JP2871515B2 - Centrifugal blower - Google Patents
Centrifugal blowerInfo
- Publication number
- JP2871515B2 JP2871515B2 JP4564695A JP4564695A JP2871515B2 JP 2871515 B2 JP2871515 B2 JP 2871515B2 JP 4564695 A JP4564695 A JP 4564695A JP 4564695 A JP4564695 A JP 4564695A JP 2871515 B2 JP2871515 B2 JP 2871515B2
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- Japan
- Prior art keywords
- blade
- plate
- section
- impeller
- cross
- 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.)
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- Structures Of Non-Positive Displacement Pumps (AREA)
Description
【発明の詳細な説明】DETAILED DESCRIPTION OF THE INVENTION
【０００１】[0001]
【産業上の利用分野】本発明は、空気調和機などに用い
られる低騒音化を図った遠心送風機に関するものであ
る。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a low noise centrifugal blower used for an air conditioner or the like.
【０００２】[0002]
【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、近年は特に高性
能化・低騒音化に対する要請が非常に強くなっており、
羽根車形状の改善による性能改善方法が提案されてい
る。2. Description of the Related Art Conventionally, centrifugal blowers have been widely used as blowers for air conditioners and the like. In recent years, demands for higher performance and lower noise have become very strong.
A method for improving performance by improving the shape of an impeller has been proposed.
【０００３】以下、図面を参照しながら、実開昭６３−
２４８２２３号公報などで提案されている従来の遠心送
風機について説明する。Hereinafter, with reference to the drawings,
A conventional centrifugal blower proposed in 248223 and the like will be described.
【０００４】図１１〜図１３は従来の遠心式送風機の構
成を示すものである。図において１は羽根車であり、複
数の羽根板２と、羽根板２を固定した主板３と、羽根板
２の反主板側端面に固定し吸込口４ａを有する側板４よ
り構成されている。５は羽根車１に直結したモ−タであ
り、羽根車１とモ−タ５を収納するケーシング６に固定
されている。７は入口端部７ａから出口端部７ｂにかけ
て湾曲しかつ出口端部７ｂの内径を吸込部最小径より大
とした吸込リングでありケーシング６に固定されてい
る。吸込リング７の出口端部７ｂは羽根車１の側板４の
吸込口４ａの近傍に挿入されている。FIGS. 11 to 13 show the configuration of a conventional centrifugal blower. In FIG. 1, reference numeral 1 denotes an impeller, which includes a plurality of blades 2, a main plate 3 to which the blades 2 are fixed, and a side plate 4 fixed to an end surface of the blades 2 on the side opposite to the main plate and having a suction port 4a. Reference numeral 5 denotes a motor directly connected to the impeller 1, which is fixed to a casing 6 that houses the impeller 1 and the motor 5. Reference numeral 7 denotes a suction ring which is curved from the inlet end 7a to the outlet end 7b and has an inner diameter of the outlet end 7b larger than the minimum diameter of the suction portion, and is fixed to the casing 6. The outlet end 7b of the suction ring 7 is inserted into the side plate 4 of the impeller 1 near the suction port 4a.
【０００５】また、羽根車１の吸込口径ｄs は羽根入口
径ｄ1 より大きく設定されている。さらに、羽根車１の
回転軸に直交する羽根断面において、主板３近傍の羽根
断面Ａ−Ａから側板４に接する羽根断面Ｂ−Ｂまでは図
１３に示す略同一断面形状としてあり、羽根断面Ｂ−Ｂ
よりさらに上の羽根上端部２a の断面では羽根板２の負
圧面側の板厚を徐々に薄くすると共に羽根板２の先端を
滑らかな曲面状にしてある（図示せず）。[0005] The inlet diameter ds of the impeller 1 is set larger than the blade inlet diameter d1. Further, in the blade cross section orthogonal to the rotation axis of the impeller 1, the blade cross section AA near the main plate 3 to the blade cross section BB in contact with the side plate 4 have substantially the same cross sectional shape as shown in FIG. -B
In the cross section of the upper end portion 2a of the blade, the thickness of the blade plate 2 on the suction side is gradually reduced, and the tip of the blade plate 2 has a smooth curved surface (not shown).
