JPH10153194A - Centrifugal fan - Google Patents
Centrifugal fanInfo
- Publication number
- JPH10153194A JPH10153194A JP31208896A JP31208896A JPH10153194A JP H10153194 A JPH10153194 A JP H10153194A JP 31208896 A JP31208896 A JP 31208896A JP 31208896 A JP31208896 A JP 31208896A JP H10153194 A JPH10153194 A JP H10153194A
- Authority
- JP
- Japan
- Prior art keywords
- blade
- fan
- centrifugal fan
- product
- area
- 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.)
- Granted
Links
Landscapes
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
Description
【０００１】[0001]
【発明の属する技術分野】本発明は騒音低減を可能とし
た遠心ファンに関するものである。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a centrifugal fan capable of reducing noise.
【０００２】[0002]
【従来の技術】遠心ファンにおいて空気は遠心力により
エネルギを与えられ、外周方向に向かうに従いエネルギ
は大きくなる。このため遠心ファン内における流速と周
速の比を一定とし、外周に向かい流速が大きくなるよう
にすれば、遠心ファン内の空気の流れを円滑にすること
ができる。2. Description of the Related Art In a centrifugal fan, air is energized by centrifugal force, and the energy increases toward the outer periphery. Therefore, if the ratio between the flow velocity and the peripheral velocity in the centrifugal fan is kept constant and the flow velocity is increased toward the outer periphery, the flow of air in the centrifugal fan can be made smooth.
【０００３】[0003]
【発明が解決しようとする課題】従来の遠心ファンにお
いて、流速と周速の比は等しくなく、これにより羽根内
の流れに乱れが生じ、騒音の発生原因となっていた。本
発明の目的は、遠心ファン内の流速と周速の比を等しく
することにより羽根内の空気の流れを円滑にし、騒音を
低減することである。In the conventional centrifugal fan, the ratio between the flow velocity and the peripheral velocity is not equal, which causes disturbance in the flow in the blades, causing noise. SUMMARY OF THE INVENTION An object of the present invention is to equalize the ratio between the flow velocity and the peripheral velocity in a centrifugal fan to smooth the air flow in the blades and reduce noise.
【０００４】[0004]
【課題を解決するための手段】上記目的は、遠心ファン
の各羽根間の間隔と羽根の高さの積からなる面積及び半
径との積を各半径位置においてほぼ等しくすることによ
り流速と周速の比を等しくし、羽根内の空気の流れを円
滑にすることによって達成できる。SUMMARY OF THE INVENTION It is an object of the present invention to provide a centrifugal fan in which the product of the area and radius, which is the product of the distance between the blades of the centrifugal fan and the height of the blades, is substantially equal at each radial position, so that the flow velocity and the peripheral speed , And smoothing the air flow in the blade.
【０００５】[0005]
【発明の実施の形態】本発明の一実施例を図１、図２に
より説明する。本発明遠心ファンは、円板状のファン本
体１、ファン本体１の所定半径位置から外周まで延び、
ファン本体１の周方向に沿って所定ピッチで形成された
複数の羽根２、ファン本体１の中心部に設けられ、図示
しない回転軸に取り付けられるハブ３等から構成され
る。遠心ファンを回転させると遠心作用により空気にエ
ネルギが与えられる。遠心ファンの側部にファンガイド
４を取り付けることにより、軸方向に沿って流れてきた
空気は羽根２の内周である入口部を通り、外周である出
口部より半径方向外方に排出される。DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS One embodiment of the present invention will be described with reference to FIGS. The centrifugal fan of the present invention extends from a predetermined radial position of the disk-shaped fan body 1 to the outer periphery of the disk-shaped fan body 1,
It comprises a plurality of blades 2 formed at a predetermined pitch along the circumferential direction of the fan main body 1, a hub 3 provided at the center of the fan main body 1, and attached to a rotating shaft (not shown). When the centrifugal fan rotates, energy is given to the air by the centrifugal action. By attaching the fan guide 4 to the side of the centrifugal fan, the air flowing along the axial direction passes through the inlet, which is the inner periphery of the blade 2, and is discharged radially outward from the outlet, which is the outer periphery. .
