JPH02223697A - Multivane fan - Google Patents
Multivane fanInfo
- Publication number
- JPH02223697A JPH02223697A JP4602989A JP4602989A JPH02223697A JP H02223697 A JPH02223697 A JP H02223697A JP 4602989 A JP4602989 A JP 4602989A JP 4602989 A JP4602989 A JP 4602989A JP H02223697 A JPH02223697 A JP H02223697A
- Authority
- JP
- Japan
- Prior art keywords
- impeller
- casing
- suction
- air
- oblong hole
- 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
- 210000005182 tip of the tongue Anatomy 0.000 claims 1
- 230000001965 increasing effect Effects 0.000 abstract description 3
- 230000002093 peripheral effect Effects 0.000 abstract description 3
- 238000000034 method Methods 0.000 abstract 1
- 230000000694 effects Effects 0.000 description 2
- 238000004378 air conditioning Methods 0.000 description 1
- 238000009423 ventilation Methods 0.000 description 1
Abstract
Description
【発明の詳細な説明】
産業上の利用分野
本発明は、空調機器および換気送風機器に使用される多
翼ファンに関するものである。DETAILED DESCRIPTION OF THE INVENTION Field of the Invention The present invention relates to a multi-blade fan used in air conditioning equipment and ventilation equipment.
従来の技術
従来、この種の多翼ファンは、第6図に示すように羽根
車101と、この羽根車101の周囲を囲む渦巻ケーシ
ング102と吸込口104を有する吸込ケーシング10
6とよ)なるケーシング106を備えた構成であった。2. Description of the Related Art Conventionally, as shown in FIG. 6, a multi-blade fan of this type has an impeller 101, a volute casing 102 surrounding the impeller 101, and a suction casing 10 having a suction port 104.
The configuration included a casing 106 (6).
発明が解決しようとする課題
上記従来の多翼ファンは、第6図に示すように、運転時
には羽根車101によシ吸込空気が昇圧されるので、羽
根車101の吸込側Aと、ケーシング106の内部Bと
で圧力差を生じ、羽根車101を通る順流aと圧力差で
吸込側へ戻ろうとする逆流すとが衝突するときに、パサ
パサという騒音が発生する欠点があった。Problems to be Solved by the Invention In the conventional multi-blade fan described above, as shown in FIG. A pressure difference is generated between the inside B of the impeller 101, and when the forward flow a passing through the impeller 101 collides with the reverse flow that tries to return to the suction side due to the pressure difference, a crackling noise is generated.
本発明は上記従来の課題に留意し、騒音の低い多翼ファ
ンを提供することを目的とするものである。The present invention has been made in consideration of the above-mentioned conventional problems, and an object of the present invention is to provide a multi-blade fan with low noise.
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、゛ブレードを有す
る羽根車と、前記羽根車の周囲を渦巻ケーシングと吸込
口を有する吸込ケーシングよりなるケーシングで囲み、
かつケーシングに吐出口を有する構成において、前記吸
込ケーシングの吐出口部分に、前記渦巻ケーシングの舌
部先端より前記羽根車の回転方向と逆方向に、0°〜e
O°の範囲に位置し、内径および外径が前記羽根車の外
径に対し、110%−120%および120%〜140
%であり、周方向の長さが40%〜6o%である長孔を
設けた多翼ファンの構成としたものである。Means for Solving the Problems In order to solve the problems, the present invention provides: an impeller having blades, surrounding the impeller with a casing consisting of a spiral casing and a suction casing having a suction port;
And in the configuration in which the casing has a discharge port, the discharge port portion of the suction casing has an angle of 0° to
O°, and the inner diameter and outer diameter are 110% - 120% and 120% - 140% of the outer diameter of the impeller.
%, and is configured as a multi-blade fan provided with elongated holes having circumferential lengths of 40% to 60%.
作 用
この構成により、ケーシング内部での大きい圧力部分の
空気が長孔より吸込側へ流れ、羽根車のブレードから吸
込側への逆流が押えられ騒音が小さくて済むこととなる
。Effect: With this configuration, the air in the high-pressure portion inside the casing flows to the suction side through the long holes, and backflow from the impeller blades to the suction side is suppressed, resulting in low noise.
