JPS60209699A - Fan - Google Patents
FanInfo
- Publication number
- JPS60209699A JPS60209699A JP6700984A JP6700984A JPS60209699A JP S60209699 A JPS60209699 A JP S60209699A JP 6700984 A JP6700984 A JP 6700984A JP 6700984 A JP6700984 A JP 6700984A JP S60209699 A JPS60209699 A JP S60209699A
- Authority
- JP
- Japan
- Prior art keywords
- suction port
- inner diameter
- casing
- impeller
- runner
- 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.)
- Pending
Links
Landscapes
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
Description
【発明の詳細な説明】
従来例の構成とその問題点
従来の送風機の羽根車及びケーシングの構成を第１図〜
第３図にもとづいて説明する。従来は、遠心力型羽根車
１０１をおおうケーシング１０２の吸込口１０３の円筒
直線部１０４の長さＵは、吸込口１ｏ３の径りに対して
第１図および第２図の場合も、２≦０．１Ｄの範囲で、
ケーシングと一体品で作られているのが通常であった。[Detailed Description of the Invention] The structure of the conventional example and its problems The structure of the impeller and casing of the conventional blower is shown in Figs.
This will be explained based on FIG. Conventionally, the length U of the cylindrical straight portion 104 of the suction port 103 of the casing 102 that covers the centrifugal impeller 101 is 2≦ in both FIGS. 1 and 2 with respect to the diameter of the suction port 1o3. In the range of 0.1D,
It was usually made in one piece with the casing.
前記羽根車１０１を回転した時に吸込まれる空気群１０
６は、前記吸込口１０３の曲率にそって心方向から軸方
向へと方向転換されるが、曲率部だけではまだ心方向が
残るので円筒直線部１０４で更に軸方向へ方向づけされ
る。しかし、円筒直線部１０４の軸方向長さが十分でな
いと請求心方向流れがまだ残り、前記羽根車１０１の側
板１０６の主板側１０７は流れが通らず、はく離し７、
ブレード１０８を有効に用いず、はく離乱流による効率
低下、騒音発生の原因となっていた。第３図は、従来例
の他の実施例であるがこの場合も、吸込口の軸方向長さ
が小さいため、同項の悪影響があった。Air group 10 sucked in when the impeller 101 is rotated
6 is turned from the central direction to the axial direction along the curvature of the suction port 103, but since the central direction still remains in the curvature portion alone, it is further directed in the axial direction at the cylindrical straight portion 104. However, if the length in the axial direction of the cylindrical straight portion 104 is not sufficient, the flow in the center direction will still remain, and the flow will not pass through the main plate side 107 of the side plate 106 of the impeller 101, causing separation 7,
The blade 108 was not used effectively, resulting in reduced efficiency and generation of noise due to separation turbulence. FIG. 3 shows another embodiment of the conventional example, and in this case as well, since the axial length of the suction port is small, the same adverse effect occurs.
発明の目的
本発明は、このような従来の欠点を解消するもので、羽
根車の吸込部の流れ及び羽根車ブレード部の流れが円滑
となり、効率、騒音等の諸性能を改善した送風機を提供
することを目的とする。Purpose of the Invention The present invention solves these conventional drawbacks, and provides a blower in which the flow in the suction section of the impeller and the flow in the impeller blade section is smooth, and various performances such as efficiency and noise are improved. The purpose is to
発明の構成
本発明は内部に遠心力型の羽根車を有したケーシングの
吸込口を、前記羽根車の内径と同径でかつ羽根車内径の
１６係〜４６％の軸方向長さの直線部を軸心側に有する
送風機で、吸込口からケーシング内への空気方向転換を
円滑にし、吸込口流れおよび羽根車側板部流れを円滑に
し、諸性能を向上することができるものである。Structure of the Invention The present invention provides an inlet of a casing having a centrifugal impeller therein, with a straight portion having the same diameter as the inner diameter of the impeller and an axial length of 16 to 46% of the inner diameter of the impeller. This is a blower that has an air filter on the axial center side, which can smoothly change the direction of air from the suction port into the casing, smooth the flow through the suction port and the impeller side plate, and improve various performances.
実施例の説明
以下、本発明の一実施例を第４図、第６図にもとづいて
説明する。DESCRIPTION OF EMBODIMENTS An embodiment of the present invention will be described below with reference to FIGS. 4 and 6.
図において、１はケーシング２と一体品で作られた吸込
口で、吸込口内径りは、羽根車３の内径Ｄ′と等しく、
円筒部１ａの軸方向長さ２′は、吸込口１の内径りに対
し、ｏ、１ｔｓＤ’≦２′≦０．４５Ｄ’（７）範囲に
とられる。羽根車３は、側板４と主板６およびブレード
６とで構成されている。In the figure, 1 is a suction port made integrally with the casing 2, and the inside diameter of the suction port is equal to the inside diameter D' of the impeller 3.
The axial length 2' of the cylindrical portion 1a is set in the range o, 1tsD'≦2'≦0.45D' (7) with respect to the inner diameter of the suction port 1. The impeller 3 includes a side plate 4, a main plate 6, and blades 6.