【０００６】遠心ファンの羽根２の外径Ｄ2における各
羽根２間の間隔及び各羽根２の高さを夫々Ｌ2及びｂ、
内径Ｄ1における各羽根２間の間隔及び各羽根２の高さ
を夫々Ｌ1及びｈとした時、入口部面積Ｓ1、出口部面積
Ｓ２は次式で表すことができる。 Ｓ１＝Ｌ1×ｈ Ｓ２＝Ｌ2×ｂ 遠心ファンが回転した時、遠心ファン内の任意の点にお
ける空気の速度成分は、周速Ｕ、流れの相対速度Ｗすな
わち流速で各羽根２に沿って流れる空気の速度がある。
なお図のＣ1、Ｃ2は遠心ファン本体１の回転によって流
れるすなわち周速と流速の合成による空気の流れ方向及
び速度を示す。この時風量Ｑは Ｑ＝Ｓ×Ｗ である。入口部相対速度Ｗ1と入口部周速Ｕ1の比を
λ1、出口部相対速度Ｗ2と出口部周速Ｕ2の比をλ2とす
ると、入口部風量Ｑ1と出口部風量Ｑ2は次式で表すこと
ができる。 Ｑ1＝Ｓ1×Ｗ1＝Ｓ1×λ1×Ｕ1 Ｑ2＝Ｓ2×Ｗ2＝Ｓ2×λ2×Ｕ2 遠心ファンの角速度をωとすると上記の式は Ｑ1＝Ｓ1×λ1×ω×Ｄ1／２ Ｑ2＝Ｓ2×λ2×ω×Ｄ2／２ となる。羽根２内の風量はＱ1＝Ｑ2であるので、 Ｓ1×λ1×ω×Ｄ1／２＝Ｓ2×λ2×ω×Ｄ2／２ となる。この時λ1＝λ2とすれば流速と周速Ｕの比は等
しくなり、空気の流れを円滑にできる。そのためには Ｓ1×Ｄ1＝Ｓ2×Ｄ2 とすればよい。これらの関係は図２に示すラジアルファ
ン、図３に示すターボファンのどちらでも成り立つもの
であり、図３に示すターボファンにおいては羽根２間の
間隔Ｌ1、Ｌ2は羽根２に垂直な距離とする。The distance between the blades 2 at the outer diameter D 2 of the blades 2 of the centrifugal fan and the height of each blade 2 are represented by L 2 and b, respectively.
When the spacing and height of each blade 2 between each blade 2 in the inner diameter D 1 was respectively L 1 and h, inlet portion area S 1, the outlet section area S2 can be expressed by the following equation. S1 = L 1 × h S2 = L 2 × b When the centrifugal fan rotates, the velocity component of the air at any point in the centrifugal fan is represented by the peripheral speed U and the relative velocity W of the flow, that is, the flow velocity, along each blade 2. There is the speed of the flowing air.
