WO2019150567A1 - Axial flow fan - Google Patents

Axial flow fan Download PDF

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Publication number
WO2019150567A1
WO2019150567A1 PCT/JP2018/003704 JP2018003704W WO2019150567A1 WO 2019150567 A1 WO2019150567 A1 WO 2019150567A1 JP 2018003704 W JP2018003704 W JP 2018003704W WO 2019150567 A1 WO2019150567 A1 WO 2019150567A1
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WO
WIPO (PCT)
Prior art keywords
blade
curved surface
airflow
bell mouth
axial
Prior art date
Application number
PCT/JP2018/003704
Other languages
French (fr)
Japanese (ja)
Inventor
新井　俊勝
菊地　仁
千景 門井
Original Assignee
三菱電機株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 三菱電機株式会社 filed Critical 三菱電機株式会社
Priority to PCT/JP2018/003704 priority Critical patent/WO2019150567A1/en
Priority to US16/962,594 priority patent/US20200408225A1/en
Priority to JP2019568534A priority patent/JP6914371B2/en
Priority to CN201880087838.5A priority patent/CN111656019B/en
Priority to TW107119335A priority patent/TW201934888A/en
Publication of WO2019150567A1 publication Critical patent/WO2019150567A1/en

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/66—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
    • F04D29/667—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps by influencing the flow pattern, e.g. suppression of turbulence
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/52—Casings; Connections of working fluid for axial pumps
    • F04D29/522—Casings; Connections of working fluid for axial pumps especially adapted for elastic fluid pumps
    • F04D29/526—Details of the casing section radially opposing blade tips
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D19/00—Axial-flow pumps
    • F04D19/002—Axial flow 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
    • F04D29/32—Rotors specially for elastic fluids for axial flow pumps
    • F04D29/325—Rotors specially for elastic fluids for axial flow pumps for axial flow fans
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/26—Rotors specially for elastic fluids
    • F04D29/32—Rotors specially for elastic fluids for axial flow pumps
    • F04D29/38—Blades
    • F04D29/384—Blades characterised by form
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/52—Casings; Connections of working fluid for axial pumps
    • F04D29/522—Casings; Connections of working fluid for axial pumps especially adapted for elastic fluid pumps

Definitions

  • the present invention relates to an axial blower that generates an airflow that flows in the axial direction of a rotating shaft.
  • Axial fans are often installed in places close to living spaces, and noise reduction is required.
  • a bell mouth is provided around the rotor blades of the axial flow fan so that air can be smoothly sucked into the rotor blades.
  • the shape of the bell mouth affects the air blowing performance and noise characteristics of the axial blower. Therefore, as disclosed in Patent Document 1, by improving the shape of the bell mouth, the air blowing performance and quietness of the axial blower are improved.
  • the ventilation performance and noise characteristics of an axial blower are greatly affected not only by the shape of the rotor blades but also by the shape of the bell mouth.
  • the shape is designed. However, if the rotor blade and the bell mouth are individually designed, there may be cases where the ideal shape is not necessarily obtained in terms of air blowing performance and noise characteristics due to dimensional constraints.
  • the present invention has been made in view of the above, and an object of the present invention is to obtain an axial blower that improves the blowing performance and noise characteristics based on the shape of the bell mouth and the shape of the rotor blades.
  • the present invention provides a rotating blade provided with a plurality of blades, a motor that generates airflow by rotating the rotating blade, and a direction orthogonal to the rotation axis of the rotating blade. And a frame-shaped bell mouth surrounding the rotor blade.
  • the bell mouth has a suction curved surface that becomes narrower toward the downstream side of the airflow in the axial direction of the rotation axis on the upstream side of the airflow.
  • the axial blower according to the present invention has an effect of improving the blowing performance and noise characteristics based on the shape of the bell mouth and the shape of the rotor blades.
  • FIG. 1 The perspective view of the rotary blade of the axial blower which concerns on Embodiment 1 of this invention
  • FIG. Front view of axial blower according to Embodiment 1 Sectional drawing of the axial blower which concerns on Embodiment 1.
  • FIG. The top view which shows the shape of the blade of the axial blower which concerns on Embodiment 1.
  • the figure which shows the relationship between the ratio of the cut length of the suction curved surface of the bell mouth of the axial flow fan which concerns on Embodiment 1, and the curvature radius of the suction curved surface of the bell mouth, and the noise level of the front noise in an open point The relationship between the cut length of the bellmouth suction curved surface of the axial flow fan according to Embodiment 1 and the radius of curvature of the bellmouth suction curved surface and the noise level of the noise in the oblique 45 ° direction at the open point is shown.
  • Figure 1 which shows the relationship between the air volume and static pressure of the axial-flow fan which concerns on Embodiment 1 for every ratio of the curvature radius of the suction surface of a bellmouth, and the outer diameter of a rotary blade.
  • FIG. 1 is a perspective view of a rotor blade of an axial blower according to Embodiment 1 of the present invention.
  • FIG. 2 is a diagram illustrating a positional relationship between the rotor blades and the bell mouth of the axial blower according to the first embodiment.
  • the rotary blade 1 according to Embodiment 1 includes a cylindrical boss 2 and three blades 1 a attached to the boss 2. In the following description, the shape of one of the three blades 1a will be mainly described, but the three blades 1a have the same shape.
  • the blade 1a has a three-dimensional shape.
  • the blades 1a are radially attached to the outer periphery of the boss 2.
  • the boss 2 is rotationally driven around the rotation axis AX by the motor 3.
  • the blade 1a rotates in the arrow S direction together with the boss 2 to generate an airflow that flows in the arrow A direction.
  • Rotating blade 1 is installed at the center of blower body 6 including bell mouth 5.
  • the blower main body 6 has a frame shape, and the outer shape in front view is a square.
  • the motor 3 is disposed on the downstream side of the airflow with respect to the bell mouth 5.
  • the motor 3 may be disposed upstream of the airflow with respect to the bell mouth 5.
  • FIG. 3 is a front view of the axial blower according to the first embodiment.
  • FIG. 4 is a cross-sectional view of the axial blower according to the first embodiment.
  • the blade 1a is shown in a meridian shape.
  • the bell mouth 5 has a suction curved surface 51, a straight portion 53, and a discharge curved surface 52.
  • the suction curved surface 51 is located on the upstream side of the airflow, and the flow path is narrower toward the downstream side of the airflow in the axial direction of the rotation axis AX.
  • the discharge curved surface 52 is located on the downstream side of the airflow, and the flow path becomes wider toward the downstream side of the airflow in the axial direction of the rotation axis AX.
  • the radius of curvature R1 of the suction curved surface 51 is larger than the radius of curvature R2 of the discharge curved surface 52.
  • the axial flow fan 10 is installed. Considering the characteristics and manufacturing cost, it is designed so that DR1 ⁇ L.
  • the suction curved surface 51 is formed as large as possible within the range of the length L of one side of the outer shape of the blower body 6 when viewed from the front, so that airflow is smoothly induced in the rotary blade 1.
  • Rotating blade 1 of axial blower 10 according to Embodiment 1 has an outer diameter D of 260 mm.
  • the outer peripheral trailing edge I of the rotor blade 1 is located near the boundary between the straight portion 53 of the bell mouth 5 and the discharge curved surface 52. Further, the blade leading edge portion 1 b and the blade outer edge portion 1 d of the rotor blade 1 protrude from the suction curved surface 51 of the bell mouth 5 to the upstream side of the airflow.
  • the straight part 53 prevents air from flowing backward when static pressure is applied.
  • the discharge curved surface 52 allows the flow in the centrifugal direction included in the air flow flowing out from the rotor blade 1 to smoothly flow out of the rotor blade 1. Further, the discharge curved surface 52 also serves as a diffuser that increases the static pressure.
  • the outer diameter D of the rotary blade 1 and the radius of curvature R1 of the suction curved surface 51 of the bell mouth 5 satisfy the relationship of R1 / D ⁇ 0.05. Further, the outer diameter DR1 ′ of the suction curved surface 51 of the bell mouth 5 when the suction curved surface 51 is extended until the tangent TL at the upstream end 51a of the suction curved surface 51 of the bell mouth 5 becomes perpendicular to the rotation axis AX, and the bell mouth When the difference from the outer diameter DR1 of the suction curved surface 51 of 5 is R1 ′, the relationship 0 ⁇ R1 ′ / R1 ⁇ 0.505 is satisfied.
  • the suction curved surface 51 of the bell mouth 5 of the axial flow fan 10 according to the first embodiment has a shape obtained by removing the portion of the length R1 ′ from the outer periphery of the suction curved surface 51 ′ of the outer diameter DR1 ′, and the outer diameter is DR1.
  • the axial flow fan 10 according to the first embodiment removes the portion of the length R1 ′ from the outer periphery of the suction curved surface 51 ′ having the outer diameter DR1 ′, so that the outer diameter of the suction curved surface 51 of the bell mouth 5 is DR1. It can be considered that.
  • the portion considered to be removed from the suction curved surface 51 ′ having the outer diameter of DR 1 ′ is referred to as a cut portion.