【０００６】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 described above will be described below.
【０００７】まず、モ−タ５の駆動力によって羽根車１
が回転すると、吸込リング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、
さらにケ−シング吹き出し口（図示せず）より吐出され
送風作用を為す。First, the impeller 1 is driven by the driving force of the motor 5.
Rotates, air is introduced into the impeller 1 through the suction ring 7, and is applied with static pressure and dynamic pressure when passing between the plurality of blade plates 2, and is discharged from the impeller 1 into the casing 6,
Further, the air is discharged from a casing outlet (not shown) to perform a blowing operation.
【０００８】このとき、羽根板２の吸込口径ｄS は羽根
入口径ｄ1 より大きく設定しているため、羽根車１の吸
込口４ａより流入する気流の平均流速は比較的低速とな
り羽根板２の先端から流入する際の衝突損失を低く抑
え、また羽根上端部２a より流入する気流に対しても羽
根上端部２a の形状を負圧面で薄く形成してあるため羽
根上端部２a における流入気流の剥離を抑制する作用を
為す。At this time, since the suction port diameter dS of the blade plate 2 is set to be larger than the blade inlet diameter d1, the average flow velocity of the airflow flowing from the suction port 4a of the impeller 1 becomes relatively low and the tip of the blade plate 2 The upper end 2a of the blade is formed thin on the negative pressure surface with respect to the airflow flowing from the upper end 2a of the blade, so that the separation of the inflow airflow at the upper end 2a of the blade is suppressed. It acts to suppress.
【０００９】[0009]
【発明が解決しようとする課題】しかしながら上記のよ
うな構成では、羽根車１内に流入した気流は吸込口４a
における軸方向の流れが羽根板２間に流入する際に流れ
の方向が半径方向へ曲がるため、側板４に近いほど気流
の曲率が大きくなり流速が低下する。ところが、側板４
近傍の羽根板２の断面形状と主板３近傍の羽根板２の断
面形状は同等であり羽根板２が気流に与える作用も同等
となる。However, in the above-described configuration, the airflow that has flowed into the impeller 1 is not supplied to the suction port 4a.
When the flow in the axial direction flows into the space between the blade plates 2, the flow direction is bent in the radial direction. Therefore, the curvature of the air flow increases and the flow velocity decreases as the air flow approaches the side plate 4. However, the side plate 4
The cross-sectional shape of the blade plate 2 in the vicinity and the cross-sectional shape of the blade plate 2 in the vicinity of the main plate 3 are equal, and the action of the blade plate 2 on the air flow is also equal.
【００１０】従って、側板４の近傍では羽根板２に流入
する気流の速度が低いために羽根板２の出口における気
流速度も低くなり、図１４に示すように羽根車１出口に
おける気流の流速分布は、側板４側では流速が主板３側
の流速にくらべ大幅に低下し遠心送風機の送風性能及び
送風効率を低下させ、さらにこの側板２近傍の流速の低
下が側板近傍の気流の剥離と乱れを引き起こし乱流騒音
を増加させるという問題があった。Therefore, near the side plate 4, the velocity of the airflow flowing into the impeller 2 is low, so that the velocity of the airflow at the exit of the impeller 2 is also low. As shown in FIG. Is that the flow velocity on the side plate 4 side is greatly reduced as compared with the flow velocity on the main plate 3 side, so that the blowing performance and efficiency of the centrifugal blower are reduced. Further, the decrease in the flow velocity near the side plate 2 causes the separation and turbulence of the air flow near the side plate. There is a problem of causing turbulence noise.