実施例
以下、本発明の一実施例を第1図〜第4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、IQlは羽根車で、そ
の周囲を渦巻ケーシング102と、吸込口104を備え
た吸込ケーシング1よりなるケーシング3で被われてい
る。前記ケーシング3は吐出口4を有し、吸込ケーシン
グ1は、吐出口4部分に渦巻ケーシング102の舌部先
端6より羽根車1010回転方向と逆方向に0°〜60
’の範囲に位置し、内径D1および外径D2が羽根車1
01の外径D0に対し110%〜120チおよび120
%〜140%であり、周方向長さlが4o%〜tso%
である長孔6が設けられている。EXAMPLE Hereinafter, an example of the present invention will be described based on FIGS. 1 to 4. Note that the same parts as in the conventional example are given the same numbers and detailed explanations are omitted. In the figure, IQl is an impeller, which is surrounded by a casing 3 consisting of a spiral casing 102 and a suction casing 1 having a suction port 104. The casing 3 has a discharge port 4, and the suction casing 1 has a discharge port 4 that is 0° to 60° in the direction opposite to the rotational direction of the impeller 1010 from the tongue tip 6 of the spiral casing 102.
', and the inner diameter D1 and outer diameter D2 are the impeller 1.
110% to 120 inches and 120 to the outer diameter D0 of 01
% to 140%, and the circumferential length l is 4o% to tso%
A long hole 6 is provided.
上記構成において、羽根車101が回転すると、吸入口
104よす空気を吸引し、羽根車101により昇圧し、
ケーシング3の内部りを通り吐出口4より吐出する。前
記ケーシング3の内部りの空気は、羽根車101の昇圧
作用により羽根車10fの吸込部C′より圧力が高くな
っており、上記羽根車101の外周や吸込口1o4と羽
根車101とのすきま104Aから、上記吸込部C′へ
戻ろうとする。しかし、上記吸込ケーシング1には長孔
5が開いているので、前記ケーシング3の内部りの圧力
に応じて、空気が吸込ケーシング1の外側の吸込部Cへ
戻り、羽根車1o1やすきま104Aからの逆流が減少
し騒音の発生が小さくて済む。In the above configuration, when the impeller 101 rotates, air is sucked into the suction port 104, and the pressure is increased by the impeller 101.
It passes through the inside of the casing 3 and is discharged from the discharge port 4. The pressure of the air inside the casing 3 is higher than that of the suction portion C' of the impeller 10f due to the pressure increasing action of the impeller 101, and the gap between the outer periphery of the impeller 101 and the suction port 1o4 and the impeller 101. From 104A, it attempts to return to the suction section C'. However, since the elongated hole 5 is opened in the suction casing 1, air returns to the suction part C outside the suction casing 1 according to the pressure inside the casing 3, and from the impeller 1o1 and the gap 104A. This reduces backflow and reduces noise generation.
また上部長孔5から吸込部Cへ戻った空気は再び吸込口
104より吸引されるので、風量が減少すること汀ない
。なお、第4図に長孔6の大きさおよび位置を変えたと
きの風量および騒音の変化を示す。これにより長孔6の
最適値を決定した。すなわち、長孔の内径り、が羽根車
外径D0に対し、1.1〜1.2で、外径D2が1.2
〜1.4、そして長さlが0.4〜0.5の範囲にあれ
ば、従来の長孔なしの場合よりも低騒音化できることが
明らかである。Furthermore, since the air that has returned to the suction portion C from the upper elongated hole 5 is sucked in again through the suction port 104, the air volume does not decrease or stagnate. Incidentally, FIG. 4 shows changes in air volume and noise when the size and position of the elongated hole 6 are changed. As a result, the optimum value for the long hole 6 was determined. That is, the inner diameter of the long hole is 1.1 to 1.2 with respect to the impeller outer diameter D0, and the outer diameter D2 is 1.2.
˜1.4, and if the length l is in the range of 0.4 to 0.5, it is clear that noise can be lowered than in the conventional case without long holes.
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
、ケーシング内部での羽根車の内側である吸込部と、羽
根車の外周部であるケーシング内部との圧力差を、ケー
シングの吸込ケーシングの吐出口部分に長孔を設けるこ
とにより均等にするものであるから、羽根車内部への気
流の逆流がなくなり、気流の乱れによる逆流前が防止さ
れ、送風量を低減することなく簡単な構造で低騒音化を
図るものである。Effects of the Invention As is clear from the description of the embodiments above, according to the present invention, the pressure difference between the suction part inside the casing, which is the inside of the impeller, and the inside of the casing, which is the outer peripheral part of the impeller, can be reduced by By providing a long hole in the discharge port of the suction casing, the airflow is made even. This eliminates the backflow of airflow into the impeller and prevents backflow due to turbulence of the airflow, without reducing the amount of air blown. It has a simple structure and aims to reduce noise.