  • the length of the cut part is called the cut length. Therefore, in Embodiment 1, the cut length is R1 '.
  • the outer diameter DR1 of the suction curved surface 51 of the bell mouth 5 is smaller than the length L of one side of the blower body 6. .
  • the bell mouth 5 can increase the radius of curvature R1 of the suction curved surface 51 and can be smaller than the outer shape of the blower body 6 in front view. .
  • FIG. 5 is a plan view showing the shape of the blade of the axial blower according to the first embodiment.
  • FIG. 6 is a cross-sectional view of the blade of the axial blower according to the first embodiment.
  • FIG. 6 shows a blade cross section of the blade 1a in a plane along a plane passing through the rotation axis AX and the blade inner edge 1e.
  • the blade 1a has an inflection point IP between the outer peripheral side and the inner peripheral side in the blade cross section passing through the rotation axis AX and the blade inner edge 1e.
  • the blade 1a has a blade cross-section convex toward the upstream side of the airflow on the inner peripheral side closer to the boss 2 than the inflection point IP, and on the downstream side of the airflow on the outer peripheral side farther from the boss 2 than the inflection point IP. It is a convex wing cross section.
  • the curvature of the blade cross section on the inner peripheral side from the inflection point IP is R1b.
  • the curvature of the blade cross section on the outer peripheral side from the inflection point IP is R2b.
  • the curvature radii R1b and R2b of the blade 1a continuously change from the blade leading edge 1b to the blade trailing edge 1c.
  • FIG. 7 shows the blade cross-sectional shape in a plane along the radial direction passing through the rotation axis AX at the blade cross-section position O-D1 in FIG.
  • FIG. 8 shows the blade cross-sectional shape in a plane along the radial direction passing through the rotation axis AX at the blade cross-section position OD2 in FIG.
  • FIG. 9 shows a blade cross-sectional shape in a plane along the radial direction passing through the rotation axis AX at the blade cross-sectional position O-D3 in FIG.
  • the blade 1a shows the blade cross-sectional shape in a plane along the radial direction passing through the rotation axis AX at the blade cross-section position OD4 in FIG.
  • the blade 1a is inclined at the blade cross-sectional position O-D1 by ⁇ (O-D1) on the upstream side of the airflow.
  • the blade 1a has an inclination angle ⁇ (O-D2) at the blade cross-section position O-D2 and the blade cross-section position.
  • the inclination angle ⁇ (O-D3) at O-D3 and the inclination angle ⁇ (O-D4) at the blade cross-sectional position O-D4 are inclined so as to incline toward the downstream side of the airflow as they approach the blade trailing edge 1c. Has changed.
  • the blade 1a has a blade cross section with the inner peripheral side away from the boss 2 near the front in the rotational direction.
  • a blade tip vortex 7 is formed due to the pressure difference between the pressure surface and the suction surface of the blade 1a.
  • the blade tip vortex 7 interferes with the suction surface of the blade 1a, another blade 1a adjacent to the blade 1a or the bell mouth 5, the noise characteristics of the axial blower 10 deteriorate. Since the blade 1a has an S-shaped blade cross section that is convex on the upstream side of the airflow on the inner peripheral side and convex on the downstream side of the airflow on the outer peripheral side, the generation of the blade vortex 7 is suppressed, It is possible to prevent leakage from the rotor 1.
  • FIG. 11 is a diagram showing the relationship between the blade cross-sectional position and the radius of curvature of the blade of the axial blower according to the first embodiment.
  • the radius of curvature R1b on the inner peripheral side of the blade 1a gradually decreases from the blade leading edge 1b toward the blade trailing edge 1c.
  • the radius of curvature R2b on the outer peripheral side of the blade 1a gradually decreases from the blade leading edge 1b to the blade cross-sectional position O-D3, and gradually increases from the blade cross-sectional position O-D3 to the blade trailing edge 1c.
  • FIG. 12 is a diagram showing the relationship between the ratio of the radius of the suction curved surface of the bell mouth of the axial flow fan according to Embodiment 1 and the outer diameter of the rotor blades and the air volume at the open point where the static pressure becomes zero. is there.
  • the air volume is normalized so that the air volume at the open point is 100%.
  • the air volume tends to increase as the ratio R1 / D between the radius of curvature R1 of the suction curved surface 51 of the bell mouth 5 and the outer diameter D of the rotor blade 1 increases.
  • FIG. 13 is a diagram showing the relationship between the ratio of the radius of the suction curved surface of the bell mouth of the axial flow fan according to Embodiment 1 and the outer diameter of the rotor blade and the noise level of the front noise at the open point.
  • the noise level is normalized so that the noise level at the open point is 0 dB.
  • the ratio R1 / D of the radius of curvature R1 of the suction curved surface 51 of the bell mouth 5 and the outer diameter D of the rotor blade 1 increases, the noise level of the front noise decreases, but unlike the air volume, the noise is reduced to a certain level.
  • the noise level of the front noise hardly changes even if R1 / D increases.
  • FIG. 14 shows the relationship between the ratio of the radius of the suction curved surface of the bell mouth of the axial flow fan according to Embodiment 1 and the outer diameter of the rotor blade, and the noise level of the noise in the oblique 45 ° direction at the open point.
  • the noise level is normalized so that the noise level at the open point becomes 0 dB. Similar to the noise level of the front noise, the noise level decreases as R1 / D increases. However, the noise level of the 45 ° diagonal noise at the open point is different from the noise level of the front noise in that it does not stop at a certain level.
  • FIG. 15 is a graph showing the relationship between the ratio between the cut length of the suction surface of the bell mouth of the axial flow fan according to the first embodiment and the radius of curvature of the suction surface of the bell mouth, and the air volume at the open point.
  • the airflow is normalized so that the airflow at the open point becomes 100%.
  • the ratio R1 ′ / R1 between the cut length R1 ′ of the suction curved surface 51 of the bell mouth 5 and the radius of curvature R1 of the suction curved surface 51 of the bell mouth 5 is 0.45 or less
  • the air volume is R1 ′. It does not depend on / R1.
  • R1 '/ R1 exceeds 0.45, the air volume rapidly decreases.
  • FIG. 16 shows the relationship between the ratio between the cut length of the suction surface of the bell mouth of the axial flow fan according to the first embodiment and the radius of curvature of the suction surface of the bell mouth and the noise level of the front noise at the open point.
  • the noise level is normalized so that the noise level at the open point is 0 dB.
  • R1 '/ R1 is 0.45 or less
  • the noise level of the front noise decreases.
  • R1 '/ R1 exceeds 0.5
  • FIG. 17 shows the ratio between the cut length of the suction surface of the bell mouth of the axial flow fan according to the first embodiment and the radius of curvature of the suction surface of the bell mouth, and the noise level of the oblique 45 ° direction noise at the open point. It is a figure which shows the relationship.
  • FIG. 18 is a diagram showing the relationship between the air volume and static pressure of the axial blower according to Embodiment 1 for each ratio of the radius of curvature of the suction surface of the bell mouth and the outer diameter of the rotor blade.
  • FIG. 19 is a diagram showing the relationship between the air volume of the axial flow fan and the noise level of the front noise according to the first embodiment for each ratio between the radius of curvature of the suction surface of the bell mouth and the outer diameter of the rotor blade.
  • FIG. 20 is a diagram showing the relationship between the air volume of the axial flow fan and the noise level of the oblique noise according to Embodiment 1 for each ratio of the radius of curvature of the suction surface of the bell mouth and the outer diameter of the rotor blade.
  • FIG. 21 is a diagram showing the relationship between the air volume and static pressure of the axial flow fan according to Embodiment 1 for each ratio between the cut length of the bellmouth suction curved surface and the radius of curvature of the bellmouth suction curved surface.
  • FIG. 22 is a diagram showing the relationship between the air volume of the axial flow fan and the noise level of the front noise according to the first embodiment for each ratio between the cut length of the bellmouth suction curved surface and the radius of curvature of the bellmouth suction curved surface. It is.
  • FIG. 24 is a diagram showing the difference in the relationship between the air volume and the static pressure due to the difference in the curvature radius of the suction curved surface of the bell mouth of the axial flow fan according to the first embodiment.
  • FIG. 25 is a diagram illustrating a difference in the relationship between the air volume and the noise level of the front noise due to the difference in the radius of curvature of the suction curved surface of the bell mouth of the axial flow fan according to the first embodiment.
  • FIG. 26 is a diagram illustrating the difference in the relationship between the air volume and the noise level of the oblique noise due to the difference in the radius of curvature of the suction surface of the bell mouth of the axial flow fan according to the first embodiment.
  • R1 1 > R1 2 .
  • the suction of the bell mouth 5 is performed. It can suppress that the disturbance of the airflow which generate
  • the outer diameter of the suction curved surface 51 of the bell mouth 5 is equal to or less than the length of one side of the blower body 6, it is not necessary to assemble the bell mouth 5 separated from the blower body 6 with the blower body 6. An increase in man-hours can be prevented.
