JPH0794838B2 - Multi-wing fan - Google Patents
Multi-wing fanInfo
- Publication number
- JPH0794838B2 JPH0794838B2 JP1070910A JP7091089A JPH0794838B2 JP H0794838 B2 JPH0794838 B2 JP H0794838B2 JP 1070910 A JP1070910 A JP 1070910A JP 7091089 A JP7091089 A JP 7091089A JP H0794838 B2 JPH0794838 B2 JP H0794838B2
- Authority
- JP
- Japan
- Prior art keywords
- blade
- main plate
- impeller
- plate side
- side plate
- 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 - Lifetime
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、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。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a multi-blade fan used in air conditioners and ventilation fans.
従来の技術 従来、この種の多翼型羽根車は、ターボ型やラジアル型
の羽根車と比し小型となり騒音も低いのでよく用いられ
るが、さらに低騒音化が要望されていた。2. Description of the Related Art Conventionally, this type of multi-blade impeller is often used because it is smaller in size and lower in noise than a turbo-type or radial-type impeller, but further noise reduction has been demanded.
このような従来の多翼型羽根車は第６図および第７図に
示すように、シャフト101に連結された主板102と、環状
の側板103とで、断面が主板102側から側板103側まで同
一であるブレード104を多数はさむように取付け、前記
シャフト101に駆動力を与えてブレード104を回転させ、
吸込側空気105をブレード入口部106へ吸い込みブレード
104で昇圧し、ブレード出口部107からスクロール106を
通って出口へ吐出される構成であった。As shown in FIGS. 6 and 7, such a conventional multiblade impeller has a main plate 102 connected to a shaft 101 and an annular side plate 103, and has a cross section from the main plate 102 side to the side plate 103 side. A large number of identical blades 104 are attached so as to be sandwiched, a driving force is applied to the shaft 101 to rotate the blades 104,
The suction side air 105 is sucked into the blade inlet section 106
The pressure was increased at 104, and it was discharged from the blade outlet 107 through the scroll 106 to the outlet.
発明が解決しようとする課題 前記従来の多翼型羽根車では、第７図に示すように吸込
口112からブレード104への気流の曲がりが吸込口112に
近いほど急であるため、これが抵抗となりブレード104
による気流の風速は側板103側ほど小さくなる。しか
し、ブレードの各断面で流速が異なるにもかかわらず同
じ断面形状となっているので、特に風量の多い羽根主板
側のブレード入口部において、ブレード後部の渦の発生
が大きかった。この結果、第８図に示すようにブレード
出口部での死水域が大きく渦音や舌部での干渉音が大き
くなっていた。DISCLOSURE OF THE INVENTION Problems to be Solved by the Invention In the conventional multi-blade impeller, the bending of the air flow from the suction port 112 to the blade 104 becomes steeper the closer to the suction port 112 as shown in FIG. Blade 104
The wind speed of the air flow due to becomes smaller on the side plate 103 side. However, since the cross-sections have the same cross-sectional shape even though the flow velocities are different in each cross section of the blade, the vortex generation at the rear part of the blade was large at the blade inlet part on the blade main plate side where the air volume was large. As a result, as shown in FIG. 8, the dead water region at the blade outlet was large, and the vortex sound and the interference sound at the tongue were large.
本発明は上記課題に留意し、ブレード各断面における流
速を平均化し乱流による騒音低下を図ることを第１の目
的とする。第２の目的は吸込側にフィルタ等の抵抗を有
する場合の吸込分布を平均化しながらブレード各断面の
流速平均化を図ることにある。The first object of the present invention is to reduce the noise due to turbulence by averaging the flow velocity in each cross section of the blade in consideration of the above problems. The second purpose is to average the flow velocity in each cross section of the blade while averaging the suction distribution when the suction side has a resistance such as a filter.
課題を解決するための手段 第１の目的を達成するために本発明の第１の技術的手段
は、主板と環状の側板によってはさむように取付けられ
た複数のブレードからなる羽根車の内径および入口角度
を、羽根車の主板側に向うにしたがって小さくした多翼
ファンの構成としたものである。Means for Solving the Problem To achieve the first object, a first technical means of the present invention is to provide an inner diameter and an inlet of an impeller composed of a plurality of blades sandwiched by a main plate and an annular side plate. The angle of the multi-blade fan is reduced toward the main plate side of the impeller.