C 1 and C 2 in the figure indicate the direction and speed of the air flowing due to the rotation of the centrifugal fan main body 1, that is, the combination of the peripheral speed and the flow velocity. At this time, the air volume Q is Q = S × W. Assuming that the ratio between the inlet relative speed W 1 and the inlet peripheral speed U 1 is λ 1 , and the ratio between the outlet relative speed W 2 and the outlet peripheral speed U 2 is λ 2 , the inlet air volume Q 1 and the outlet air volume Q 2 can be represented by the following equation. Q 1 = S 1 × W 1 = S 1 × λ 1 × U 1 Q 2 = S 2 × W 2 = S 2 × λ 2 × U 2 Assuming that the angular velocity of the centrifugal fan is ω, the above equation becomes Q 1 = S 1 × λ 1 × ω × D 1/2 Q 2 = the S 2 × λ 2 × ω × D 2/2. Since the air volume in the blade 2 is the Q 1 = Q 2, the S 1 × λ 1 × ω × D 1/2 = S 2 × λ 2 × ω × D 2/2. At this time, if λ 1 = λ 2 , the ratio between the flow velocity and the peripheral velocity U becomes equal, and the air flow can be made smooth. For that purpose, S 1 × D 1 = S 2 × D 2 may be set. These relationships hold for both the radial fan shown in FIG. 2 and the turbo fan shown in FIG. 3. In the turbo fan shown in FIG. 3, the distances L 1 and L 2 between the blades 2 are distances perpendicular to the blades 2. And
【０００７】図５に本発明の効果を確認するため、入口
面積Ｓ1と出口面積Ｓ2の比率を変え騒音と風量を測定し
た結果を示す。実験は外径Ｄ2がφ６８、内径Ｄ1がφ４
３、羽根２の入口での高さｈ及び出口での高さｂが夫々
９ｍｍ、６ｍｍの従来の遠心ラジアルファンを用い、出
口高さｂを変えることにより入口面積Ｓ１と出口面積Ｓ
２の比率を変えたもので測定を行った。遠心ファンの回
転数は１００００ｒｐｍ一定とした。実験で用いた遠心
ファンはＤ1／Ｄ2＝０．６３である。実験結果をみると
図５の黒印で示す従来の遠心ファンはＳ2／Ｓ1＝１．１
３であるため、Ｓ1×Ｄ1＝０．５６×Ｓ2×Ｄ2となって
いる。出口面積Ｓ2を小さくしていくと、騒音レベルは
低くなり、これは出口面積Ｓ2を小さくすることによ
り、Ｓ2×Ｄ2の値がＳ1×Ｄ1の値に近づくためである。
出口／入口面積比が０．９で従来の遠心ファンより３
（≒６２−５９）ｄＢ低くなり、本発明の効果を見るこ
とができる。この時入口面積Ｓ1、内径Ｄ1と出口面積Ｓ
2、外径Ｄ2の関係は Ｓ1×Ｄ1＝０．７×Ｓ2×Ｄ2 となる。騒音レベルはＳ2／Ｓ1＝０．５５で最も低くな
り、この時 Ｓ1×Ｄ1＝１．１５×Ｓ2×Ｄ2 である。上記した如く入口面積と内径の積及び出口面積
と外径の積をほぼ等しくした時すなわち入口面積Ｓ1、
出口面積Ｓ2の比がＳ2／Ｓ1＝０．６３の時騒音レベル
が最少となるはずであるが、図５に示す実験結果はそう
はなっていない。これは上記計算式は理想的なモデルで
求めたものであるためである。図５の実験結果からは、 Ｓ1×Ｄ1＝（１±０．３）×Ｓ2×Ｄ2 とすると騒音レベルが低くなると共に風量もほぼ同等と
なることが分かる。すなわち前記積を正確に等しくする
必要はなく、３０％のマージンを持たせることができ
る。FIG. 5 shows the results of measuring the noise and air flow while changing the ratio of the entrance area S 1 to the exit area S 2 to confirm the effect of the present invention. Experiments outer diameter D 2 is Fai68, the inner diameter D 1 is φ4
3. Using a conventional centrifugal radial fan having a height h at the inlet of the blade 2 and a height b at the outlet of 9 mm and 6 mm, respectively, and changing the outlet height b to change the inlet area S1 and the outlet area S.
The measurement was performed with the ratio of 2 changed. The rotation speed of the centrifugal fan was constant at 10,000 rpm. Centrifugal fan used in the experiment is D 1 / D 2 = 0.63. Looking at the experimental results, the conventional centrifugal fan indicated by black marks in FIG. 5 has S 2 / S 1 = 1.1.
3, S 1 × D 1 = 0.56 × S 2 × D 2 . As you reduce the exit area S 2, the noise level is low, this is by reducing the exit area S 2, a value of S 2 × D 2 is to approach the value of S 1 × D 1.