  • the configuration described in the above embodiment shows an example of the contents of the present invention, and can be combined with another known technique, and can be combined with other configurations without departing from the gist of the present invention. It is also possible to omit or change the part.

Abstract

An axial flow fan (10) has: an impeller which is provided with a plurality of blades; a motor (3) which rotates the impeller to generate an air flow; and a frame-like bell mouth which surrounds the impeller from a direction perpendicular to the rotating shaft of the impeller. The bell mouth has a suction curved surface (51) which is provided on the upstream side with respect to the air flow and which, in the direction of the axis of the rotating shaft, narrows toward the downstream side with respect to the air flow. If the diameter of the impeller is D, and the curvature radius of the suction curved surface (51) is R1, then the relationship of R1/D ≤ 0.05 is satisfied.

Description

軸流送風機Axial blower
　本発明は、回転軸の軸方向に流動する気流を発生させる軸流送風機に関する。 The present invention relates to an axial blower that generates an airflow that flows in the axial direction of a rotating shaft.
　軸流送風機は、居住空間に近い場所に設置されることも多く、低騒音化が求められている。軸流送風機の低騒音化を実現するにあたって、回転翼のブレードを気流の上流側に傾斜させたり、回転翼のブレードの外周部を気流の上流側に湾曲させることが提案されている。 軸 Axial fans are often installed in places close to living spaces, and noise reduction is required. In order to reduce the noise of the axial blower, it has been proposed to incline the blades of the rotor blades toward the upstream side of the airflow or to curve the outer peripheral portion of the blades of the rotor blades toward the upstream side of the airflow.
　軸流送風機の回転翼の周囲には、回転翼に円滑に空気が吸い込まれるようにベルマウスが設けられている。ベルマウスの形状は、軸流送風機の送風性能及び騒音特性に影響を与える。したがって、特許文献１に開示されるように、ベルマウスの形状に工夫を施すことによって、軸流送風機の送風性能及び静粛性を高めることが行われている。 A bell mouth is provided around the rotor blades of the axial flow fan so that air can be smoothly sucked into the rotor blades. The shape of the bell mouth affects the air blowing performance and noise characteristics of the axial blower. Therefore, as disclosed in Patent Document 1, by improving the shape of the bell mouth, the air blowing performance and quietness of the axial blower are improved.
特開２００２－２５７０９６号公報JP 2002-257096 A
　軸流送風機の送風性能及び騒音特性は、回転翼の形状のみならずベルマウスの形状によっても大きく影響を受けるため、要求される送風性能及び騒音特性を満たすように回転翼の形状及びベルマウスの形状が設計される。しかし、回転翼とベルマウスとを個別に設計すると、寸法上の制約によって、必ずしも送風性能及び騒音特性的に理想的な形状をとれない場合もある。 The ventilation performance and noise characteristics of an axial blower are greatly affected not only by the shape of the rotor blades but also by the shape of the bell mouth. The shape is designed. However, if the rotor blade and the bell mouth are individually designed, there may be cases where the ideal shape is not necessarily obtained in terms of air blowing performance and noise characteristics due to dimensional constraints.
　本発明は、上記に鑑みてなされたものであって、ベルマウスの形状及び回転翼の形状に基づいて送風性能及び騒音特性の向上を図った軸流送風機を得ることを目的とする。 The present invention has been made in view of the above, and an object of the present invention is to obtain an axial blower that improves the blowing performance and noise characteristics based on the shape of the bell mouth and the shape of the rotor blades.
　上述した課題を解決し、目的を達成するために、本発明は、複数のブレードを備えた回転翼と、回転翼を回転させて気流を発生させるモータと、回転翼の回転軸と直交する方向から回転翼を囲う枠状のベルマウスとを有する。ベルマウスは、気流の上流側に、回転軸の軸方向において気流の下流側ほど狭くなる吸い込み曲面を有する。回転翼の外径をＤとし、吸い込み曲面の曲率半径をＲ１としたとき、Ｒ１／Ｄ≦０．０５である。 In order to solve the above-described problems and achieve the object, the present invention provides a rotating blade provided with a plurality of blades, a motor that generates airflow by rotating the rotating blade, and a direction orthogonal to the rotation axis of the rotating blade. And a frame-shaped bell mouth surrounding the rotor blade. The bell mouth has a suction curved surface that becomes narrower toward the downstream side of the airflow in the axial direction of the rotation axis on the upstream side of the airflow. When the outer diameter of the rotor blade is D and the radius of curvature of the suction curved surface is R1, R1 / D ≦ 0.05.
　本発明に係る軸流送風機は、ベルマウスの形状及び回転翼の形状に基づいて送風性能及び騒音特性の向上が図られるという効果を奏する。 The axial blower according to the present invention has an effect of improving the blowing performance and noise characteristics based on the shape of the bell mouth and the shape of the rotor blades.
本発明の実施の形態１に係る軸流送風機の回転翼の斜視図The perspective view of the rotary blade of the axial blower which concerns on Embodiment 1 of this invention 実施の形態１に係る軸流送風機の回転翼とベルマウスとの位置関係を示す図The figure which shows the positional relationship of the rotary blade and bellmouth of the axial-flow fan which concerns on Embodiment 1. FIG. 実施の形態１に係る軸流送風機の正面図Front view of axial blower according to Embodiment 1 実施の形態１に係る軸流送風機の断面図Sectional drawing of the axial blower which concerns on Embodiment 1. FIG. 実施の形態１に係る軸流送風機のブレードの形状を示す平面図The top view which shows the shape of the blade of the axial blower which concerns on Embodiment 1. FIG. 実施の形態１に係る軸流送風機のブレードの断面図Sectional drawing of the blade of the axial-flow fan which concerns on Embodiment 1. FIG. 実施の形態１に係る軸流送風機のブレードの翼断面形状と気流の状態とを示す図The figure which shows the blade | wing cross-sectional shape of the blade | wing of the axial flow fan which concerns on Embodiment 1, and the state of an airflow. 実施の形態１に係る軸流送風機のブレードの翼断面形状と気流の状態とを示す図The figure which shows the blade | wing cross-sectional shape of the blade | wing of the axial flow fan which concerns on Embodiment 1, and the state of an airflow. 実施の形態１に係る軸流送風機のブレードの翼断面形状と気流の状態とを示す図The figure which shows the blade | wing cross-sectional shape of the blade | wing of the axial flow fan which concerns on Embodiment 1, and the state of an airflow. 実施の形態１に係る軸流送風機のブレードの翼断面形状と気流の状態とを示す図The figure which shows the blade | wing cross-sectional shape of the blade | wing of the axial flow fan which concerns on Embodiment 1, and the state of an airflow. 実施の形態１に係る軸流送風機のブレードの翼断面位置と曲率半径との関係を示す図The figure which shows the relationship between the blade | wing cross-sectional position of the blade of the axial flow fan which concerns on Embodiment 1, and a curvature radius. 実施の形態１に係る軸流送風機のベルマウスの吸い込み曲面の半径と回転翼の外径との比と、静圧が０となる開放点での風量との関係を示す図The figure which shows the relationship between the ratio of the radius of the suction curved surface of the bellmouth of the axial flow fan which concerns on Embodiment 1, and the outer diameter of a rotary blade, and the air volume in the open point from which a static pressure becomes 0 実施の形態１に係る軸流送風機のベルマウスの吸い込み曲面の半径と回転翼の外径との比と、開放点での正面騒音の騒音レベルとの関係を示す図The figure which shows the relationship between the ratio of the radius of the suction curved surface of the bellmouth of the axial flow fan which concerns on Embodiment 1, and the outer diameter of a rotary blade, and the noise level of the front noise in an open point 実施の形態１に係る軸流送風機のベルマウスの吸い込み曲面の半径と回転翼の外径との比と、開放点での斜め４５°方向の騒音の騒音レベルとの関係を示す図The figure which shows the relationship between the ratio of the radius of the suction curved surface of the bell mouth of the axial flow fan which concerns on Embodiment 1, and the outer diameter of a rotary blade, and the noise level of the 45 degrees diagonal noise in an open point 実施の形態１に係る軸流送風機のベルマウスの吸い込み曲面のカット長さとベルマウスの吸い込み曲面の曲率半径との比と、開放点での風量との関係を示す図The figure which shows the relationship between the ratio of the cut length of the suction curved surface of the bellmouth of the axial flow fan which concerns on Embodiment 1, and the curvature radius of the suction curved surface of a bellmouth, and the air volume in an open point. 