JPH0270997A - Centrifugal blower - Google Patents
Centrifugal blowerInfo
- Publication number
- JPH0270997A JPH0270997A JP22273688A JP22273688A JPH0270997A JP H0270997 A JPH0270997 A JP H0270997A JP 22273688 A JP22273688 A JP 22273688A JP 22273688 A JP22273688 A JP 22273688A JP H0270997 A JPH0270997 A JP H0270997A
- Authority
- JP
- Japan
- Prior art keywords
- blade
- cross
- section
- plate
- main 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.)
- Granted
Links
- 239000012530 fluid Substances 0.000 abstract description 10
- 238000009826 distribution Methods 0.000 abstract description 5
- 230000007423 decrease Effects 0.000 abstract description 3
- 238000000034 method Methods 0.000 abstract description 2
- 230000003247 decreasing effect Effects 0.000 abstract 1
- 238000006073 displacement reaction Methods 0.000 abstract 1
- 238000004519 manufacturing process Methods 0.000 abstract 1
- 238000000926 separation method Methods 0.000 description 5
- 230000006866 deterioration Effects 0.000 description 3
- 238000010586 diagram Methods 0.000 description 3
- 230000003068 static effect Effects 0.000 description 3
- 230000000694 effects Effects 0.000 description 2
- 241000257465 Echinoidea Species 0.000 description 1
- 238000007664 blowing Methods 0.000 description 1
- 239000003795 chemical substances by application Substances 0.000 description 1
- 210000003746 feather Anatomy 0.000 description 1
- 238000001746 injection moulding Methods 0.000 description 1
- 238000003466 welding Methods 0.000 description 1
Landscapes
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
Description
【発明の詳細な説明】
産業上の利用分野
本発明は、空気調和機などに用いられる遠心送風機特に
その空力性能の改善・低騒音化に関するものである。DETAILED DESCRIPTION OF THE INVENTION Field of the Invention The present invention relates to a centrifugal blower used in an air conditioner or the like, and particularly to improvement of its aerodynamic performance and reduction in noise.
従来の技術
従来より、遠心送風機は、空気調和機などの送風機とし
て幅広く使用されており、その送風機騒音に大きな関心
がもたれてきた。BACKGROUND OF THE INVENTION Conventionally, centrifugal blowers have been widely used as blowers for air conditioners and the like, and there has been a great deal of interest in the noise caused by the blowers.
そのため、羽根車の羽根の断面形状を翼形に形成し、流
体騒音を低減する方法がとられることがあった。Therefore, a method has been taken in which the cross-sectional shape of the blades of the impeller is formed into an airfoil shape to reduce fluid noise.
以下図面を参照し々から、上述したような従来の遠心送
風機について説明する。The conventional centrifugal blower as described above will be described below with reference to the drawings.
第6図は従来の遠心送風機の構造を示すものである。第
5図において、1はプラスチック製の羽根車であり、断
面形状が翼形の複数の羽根板2と、前記羽根板と一体に
成形した主板3と、前記羽根板2の反主板側端面に溶着
固定した側板4より構成されている。6は羽根車1に直
結した電動機であり、羽根車1と電動機5を収納するケ
ーシング6に固定されている。7はケーシングeK、設
ケタ吸込口6aにはめ込まれた吸込ベルマウスである。FIG. 6 shows the structure of a conventional centrifugal blower. In FIG. 5, reference numeral 1 denotes a plastic impeller, which includes a plurality of blade plates 2 having an airfoil cross-sectional shape, a main plate 3 formed integrally with the blade plates, and an end surface of the blade plates 2 on the side opposite to the main plate. It is composed of side plates 4 fixed by welding. 6 is an electric motor directly connected to the impeller 1, and is fixed to a casing 6 that houses the impeller 1 and the electric motor 5. 7 is a suction bell mouth fitted into the casing eK and the installed girder suction port 6a.
第6図は前記羽根板2を羽根車1の回転軸に直交する平
面D−D、 E−E、 F−Fの各断面での断面形
状を示したものであり、略同一断面形状となっている。FIG. 6 shows the cross-sectional shape of the blade plate 2 taken along planes D-D, E-E, and F-F perpendicular to the rotation axis of the impeller 1, and the blades have substantially the same cross-sectional shape. ing.
又、β は気流の流入角、β1 に羽○ 根入口角である。Also, β is the inflow angle of the airflow, and β1 is the feather ○ This is the root entrance angle.