【００１１】本発明は上記課題に鑑み、側板側の気流流
速を増速し、羽根車出口における気流分布を均一化する
ことにより送風性能を改善し、側板近傍の気流の剥離と
乱れを抑制することにより、乱流騒音を低減することの
できる遠心送風機を提供するものである。SUMMARY OF THE INVENTION In view of the above problems, the present invention increases the airflow velocity on the side plate side, makes the airflow distribution at the impeller outlet uniform, improves the air blowing performance, and suppresses the separation and turbulence of the airflow near the side plate. Accordingly, a centrifugal blower capable of reducing turbulent noise is provided.
【００１２】[0012]
【課題を解決するための手段】上記課題を解決するため
に本発明の遠心送風機は、主板と複数の羽根板と吸込口
を有する側板から成る羽根車と、側板の吸込口に挿入し
た吸込リングとを有し、前記羽根車の回転軸に直交する
羽根断面において、主板近傍羽根断面の羽根出口角β2h
に対して側板に接する羽根断面の羽根出口角β2sをβ2h
＋５゜≦β2s≦β2h＋１５゜として主板から側板までの
羽根の断面形状を連続的に変化させ、かつ主板近傍羽根
断面から側板に接する羽根断面までの羽根取付角の平均
値γo を４３゜≦γo ≦４６゜としたのである。In order to solve the above-mentioned problems, a centrifugal blower according to the present invention comprises an impeller comprising a main plate, a plurality of blade plates and a side plate having a suction port, and a suction ring inserted into a suction port of the side plate. And a blade exit angle β2h of a blade cross section near the main plate in a blade cross section orthogonal to the rotation axis of the impeller.
The blade exit angle β2s of the blade cross-section in contact with the side plate to β2h
+ 5 ° ≦ β2s ≦ β2h + 15 °, continuously changing the cross-sectional shape of the blade from the main plate to the side plate, and setting the average value γo of the blade mounting angle from the cross section of the blade near the main plate to the cross section of the blade in contact with the side plate as 43 ° ≦ γo ≦ 46 °.
【００１３】また他の本発明の遠心送風機は、上記構成
に加えて前記羽根車の回転軸に直交する各羽根断面にお
いて、各羽根板断面形状を翼形に形成したうえ、羽根入
口部を主板部の羽根断面に内包させた構成を備えるもの
である。According to another centrifugal blower of the present invention, in addition to the above-described structure, in each blade cross section orthogonal to the rotation axis of the impeller, each blade plate has a blade-shaped cross-sectional shape, and the blade inlet portion has a main plate. It is provided with a configuration included in the blade section of the section.
【００１４】[0014]
【作用】本発明では、主板側の羽根板の羽根出口角に対
して側板側の羽根板の羽根出口角を適正な範囲内で大き
くすることにより、側板側の羽根板の仕事量を主板側羽
根板の仕事量より増加させて側板側の流速を増速させ羽
根車出口における気流分布を均一化するとともに、側板
近傍の流れの急減速による流れの乱れの発生の抑制及び
側板表面の乱流境界層の発達と剥離による流れの乱れを
抑制し、流れの乱れによる乱流騒音の発生を抑える。さ
らに、主板近傍羽根断面から側板に接する羽根断面まで
の羽根取付角の平均値を適正な値に設定することによ
り、各羽根断面において羽根圧力面および負圧面におけ
る気流の剥離を抑制し、側板側の羽根出口角増加を効果
的に発生させる。According to the present invention, the work volume of the side plate-side blade is increased by increasing the blade exit angle of the side plate-side blade within an appropriate range with respect to the blade exit angle of the main plate-side blade. Increasing the work volume of the blade plate to increase the flow velocity on the side plate side to equalize the airflow distribution at the exit of the impeller, suppress the occurrence of flow turbulence due to rapid deceleration of the flow near the side plate, and turbulence on the side plate surface The turbulence of the flow due to the development and separation of the boundary layer is suppressed, and the generation of turbulent noise due to the turbulence of the flow is suppressed. Furthermore, by setting the average value of the blade mounting angle from the blade cross section near the main plate to the blade cross section in contact with the side plate to an appropriate value, the separation of the airflow on the blade pressure surface and the negative pressure surface in each blade cross section is suppressed, and the side plate side Effectively increases the blade exit angle.