Outlet / inlet area ratio is 0.9, 3 times higher than conventional centrifugal fan
(# 62-59) dB lower, and the effect of the present invention can be seen. At this time, the inlet area S 1 , the inner diameter D 1 and the outlet area S
2. The relationship between the outer diameter D 2 is S 1 × D 1 = 0.7 × S 2 × D 2 . The noise level is lowest when S 2 / S 1 = 0.55, and then S 1 × D 1 = 1.15 × S 2 × D 2 . As described above, when the product of the inlet area and the inner diameter and the product of the outlet area and the outer diameter are substantially equal, ie, the inlet area S 1 ,
When the ratio of the exit area S 2 is S 2 / S 1 = 0.63, the noise level should be minimal, but the experimental results shown in FIG. 5 do not. This is because the above calculation formula is obtained by an ideal model. From the experimental results shown in FIG. 5, it can be seen that when S 1 × D 1 = (1 ± 0.3) × S 2 × D 2 , the noise level is reduced and the air volume is almost the same. That is, it is not necessary to make the products exactly equal, and a 30% margin can be provided.
【０００８】図４に示す如く内径から外径まで流路の面
積と径の積が等しい形状にした場合が最も効果的である
が、入口面積Ｓ1と内径Ｄ1の積及び出口面積Ｓ2と外径
Ｄ2の積をほぼ等しくし、入口高さｈから出口高さｂま
で羽根の高さを直線で変えた図１に示す形状でも上記の
ように効果を得ることができる。As shown in FIG. 4, it is most effective to make the shape of the product of the area and the diameter of the flow passage equal from the inner diameter to the outer diameter, but the product of the inlet area S 1 and the inner diameter D 1 and the outlet area S 2 are the most effective. and approximately equal to the product of the outer diameter D 2, it is possible to obtain the effects as described above in the shape shown in FIG. 1 for changing the height of the blade in a straight line inlet from the height h to the outlet height b.
【０００９】また図６のように遠心ファンの羽根２の一
部に側板５を取り付ければ、ファンガイド４を使用する
ことなく、同様の効果を得ることができる。If the side plate 5 is attached to a part of the blade 2 of the centrifugal fan as shown in FIG. 6, the same effect can be obtained without using the fan guide 4.
【００１０】[0010]
【発明の効果】本発明によれば遠心ファンの性能を落と
すことなく騒音レベルをさげることができる。According to the present invention, the noise level can be reduced without deteriorating the performance of the centrifugal fan.
【図１】本発明実施例の遠心ファンの断面図。FIG. 1 is a sectional view of a centrifugal fan according to an embodiment of the present invention.
【図２】ラジアルファンの正面図。FIG. 2 is a front view of the radial fan.
【図３】ターボファンの正面図。FIG. 3 is a front view of a turbo fan.
【図４】本発明の他の実施例の遠心ファンの断面図。FIG. 4 is a sectional view of a centrifugal fan according to another embodiment of the present invention.
【図５】本発明の効果を示す実験測定図。FIG. 5 is an experimental measurement diagram showing the effect of the present invention.
【図６】本発明の他の実施例の遠心ファンの断面図。FIG. 6 is a sectional view of a centrifugal fan according to another embodiment of the present invention.
１はファン本体、２は羽根、３はハブ、４はファンガイ
ド、５は側板である。1 is a fan body, 2 is a blade, 3 is a hub, 4 is a fan guide, and 5 is a side plate.
Claims (2)
外周まで延びた羽根をファン本体の周方向に沿って所定
ピッチで形成し、軸方向に沿う空気を半径方向外方に流
すようにした遠心ファンであって、 各羽根間の間隔と羽根の高さの積からなる面積及び半径
との積が各半径位置においてほぼ等しくなるようにした
ことを特徴とする遠心ファン1. A blade extending from a predetermined radial position to an outer periphery of a disk-shaped fan main body at a predetermined pitch along a circumferential direction of the fan main body so that air along an axial direction flows radially outward. Centrifugal fan, characterized in that the product of the area and radius of the product of the spacing between each blade and the height of the blade is substantially equal at each radial position.
々Ｓ1、Ｓ2とし、各羽根の内径及び外径を夫々Ｄ1、Ｄ2
とした時、 Ｓ1×Ｄ1＝（１±０．３）×Ｓ2×Ｄ2 の関係式を満足するように、各羽根の高さ、大きさ及び
間隔を設定したことを特徴とする請求項１記載の遠心フ
ァン。2. The area of each blade inlet and outlet is defined as S 1 and S 2, and the inner and outer diameters of each blade are defined as D 1 and D 2, respectively.