第２の目的を達成する第２の技術的手段は、第１の技術
的手段の羽根車に加えて、羽根車の外径も、羽根車の主
板側に向うにしたがって小さくした多翼ファンの構成と
したものである。The second technical means for achieving the second object is, in addition to the impeller of the first technical means, a multi-blade fan in which the outer diameter of the impeller is reduced toward the main plate side of the impeller. It is configured.
作用 第１の技術的手段の構成により、特に風量の多い羽根主
板側では、内径が小さいためブレード入口部で周速が小
さくなり、吸い込まれた空気がブレード入口部で衝突す
る力が弱まり、ブレードの裏にできる渦が小さくなる。
また入口角度が主板側で小さくなっており入ってくる空
気の角度に合致し渦の発生が小さくなる。Action With the configuration of the first technical means, especially on the blade main plate side where the air volume is large, since the inner diameter is small, the peripheral speed is reduced at the blade inlet portion, and the force with which the sucked air collides at the blade inlet portion is weakened. The vortex on the back of is small.
Also, the inlet angle is smaller on the main plate side, which matches the angle of the incoming air, and the generation of vortices is reduced.
第２の技術的手段の構成により、側板側の内径と主板側
の内径の比率を大きくすることができ、吸込口からブレ
ードへの気流の曲がりの抵抗が緩和され、側板側から主
板側での風量が均一に近づき、主板側での吸込風速が従
来より低下し、渦の発生が小さい。また第１の技術的手
段と同じ作用も同時に働く。With the configuration of the second technical means, the ratio of the inner diameter on the side plate side to the inner diameter on the main plate side can be increased, the resistance to the bending of the air flow from the suction port to the blade is mitigated, and the side plate side to the main plate side is relieved. The air volume approaches uniform, the suction air velocity on the main plate side is lower than before, and the generation of vortices is small. Also, the same action as the first technical means works at the same time.
実施例 まず、本発明の第１の技術的手段による一実施例を第１
図〜第３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。Embodiment First, one embodiment of the first technical means of the present invention will be described.
The description will be made with reference to FIGS. The same parts as those of the conventional example are designated by the same reference numerals, and detailed description thereof will be omitted.
図において、102は主板でシャフト101にナット108で取
り付けられ、外縁面に相対する環状の側板103で複数の
ブレード１をはさんで固定して多翼型羽根車２を構成し
ている。In the figure, a main plate 102 is attached to a shaft 101 with a nut 108, and a plurality of blades 1 are sandwiched and fixed by an annular side plate 103 facing the outer edge surface to form a multiblade impeller 2.
第１図及び第２図に示すようにブレード１の側面形状
は、横断面における入口角β１が、主板側ブレード入口
角β1-Mから側板側ブレード入口角β1-Rになるまで、側
板側から主板側へしだいに小さくなり、内径は側板側内
径D1-Rから主板側内径D1-Mへ、しだいに小さくなってい
る。As shown in FIGS. 1 and 2, the side surface shape of the blade 1 is such that the inlet angle β 1 in the cross section changes from the main plate side blade inlet angle β 1 -M to the side plate side blade inlet angle β 1 -R . The diameter gradually decreases from the side plate side to the main plate side, and the inner diameter gradually decreases from the side plate side inner diameter D 1 -R to the main plate side inner diameter D 1 -M .
上記構成において、シャフト101から伝えられた駆動力
により多翼羽根車２が回転すると、側板103の吸込口の
空気３が吸込まれブレード１の入口部４にくるが、この
とき主板側の入口部４は直径が小さいので、周速が小さ
い。また主板側の入口部４は流入角に合致した入口角と
なっているので、入口部４での衝突が小さい。このため
ブレード背面での渦が減少し、発生音も小さくなる。In the above structure, when the multiblade impeller 2 is rotated by the driving force transmitted from the shaft 101, the air 3 at the suction port of the side plate 103 is sucked and comes to the inlet part 4 of the blade 1. At this time, the inlet part on the main plate side is provided. Since No. 4 has a small diameter, the peripheral speed is small. Further, since the inlet portion 4 on the main plate side has an inlet angle that matches the inflow angle, the collision at the inlet portion 4 is small. For this reason, the vortex on the back surface of the blade is reduced, and the generated sound is also reduced.
つぎに本発明の第２の技術的手段による一実施例を第４
図および第５図にもとづき説明する。図に示すように、
ブレード５は主板102と環状の側板６にはさんで主板102
の外縁面に多数固定して多翼型羽根車７を構成しシャフ
ト101にノット108で取り付けている。Next, a fourth embodiment according to the second technical means of the present invention will be described.