【００１５】また、羽根車の回転軸に直交する各羽根断
面において、各羽根入口部断面を主板部の羽根入口部断
面に内包させることにより、側板側の羽根板後縁部は羽
根車回転方向に前傾するが羽根板前縁部は主板に対して
傾斜することはなく、羽根板は羽根板の厚みが大きい前
縁部が主板に垂直に接することになり、主板と羽根板の
接合強度が増加し、送風性能を向上させ送風騒音を低減
させたうえ、羽根車の機械的強度を高めることができ
る。しかも、羽根車を制作する際には、羽根板を負圧面
側と圧力面側に分割した別体の可動金型で成形すること
により、羽根板と主板の樹脂一体成形を可能にする。Further, in each blade section orthogonal to the rotation axis of the impeller, each blade inlet section is included in the blade inlet section of the main plate section, so that the trailing edge of the blade on the side plate side is in the impeller rotation direction. The front edge of the blade plate does not tilt with respect to the main plate, and the front edge portion of the blade plate where the thickness of the blade plate is large comes into perpendicular contact with the main plate, and the joining strength between the main plate and the blade plate is reduced. It is possible to improve the blowing performance, reduce the blowing noise and increase the mechanical strength of the impeller. In addition, when the impeller is manufactured, the blade plate and the main plate can be integrally molded with a resin by forming the blade plate with a separate movable mold that is divided into a suction surface side and a pressure surface side.
【００１６】[0016]
【実施例】以下、本発明による第１の実施例について、
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、同一の符号を付けて説明を
省略する。DESCRIPTION OF THE PREFERRED EMBODIMENTS Hereinafter, a first embodiment according to the present invention will be described.
This will be described with reference to the drawings. The same parts as in the conventional example are denoted by the same reference numerals to avoid duplication, and description thereof will be omitted.
【００１７】図１〜図５は本発明の第１の実施例におけ
る遠心送風機の構造を示すものである。1 to 5 show the structure of a centrifugal blower according to a first embodiment of the present invention.
【００１８】８は羽根車であり、複数の羽根板９と、主
板１０と、側板１１とで構成している。１１a は側板１
１に設けた吸込口である。羽根車８の吸込口径Ｄs は、
羽根入口径Ｄ1 より大きく設定してある。Reference numeral 8 denotes an impeller, which comprises a plurality of blades 9, a main plate 10, and side plates 11. 11a is the side plate 1
This is the suction port provided in 1. The suction diameter Ds of the impeller 8 is
It is set larger than the blade inlet diameter D1.
【００１９】さらに、羽根車８の回転軸に直交する羽根
断面において、主板１０近傍の断面線Ｃ−Ｃにおける羽
根板断面９h の羽根出口角β2hを３５゜に設定し、この
β2hに対して側板１１に接する断面線Ｄ−Ｄにおける羽
根板断面９s の羽根出口角β2sをβ2h＋５゜≦β2s≦β
2h＋１５゜の範囲内に設定してあり、主板１０近傍から
側板１１に接する部分までの羽根板９の断面形状を連続
的に変化させてある。Further, in the blade section perpendicular to the rotation axis of the impeller 8, the blade exit angle β2h of the blade section 9h at the section line CC near the main plate 10 is set to 35 °, and the side plate is The blade exit angle β2s of the blade section 9s at the section line DD tangent to 11 is β2h + 5 ° ≦ β2s ≦ β
It is set within the range of 2h + 15 °, and the sectional shape of the blade plate 9 from the vicinity of the main plate 10 to the portion in contact with the side plate 11 is continuously changed.