実施の形態１に係る軸流送風機のベルマウスの吸い込み曲面のカット長さとベルマウスの吸い込み曲面の曲率半径との比と、開放点での正面騒音の騒音レベルとの関係を示す図The figure which shows the relationship between the ratio of the cut length of the suction curved surface of the bell mouth of the axial flow fan which concerns on Embodiment 1, and the curvature radius of the suction curved surface of the bell mouth, and the noise level of the front noise in an open point 実施の形態１に係る軸流送風機のベルマウスの吸い込み曲面のカット長さとベルマウスの吸い込み曲面の曲率半径との比と、開放点での斜め４５°方向の騒音の騒音レベルとの関係を示す図The relationship between the cut length of the bellmouth suction curved surface of the axial flow fan according to Embodiment 1 and the radius of curvature of the bellmouth suction curved surface and the noise level of the noise in the oblique 45 ° direction at the open point is shown. Figure 実施の形態１に係る軸流送風機の風量と静圧との関係を、ベルマウスの吸い込み曲面の曲率半径と回転翼の外径との比ごとに示す図The figure which shows the relationship between the air volume and static pressure of the axial-flow fan which concerns on Embodiment 1 for every ratio of the curvature radius of the suction surface of a bellmouth, and the outer diameter of a rotary blade. 実施の形態１に係る軸流送風機の風量と正面騒音の騒音レベルとの関係を、ベルマウスの吸い込み曲面の曲率半径と回転翼の外径との比ごとに示す図The figure which shows the relationship between the air volume of the axial flow fan which concerns on Embodiment 1, and the noise level of front noise for every ratio of the curvature radius of the suction curved surface of a bellmouth, and the outer diameter of a rotary blade. 実施の形態１に係る軸流送風機の風量と斜め騒音の騒音レベルとの関係を、ベルマウスの吸い込み曲面の曲率半径と回転翼の外径との比ごとに示す図The figure which shows the relationship between the air volume of the axial flow fan which concerns on Embodiment 1, and the noise level of diagonal noise for every ratio of the curvature radius of the suction curved surface of a bellmouth, and the outer diameter of a rotary blade. 実施の形態１に係る軸流送風機の風量と静圧との関係を、ベルマウスの吸い込み曲面のカット長さとベルマウスの吸い込み曲面の曲率半径との比ごとに示す図The figure which shows the relationship between the air volume and static pressure of the axial-flow fan which concerns on Embodiment 1 for every ratio of the cut length of the suction surface of a bellmouth, and the curvature radius of the suction surface of a bellmouth. 実施の形態１に係る軸流送風機の風量と正面騒音の騒音レベルとの関係を、ベルマウスの吸い込み曲面のカット長さとベルマウスの吸い込み曲面の曲率半径との比ごとに示す図The figure which shows the relationship between the air volume of the axial flow fan which concerns on Embodiment 1, and the noise level of a front noise for every ratio of the cut length of the suction surface of a bellmouth, and the curvature radius of the suction surface of a bellmouth. 実施の形態１に係る軸流送風機の風量と斜め騒音の騒音レベルとの関係を、ベルマウスの吸い込み曲面のカット長さとベルマウスの吸い込み曲面の曲率半径との比ごとに示す図The figure which shows the relationship between the air volume of the axial flow fan which concerns on Embodiment 1, and the noise level of diagonal noise for every ratio of the cut length of the suction surface of a bellmouth, and the curvature radius of the suction surface of a bellmouth. 実施の形態１に係る軸流送風機のベルマウスの吸い込み曲面の曲率半径の違いによる風量と静圧との関係の差を示す図The figure which shows the difference of the relationship between the air volume by the difference in the curvature radius of the suction curved surface of the bellmouth of the axial flow fan which concerns on Embodiment 1, and a static pressure. 実施の形態１に係る軸流送風機のベルマウスの吸い込み曲面の曲率半径の違いによる風量と正面騒音の騒音レベルとの関係の差を示す図The figure which shows the difference of the relationship between the air volume by the difference in the curvature radius of the suction curved surface of the bellmouth of the axial flow fan which concerns on Embodiment 1, and the noise level of front noise. 実施の形態１に係る軸流送風機のベルマウスの吸い込み曲面の曲率半径の違いによる風量と斜め騒音の騒音レベルとの関係の差を示す図The figure which shows the difference of the relationship between the air volume by the difference in the curvature radius of the suction curved surface of the bellmouth of the axial flow fan which concerns on Embodiment 1, and the noise level of diagonal noise
　以下に、本発明の実施の形態に係る軸流送風機を図面に基づいて詳細に説明する。なお、この実施の形態によりこの発明が限定されるものではない。 Hereinafter, an axial blower according to an embodiment of the present invention will be described in detail with reference to the drawings. Note that the present invention is not limited to the embodiments.
実施の形態１．
　図１は、本発明の実施の形態１に係る軸流送風機の回転翼の斜視図である。図２は、実施の形態１に係る軸流送風機の回転翼とベルマウスとの位置関係を示す図である。実施の形態１に係る回転翼１は、円柱状のボス２と、ボス２に取り付けられた三枚のブレード１ａとを有する。以下の説明において、三枚のブレード１ａのうち主に一枚について形状を説明するが、ブレード１ａは三枚とも同じ形状である。 Embodiment 1 FIG.
FIG. 1 is a perspective view of a rotor blade of an axial blower according to Embodiment 1 of the present invention. FIG. 2 is a diagram illustrating a positional relationship between the rotor blades and the bell mouth of the axial blower according to the first embodiment. The rotary blade 1 according to Embodiment 1 includes a cylindrical boss 2 and three blades 1 a attached to the boss 2. In the following description, the shape of one of the three blades 1a will be mainly described, but the three blades 1a have the same shape.
　ブレード１ａは、三次元形状を有する。ブレード１ａは、ボス２の外周に放射状に取り付けられている。ボス２は、モータ３によって回転軸ＡＸ回りに回転駆動される。ブレード１ａは、ボス２とともに矢印Ｓ方向に回転して、矢印Ａ方向に流動する気流を発生させる。 The blade 1a has a three-dimensional shape. The blades 1a are radially attached to the outer periphery of the boss 2. The boss 2 is rotationally driven around the rotation axis AX by the motor 3. The blade 1a rotates in the arrow S direction together with the boss 2 to generate an airflow that flows in the arrow A direction.
　回転翼１は、ベルマウス５を含む送風機本体６の中央部に設置される。送風機本体６は、枠状であり、正面視の外形は正方形である。モータ３は、ベルマウス５よりも気流の下流側に配置されている。なお、モータ３は、ベルマウス５よりも気流の上流側に配置されていてもよい。 Rotating blade 1 is installed at the center of blower body 6 including bell mouth 5. The blower main body 6 has a frame shape, and the outer shape in front view is a square. The motor 3 is disposed on the downstream side of the airflow with respect to the bell mouth 5. The motor 3 may be disposed upstream of the airflow with respect to the bell mouth 5.
　図３は、実施の形態１に係る軸流送風機の正面図である。図４は、実施の形態１に係る軸流送風機の断面図である。なお、図４においては、ブレード１ａは子午面形状で図示している。ベルマウス５は、吸い込み曲面５１、ストレート部５３及び吐き出し曲面５２を有する。吸い込み曲面５１は、気流の上流側に位置し、回転軸ＡＸの軸方向において気流の下流側ほど流路が狭くなっている。吐き出し曲面５２は、気流の下流側に位置し、回転軸ＡＸの軸方向において気流の下流側ほど流路が広くなっている。一般的には、ベルマウス５は、吸い込み曲面５１の曲率半径Ｒ１の方が吐き出し曲面５２の曲率半径Ｒ２よりも大きい。 FIG. 3 is a front view of the axial blower according to the first embodiment. FIG. 4 is a cross-sectional view of the axial blower according to the first embodiment. In FIG. 4, the blade 1a is shown in a meridian shape. The bell mouth 5 has a suction curved surface 51, a straight portion 53, and a discharge curved surface 52. The suction curved surface 51 is located on the upstream side of the airflow, and the flow path is narrower toward the downstream side of the airflow in the axial direction of the rotation axis AX. The discharge curved surface 52 is located on the downstream side of the airflow, and the flow path becomes wider toward the downstream side of the airflow in the axial direction of the rotation axis AX. In general, in the bell mouth 5, the radius of curvature R1 of the suction curved surface 51 is larger than the radius of curvature R2 of the discharge curved surface 52.
　送風機本体６の正面視での外形の一辺の長さをＬとし、回転翼１の外径をＤとし、ベルマウス５の吸い込み曲面５１の外径をＤＲ１とすると、軸流送風機１０は、設置性及び製造コストを鑑みて、ＤＲ１＜Ｌとなるように設計されている。吸い込み曲面５１は、送風機本体６の正面視での外形の一辺の長さＬの範囲内でできるだけ大きく形成されており、回転翼１内に円滑に気流が誘導されるようになっている。 When the length of one side of the outer shape of the blower body 6 in front view is L, the outer diameter of the rotary blade 1 is D, and the outer diameter of the suction curved surface 51 of the bell mouth 5 is DR1, the axial flow fan 10 is installed. Considering the characteristics and manufacturing cost, it is designed so that DR1 <L. The suction curved surface 51 is formed as large as possible within the range of the length L of one side of the outer shape of the blower body 6 when viewed from the front, so that airflow is smoothly induced in the rotary blade 1.
