JP2702755B2 - Axial fan - Google Patents
Axial fanInfo
- Publication number
- JP2702755B2 JP2702755B2 JP63273580A JP27358088A JP2702755B2 JP 2702755 B2 JP2702755 B2 JP 2702755B2 JP 63273580 A JP63273580 A JP 63273580A JP 27358088 A JP27358088 A JP 27358088A JP 2702755 B2 JP2702755 B2 JP 2702755B2
- Authority
- JP
- Japan
- Prior art keywords
- fan
- blade
- axial fan
- filter
- axial
- Prior art date
- Legal status (The legal status 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 status listed.)
- Expired - Fee Related
Links
Landscapes
- Structures Of Non-Positive Displacement Pumps (AREA)
Description
【発明の詳細な説明】 産業上の利用分野 本発明は、換気送風機器等に使用される軸流ファンに
関するものである。Description: BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an axial fan used for a ventilation blower or the like.
従来の技術 従来、この種の軸流ファンは、第３図および第４図に
示すようにブレード３の周方向断面は軸流ファン７のど
の半径方向位置においても、一円弧翼または複数の円弧
翼または薄肉翼型であり、半径方向位置の変化により弦
長ｌが異なるだけで、曲率や肉厚は弦長ｌに比例して変
化させる構成であった。2. Description of the Related Art Conventionally, as shown in FIGS. 3 and 4, a circumferential section of a blade 3 has a circular arc blade or a plurality of circular arcs at any radial position of the axial fan 7 as shown in FIGS. It is a wing or a thin wing type, and the curvature and the wall thickness are changed in proportion to the chord length l only by changing the chord length l according to the change in the radial position.
発明が解決しようとする課題 上記従来の軸流ファン７は、第４図ａに示すように吸
込口１に何もないときには、第４図ｂに示すように運転
時には、無衝突流入となるようになっているが、第５図
に示すように前記吸込口１に格子またはフィルター２が
設けられたときにはその格子またはフィルター２の後流
側の絶対速度CMは軸方向に平行ではないため、ブレード
３に対して無衝突ではなく流入角αを持って流れは流入
する。この流入角αは前記格子またはフィルター２の後
部の流れが一様でないため各ブレードおよび半径方向位
置で流入角αはすべて異なる。したがって、あらかじめ
前記ブレード３のどの場所でも無衝突流入になるよう設
計することはできない。流入角αが存在すると、前記ブ
レード３の前縁４において背面側５に大きな剥離流れ６
を生じ騒音が急上昇する課題があった。Problems to be Solved by the Invention When the conventional axial flow fan 7 has nothing in the suction port 1 as shown in FIG. 4A, it has a collisionless inflow during operation as shown in FIG. 4B. because the going on, but when the grating or filter 2 is provided in the inlet 1 as shown in Fig. 5 the absolute velocity C M of the downstream side of the grid or filter 2 are not parallel to the axial direction, The flow flows into the blade 3 not at no collision but at an inflow angle α. This inflow angle α is different at each blade and radial position because the flow behind the grid or filter 2 is not uniform. Therefore, it is not possible to design the blade 3 in advance so as to have no collision inflow at any place. When the inflow angle α exists, a large separation flow 6 on the back side 5 at the leading edge 4 of the blade 3
There is a problem that noise rises sharply.
本発明は上記従来の課題に留意し、騒音の低い軸流フ
ァンを提供することを目的とするものである。SUMMARY OF THE INVENTION An object of the present invention is to provide an axial fan having low noise while keeping the above conventional problems in mind.
課題を解決するための手段 この課題を解決するために本発明は、軸流ファンの前
面に気流の吸込口を有し、この吸込口に格子またはフィ
ルターを設けた送風機において、前記軸流ファンのブレ
ードの周方向断面の前縁の背面側に、弦長に対し、前縁
より０％〜５％離して、２％〜10％の周方向長さで、か
つ１％〜５％の曲率半径の半円状の肉厚部を設けた軸流
ファンの構成としたものである。Means for Solving the Problems In order to solve this problem, the present invention has an airflow suction port on the front surface of an axial flow fan, and in a blower provided with a lattice or a filter at the suction port, Behind the leading edge of the circumferential section of the blade, at a circumferential length of 2% to 10% and a radius of curvature of 1% to 5%, apart from the leading edge by 0% to 5% with respect to the chord length. The axial flow fan is provided with a semicircular thick portion.
作用 この構成により、格子およびフィルターより吸引され
た空気は、乱れているにもかかわらずブレートの前縁の
背面側に設けた肉厚部により剥離流れが押えられ騒音が
小さくて済むこととなる。Operation With this configuration, the air sucked from the grid and the filter is disturbed by the thick portion provided on the back surface side of the leading edge of the plate despite the disturbance, so that the noise can be reduced by suppressing the separation flow.