【００２０】また、羽根板断面９h の羽根取付角γh を
４５゜とし、羽根板断面９s の羽根取付角γs を４３゜
に設定し、主板１０近傍の羽根板断面９h から側板１１
に接する羽根板断面９s までの羽根取付角の平均値γo
を４４．５゜として４３゜≦γo ≦４６゜の範囲内に設
定してある。Further, the blade mounting angle γh of the blade plate section 9h is set to 45 °, the blade mounting angle γs of the blade plate section 9s is set to 43 °, and the side plate 11 is cut from the blade plate cross section 9h near the main plate 10.
Mean value of blade mounting angle γo up to 9s of blade plate section in contact with
Is set to 44.5 ° within a range of 43 ° ≦ γo ≦ 46 °.
【００２１】また、断面線Ｄ−Ｄよりさらに上の羽根上
端部９a の羽根断面では羽根板９の負圧面側の板厚を徐
々に薄くすると共に羽根板９a の先端を滑らかな曲面状
にしてある（図示せず）。Further, in the blade cross section of the upper end portion 9a of the blade which is higher than the sectional line DD, the thickness of the blade 9 on the negative pressure side is gradually reduced and the tip of the blade 9a is formed into a smooth curved surface. (Not shown).
【００２２】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 described above will be described below.
【００２３】まず、モ−タ５の駆動力によって羽根車８
が回転すると、吸込リング７を介して空気が羽根車８内
に導入され、複数の羽根板９間を通過する際に静圧と動
圧を付加され羽根車８からケーシング６内に吐出され、
さらにケ−シング吹き出し口（図示せず）より吐出され
送風作用を為す。First, the impeller 8 is driven by the driving force of the motor 5.
Is rotated, air is introduced into the impeller 8 through the suction ring 7, static pressure and dynamic pressure are applied when passing between the plurality of blade plates 9, and the air is discharged from the impeller 8 into the casing 6,
Further, the air is discharged from a casing outlet (not shown) to perform a blowing operation.
【００２４】このとき、従来例と同様に羽根板９の吸込
口径Ｄs は羽根入口径Ｄ1 より大きく設定しているた
め、羽根車１の吸込口１１ａより流入する気流の平均流
速は比較的低速となり羽根板９の先端から流入する際の
衝突損失を低く抑え、また羽根の上端部より流入する気
流に対しても羽根上端部９a の形状を負圧面で薄く形成
してあるため上端部９a における流入気流の剥離を抑制
する作用を為す。At this time, as in the conventional example, the suction port diameter Ds of the blade plate 9 is set to be larger than the blade inlet diameter D1, so that the average flow velocity of the airflow flowing from the suction port 11a of the impeller 1 becomes relatively low. Collision loss at the time of inflow from the tip of the blade plate 9 is kept low, and the shape of the blade upper end 9a is made thinner on the negative pressure surface against the airflow flowing from the upper end of the blade. It acts to suppress airflow separation.
【００２５】本実施例では、主板１０側の羽根板断面９
h の羽根出口角β2hに対して側板１１側の羽根板断面９
s の羽根出口角β2sを大きくしていることにより、側板
１１側の羽根板９の仕事量を主板１０側羽根板９の仕事
量より増加させている。これによって、図６に示すよう
に側板側１１の羽根車８出口の流速を増速させ、羽根車
８出口における気流分布を均一化し、送風性能は向上す
る。さらに、この作用によって側板１１近傍の流れの急
減速による流れの乱れの発生を抑制し、かつ側板１１表
面の乱流境界層の発達と剥離による流れの乱れを抑制
し、流れの乱れによる乱流騒音の発生が低減される。In this embodiment, the blade plate section 9 on the main plate 10 side
h for the blade exit angle β2h, the blade plate cross section 9 on the side plate 11 side
By increasing the blade exit angle β2s of s, the work amount of the blade plate 9 on the side plate 11 side is made larger than the work amount of the blade plate 9 on the main plate 10 side. Thus, as shown in FIG. 6, the flow velocity at the exit of the impeller 8 on the side plate 11 is increased, the airflow distribution at the exit of the impeller 8 is made uniform, and the blowing performance is improved. Further, by this action, the occurrence of flow turbulence due to rapid deceleration of the flow near the side plate 11 is suppressed, and the flow turbulence due to the development and separation of the turbulent boundary layer on the surface of the side plate 11 is suppressed. Noise generation is reduced.