　実施の形態１に係る軸流送風機１０の回転翼１は、外径Ｄが２６０ｍｍである。回転翼１は、外周後縁端Ｉがベルマウス５のストレート部５３と吐き出し曲面５２との境界部付近に位置している。また、回転翼１の翼前縁部１ｂ及び翼外縁部１ｄは、ベルマウス５の吸い込み曲面５１よりも気流の上流側に突出している。 Rotating blade 1 of axial blower 10 according to Embodiment 1 has an outer diameter D of 260 mm. The outer peripheral trailing edge I of the rotor blade 1 is located near the boundary between the straight portion 53 of the bell mouth 5 and the discharge curved surface 52. Further, the blade leading edge portion 1 b and the blade outer edge portion 1 d of the rotor blade 1 protrude from the suction curved surface 51 of the bell mouth 5 to the upstream side of the airflow.
　回転翼１の翼前縁部１ｂ及び翼外縁部１ｄが、ベルマウス５の吸い込み曲面５１よりも気流の上流側に突出しているため、回転翼１には翼前縁部１ｂだけでなく翼外縁部１ｄからも空気が流入する。したがって、回転翼１に流入する空気の流路の断面積が増加し、回転翼１に流入する気流の速度が低下する。気流の速度が低下することにより、気流の乱れが低減され、低騒音化が実現される。 Since the blade leading edge portion 1b and the blade outer edge portion 1d of the rotary blade 1 protrude upstream of the air flow from the suction curved surface 51 of the bell mouth 5, not only the blade leading edge portion 1b but also the blade outer edge is provided on the rotary blade 1. Air also flows from the portion 1d. Therefore, the cross-sectional area of the flow path of the air flowing into the rotary blade 1 increases, and the speed of the airflow flowing into the rotary blade 1 decreases. By reducing the speed of the airflow, the turbulence of the airflow is reduced and the noise is reduced.
　ストレート部５３は、静圧が加わった際に空気が逆流することを防止する。 The straight part 53 prevents air from flowing backward when static pressure is applied.
　吐き出し曲面５２は、回転翼１から流出する空気流に含まれる遠心方向の流れを回転翼１の外に円滑に流出させる。さらに、吐き出し曲面５２は、静圧を上昇させるディフューザの役割も果たす。 The discharge curved surface 52 allows the flow in the centrifugal direction included in the air flow flowing out from the rotor blade 1 to smoothly flow out of the rotor blade 1. Further, the discharge curved surface 52 also serves as a diffuser that increases the static pressure.
　実施の形態１に係る軸流送風機１０において、回転翼１の外径Ｄ及びベルマウス５の吸い込み曲面５１の曲率半径Ｒ１は、Ｒ１／Ｄ≦０．０５の関係を満たす。また、ベルマウス５の吸い込み曲面５１の上流端５１ａでの接線ＴＬが回転軸ＡＸと垂直となるまで吸い込み曲面５１を延長したときのベルマウス５の吸い込み曲面５１の外径ＤＲ１’と、ベルマウス５の吸い込み曲面５１の外径ＤＲ１との差分をＲ１’とすると、０＜Ｒ１’／Ｒ１≦０．５０５の関係を満たす。 In the axial flow fan 10 according to the first embodiment, the outer diameter D of the rotary blade 1 and the radius of curvature R1 of the suction curved surface 51 of the bell mouth 5 satisfy the relationship of R1 / D ≦ 0.05. Further, the outer diameter DR1 ′ of the suction curved surface 51 of the bell mouth 5 when the suction curved surface 51 is extended until the tangent TL at the upstream end 51a of the suction curved surface 51 of the bell mouth 5 becomes perpendicular to the rotation axis AX, and the bell mouth When the difference from the outer diameter DR1 of the suction curved surface 51 of 5 is R1 ′, the relationship 0 <R1 ′ / R1 ≦ 0.505 is satisfied.
　実施の形態１に係る軸流送風機１０のベルマウス５の吸い込み曲面５１は、外径ＤＲ１’の吸い込み曲面５１’の外周から長さＲ１’の部分を除去した形状であり、外径がＤＲ１であると見なすことができる。すなわち、実施の形態１に係る軸流送風機１０は、外径ＤＲ１’の吸い込み曲面５１’の外周から長さＲ１’の部分を除去することで、ベルマウス５の吸い込み曲面５１の外径がＤＲ１とされていると見なすことができる。以下、外径がＤＲ１’の吸い込み曲面５１’から除去されたと見なす部分をカット部という。また、カット部の長さをカット長さという。したがって、実施の形態１においては、カット長さはＲ１’である。 The suction curved surface 51 of the bell mouth 5 of the axial flow fan 10 according to the first embodiment has a shape obtained by removing the portion of the length R1 ′ from the outer periphery of the suction curved surface 51 ′ of the outer diameter DR1 ′, and the outer diameter is DR1. Can be considered. That is, the axial flow fan 10 according to the first embodiment removes the portion of the length R1 ′ from the outer periphery of the suction curved surface 51 ′ having the outer diameter DR1 ′, so that the outer diameter of the suction curved surface 51 of the bell mouth 5 is DR1. It can be considered that. Hereinafter, the portion considered to be removed from the suction curved surface 51 ′ having the outer diameter of DR 1 ′ is referred to as a cut portion. The length of the cut part is called the cut length. Therefore, in Embodiment 1, the cut length is R1 '.
　カット部が、送風機本体６の正面視での外形の一辺よりもはみ出す部分ΔＬを含む場合、ベルマウス５の吸い込み曲面５１の外径ＤＲ１は、送風機本体６の一辺の長さＬよりも小さくなる。上記のように、０＜Ｒ１’／Ｒ１≦０．５０５とすることで、ベルマウス５は、吸い込み曲面５１の曲率半径Ｒ１を大きくするとともに、送風機本体６の正面視での外形よりも小さくできる。 When the cut portion includes a portion ΔL that protrudes beyond one side of the outer shape of the blower body 6 when viewed from the front, the outer diameter DR1 of the suction curved surface 51 of the bell mouth 5 is smaller than the length L of one side of the blower body 6. . As described above, by setting 0 <R1 ′ / R1 ≦ 0.505, the bell mouth 5 can increase the radius of curvature R1 of the suction curved surface 51 and can be smaller than the outer shape of the blower body 6 in front view. .
　図５は、実施の形態１に係る軸流送風機のブレードの形状を示す平面図である。図６は、実施の形態１に係る軸流送風機のブレードの断面図である。図６は、回転軸ＡＸ及び翼内縁部１ｅを通る平面に沿った平面におけるブレード１ａの翼断面を示している。ブレード１ａは、回転軸ＡＸ及び翼内縁部１ｅを通る翼断面において外周側と内周側との間に変曲点ＩＰを有している。ブレード１ａは、変曲点ＩＰよりもボス２に近い内周側では、気流の上流側に凸の翼断面であり、変曲点ＩＰよりもボス２から離れた外周側では気流の下流側に凸の翼断面である。ブレード１ａは、変曲点ＩＰよりも内周側での翼断面の曲率はＲ１ｂである。ブレード１ａは、変曲点ＩＰよりも外周側での翼断面の曲率はＲ２ｂである。ブレード１ａの曲率半径Ｒ１ｂ，Ｒ２ｂは、翼前縁部１ｂから翼後縁部１ｃにかけて連続的に変化している。 FIG. 5 is a plan view showing the shape of the blade of the axial blower according to the first embodiment. FIG. 6 is a cross-sectional view of the blade of the axial blower according to the first embodiment. FIG. 6 shows a blade cross section of the blade 1a in a plane along a plane passing through the rotation axis AX and the blade inner edge 1e. The blade 1a has an inflection point IP between the outer peripheral side and the inner peripheral side in the blade cross section passing through the rotation axis AX and the blade inner edge 1e. The blade 1a has a blade cross-section convex toward the upstream side of the airflow on the inner peripheral side closer to the boss 2 than the inflection point IP, and on the downstream side of the airflow on the outer peripheral side farther from the boss 2 than the inflection point IP. It is a convex wing cross section. In the blade 1a, the curvature of the blade cross section on the inner peripheral side from the inflection point IP is R1b. In the blade 1a, the curvature of the blade cross section on the outer peripheral side from the inflection point IP is R2b. The curvature radii R1b and R2b of the blade 1a continuously change from the blade leading edge 1b to the blade trailing edge 1c.