上記構成において、羽根車３を回転することにより吸込
まれた空気群７は、吸込口１より流入するが、吸込口の
軸方向長さが長いため、吸込口１の出口ではすべての空
気群が軸方向に方向転換され、従来のように吸込口曲率
部付近の流れ８が方向転換されにくいことはない。次に
、吸込口１の出口まで来た流れは、ブレード７により径
方向に方向転換されようとするが、すべての流れが軸方
向へ向いているので、従来よりは、径方向への方向転換
が容易である。従って、側板４の主板側での流れの通過
しない部分９は従来よりはるかに小さく、より有効にブ
レードを用いることになり、はく離や乱流も小さく、騒
音や効率に有利となる。In the above configuration, the air group 7 sucked in by rotating the impeller 3 flows through the suction port 1, but since the suction port is long in the axial direction, all the air groups are absorbed at the outlet of the suction port 1. The direction is changed in the axial direction, and the flow 8 near the suction port curvature is not easily changed in direction as in the conventional case. Next, the flow that has reached the outlet of the suction port 1 attempts to be redirected in the radial direction by the blades 7, but since all the flows are oriented in the axial direction, it is easier to redirect the flow in the radial direction than in the past. is easy. Therefore, the portion 9 on the side of the main plate of the side plate 4 through which the flow does not pass is much smaller than in the past, and the blades can be used more effectively, resulting in less separation and turbulence, which is advantageous in terms of noise and efficiency.
第６図は、直径２００ ｔｍｎの遠心力型羽根車におい
て、ケーシングの吸込口１の直線部長さを変化させて性
能（効率、比騒音）を測定したものであり、効率及び比
騒音の値は、最適値があり、直線部長さの内径に対する
比が１５係〜４６係の範囲で用いると良い性能が得られ
ることを示している。Figure 6 shows the performance (efficiency, specific noise) of a centrifugal impeller with a diameter of 200 tmn, measured by changing the length of the straight section of the suction port 1 of the casing, and the values of efficiency and specific noise are , there is an optimum value, and it is shown that good performance can be obtained when the ratio of the length of the straight part to the inner diameter is in the range of 15 to 46.
発明の効果
このように本発明によれば、多翼ファンの側板側ケース
の吸込部の円筒部の軸方向長さを従来より大きく、吸込
口内径の１６％〜４６チとすることにより、吸込口付近
の流れを円滑にし、まだブレードの有効長を大とし、性
能向上させる効果を発揮する。Effects of the Invention As described above, according to the present invention, the axial length of the cylindrical part of the suction part of the side plate side case of the multi-blade fan is made larger than before, from 16% to 46 inches of the inner diameter of the suction port. It smooths the flow around the mouth, increases the effective length of the blade, and improves performance.
第１図は、従来例の多翼ファンの断面図、第２図は、従
来例の多翼ファンの吸込部および羽根車の流れを示す断
面図、第３図は従来の他の実施例の多翼ファンの断面図
、第４図は本発明の一実施例の多翼ファンの断面図、第
５図は本発明の一実施例の多翼ファンの吸込部および羽
根車の流れを示す断面図、第６図は吸込部軸方内高さの
性能に及ぼす影響を示すグラフである。
１・・・・・吸込口、２・・・・・ケーシング、３・・
・・・遠心力型羽根車。
代理人の氏名 弁理士 中 尾 敏 男 ほか１名実
Ｉ ＵＡ
第２図
Ｑｉ：十
Ｑ 藉Ｉ−咥）Fig. 1 is a cross-sectional view of a conventional multi-blade fan, Fig. 2 is a cross-sectional view showing the flow of the suction section and impeller of a conventional multi-blade fan, and Fig. 3 is a cross-sectional view of another conventional multi-blade fan. FIG. 4 is a cross-sectional view of a multi-blade fan according to an embodiment of the present invention, and FIG. 5 is a cross-sectional view showing the flow of the suction section and impeller of a multi-blade fan according to an embodiment of the present invention. 6 are graphs showing the influence of the axial inner height of the suction section on performance. 1...Suction port, 2...Casing, 3...
...Centrifugal impeller. Name of agent: Patent attorney Toshio Nakao and one other person
I UA Figure 2 Qi: 10Q 藉I-咥)
Claims (1)
前記羽根車の内径と略同径で、かつ前記吸込口の径の１
６〜４５ｑ６の軸方向長さの円筒部して用いる送風機に
関する。The suction port of the casing, which has a centrifugal impeller inside, has approximately the same diameter as the inner diameter of the impeller, and is 1 part of the diameter of the suction port.
The present invention relates to a blower used as a cylindrical portion having an axial length of 6 to 45q6.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP6700984A JPS60209699A (en) | 1984-04-04 | 1984-04-04 | Fan |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP6700984A JPS60209699A (en) | 1984-04-04 | 1984-04-04 | Fan |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPS60209699A true JPS60209699A (en) | 1985-10-22 |
Family
ID=13332490
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP6700984A Pending JPS60209699A (en) | 1984-04-04 | 1984-04-04 | Fan |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS60209699A (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR100416781B1 (en) * | 2001-08-13 | 2004-01-31 | 엘지전자 주식회사 | A fan housing |
| WO2014147942A1 (en) * | 2013-03-19 | 2014-09-25 | パナソニック株式会社 | Blower device |
-
1984
- 1984-04-04 JP JP6700984A patent/JPS60209699A/en active Pending
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR100416781B1 (en) * | 2001-08-13 | 2004-01-31 | 엘지전자 주식회사 | A fan housing |
| WO2014147942A1 (en) * | 2013-03-19 | 2014-09-25 | パナソニック株式会社 | Blower device |
| JP2014181601A (en) * | 2013-03-19 | 2014-09-29 | Panasonic Corp | Blower |
| US9915273B2 (en) | 2013-03-19 | 2018-03-13 | Panasonic Intellectual Property Management Co., Ltd. | Blower device |
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