【００２６】しかし、側板１１側の羽根板断面９s の羽
根出口角β2sを大きくする場合、主板１０側の羽根板断
面９h の羽根出口角β2hに比較して羽根出口角β2sをあ
まり大きくし過ぎると羽根板断面９s の後縁部での気流
角度と羽根板断面９s の後縁部角度との差が拡大するた
め、羽根板断面９s の後縁部の流れが剥離しやすくな
り、損失が増加するとともに乱流騒音が増加する。従っ
て、羽根出口角β2sの最適値が存在する。However, when increasing the blade exit angle β2s of the blade plate section 9s on the side plate 11 side, if the blade exit angle β2s is too large compared to the blade exit angle β2h of the blade plate section 9h on the main plate 10 side. Since the difference between the airflow angle at the trailing edge of the slat section 9s and the trailing edge angle of the slat section 9s is enlarged, the flow at the trailing edge of the slat section 9s is likely to be separated, increasing the loss. At the same time, turbulent noise increases. Therefore, there is an optimum value of the blade outlet angle β2s.
【００２７】図７は主板１０側の羽根板断面９h の羽根
出口角β2hに対する側板１１側の羽根板断面９s の羽根
出口角β2sの値と遠心送風機の送風騒音の関係を示すも
のであり、羽根出口角β2sをβ2h＋αと表現すると、α
が５゜≦α≦１５゜の範囲であれば騒音レベルは十分低
い値となる。また、羽根板９周りの気流が剥離せずに流
動するためには羽根板９の取付角γが適正に設定される
必要がある。図８は主板１０近傍の羽根板断面９h から
側板１１に接する羽根板断面９s までの羽根取付角γの
平均値γo と遠心送風機の送風騒音の関係を示すもので
あり、γo が４３゜≦γo ≦４６゜の範囲であれば騒音
レベルは十分低い値となる。FIG. 7 shows the relationship between the value of the blade outlet angle β2s of the blade plate section 9s on the side plate 11 side with respect to the blade outlet angle β2h of the blade plate section 9h on the main plate 10 side and the blowing noise of the centrifugal blower. When the exit angle β2s is expressed as β2h + α, α
Is within the range of 5 ° ≦ α ≦ 15 °, the noise level is a sufficiently low value. In addition, in order for the airflow around the blade plate 9 to flow without separating, the mounting angle γ of the blade plate 9 needs to be appropriately set. FIG. 8 shows the relationship between the average value γo of the blade mounting angle γ from the blade plate section 9h near the main plate 10 to the blade plate section 9s in contact with the side plate 11 and the blowing noise of the centrifugal blower, where γo is 43 ° ≦ γo. If it is in the range of ≦ 46 °, the noise level is a sufficiently low value.
【００２８】以上のように本実施例の遠心式送風機は、
羽根車８の回転軸に直交する羽根断面において、主板１
０近傍の断面線Ｃ−Ｃにおける羽根板断面９h の羽根出
口角β2hに対して側板１１に接する断面線Ｄ−Ｄにおけ
る羽根板断面９s の羽根出口角β2sをβ2h＋５゜≦β2s
≦β2h＋１５゜の範囲内に設定し、主板１０近傍から側
板１１に接する部分までの羽根板９の断面形状を連続的
に変化させ、かつ、主板１０近傍の羽根板断面９h から
側板１１に接する羽根板断面９s までの羽根取付角の平
均値γo を４３゜≦γo ≦４６゜の範囲内に設定するこ
とにより、羽根車８出口の気流速度分布を均一化して送
風性能を向上させると共に、側板１１側の羽根板断面９
s の後縁部の流れの剥離を抑制し、各羽根断面において
羽根圧力面および負圧面における気流の剥離を抑制する
ため、送風性能の向上と送風騒音の低減を効果的に実現
することができる。As described above, the centrifugal blower of this embodiment is
In a blade section perpendicular to the rotation axis of the impeller 8, the main plate 1
The blade exit angle β2s of the blade section 9s at the section line DD which is in contact with the side plate 11 is β2h + 5 ° ≦ β2s with respect to the blade exit angle β2h of the section section 9h at the section line CC near 0.