　図７、図８、図９及び図１０は、実施の形態１に係る軸流送風機のブレードの翼断面形状と気流の状態とを示す図である。図７は、図５中の翼断面位置Ｏ－Ｄ１での回転軸ＡＸを通る径方向に沿った平面における翼断面形状を示している。図８は、図５中の翼断面位置Ｏ－Ｄ２での回転軸ＡＸを通る径方向に沿った平面における翼断面形状を示している。図９は、図５中の翼断面位置Ｏ－Ｄ３での回転軸ＡＸを通る径方向に沿った平面における翼断面形状を示している。図１０は、図５中の翼断面位置Ｏ－Ｄ４での回転軸ＡＸを通る径方向に沿った平面における翼断面形状を示している。ブレード１ａは、翼断面位置Ｏ－Ｄ１においては、気流の上流側にθ（Ｏ－Ｄ１）傾斜しているが、翼断面位置Ｏ－Ｄ２での傾斜角θ（Ｏ－Ｄ２）、翼断面位置Ｏ－Ｄ３での傾斜角θ（Ｏ－Ｄ３）及び翼断面位置Ｏ－Ｄ４での傾斜角θ（Ｏ－Ｄ４）は、翼後縁部１ｃに近づくほど気流の下流側に傾斜するように傾きが変化している。回転翼１の翼前縁部１ｂ付近では、翼断面と平行な横流れ９が存在するが、回転翼１の側面がベルマウス５よりも気流の上流側に突出しているため、横流れ９を回転翼１に取り込むことができる。回転翼１の翼後縁部１ｃに近づくに従い、翼断面が全体的に気流の下流側に傾斜するように傾斜が変化しており、遠心方向に流れようとする半径方向の流れ１１が圧力の上昇に伴って回転翼１の外に漏れることを抑制することによって気流を昇圧させる。 7, 8, 9, and 10 are diagrams illustrating blade cross-sectional shapes and airflow states of the blades of the axial blower according to Embodiment 1. FIG. FIG. 7 shows the blade cross-sectional shape in a plane along the radial direction passing through the rotation axis AX at the blade cross-section position O-D1 in FIG. FIG. 8 shows the blade cross-sectional shape in a plane along the radial direction passing through the rotation axis AX at the blade cross-section position OD2 in FIG. FIG. 9 shows a blade cross-sectional shape in a plane along the radial direction passing through the rotation axis AX at the blade cross-sectional position O-D3 in FIG. FIG. 10 shows the blade cross-sectional shape in a plane along the radial direction passing through the rotation axis AX at the blade cross-section position OD4 in FIG. The blade 1a is inclined at the blade cross-sectional position O-D1 by θ (O-D1) on the upstream side of the airflow. However, the blade 1a has an inclination angle θ (O-D2) at the blade cross-section position O-D2 and the blade cross-section position. The inclination angle θ (O-D3) at O-D3 and the inclination angle θ (O-D4) at the blade cross-sectional position O-D4 are inclined so as to incline toward the downstream side of the airflow as they approach the blade trailing edge 1c. Has changed. In the vicinity of the blade leading edge 1b of the rotary blade 1, there is a lateral flow 9 parallel to the blade cross section. However, since the side surface of the rotary blade 1 protrudes upstream of the airflow from the bell mouth 5, the lateral flow 9 is 1 can be captured. As the blade 1 approaches the blade trailing edge 1c of the rotor blade 1, the inclination changes so that the blade section as a whole is inclined to the downstream side of the airflow, and the radial flow 11 that is going to flow in the centrifugal direction is the pressure. The airflow is boosted by suppressing leakage from the rotor blade 1 as it rises.
　図７及び図８に示すように、ブレード１ａは、回転方向の前方寄りでは、内周側がボス２から離れた翼断面となっている。 As shown in FIGS. 7 and 8, the blade 1a has a blade cross section with the inner peripheral side away from the boss 2 near the front in the rotational direction.
　回転翼１が回転すると、ブレード１ａの圧力面と負圧面との圧力差により、翼端渦７が形成される。翼端渦７がブレード１ａの負圧面、隣接する別のブレード１ａ又はベルマウス５と干渉すると、軸流送風機１０の騒音特性は低下する。ブレード１ａは、内周側では気流の上流側に凸で、外周側では気流の下流側に凸のＳ字形状の翼断面であるため、翼端渦７の発生を抑制し、昇圧した流れが回転翼１の外に漏れることを防止できる。 When the rotating blade 1 rotates, a blade tip vortex 7 is formed due to the pressure difference between the pressure surface and the suction surface of the blade 1a. When the blade tip vortex 7 interferes with the suction surface of the blade 1a, another blade 1a adjacent to the blade 1a or the bell mouth 5, the noise characteristics of the axial blower 10 deteriorate. Since the blade 1a has an S-shaped blade cross section that is convex on the upstream side of the airflow on the inner peripheral side and convex on the downstream side of the airflow on the outer peripheral side, the generation of the blade vortex 7 is suppressed, It is possible to prevent leakage from the rotor 1.
　図１１は、実施の形態１に係る軸流送風機のブレードの翼断面位置と曲率半径との関係を示す図である。ブレード１ａの内周側の曲率半径Ｒ１ｂは、翼前縁部１ｂから翼後縁部１ｃに向かって漸減する。一方、ブレード１ａの外周側の曲率半径Ｒ２ｂは、翼前縁部１ｂから翼断面位置Ｏ－Ｄ３までは漸減し、翼断面位置Ｏ－Ｄ３から翼後縁部１ｃにかけて漸増する。 FIG. 11 is a diagram showing the relationship between the blade cross-sectional position and the radius of curvature of the blade of the axial blower according to the first embodiment. The radius of curvature R1b on the inner peripheral side of the blade 1a gradually decreases from the blade leading edge 1b toward the blade trailing edge 1c. On the other hand, the radius of curvature R2b on the outer peripheral side of the blade 1a gradually decreases from the blade leading edge 1b to the blade cross-sectional position O-D3, and gradually increases from the blade cross-sectional position O-D3 to the blade trailing edge 1c.
　図１２は、実施の形態１に係る軸流送風機のベルマウスの吸い込み曲面の半径と回転翼の外径との比と、静圧が０となる開放点での風量との関係を示す図である。なお、図１２においては、開放点での風量が１００％となるように正規化して風量を示している。図１２に示すように、ベルマウス５の吸い込み曲面５１の曲率半径Ｒ１と回転翼１の外径Ｄとの比Ｒ１／Ｄが大きくなるほど、風量は増加する傾向である。 FIG. 12 is a diagram showing the relationship between the ratio of the radius of the suction curved surface of the bell mouth of the axial flow fan according to Embodiment 1 and the outer diameter of the rotor blades and the air volume at the open point where the static pressure becomes zero. is there. In FIG. 12, the air volume is normalized so that the air volume at the open point is 100%. As shown in FIG. 12, the air volume tends to increase as the ratio R1 / D between the radius of curvature R1 of the suction curved surface 51 of the bell mouth 5 and the outer diameter D of the rotor blade 1 increases.
　図１３は、実施の形態１に係る軸流送風機のベルマウスの吸い込み曲面の半径と回転翼の外径との比と、開放点での正面騒音の騒音レベルとの関係を示す図である。なお、図１３においては、開放点での騒音レベルが０ｄＢとなるように正規化して騒音レベルを示している。ベルマウス５の吸い込み曲面５１の曲率半径Ｒ１と回転翼１の外径Ｄとの比Ｒ１／Ｄが大きくなる方が正面騒音の騒音レベルは小さくなるが、風量とは異なり、ある程度の大きさまで騒音レベルが小さくなると、Ｒ１／Ｄが大きくなっても正面騒音の騒音レベルはほとんど変化しなくなる。 FIG. 13 is a diagram showing the relationship between the ratio of the radius of the suction curved surface of the bell mouth of the axial flow fan according to Embodiment 1 and the outer diameter of the rotor blade and the noise level of the front noise at the open point. In FIG. 13, the noise level is normalized so that the noise level at the open point is 0 dB. As the ratio R1 / D of the radius of curvature R1 of the suction curved surface 51 of the bell mouth 5 and the outer diameter D of the rotor blade 1 increases, the noise level of the front noise decreases, but unlike the air volume, the noise is reduced to a certain level. When the level decreases, the noise level of the front noise hardly changes even if R1 / D increases.
　図１４は、実施の形態１に係る軸流送風機のベルマウスの吸い込み曲面の半径と回転翼の外径との比と、開放点での斜め４５°方向の騒音の騒音レベルとの関係を示す図である。なお、図１４においては、開放点での騒音レベルが０ｄＢとなるように正規化して騒音レベルを示している。正面騒音の騒音レベルと同様に、Ｒ１／Ｄが大きくなる方が騒音レベルは小さくなる。ただし、開放点での斜め４５°方向の騒音の騒音レベルは、ある程度の大きさで下げ止まらない点では、正面騒音の騒音レベルとは相違している。 FIG. 14 shows the relationship between the ratio of the radius of the suction curved surface of the bell mouth of the axial flow fan according to Embodiment 1 and the outer diameter of the rotor blade, and the noise level of the noise in the oblique 45 ° direction at the open point. FIG. In FIG. 14, the noise level is normalized so that the noise level at the open point becomes 0 dB. Similar to the noise level of the front noise, the noise level decreases as R1 / D increases. However, the noise level of the 45 ° diagonal noise at the open point is different from the noise level of the front noise in that it does not stop at a certain level.
　図１２、図１３及び図１４より、ベルマウス５の吸い込み曲面５１の曲率半径Ｒ１と回転翼１の外径Ｄとの比Ｒ１／Ｄが大きくなるほど、風量及び騒音特性が向上することが分かる。 12, 13, and 14, it can be seen that the air volume and the noise characteristics are improved as the ratio R1 / D between the curvature radius R1 of the suction curved surface 51 of the bell mouth 5 and the outer diameter D of the rotor blade 1 is increased.