A description will be given based on FIG. 5 and FIG. As shown in the figure,
The blade 5 is sandwiched between the main plate 102 and the annular side plate 6, and the main plate 102
The multi-blade impeller 7 is configured by fixing a large number to the outer edge surface of and is attached to the shaft 101 with the knot 108.
上記羽根車７の外径は側板側に向うにしたがって大きく
なっており、また第１の技術的手段と同様、入口角β１
が、主板側ブレード入口角β1-Mから側板側ブレード入
口角β1-Rになるまで、側板側から主板側へしだいに小
さくなり、内径は側板側内径D1-Rから主板側内径D
1-Mへ、しだいに小さくなっている。The outer diameter of the impeller 7 increases toward the side plate, and the inlet angle β 1 is the same as in the first technical means.
From the side plate side blade inlet angle β 1-M to the side plate side blade inlet angle β 1-R , gradually decreases from the side plate side to the main plate side, and the inner diameter is from the side plate side inner diameter D 1-R to the main plate side inner diameter D.
It is getting smaller gradually to 1-M .
上記構成において、シャフト101から伝えられた駆動力
により多翼羽根車７が回転すると、吸込口の空気８が吸
込まれブレード入口部にくるが、外径と内径共に側板側
が大きくなっているので、吸込口からブレード５への気
流の曲がりの抵抗が緩和され、側板側から主板側での風
量が均一に近づき、主板側での吸込風速が従来より低下
し、渦の発生が小さい。また、前記第１の技術的手段で
説明したことと同様に、ブレード入口部での衝突が小さ
く、このためブレード背面での渦が減少し、発生音も小
さくなる。そしてブレード５の主板側の幅と側板側の幅
の比率は第１の技術的手段によるブレード１と同様であ
って外径は側板側が大きくなっているものであるから同
一風量の能力で吸込面積を大きくとれるものであるから
フィルタを装着したときの吸込分布を平均化できる。In the above configuration, when the multi-blade impeller 7 is rotated by the driving force transmitted from the shaft 101, the air 8 at the suction port is sucked and comes to the blade inlet part, but both the outer diameter and the inner diameter are large on the side plate side. The resistance to bending of the air flow from the suction port to the blade 5 is relaxed, the air volume from the side plate side to the main plate side approaches evenly, the suction wind speed on the main plate side is lower than in the conventional case, and the generation of vortices is small. Further, as in the case of the first technical means, the collision at the blade entrance is small, so that the vortices on the back surface of the blade are reduced and the generated sound is also reduced. The ratio of the width of the blade 5 on the main plate side to the width on the side plate side is the same as that of the blade 1 according to the first technical means, and the outer diameter of the blade 5 is larger on the side plate side. Since a large value can be obtained, the suction distribution when the filter is attached can be averaged.
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
ば羽根車の側板から主板側までの吸込風量を均一するこ
とと、ブレード入口部での衝突力を小さくし、ブレード
背面側での渦の発生を押えるものであるから、送風量を
低減することなく低騒音を図るものである。また、風量
を変えることなく羽根車の主板側内径より側板側の内径
を高比率で大きくできることにより、フィルタを取付け
た場合の吸込分布の均一化により炉過効率を向上でき
る。EFFECTS OF THE INVENTION As is apparent from the above description of the embodiments, according to the present invention, the suction air volume from the side plate to the main plate side of the impeller is made uniform, and the collision force at the blade inlet is reduced to reduce the back surface of the blade. Since it suppresses the generation of vortices on the side, it aims at low noise without reducing the air flow rate. Further, since the inner diameter of the side plate side of the impeller can be increased at a high ratio without changing the air volume, the suction distribution can be made uniform when the filter is attached, and the furnace overefficiency can be improved.