以上のように構成された遠心送風機について、以下その
動作について説明する。The operation of the centrifugal blower configured as above will be described below.
まず、電動機5の駆動力によって羽根車1が回転すると
、吸込ベルマウス7を介して空気が羽根車1内に導入さ
れ、複数の羽根板2間を通過する際に静圧と動圧を付加
され羽根車1からケーシング6内に吐出される。その後
、ケーシングθ内で動圧の一部は静圧に変換されてケー
シングθ外に吐出され送風作用を為す。First, when the impeller 1 is rotated by the driving force of the electric motor 5, air is introduced into the impeller 1 via the suction bell mouth 7, and as it passes between the plurality of blade plates 2, it applies static pressure and dynamic pressure. and is discharged from the impeller 1 into the casing 6. Thereafter, a part of the dynamic pressure is converted into static pressure within the casing θ and is discharged outside the casing θ to perform a blowing action.
このとき、羽根車1内に流入する気流の流入角β は第
7図に示すように、羽根車内の軸方同位置によって異な
っており、主板側に比べ側板側で小さくなるのが一般的
である。従って、羽根人口角β と気流流入角β の関
係は第8図に示すよ1
Q
うに、はとんどの位置で不一致となる。ただし、羽根板
2の断面形状は翼形状としているため、羽根人口角β
と気流流入角β との差が小さい範1
。At this time, as shown in Fig. 7, the inflow angle β of the airflow flowing into the impeller 1 differs depending on the same axial position within the impeller, and is generally smaller on the side plate side than on the main plate side. be. Therefore, the relationship between the blade population angle β and the airflow inflow angle β is as shown in Figure 8.
Q: Sea urchin is inconsistent in most positions. However, since the cross-sectional shape of the blade plate 2 is wing-shaped, the blade population angle β
Range 1 where the difference between and the airflow inflow angle β is small
.
囲(図中斜線域)では、気流は羽根板2表面に沿って流
れる。In the area (hatched area in the figure), the airflow flows along the surface of the vane plate 2.
しかし、上記以外の部分では羽根人口角β と気流流入
角β。との差が大きすぎるため、気流が羽根板2の表面
に沿って流れず、第9図に示すように主板3側の断面で
は羽根板2の翼腹面2a側で気流が剥離し、側板4側の
断面では羽根板2の翼背面2b側で気流が剥離する。However, in areas other than the above, the blade population angle β and airflow inflow angle β. Since the difference between the blade plate 2 and In the side cross section, the airflow separates on the blade back surface 2b side of the blade plate 2.
この様な羽根板2周辺での気流の剥離は、流体効率を劣
化させ空力性能を劣化させると共に流体騒音を増加させ
る原因となっている。Such separation of airflow around the vane plate 2 causes deterioration of fluid efficiency, deterioration of aerodynamic performance, and increase of fluid noise.
発明が解決しようとする課題
以上のように従来の遠心送風機は、翼形に成形した羽根
板2の主板3側及び側板4側の部位で、翼腹面2a及び
翼背面2bで流れが剥離し易いため、空力性能が劣化し
、流体騒音が増加するなどの課題があった。Problems to be Solved by the Invention As described above, in the conventional centrifugal blower, the flow tends to separate at the blade ventral surface 2a and the blade rear surface 2b at the main plate 3 side and side plate 4 side of the blade plate 2 formed into an airfoil shape. Therefore, there were problems such as deterioration of aerodynamic performance and increase of fluid noise.
本発明は上記課題に鑑み、羽根車1内に流入した気流が
羽根板2間に流入する際の気流の剥離を防止し、空力性
能が高く、かつ流体麗音の低い低騒音の遠心送風機を提
供することを目的とするものである。In view of the above-mentioned problems, the present invention provides a low-noise centrifugal blower that prevents separation of the airflow when the airflow that flows into the impeller 1 flows between the blade plates 2, has high aerodynamic performance, and has low fluid noise. The purpose is to provide
課題を解決するための手段
本発明は上記課題を解決するだめ、羽根車の回転軸に直
交する各平面で羽根板を切断した時の断面において、羽
根板の羽根入口径を主板近傍断面から側板近傍断面に向
って漸次拡大すると共に、主板近傍の羽根板断面形状を
基準の翼形状として、翼背面線は各断面で略同一とし、
各断面の翼前縁を前記基準翼形状の翼背面線に近接させ
て羽根板の形状を形成するものである。Means for Solving the Problems In order to solve the above-mentioned problems, the present invention aims to change the blade inlet diameter of the blade plate from the cross section near the main plate to the side plate in a cross section when the blade plate is cut along each plane perpendicular to the rotation axis of the impeller. While gradually expanding toward the nearby cross section, the blade back surface line is approximately the same in each cross section, with the blade plate cross section shape near the main plate as the standard blade shape,
The blade shape is formed by bringing the blade leading edge of each section close to the blade back line of the reference blade shape.