The height, size and spacing of each blade are set so as to satisfy the relational expression of S 1 × D 1 = (1 ± 0.3) × S 2 × D 2 The centrifugal fan according to claim 1.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP31208896A JP3391199B2 (en) | 1996-11-22 | 1996-11-22 | Centrifugal fan |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP31208896A JP3391199B2 (en) | 1996-11-22 | 1996-11-22 | Centrifugal fan |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH10153194A true JPH10153194A (en) | 1998-06-09 |
| JP3391199B2 JP3391199B2 (en) | 2003-03-31 |
Family
ID=18025097
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP31208896A Expired - Fee Related JP3391199B2 (en) | 1996-11-22 | 1996-11-22 | Centrifugal fan |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP3391199B2 (en) |
Cited By (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2000029681A1 (en) * | 1998-11-16 | 2000-05-25 | Toto Ltd. | Toilet device and toilet device designing method |
| CN100348373C (en) * | 2004-03-04 | 2007-11-14 | 日立工机株式会社 | Power tool |
| CN102192188A (en) * | 2010-03-09 | 2011-09-21 | 罗伯特·博世有限公司 | Hand-held machine tool fan |
| JP2012529585A (en) * | 2009-06-08 | 2012-11-22 | マン・ディーゼル・アンド・ターボ・エスイー | Compressor impeller |
| WO2012163001A1 (en) * | 2011-06-01 | 2012-12-06 | 中山大洋电机制造有限公司 | Cooling fan and motor applying cooling fan |
| WO2014168790A1 (en) * | 2013-04-08 | 2014-10-16 | Apple Inc. | Improving fan performance by increasing effective blade height in a tolerance neutral manner |
| US20150184663A1 (en) * | 2013-12-30 | 2015-07-02 | Dongbu Daewoo Electronics Corporation | Centrifugal fan for devices including refrigerators |
| JP2016133105A (en) * | 2015-01-22 | 2016-07-25 | 株式会社東芝 | Electric blower |
| WO2019235421A1 (en) * | 2018-06-05 | 2019-12-12 | 株式会社村田製作所 | Blowing device and fluid control device |
-
1996
- 1996-11-22 JP JP31208896A patent/JP3391199B2/en not_active Expired - Fee Related
Cited By (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2000029681A1 (en) * | 1998-11-16 | 2000-05-25 | Toto Ltd. | Toilet device and toilet device designing method |
| CN100348373C (en) * | 2004-03-04 | 2007-11-14 | 日立工机株式会社 | Power tool |
| JP2012529585A (en) * | 2009-06-08 | 2012-11-22 | マン・ディーゼル・アンド・ターボ・エスイー | Compressor impeller |
| CN102192188A (en) * | 2010-03-09 | 2011-09-21 | 罗伯特·博世有限公司 | Hand-held machine tool fan |
| WO2012163001A1 (en) * | 2011-06-01 | 2012-12-06 | 中山大洋电机制造有限公司 | Cooling fan and motor applying cooling fan |
| WO2014168790A1 (en) * | 2013-04-08 | 2014-10-16 | Apple Inc. | Improving fan performance by increasing effective blade height in a tolerance neutral manner |
| US9334867B2 (en) | 2013-04-08 | 2016-05-10 | Apple Inc. | Fan performance by increasing effective blade height in a tolerance neutral manner |
| US20150184663A1 (en) * | 2013-12-30 | 2015-07-02 | Dongbu Daewoo Electronics Corporation | Centrifugal fan for devices including refrigerators |
| US9885361B2 (en) * | 2013-12-30 | 2018-02-06 | Dongbu Daewoo Electronics Corporation | Centrifugal fan for devices including refrigerators |
| JP2016133105A (en) * | 2015-01-22 | 2016-07-25 | 株式会社東芝 | Electric blower |
| WO2019235421A1 (en) * | 2018-06-05 | 2019-12-12 | 株式会社村田製作所 | Blowing device and fluid control device |
Also Published As
| Publication number | Publication date |
|---|---|
| JP3391199B2 (en) | 2003-03-31 |
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