実 施 例 以下、本発明の一実施例を第１図および第２図にもと
づき説明する。なお従来例と同一箇所には同一番号を付
し、詳細な説明は省略する。図において、11は送風機ま
たは換気扇で吸入口１に格子またはフィルター２が設け
られている。12は軸流ファンで本体13内部に取付けられ
た電動機14のシャフト15に係止されている。Embodiment An embodiment of the present invention will be described below with reference to FIGS. 1 and 2. The same parts as those in the conventional example are denoted by the same reference numerals, and detailed description is omitted. In the figure, reference numeral 11 denotes a blower or a ventilation fan provided with a lattice or a filter 2 at an inlet 1. Numeral 12 denotes an axial fan which is locked to a shaft 15 of a motor 14 mounted inside the main body 13.
前記軸流ファン12のブレード16の周方向断面は、第１
図のように前縁４の背面側５には、弦長ｌに対し、前縁
より０％〜５％離して、２％〜10％の周方向長さで、か
つ１％〜５％の曲率半径の半円状の肉厚部17が設けられ
ている。この肉厚部17は、前記軸流ファン12の各半径位
置の弦長ｌに比例した大きさ、または弦長ｌによらず一
定の大きさで設けられている。The circumferential cross section of the blade 16 of the axial fan 12 is the first
As shown in the figure, on the back side 5 of the leading edge 4, the circumferential length of 2% to 10% and 1% to 5% of the chord length 1 are 0% to 5% apart from the leading edge. A semicircular thick portion 17 having a radius of curvature is provided. The thick portion 17 is provided with a size proportional to the chord length l at each radial position of the axial flow fan 12, or a fixed size regardless of the chord length l.
上記構成において、電動機14によって軸流ファン12が
回転すると、格子またはフィルター２より吸引された空
気は、前記格子またはフィルター２の後部で乱れを生じ
前記軸流ファン12のブレード16に対し、種々の流入角α
を持って流入する。このとき前記ブレード16の前縁４の
背面側５に剥離を生じようとするが、前記肉厚部17が設
けられているので、剥離が小さくなり騒音の発生が小さ
くてすむ。なお第６図に、肉厚部17の大きさを変えたと
きの風量および騒音の変化を示す。これにより肉厚部17
の形状の最適値を決定した。また肉厚部17の前縁よりの
距離については、弦長ｌに対し５％以内であれば性能上
の変化がなく、製造上は離す方が作りやすい。また肉厚
部17の大きさも、弦長ｌの比例した大きさと一定の大き
さで設けるのとで性能上の差がなく、製造上は一定の方
が作りやすい。In the above configuration, when the axial fan 12 is rotated by the electric motor 14, air sucked from the grid or the filter 2 causes turbulence at the rear of the grid or the filter 2, and the blades 16 of the axial fan 12 have various shapes. Inflow angle α
Inflow with. At this time, peeling is attempted to occur on the back side 5 of the front edge 4 of the blade 16, but since the thick portion 17 is provided, the peeling is small and the generation of noise is small. FIG. 6 shows changes in air volume and noise when the thickness of the thick portion 17 is changed. With this, the thick part 17
The optimal value of the shape was determined. If the distance from the leading edge of the thick portion 17 is within 5% of the chord length l, there is no change in performance, and it is easier to make the distance apart in manufacturing. Also, the thickness of the thick portion 17 is not different in performance between the case where it is provided in proportion to the chord length 1 and the case where it is provided in a fixed size.
発明の効果 以上の実施例の説明より明らかなように本発明によれ
ば、換気扇または送風機において吸入口に格子またはフ
ィルターについた場合に空気の流れの剥離が発生する軸
流ファンのブレード前縁の背面部に半円状の肉厚部を設
けることにより、流れの剥離を減少させファン回転の騒
音を減少させることができる。Effects of the Invention As is clear from the description of the above embodiments, according to the present invention, in the case of a ventilation fan or a blower, when a grid or a filter is attached to the suction port of the ventilation fan or the blade leading edge of the axial flow fan where the flow of air occurs. By providing a semicircular thick portion on the back surface, flow separation can be reduced, and noise of fan rotation can be reduced.
第１図（ａ），（ｂ）は本発明の一実施例の軸流ファン
のブレード断面図、第２図は同軸流ファンの断面図、第
３図（ａ），（ｂ），（ｃ）は従来の軸流ファンのブレ
ードの断面図、第４図（ａ）は同軸流ファンの吸込口に
格子またはフィルターがないときの断面図、第４図
（ｂ）は同軸流ファンの流入風の流れを説明する図、第
５図（ａ）は同軸流ファンの吸込口に格子またはフィル
ターがある場合の断面図、第５図（ｂ）は同軸流ファン
の流入風の流れを説明する図、第６図は肉厚部の形状と
性能との関連を示す図である。 ４……前縁、５……背面側、12……軸流ファン、16……
ブレード、17……肉厚部、18……前縁部ブレード肉厚。1 (a) and 1 (b) are sectional views of a blade of an axial fan according to an embodiment of the present invention, FIG. 2 is a sectional view of a coaxial fan, and FIGS. 3 (a), (b) and (c). ) Is a cross-sectional view of a blade of a conventional axial fan, FIG. 4 (a) is a cross-sectional view when a lattice or a filter is not provided at a suction port of a coaxial flow fan, and FIG. FIG. 5 (a) is a cross-sectional view in the case where a lattice or a filter is provided at the suction port of the coaxial flow fan, and FIG. 5 (b) is a diagram illustrating the flow of inflow air from the coaxial flow fan. FIG. 6 shows the relationship between the shape of the thick portion and the performance. 4 ... front edge, 5 ... rear side, 12 ... axial flow fan, 16 ...