.Ltoreq..beta.2h + 15.degree., The cross-sectional shape of the wing plate 9 from the vicinity of the main plate 10 to the portion in contact with the side plate 11 is continuously changed, and the wing plate 9 is in contact with the side plate 11 from the wing plate cross-section 9h near the main plate 10. By setting the average value γo of the blade mounting angles up to the plate cross section 9s within the range of 43 ° ≦ γo ≦ 46 °, the airflow velocity distribution at the exit of the impeller 8 is made uniform, and the air blowing performance is improved. Side slat section 9
The separation of the flow at the trailing edge of the s is suppressed, and the separation of the airflow at the blade pressure surface and the negative pressure surface at each blade cross-section can be effectively improved, thereby improving the blowing performance and reducing the blowing noise. .
【００２９】尚、本実施例では羽根板９の吸込口径Ｄs
は羽根入口径Ｄ1 より大きく設定しているが、羽根入口
径Ｄ1 を羽根車外径Ｄ2 に対して０．６７５Ｄ2 ≦Ｄ1
≦０．８Ｄ2 としたうえ、前記側板１１の吸込口径Ｄs
を０．７５Ｄ2 ≦Ｄs ≦０．９Ｄ2 の範囲に設定するの
が望ましい。また、主板１０近傍の羽根板断面９h の羽
根出口角β2hを３５゜に設定したが、３０゜≦β2h≦４
５゜の範囲に設定するのが望ましい。In this embodiment, the suction aperture Ds of the blade 9 is
Is set to be larger than the blade inlet diameter D1, but the blade inlet diameter D1 is set to 0.675 D2 ≤ D1 with respect to the impeller outer diameter D2.
.Ltoreq.0.8D2, and the suction port diameter Ds of the side plate 11.
Is desirably set in the range of 0.75D2 .ltoreq.Ds .ltoreq.0.9D2. Although the blade outlet angle β2h of the blade plate cross section 9h near the main plate 10 is set to 35 °, 30 ° ≦ β2h ≦ 4
It is desirable to set it within the range of 5 °.
【００３０】次に、本発明による遠心送風機の第２の実
施例について図面を参照しながら説明する。Next, a second embodiment of the centrifugal blower according to the present invention will be described with reference to the drawings.
【００３１】図９は、本発明の第２の実施例による遠心
送風機の羽根板断面形状を示すものである。第１の実施
例と異なるのは、羽根車８の回転軸に直交する断面にお
いて、主板１０近傍の羽根板断面１２a から側板１１近
傍の羽根板断面１２b までの各断面形状を翼型に形成し
たうえ、羽根前縁部形状が主板１０近傍の羽根断面形状
１２a の羽根前縁部形状に内包させる形状とした点にあ
る。FIG. 9 shows a sectional shape of a blade of a centrifugal blower according to a second embodiment of the present invention. The difference from the first embodiment is that in the cross section orthogonal to the rotation axis of the impeller 8, each cross-sectional shape from the blade plate cross section 12a near the main plate 10 to the blade plate cross section 12b near the side plate 11 is formed into an airfoil. Further, the shape of the leading edge of the blade is such that the shape of the leading edge of the blade in the blade sectional shape 12a near the main plate 10 is included.
【００３２】以上のように構成された第２の実施例の遠
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 of the second embodiment configured as described above will be described below.