作 用
従って、羽根板の各断面形状を翼形に保ったうえで、主
板近傍断面から側板近傍断面にかけて羽根人口角が徐々
に小さくなり、各断面において羽根人口角と気流流入角
との差が減少し、羽根車に流入した気流が羽根板間に流
入する際の気流の剥離を抑制する。このため、流体効率
が向上し空力性能が向上するとともに、流体騒音が低下
する。Function: Therefore, while maintaining the cross-sectional shape of each blade plate in the shape of an airfoil, the blade population angle gradually decreases from the cross section near the main plate to the cross section near the side plate, and the difference between the blade population angle and the airflow inflow angle in each cross section increases. This suppresses separation of the airflow when the airflow that flows into the impeller flows between the blade plates. Therefore, fluid efficiency is improved, aerodynamic performance is improved, and fluid noise is reduced.
実施例
以下、本発明の一実施例について、図面を参照しながら
説明する。尚、従来例と同一部分については重複を避け
るため、同一の番号を付けて説明を省略する。EXAMPLE Hereinafter, an example of the present invention will be described with reference to the drawings. Incidentally, in order to avoid duplication, the same parts as in the conventional example are given the same numbers and the description thereof will be omitted.
第1図は、本発明の実施例における遠心送風機の構造を
示すものである。FIG. 1 shows the structure of a centrifugal blower in an embodiment of the present invention.
8はプラスチック製の羽根車であシ、複数の羽によって
構成しである。8 is a plastic impeller, which is composed of a plurality of blades.
第2図は羽根車8を回転軸を含んだ平面で切断した時の
要部断面図であり、羽根板9の羽根入口径D1 を主板
部断面の径D1aに対し、側板部断面の径D1bをD1
b=1.16×D1a とし、さらに主板部から側板部
にかけて羽根入口径D1 を漸次拡大しである。又、側
板11の入口径D0は羽根板11の側板部の羽根入口径
D1bと略同一にしている。FIG. 2 is a cross-sectional view of the main part of the impeller 8 taken along a plane including the rotation axis, and shows the blade inlet diameter D1 of the blade plate 9 relative to the diameter D1a of the main plate cross-section and the diameter D1b of the side plate cross-section. D1
b=1.16×D1a, and the blade inlet diameter D1 is gradually expanded from the main plate part to the side plate part. Further, the inlet diameter D0 of the side plate 11 is made substantially the same as the blade inlet diameter D1b of the side plate portion of the blade plate 11.
第3図は羽根車8を回転軸に直交する平面で切断した時
の羽根板の断面図である。FIG. 3 is a sectional view of the blade plate when the impeller 8 is cut along a plane perpendicular to the rotation axis.
羽根板9は主板部での断面形状Hを基本の翼形状とし、
翼背面線12は各断面で略同一としてあリ、各断面にお
いて翼前縁13を基本翼断面形状Hの翼背面線12に近
接して設定し、翼腹面線14は翼前縁13と翼後縁16
をなめらかな曲線で結んでいる。The blade plate 9 has a cross-sectional shape H at the main plate portion as a basic blade shape,
The wing dorsal line 12 is substantially the same in each section, and in each section, the wing leading edge 13 is set close to the wing dorsal line 12 of the basic wing cross-sectional shape H, and the wing ventral line 14 is set close to the wing dorsal line 12 in each cross section. trailing edge 16
are connected by a smooth curve.
以上のように構成された遠心送風機の動作について以下
で説明する。The operation of the centrifugal blower configured as above will be explained below.