第1図は本発明の一実施例の多翼7アンの側面図、第2
図は同多翼ファンの斜視図、第3図は同多翼ファンの断
面図、第4図は同多翼ファンの長孔の形状と性能との関
連図、第5図は従来の多翼ファンのfP+視図1第6図
は同多翼ファンの断面図である。
1・・・・・・吸込ケーシング、3・・・・・・ケーシ
ング、4・・・・・・吐出口、6・・・・・・長孔、6
・・・・・・舌部、101・・・・・・羽根車、102
・・・・・・渦巻ケーシング、104・・・・・・吸込
口。
代理人の氏名 弁理士 粟 野 重 孝 ほか1名a5
味Fig. 1 is a side view of a multi-blade 7-ang according to an embodiment of the present invention;
The figure is a perspective view of the multi-blade fan, Fig. 3 is a cross-sectional view of the multi-blade fan, Fig. 4 is a relationship between the long hole shape and performance of the multi-blade fan, and Fig. 5 is a conventional multi-blade fan. FIG. 6, which is an fP+ view of the fan, is a sectional view of the multi-blade fan. 1... Suction casing, 3... Casing, 4... Discharge port, 6... Elongated hole, 6
...Tongue, 101... Impeller, 102
...Volume casing, 104...Suction port. Name of agent: Patent attorney Shigetaka Awano and one other person A5 Aji
Claims (1)
を有する吸込ケーシングよりなるケーシングで囲み、前
記ケーシングには吐出口を設け、前記吸込ケーシングの
吐出口部分に、前記渦巻ケーシング舌部先端より前記羽
根車の回転方向と逆方向に、0°〜60゜の範囲に位置
し、内径および外径が前記羽根車の外径に対し、110
%〜120%および120%〜140%であり、周方向
の長さが40%〜50%である長孔を設けた多翼ファン
。An impeller having blades is surrounded by a casing consisting of a spiral casing and a suction casing having a suction port, the casing is provided with a discharge port, and the impeller is inserted into the discharge port portion of the suction casing from the tip of the tongue of the spiral casing. is located in the range of 0° to 60° in the opposite direction to the rotational direction of the impeller, and has an inner diameter and an outer diameter of 110° with respect to the outer diameter of the impeller.
% to 120% and 120% to 140%, and the length in the circumferential direction is 40% to 50%.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP4602989A JPH0788839B2 (en) | 1989-02-27 | 1989-02-27 | Multi-wing fan |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP4602989A JPH0788839B2 (en) | 1989-02-27 | 1989-02-27 | Multi-wing fan |
Publications (2)
Publication Number | Publication Date |
---|---|
JPH02223697A true JPH02223697A (en) | 1990-09-06 |
JPH0788839B2 JPH0788839B2 (en) | 1995-09-27 |
Family
ID=12735619
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP4602989A Expired - Lifetime JPH0788839B2 (en) | 1989-02-27 | 1989-02-27 | Multi-wing fan |
Country Status (1)
Country | Link |
---|---|
JP (1) | JPH0788839B2 (en) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
KR100420516B1 (en) * | 2001-07-26 | 2004-03-02 | 엘지전자 주식회사 | Turbo-sirocco fan Assembly |
-
1989
- 1989-02-27 JP JP4602989A patent/JPH0788839B2/en not_active Expired - Lifetime
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
KR100420516B1 (en) * | 2001-07-26 | 2004-03-02 | 엘지전자 주식회사 | Turbo-sirocco fan Assembly |
Also Published As
Publication number | Publication date |
---|---|
JPH0788839B2 (en) | 1995-09-27 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
TWI391564B (en) | Axial-flow fan | |
US7972110B2 (en) | Centrifugal blower | |
TWI290978B (en) | Fan and fan housing with toothed-type connecting elements | |
JP2002243188A (en) | Turbo fan for ceiling cassette type air conditioner | |
JPS63124900A (en) | Axial blower | |
US20060024160A1 (en) | Centrifugal blower having auxiliary radial inlet | |
JP2001271790A (en) | Centrifugal impeller and air cleaner | |
TWI391567B (en) | Axial-flow fan | |
JPS60145497A (en) | Centrifugal blower | |
JP2006307651A (en) | Multiblade fan | |
JP2006077723A (en) | Multi-blade fan | |
US7223068B2 (en) | Housing for axial flow heat-dissipating fan | |
JP3801162B2 (en) | Propeller fan | |
JPWO2008093390A1 (en) | Multi-blade centrifugal blower | |
JP5448874B2 (en) | Multiblade centrifugal fan and air conditioner using the same | |
JPH02223697A (en) | Multivane fan | |
JPH05149297A (en) | Centrifugal fan | |
JP2006125229A (en) | Sirocco fan | |
WO1998053211A1 (en) | Multi-blade centrifugal fan | |
JPH05296195A (en) | Axial fan | |
JPH10311294A (en) | Centrifugal blower | |
JP3084790B2 (en) | Propeller fan | |
US20060110252A1 (en) | Impeller for axial-flow heat-dissipating fan | |
KR200497415Y1 (en) | Airfoil blades for centrifugal impeller | |
JP2004308442A (en) | Centrifugal fan |