is compact and the fluctuation in pressure on the blade surface of the centrifugal fan 100 can be reduced by reducing the turbulent noise, the dynamic balance of the centrifugal fan 100 is improved and the centrifugal fan 100 is installed in an indoor unit of an air conditioner. In addition, the distance from the peripheral parts can be reduced, and as a result, the indoor unit of the air conditioner can be made compact.

以上のように、本発明に係る送風装置の乱流騒音低減が可能となるので、家庭用及び業務用の各種形式の空気調和機の室内機に適用することができる。   As described above, since the turbulent flow noise of the blower according to the present invention can be reduced, it can be applied to indoor units of various types of air conditioners for home use and business use.

１００ 遠心ファン
１０１ 主板
１０２ シュラウド
１０３ 翼
１０９ そり
１１１ 翼前縁
１１２ 翼後縁
１１３ キャンバーライン
１１４ 出口角
１２０ 回転軸
１８０ 主流
１８１ 吹出流
１８２ 乱れ
１９０ 揚力
２０９ 湾曲部
２１０ 傾斜角
２１１ 傾斜角
３０３ 翼
３０９ そり
３１０ コーナー角 100 Centrifugal fan 101 Main plate 102 Shroud 103 Wing 109 Sled 111 Wing leading edge 112 Wing trailing edge 113 Camber line 114 Exit angle 120 Rotating shaft 180 Main flow 181 Blowing flow 182 Disturbance 190 Lifting force 209 Curved portion 210 Inclination angle 211 Inclination angle 303 Blade 309 Sled 310 Corner angle

Claims (2)

主板と、
前記主板に対向配置される略中空円錐台形状のシュラウドと、
前記主板と前記シュラウドとの間に配置される翼と、
を有する遠心ファンにおいて、
前記翼前縁の回転軸方向のそりが、前記シュラウドから前記主板方向に従って、前記そりと前記回転軸との距離が小さくなり、ある所定の箇所から前記そりと前記回転軸との距離が大きくなるように湾曲し、
前記翼後縁が、前記シュラウドと前記翼後縁との接合部から前記主板に向かうに従って、回転方向側に寄っている、
ことを特徴とする、遠心ファン。 A main plate,
A substantially hollow frustoconical shroud disposed opposite to the main plate;
A wing disposed between the main plate and the shroud;
In a centrifugal fan having
The warpage of the blade leading edge in the rotation axis direction is such that the distance between the sled and the rotation shaft decreases in accordance with the main plate direction from the shroud, and the distance between the sled and the rotation shaft increases from a predetermined position. Curved and
The wing trailing edge is closer to the rotational direction side toward the main plate from the joint between the shroud and the wing trailing edge.
A centrifugal fan characterized by that. 前記翼後縁において、前記翼と前記主板とで構成される傾斜角が、前記翼と前記シュラウドとの接合部と前記翼と前記主板との接合部とを結ぶ直線と前記主板とで構成される傾斜角よりも大きくなるように湾曲部を有することを特徴とする、請求項１に記載の遠心ファン。   In the wing trailing edge, an inclination angle formed by the wing and the main plate is configured by a straight line connecting the joint portion between the wing and the shroud and the joint portion between the wing and the main plate and the main plate. The centrifugal fan according to claim 1, wherein the centrifugal fan has a curved portion so as to be larger than an inclination angle.
JP2015207700A 2015-10-22 2015-10-22 Centrifugal fan Pending JP2017078386A (en)

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JP3405287B2 (en) * 1999-10-20 2003-05-12 ダイキン工業株式会社 Centrifugal fan
JP3391318B2 (en) * 1999-11-16 2003-03-31 ダイキン工業株式会社 Centrifugal fan and air conditioner equipped with the fan
JP3861008B2 (en) * 2002-01-10 2006-12-20 三菱重工業株式会社 Turbofan and air conditioner equipped with the same
JP4396775B2 (en) * 2007-11-26 2010-01-13 ダイキン工業株式会社 Centrifugal fan
JP4612084B2 (en) * 2008-08-29 2011-01-12 株式会社日立産機システム Centrifugal fan and air fluid machine using the same
WO2012140690A1 (en) * 2011-04-12 2012-10-18 三菱電機株式会社 Turbofan and air conditioner

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2019011734A (en) * 2017-06-30 2019-01-24 株式会社川本製作所 Blower impeller

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