Blade, 17: Thick part, 18: Leading edge blade thickness.
Claims (1)
この吸込口に格子またはフィルターを設けた送風機にお
いて、前記軸流ファンのブレードの周方向断面の前縁の
背面側に、弦長に対し、前縁より０％〜５％離して、２
％〜10％の周方向長さで、かつ１％〜５％の曲率半径の
半円状の肉厚部を設けた軸流ファン。1. An airflow suction port is provided on a front surface of an axial fan.
In the blower provided with a lattice or a filter at the suction port, on the back side of the front edge of the circumferential section of the blade of the axial fan, 0% to 5% apart from the front edge with respect to the chord length, 2%
An axial fan having a semicircular thick portion having a circumferential length of 1% to 10% and a radius of curvature of 1% to 5%.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP63273580A JP2702755B2 (en) | 1988-10-28 | 1988-10-28 | Axial fan |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP63273580A JP2702755B2 (en) | 1988-10-28 | 1988-10-28 | Axial fan |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH02119699A JPH02119699A (en) | 1990-05-07 |
| JP2702755B2 true JP2702755B2 (en) | 1998-01-26 |
Family
ID=17529779
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP63273580A Expired - Fee Related JP2702755B2 (en) | 1988-10-28 | 1988-10-28 | Axial fan |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2702755B2 (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US7824154B2 (en) | 2006-06-09 | 2010-11-02 | Nidec Corporation | Motor having heat-dissipating structure for circuit component and fan unit including the motor |
| US20110262271A1 (en) * | 2010-04-27 | 2011-10-27 | Minebea Motor Manufacturing Corporation | Axial fan |
Families Citing this family (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH04315000A (en) * | 1991-04-12 | 1992-11-06 | Daikin Ind Ltd | Propeller fan |
| JP4513200B2 (en) * | 2000-10-11 | 2010-07-28 | 株式会社デンソー | Centrifugal multi-blade fan |
| JP4974605B2 (en) * | 2006-08-03 | 2012-07-11 | 新明和工業株式会社 | Impeller and underwater mixer |
| JP2009299553A (en) * | 2008-06-12 | 2009-12-24 | Fuji Electric Retail Systems Co Ltd | Propeller fan |
| WO2020194756A1 (en) * | 2019-03-28 | 2020-10-01 | 三菱電機株式会社 | Propeller fan and air blowing apparatus |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS564700U (en) * | 1979-06-25 | 1981-01-16 |
-
1988
- 1988-10-28 JP JP63273580A patent/JP2702755B2/en not_active Expired - Fee Related
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US7824154B2 (en) | 2006-06-09 | 2010-11-02 | Nidec Corporation | Motor having heat-dissipating structure for circuit component and fan unit including the motor |
| US20110262271A1 (en) * | 2010-04-27 | 2011-10-27 | Minebea Motor Manufacturing Corporation | Axial fan |
| US8961124B2 (en) * | 2010-04-27 | 2015-02-24 | Minebea Co., Ltd. | Axial fan |
Also Published As
| Publication number | Publication date |
|---|---|
| JPH02119699A (en) | 1990-05-07 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| JPH0660638B2 (en) | Mixed flow impeller | |
| JPS60145497A (en) | Centrifugal blower | |
| JP2001271790A (en) | Centrifugal impeller and air cleaner | |
| JP2702755B2 (en) | Axial fan | |
| CN110914553B (en) | Impeller, blower and air conditioner | |
| TWI529308B (en) | Impeller and the use of impeller shaft flow blower | |
| JP2718943B2 (en) | Axial fan | |
| JP2000110783A (en) | Centrifugal fan | |
| JP2769211B2 (en) | Blower | |
| JPH0121198Y2 (en) | ||
| JP2003035294A (en) | Impeller for multiblade blower and multiblade blower equipped therewith | |
| JPH02248693A (en) | Multiblade fan | |
| JP3510328B2 (en) | Centrifugal fan | |
| JP4243105B2 (en) | Impeller | |
| JP3607769B2 (en) | Centrifugal blower | |
| JPH03156197A (en) | Axial fan | |
| JPH0639957B2 (en) | Axial blower | |
| JPH0330742Y2 (en) | ||
| JPH01315696A (en) | Fan for air-conditioner | |
| JPH053760Y2 (en) | ||
| JP3052591B2 (en) | Electric blower impeller | |
| JPS61104194A (en) | Fan | |
| JPH04159498A (en) | Impeller of multiblade fan | |
| JPS6210495A (en) | Blower | |
| JPH08170599A (en) | Blower impeller |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| FPAY | Renewal fee payment (event date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20081003 Year of fee payment: 11 |
|
| LAPS | Cancellation because of no payment of annual fees |