羽根板9は主板部から側板部に向って羽根入口径D1が
大となり、かつ各断面で翼前縁13を主板部の基本翼断
面形状Hの翼背面線12に近接させているため、羽根入
口角β1が主板部から側板部に向って漸次減少する。一
方、羽根車8に流入した気流は、羽根板9間に流入する
際には主板部では流入角β。が大きく、側板部では流入
角β。が小さくなる傾向であるから、羽根入口角β1
の分布と気流流入角β。の分布の傾向が一致する。従っ
て、羽根板9の各断面において、羽根人口角β1と気流
流入角β。の大きなズレがなくなり、流入気流の剥離が
抑制される。In the blade plate 9, the blade inlet diameter D1 increases from the main plate part to the side plate part, and the blade leading edge 13 in each cross section is brought close to the blade back line 12 of the basic blade cross-sectional shape H of the main plate part. The entrance angle β1 gradually decreases from the main plate portion to the side plate portions. On the other hand, when the airflow that has entered the impeller 8 flows between the blade plates 9, the airflow has an inflow angle β at the main plate portion. is large, and the inflow angle is β at the side plate. has a tendency to become smaller, so the blade entrance angle β1
distribution and airflow inflow angle β. The trends of the distributions match. Therefore, in each cross section of the blade plate 9, the blade population angle β1 and the airflow inflow angle β. This eliminates large deviations in the flow rate and prevents separation of the incoming airflow.
第4図は、空力特性と騒音特性を示したものであるが、
従来の遠心送風機に比べ、小流量域を除いては静圧が高
くとれ、騒音が低くなっておシ、幅広い動作点で空力性
能が向上し、流体騒音が低下している。なお、第4図に
おいて、実線は本発明の例を示し、破線は従来例を示す
。Figure 4 shows the aerodynamic characteristics and noise characteristics.
Compared to conventional centrifugal blowers, it has higher static pressure and lower noise except in small flow areas, improves aerodynamic performance over a wide range of operating points, and reduces fluid noise. In addition, in FIG. 4, a solid line shows an example of the present invention, and a broken line shows a conventional example.
しかも、羽根板9の各断面形状は全て主板部の基本翼断
面形状Hに内包されるため、羽根板9と主板1oとをイ
ンジェクション成形等の一体成形する場合でも金型から
離脱が容易で、生産性の高い構造とすることができる等
実用効果の大きいものである。Moreover, since each cross-sectional shape of the blade plate 9 is all included in the basic blade cross-sectional shape H of the main plate portion, even when the blade plate 9 and the main plate 1o are integrally molded by injection molding or the like, they can be easily removed from the mold. This has great practical effects, such as being able to create a structure with high productivity.
発明の効果
以上のように本発明の遠心送風機は、羽根車の回転軸に
直交する各平面で羽根板を切断した時の断面において、
羽根板の羽根入口径を主板近傍断面から側板近傍断面に
向って漸次拡大すると共に、主板近傍の羽根板断面形状
を基準の翼形状として、各断面で翼背面線を略同一とし
翼前縁を前記基準翼形状の翼背面線に近接させて羽根板
の形状を形成しているため、羽根板の入口部での流入気
流の剥離を抑制し、空力性能を向上させると共に流体騒
音を低減する効果がある。Effects of the Invention As described above, the centrifugal blower of the present invention has a cross section when the blade plate is cut along each plane perpendicular to the rotation axis of the impeller.
The diameter of the blade inlet of the blade plate is gradually expanded from the cross section near the main plate to the cross section near the side plate, and the cross-sectional shape of the blade plate near the main plate is taken as the standard blade shape, and the blade back line is approximately the same in each cross section, and the leading edge of the blade is Since the shape of the vane is formed close to the blade dorsal line of the reference vane shape, separation of the incoming airflow at the inlet of the vane is suppressed, improving aerodynamic performance and reducing fluid noise. There is.
第1図は本発明の一実施例による遠心送風機の断面図、
第2図は第1図の羽根車の要部断面図、第3図は第2図
のA−C断面を重ね合わせた断面図、第4図は本実施例
による空力性能・騒音性能特性図、第5図は従来の遠心
送風機の断面図、第6図は第6図のD−F断面図、第7
図は従来例における羽根入口部の気流流入角の分布特性
図、第8図は第5図のD−D断面における流れの模式図
、第9図は第6図のF−F断面における流れの模式%式
%
代理人の氏名 弁理士 粟 野 重 孝 ほか1名第
図
萬
図
量
?
羽 根 板
13−− 1 iFl 織
第
図FIG. 1 is a sectional view of a centrifugal blower according to an embodiment of the present invention;
Fig. 2 is a cross-sectional view of the main part of the impeller shown in Fig. 1, Fig. 3 is a cross-sectional view of the A-C cross section of Fig. 2 superimposed, and Fig. 4 is a diagram of aerodynamic performance and noise performance characteristics according to this embodiment. , Fig. 5 is a sectional view of a conventional centrifugal blower, Fig. 6 is a sectional view taken along line D-F in Fig.