第１図は本発明の第１の技術的手段の実施例を示す多翼
ファンの正面図、第２図は同多翼ファンの側断面図、第
３図は同多翼ファンのブレードの背面の渦の発生を示す
説明図、第４図は同第２の技術的手段の実施例を示す多
翼ファンの正面図、第５図は同多翼ファンの側断面図、
第６図は従来の多翼ファンの正面図、第７図は同多翼フ
ァンの側断面図、第８図は同多翼ファンのブレードの背
面の渦の発生を示す説明図である。 １……ブレード、５……ブレード、６……側板、102…
…主板、103……側板。FIG. 1 is a front view of a multi-blade fan showing an embodiment of a first technical means of the present invention, FIG. 2 is a side sectional view of the multi-blade fan, and FIG. 3 is a back surface of a blade of the multi-blade fan. FIG. 4 is a front view of a multi-blade fan showing an embodiment of the second technical means, FIG. 5 is a side sectional view of the multi-blade fan,
FIG. 6 is a front view of a conventional multi-blade fan, FIG. 7 is a side sectional view of the multi-blade fan, and FIG. 8 is an explanatory diagram showing generation of vortices on the back surface of the blade of the multi-blade fan. 1 ... Blade, 5 ... Blade, 6 ... Side plate, 102 ...
… Main plate, 103 …… Side plate.
───────────────────────────────────────────────────── フロントページの続き (72)発明者 佐野 潔 大阪府門真市大字門真1006番地 松下電器 産業株式会社内 (72)発明者 中村 邦夫 大阪府門真市大字門真1006番地 松下電器 産業株式会社内 (72)発明者 鈴木 創三 大阪府東大阪市高井田本通３丁目22番地 松下冷機株式会社内 (56)参考文献 特開 昭49−118016（ＪＰ，Ａ) 特開 昭62−271995（ＪＰ，Ａ) ─────────────────────────────────────────────────── ─── Continuation of front page (72) Inventor Kiyoshi Sano 1006 Kadoma, Kadoma City, Osaka Prefecture Matsushita Electric Industrial Co., Ltd. (72) Kunio Nakamura, 1006 Kadoma, Kadoma City, Osaka Matsushita Electric Industrial Co., Ltd. 72) Inventor Sozo Suzuki 3-22 Takaidahondori, Higashi-Osaka City, Osaka Prefecture Matsushita Refrigerating Machinery Co., Ltd. (56) References JP-A-49-118016 (JP, A) JP-A-62-271995 (JP, A) )
Claims (2)
付けられた複数のブレードからなる羽根車の内径および
入口角度を、羽根車の主板側に向うにしたがって小さく
した多翼ファン。1. A multi-blade fan in which an inner diameter and an inlet angle of an impeller composed of a plurality of blades sandwiched between a main plate and an annular side plate are made smaller toward the main plate side of the impeller.
したがって小さくした請求項１記載の多翼ファン。2. The multi-blade fan according to claim 1, wherein the outer diameter of the impeller is reduced toward the main plate side of the impeller.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1070910A JPH0794838B2 (en) | 1989-03-23 | 1989-03-23 | Multi-wing fan |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1070910A JPH0794838B2 (en) | 1989-03-23 | 1989-03-23 | Multi-wing fan |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH02248693A JPH02248693A (en) | 1990-10-04 |
| JPH0794838B2 true JPH0794838B2 (en) | 1995-10-11 |
Family
ID=13445142
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP1070910A Expired - Lifetime JPH0794838B2 (en) | 1989-03-23 | 1989-03-23 | Multi-wing fan |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH0794838B2 (en) |
Families Citing this family (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH05321891A (en) * | 1992-05-21 | 1993-12-07 | Matsushita Seiko Co Ltd | Multiblade fan |
| JP2003090298A (en) * | 2001-09-17 | 2003-03-28 | Nippon Soken Inc | Centrifugal fan |
| US7794198B2 (en) | 2003-06-23 | 2010-09-14 | Panasonic Corporation | Centrifugal fan and apparatus using the same |
| JP5267049B2 (en) * | 2008-10-29 | 2013-08-21 | 株式会社デンソー | Centrifugal multi-blade fan |
| JP6143596B2 (en) * | 2013-07-30 | 2017-06-07 | サンデンホールディングス株式会社 | Centrifugal blower and vehicle air conditioner equipped with the centrifugal blower |
| CN109458359A (en) * | 2018-12-26 | 2019-03-12 | 中国船舶重工集团公司第七0三研究所 | A kind of blade profile improving helium compressor single-stage pressure ratio |
Family Cites Families (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS49118016A (en) * | 1973-03-14 | 1974-11-12 | ||
| JPS62271995A (en) * | 1986-05-19 | 1987-11-26 | Matsushita Seiko Co Ltd | Multi blade type impeller |
-
1989
- 1989-03-23 JP JP1070910A patent/JPH0794838B2/en not_active Expired - Lifetime
Also Published As
| Publication number | Publication date |
|---|---|
| JPH02248693A (en) | 1990-10-04 |
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