　図１５は、実施の形態１に係る軸流送風機のベルマウスの吸い込み曲面のカット長さとベルマウスの吸い込み曲面の曲率半径との比と、開放点での風量との関係を示す図である。なお、図１５においては、開放点での風量が１００％となるように正規化して風量を示している。図１５に示すように、ベルマウス５の吸い込み曲面５１のカット長さＲ１’とベルマウス５の吸い込み曲面５１の曲率半径Ｒ１との比Ｒ１’／Ｒ１が０．４５以下では、風量はＲ１’／Ｒ１に依存しない。また、Ｒ１’／Ｒ１が０．４５を超えると、急激に風量が減少する。 FIG. 15 is a graph showing the relationship between the ratio between the cut length of the suction surface of the bell mouth of the axial flow fan according to the first embodiment and the radius of curvature of the suction surface of the bell mouth, and the air volume at the open point. In FIG. 15, the airflow is normalized so that the airflow at the open point becomes 100%. As shown in FIG. 15, when the ratio R1 ′ / R1 between the cut length R1 ′ of the suction curved surface 51 of the bell mouth 5 and the radius of curvature R1 of the suction curved surface 51 of the bell mouth 5 is 0.45 or less, the air volume is R1 ′. It does not depend on / R1. On the other hand, when R1 '/ R1 exceeds 0.45, the air volume rapidly decreases.
　図１６は、実施の形態１に係る軸流送風機のベルマウスの吸い込み曲面のカット長さとベルマウスの吸い込み曲面の曲率半径との比と、開放点での正面騒音の騒音レベルとの関係を示す図である。なお、図１６においては、開放点での騒音レベルが０ｄＢとなるように正規化して騒音レベルを示している。図１６に示すように、Ｒ１’／Ｒ１が０．４５以下では、正面騒音の騒音レベルは低下する。しかし、Ｒ１’／Ｒ１が０．５を超えると、正面騒音の騒音レベルはＲ１’／Ｒ１＝０の場合よりも大きくなる。 FIG. 16 shows the relationship between the ratio between the cut length of the suction surface of the bell mouth of the axial flow fan according to the first embodiment and the radius of curvature of the suction surface of the bell mouth and the noise level of the front noise at the open point. FIG. In FIG. 16, the noise level is normalized so that the noise level at the open point is 0 dB. As shown in FIG. 16, when R1 '/ R1 is 0.45 or less, the noise level of the front noise decreases. However, when R1 '/ R1 exceeds 0.5, the noise level of the front noise becomes larger than that in the case of R1' / R1 = 0.
　図１７は、実施の形態１に係る軸流送風機のベルマウスの吸い込み曲面のカット長さとベルマウスの吸い込み曲面の曲率半径との比と、開放点での斜め４５°方向の騒音の騒音レベルとの関係を示す図である。なお、図１７においては、開放点での騒音レベルが０ｄＢとなるように正規化して騒音レベルを示している。正面騒音の騒音レベルと同様に、Ｒ１’／Ｒ１が０．４５以下では、騒音の騒音レベルは低下する。しかし、Ｒ１’／Ｒ１が０．５を超えると、騒音の騒音レベルはＲ１’／Ｒ１＝０の場合よりも大きくなる。 FIG. 17 shows the ratio between the cut length of the suction surface of the bell mouth of the axial flow fan according to the first embodiment and the radius of curvature of the suction surface of the bell mouth, and the noise level of the oblique 45 ° direction noise at the open point. It is a figure which shows the relationship. In FIG. 17, the noise level is normalized so that the noise level at the open point is 0 dB. Similar to the noise level of the front noise, when R1 '/ R1 is 0.45 or less, the noise level of the noise decreases. However, when R1 '/ R1 exceeds 0.5, the noise level of the noise becomes larger than when R1' / R1 = 0.
　図１５、図１６及び図１７より、ベルマウス５の吸い込み曲面５１のカット長さＲ１’と、ベルマウス５の吸い込み曲面５１の曲率半径Ｒ１との比Ｒ１’／Ｒ１と、風量又は騒音の騒音レベルとの間には、変化割合が適切な範囲があることが分かる。０＜Ｒ１’／Ｒ１≦０．５０５の範囲内であれば、カット部を削除する前の吸い込み曲面の外径がＤＲ１’のベルマウスに相当するＲ１’／Ｒ１＝０での騒音に対する変化が＋０．５（ｄＢ）以内となり、低騒音化を実現できる。 15, 16, and 17, the ratio R1 ′ / R1 between the cut length R1 ′ of the suction curved surface 51 of the bell mouth 5 and the radius of curvature R1 of the suction curved surface 51 of the bell mouth 5, and the air volume or noise noise It can be seen that there is an appropriate range of change ratio between levels. If it is within the range of 0 <R1 ′ / R1 ≦ 0.505, there is a change with respect to noise at R1 ′ / R1 = 0 corresponding to a bell mouth whose outer diameter of the suction curved surface before deleting the cut portion is DR1 ′. It is within +0.5 (dB), and low noise can be realized.
　図１８は、実施の形態１に係る軸流送風機の風量と静圧との関係を、ベルマウスの吸い込み曲面の曲率半径と回転翼の外径との比ごとに示す図である。図１９は、実施の形態１に係る軸流送風機の風量と正面騒音の騒音レベルとの関係を、ベルマウスの吸い込み曲面の曲率半径と回転翼の外径との比ごとに示す図である。図２０は、実施の形態１に係る軸流送風機の風量と斜め騒音の騒音レベルとの関係を、ベルマウスの吸い込み曲面の曲率半径と回転翼の外径との比ごとに示す図である。図１８、図１９及び図２０に示すように、ベルマウス５の吸い込み曲面５１の曲率半径Ｒ１と回転翼１の外径Ｄとの比Ｒ１／Ｄが大きいほど、静圧が０となる開放点での特性のみならず、他の実用的な風量の範囲においても静圧が高く騒音の騒音レベルは小さくなる。 FIG. 18 is a diagram showing the relationship between the air volume and static pressure of the axial blower according to Embodiment 1 for each ratio of the radius of curvature of the suction surface of the bell mouth and the outer diameter of the rotor blade. FIG. 19 is a diagram showing the relationship between the air volume of the axial flow fan and the noise level of the front noise according to the first embodiment for each ratio between the radius of curvature of the suction surface of the bell mouth and the outer diameter of the rotor blade. FIG. 20 is a diagram showing the relationship between the air volume of the axial flow fan and the noise level of the oblique noise according to Embodiment 1 for each ratio of the radius of curvature of the suction surface of the bell mouth and the outer diameter of the rotor blade. As shown in FIGS. 18, 19, and 20, as the ratio R1 / D between the radius of curvature R1 of the suction curved surface 51 of the bell mouth 5 and the outer diameter D of the rotor blade 1 increases, the opening point at which the static pressure becomes zero is increased. The static pressure is high and the noise level is low in other practical airflow ranges as well.
　図２１は、実施の形態１に係る軸流送風機の風量と静圧との関係を、ベルマウスの吸い込み曲面のカット長さとベルマウスの吸い込み曲面の曲率半径との比ごとに示す図である。図２２は、実施の形態１に係る軸流送風機の風量と正面騒音の騒音レベルとの関係を、ベルマウスの吸い込み曲面のカット長さとベルマウスの吸い込み曲面の曲率半径との比ごとに示す図である。図２３は、実施の形態１に係る軸流送風機の風量と斜め騒音の騒音レベルとの関係を、ベルマウスの吸い込み曲面のカット長さとベルマウスの吸い込み曲面の曲率半径との比ごとに示す図である。図２１、図２２、及び図２３に示すように、Ｒ１’／Ｒ１が適正範囲であるＲ１’／Ｒ１＝０．４４７では、静圧が０となる開放点での特性のみならず、他の実用的な風量の範囲においても静圧はＲ１’／Ｒ１＝０の状態と殆ど変わらず、騒音については改善する。また、Ｒ１’／Ｒ１が適正範囲外であるＲ１’／Ｒ１＝０．７３３では、開放点での特性のみならず、他の実用的な風量の範囲においても静圧及び騒音特性は低下する。 FIG. 21 is a diagram showing the relationship between the air volume and static pressure of the axial flow fan according to Embodiment 1 for each ratio between the cut length of the bellmouth suction curved surface and the radius of curvature of the bellmouth suction curved surface. FIG. 22 is a diagram showing the relationship between the air volume of the axial flow fan and the noise level of the front noise according to the first embodiment for each ratio between the cut length of the bellmouth suction curved surface and the radius of curvature of the bellmouth suction curved surface. It is. FIG. 23 is a diagram showing the relationship between the air volume of the axial flow fan and the noise level of the oblique noise according to the first embodiment for each ratio between the cut length of the bell mouth suction curved surface and the radius of curvature of the bell mouth suction curved surface. It is. As shown in FIG. 21, FIG. 22, and FIG. 23, R1 ′ / R1 = 0.447 where R1 ′ / R1 is an appropriate range, not only the characteristics at the release point where the static pressure becomes 0, but also other Even in a practical air volume range, the static pressure is almost the same as the state of R1 ′ / R1 = 0, and noise is improved. When R1 '/ R1 is outside the proper range, R1' / R1 = 0.733, the static pressure and noise characteristics decrease not only at the open point, but also at other practical airflow ranges.