The figure shows the distribution characteristics of the airflow inlet angle at the vane inlet in the conventional example, Figure 8 is a schematic diagram of the flow at the D-D cross section in Figure 5, and Figure 9 shows the flow at the F-F cross section in Figure 6. Model % formula % Agent's name Patent attorney Shigetaka Awano and 1 other person Figure 1: Quantity? Vane plate 13-- 1 iFl weave diagram
Claims (1)
根板の反主板側端面に固定した側板とで羽根車を構成し
、前記羽根車の回転軸に直交する各平面で羽根板を切断
した時の断面において、羽根板の羽根入口径を主板部断
面から側板部断面に向って漸次拡大すると共に、羽根板
の主板部の断面形状を基準の翼形状として翼背面線を各
断面で略同一とし、各断面において翼前縁を前記基準翼
形状の翼背面線に近接させて翼形状を形成した遠心送風
機。An impeller is constituted by a plurality of blade plates, a main plate to which the blade plates are fixed, and a side plate fixed to the end surface of the blade plate on the side opposite to the main plate, and the blade plate is fixed in each plane perpendicular to the rotation axis of the impeller. In the cross section when cut, the blade inlet diameter of the blade plate is gradually expanded from the main plate section to the side plate section, and the blade back line is set in each cross section using the cross-sectional shape of the main plate section of the blade plate as the standard blade shape. A centrifugal blower in which the blade shapes are substantially the same and each cross section has a blade leading edge close to a blade back line of the reference blade shape.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP63222736A JP2537987B2 (en) | 1988-09-06 | 1988-09-06 | Centrifugal blower |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP63222736A JP2537987B2 (en) | 1988-09-06 | 1988-09-06 | Centrifugal blower |
Publications (2)
Publication Number | Publication Date |
---|---|
JPH0270997A true JPH0270997A (en) | 1990-03-09 |
JP2537987B2 JP2537987B2 (en) | 1996-09-25 |
Family
ID=16787095
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP63222736A Expired - Lifetime JP2537987B2 (en) | 1988-09-06 | 1988-09-06 | Centrifugal blower |
Country Status (1)
Country | Link |
---|---|
JP (1) | JP2537987B2 (en) |
Cited By (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2005320881A (en) * | 2004-05-07 | 2005-11-17 | Matsushita Electric Ind Co Ltd | Turbo fan and air conditioner using the same |
JP2007170331A (en) * | 2005-12-26 | 2007-07-05 | Daikin Ind Ltd | Turbofan and indoor unit of air conditioner using it |
JP2007170771A (en) * | 2005-12-26 | 2007-07-05 | Daikin Ind Ltd | Turbofan and indoor unit of air conditioner using the same |
WO2009139422A1 (en) * | 2008-05-14 | 2009-11-19 | ダイキン工業株式会社 | Centrifugal fan |
US8870541B2 (en) | 2010-03-16 | 2014-10-28 | Denso Corporation | Centrifugal multiblade fan |
WO2023032762A1 (en) * | 2021-09-02 | 2023-03-09 | 株式会社デンソー | Centrifugal fan |
-
1988
- 1988-09-06 JP JP63222736A patent/JP2537987B2/en not_active Expired - Lifetime
Cited By (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2005320881A (en) * | 2004-05-07 | 2005-11-17 | Matsushita Electric Ind Co Ltd | Turbo fan and air conditioner using the same |
JP4590923B2 (en) * | 2004-05-07 | 2010-12-01 | パナソニック株式会社 | Turbofan and air conditioner using the same |
JP2007170331A (en) * | 2005-12-26 | 2007-07-05 | Daikin Ind Ltd | Turbofan and indoor unit of air conditioner using it |
JP2007170771A (en) * | 2005-12-26 | 2007-07-05 | Daikin Ind Ltd | Turbofan and indoor unit of air conditioner using the same |
WO2009139422A1 (en) * | 2008-05-14 | 2009-11-19 | ダイキン工業株式会社 | Centrifugal fan |
US8870541B2 (en) | 2010-03-16 | 2014-10-28 | Denso Corporation | Centrifugal multiblade fan |
WO2023032762A1 (en) * | 2021-09-02 | 2023-03-09 | 株式会社デンソー | Centrifugal fan |
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