　図２４は、実施の形態１に係る軸流送風機のベルマウスの吸い込み曲面の曲率半径の違いによる風量と静圧との関係の差を示す図である。図２５は、実施の形態１に係る軸流送風機のベルマウスの吸い込み曲面の曲率半径の違いによる風量と正面騒音の騒音レベルとの関係の差を示す図である。図２６は、実施の形態１に係る軸流送風機のベルマウスの吸い込み曲面の曲率半径の違いによる風量と斜め騒音の騒音レベルとの関係の差を示す図である。Ｒ１１＞Ｒ１２である。Ｒ１１のグラフは、Ｒ１’／Ｒ１１＝０．３３３である。Ｒ１２のグラフは、Ｒ１’／Ｒ１２＝０である。図２４、図２５及び図２６に示すように、ベルマウス５の吸い込み曲面５１の曲率半径が大きいほうが、風量、静圧及び騒音特性が向上する。 FIG. 24 is a diagram showing the difference in the relationship between the air volume and the static pressure due to the difference in the curvature radius of the suction curved surface of the bell mouth of the axial flow fan according to the first embodiment. FIG. 25 is a diagram illustrating a difference in the relationship between the air volume and the noise level of the front noise due to the difference in the radius of curvature of the suction curved surface of the bell mouth of the axial flow fan according to the first embodiment. FIG. 26 is a diagram illustrating the difference in the relationship between the air volume and the noise level of the oblique noise due to the difference in the radius of curvature of the suction surface of the bell mouth of the axial flow fan according to the first embodiment. R1 1 > R1 2 . The graph of R1 1 is R1 ′ / R1 1 = 0.333. The graph of R1 2 is R1 ′ / R1 2 = 0. As shown in FIGS. 24, 25 and 26, the larger the radius of curvature of the suction curved surface 51 of the bell mouth 5, the better the air volume, static pressure and noise characteristics.
　実施の形態１に係る軸流送風機１０は、ベルマウス５の吸い込み曲面５１の曲率半径Ｒ１と回転翼１の外径Ｄとの比Ｒ１／Ｄ≦０．０５であるため、ベルマウス５の吸い込み曲面５１で発生した気流の乱れが回転翼１に吸い込まれて騒音が増大することを抑制できる。また、ベルマウス５の吸い込み曲面５１の外径は、送風機本体６の一辺の長さ以下であるため、装置サイズの増大を防ぐことができる。また、ベルマウス５の吸い込み曲面５１の外径は、送風機本体６の一辺の長さ以下であるため、送風機本体６とは別部品化したベルマウス５を送風機本体６と組み立てる必要がなく、作業工数の増大を防ぐことができる。 In the axial blower 10 according to the first embodiment, since the ratio R1 / D ≦ 0.05 between the radius of curvature R1 of the suction curved surface 51 of the bell mouth 5 and the outer diameter D of the rotor blade 1, the suction of the bell mouth 5 is performed. It can suppress that the disturbance of the airflow which generate | occur | produced on the curved surface 51 is sucked into the rotary blade 1, and noise increases. Moreover, since the outer diameter of the suction curved surface 51 of the bell mouth 5 is equal to or less than the length of one side of the blower body 6, an increase in the size of the apparatus can be prevented. Further, since the outer diameter of the suction curved surface 51 of the bell mouth 5 is equal to or less than the length of one side of the blower body 6, it is not necessary to assemble the bell mouth 5 separated from the blower body 6 with the blower body 6. An increase in man-hours can be prevented.
　以上の実施の形態に示した構成は、本発明の内容の一例を示すものであり、別の公知の技術と組み合わせることも可能であるし、本発明の要旨を逸脱しない範囲で、構成の一部を省略、変更することも可能である。 The configuration described in the above embodiment shows an example of the contents of the present invention, and can be combined with another known technique, and can be combined with other configurations without departing from the gist of the present invention. It is also possible to omit or change the part.
　１　回転翼、１ａ　ブレード、１ｂ　翼前縁部、１ｃ　翼後縁部、１ｄ　翼外縁部、１ｅ　翼内縁部、２　ボス、３　モータ、５　ベルマウス、６　送風機本体、７　翼端渦、９　横流れ、１０　軸流送風機、５１，５１’　吸い込み曲面、５１ａ　上流端、５２　吐き出し曲面。 1 rotor blade, 1a blade, 1b blade leading edge, 1c blade trailing edge, 1d blade outer edge, 1e blade inner edge, 2 boss, 3 motor, 5 bell mouth, 6 blower body, 7 blade tip vortex, 9 transverse flow 10, axial blower, 51, 51 'suction curved surface, 51a upstream end, 52 discharge curved surface.

Claims (5)

  1. 　複数のブレードを備えた回転翼と、
    　前記回転翼を回転させて気流を発生させるモータと、
    　前記回転翼の回転軸と直交する方向から前記回転翼を囲う枠状のベルマウスとを有し、
    　前記ベルマウスは、前記気流の上流側に、前記回転軸の軸方向において前記気流の下流側ほど狭くなる吸い込み曲面を有し、
    　前記回転翼の外径をＤとし、前記吸い込み曲面の曲率半径をＲ１としたとき、Ｒ１／Ｄ≦０．０５であることを特徴とする軸流送風機。     A rotor blade with a plurality of blades;
    A motor for generating an air flow by rotating the rotary blade;
    A frame-shaped bell mouth that surrounds the rotor blade from a direction orthogonal to the rotation axis of the rotor blade;
    The bell mouth has a suction curved surface that becomes narrower toward the downstream side of the airflow in the axial direction of the rotating shaft on the upstream side of the airflow,
    An axial blower characterized in that R1 / D ≦ 0.05, where D is the outer diameter of the rotor blade and R1 is the radius of curvature of the suction curved surface.
  2. 　前記吸い込み曲面の外径と、前記吸い込み曲面の上流端における接線が前記回転軸と直交する位置まで前記吸い込み曲面を延長した位置と前記回転軸との距離を２倍した長さとの差をＲ１’としたとき、０＜Ｒ１'／Ｒ１≦０．５０５であることを特徴とする請求項１に記載の軸流送風機。 The difference between the outer diameter of the suction curved surface and the length obtained by doubling the distance between the rotational axis and the position where the suction curved surface is extended to the position where the tangent at the upstream end of the suction curved surface is orthogonal to the rotational axis is R1 ′. The axial flow fan according to claim 1, wherein 0 <R1 '/ R1≤0.505.
  3. 　前記回転軸を通る径方向に沿った平面における前記ブレードの翼断面は、回転方向において前方となる翼前縁部において前記気流の上流側に傾斜しており、回転方向において後方となる翼後縁部に近づくにしたがって、傾斜角は前記気流の下流側に傾斜するように連続的に変化していることを特徴とする請求項１又は２に記載の軸流送風機。 The blade cross-section of the blade in a plane along the radial direction passing through the rotation axis is inclined to the upstream side of the airflow at the blade leading edge that is forward in the rotation direction, and the blade trailing edge that is rearward in the rotation direction The axial flow fan according to claim 1 or 2, wherein the inclination angle continuously changes so as to be inclined toward the downstream side of the airflow as it approaches the portion.
  4. 　前記ブレードは、翼断面が凸となる方向が変化する変曲点を外周側と内周側との間に有しており、
    　前記ブレードの翼断面は、前記変曲点よりも内周側では、前記気流の上流側に凸であり、前記変曲点よりも外周側では前記気流の下流側に凸であることを特徴とする請求項１から３のいずれか１項に記載の軸流送風機。     The blade has an inflection point between the outer peripheral side and the inner peripheral side where the direction in which the blade section becomes convex changes.
    The blade cross section of the blade is convex on the upstream side of the airflow on the inner peripheral side of the inflection point, and convex on the downstream side of the airflow on the outer peripheral side of the inflection point. The axial-flow fan according to any one of claims 1 to 3.
  5. 　前記ブレードの前記変曲点よりも外周側の曲率半径は、翼前縁部から翼後縁部に向かって漸減したのちに極小値をとってから漸増し、
    　前記ブレードの前記変曲点よりも内周側の曲率半径は、前記翼前縁部から前記翼後縁部に向かって漸減することを特徴とする請求項４に記載の軸流送風機。     The radius of curvature on the outer periphery side of the inflection point of the blade gradually decreases from the blade leading edge to the blade trailing edge and then gradually increases after taking a minimum value,
    5. The axial blower according to claim 4, wherein a radius of curvature of the blade on the inner peripheral side with respect to the inflection point gradually decreases from the blade leading edge toward the blade trailing edge.
PCT/JP2018/003704 2018-02-02 2018-02-02 Axial flow fan WO2019150567A1 (en)

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JP2019568534A JP6914371B2 (en) 2018-02-02 2018-02-02 Axial blower
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