【００３３】第１の実施例と同様に、主板１０近傍の羽
根板断面１２a の羽根出口角β2hに対して側板１１に接
する羽根板断面１２b の羽根出口角β2sをβ2h＋５゜≦
β2s≦β2h＋１５゜の範囲内に設定し、主板１０近傍か
ら側板１１に接する部分までの羽根板９の断面形状を連
続的に変化させ、かつ、主板１０近傍の羽根板断面９h
から側板１１に接する羽根板断面９s までの羽根取付角
の平均値γo を４３゜≦γo≦４６゜の範囲内に設定し
てあるので、送風性能が向上し送風騒音が低減する。Similarly to the first embodiment, the blade outlet angle β2s of the blade plate section 12b in contact with the side plate 11 is set to β2h + 5 ° ≦ the blade outlet angle β2h of the blade plate section 12a near the main plate 10.
β2s ≦ β2h + 15 °, the cross-sectional shape of the blade 9 from the vicinity of the main plate 10 to the portion in contact with the side plate 11 is continuously changed, and the cross-section 9h of the blade near the main plate 10
Is set within the range of 43 ° ≦ γo ≦ 46 °, so that the blowing performance is improved and the blowing noise is reduced.
【００３４】さらに、主板１０近傍の羽根板断面１２a
から側板１１近傍の羽根板断面１２b までの各断面形状
を羽根前縁部形状が主板１０近傍の羽根断面形状１２a
の羽根前縁部形状に内包させる形状としており、羽根板
１２の後縁部は羽根車８の回転方向に前傾するが、羽根
板１２の前縁部は傾斜することがないため、羽根板１２
は羽根の厚みが大きい前縁部が主板１０に略垂直に接す
ることになり、主板１０と羽根板１２の接合強度が増加
し、羽根車８の機械的強度を高めることができる。Further, the blade plate section 12a near the main plate 10
From the blade plate section 12b near the side plate 11 to the blade cross section 12a near the main plate 10
The rear edge of the blade plate 12 tilts forward in the rotation direction of the impeller 8, but the front edge of the blade plate 12 does not tilt. 12
The leading edge of the blade having a large thickness comes into contact with the main plate 10 substantially perpendicularly, so that the bonding strength between the main plate 10 and the blade plate 12 increases, and the mechanical strength of the impeller 8 can be increased.
【００３５】しかも、羽根車８を制作する際には、図１
０に示すように羽根板１２の負圧面側に接し羽根車８の
回転軸方向にスライドする金型１３と、羽根板１２の圧
力面側に接し羽根車８の半径方向にスライドする金型１
４とに分割した別体の可動金型で成形することにより、
羽根板１２と主板１０の樹脂一体成形を可能とし、羽根
車８の組立精度向上と生産性の向上を実現することがで
きる。Moreover, when producing the impeller 8, FIG.
As shown in FIG. 0, a mold 13 that contacts the negative pressure surface side of the blade plate 12 and slides in the rotation axis direction of the impeller 8, and a mold 1 that contacts the pressure surface side of the blade plate 12 and slides in the radial direction of the impeller 8.
By molding with a separate movable mold divided into 4 and
It is possible to integrally mold the blade plate 12 and the main plate 10 with resin, and it is possible to improve the assembling accuracy of the impeller 8 and the productivity.
【００３６】以上のように、本実施例の遠心送風機は、
羽根車８の回転軸に直交する断面において、主板１０近
傍の羽根板断面１２a から側板１１近傍の羽根板断面１
２bまでの各断面形状を翼形に形成したうえ、羽根前縁
部形状が主板１０近傍の羽根断面形状１２a の羽根前縁
部形状に内包させる構成を備えることにより、送風性能
が向上し送風騒音が低減すると共に、羽根車８の機械的
強度を向上させることができ、かつ可動金型用いて羽根
板１２と主板１０の樹脂一体成形を可能とし、羽根車８
の組立精度向上と生産性の向上をも実現することができ
る実用効果大なるものである。As described above, the centrifugal blower of this embodiment is
In the cross section orthogonal to the rotation axis of the impeller 8, the cross section 12a near the main plate 10 to the cross section 1 near the side plate 11
By providing a configuration in which each cross-sectional shape up to 2b is formed into an airfoil shape, and the front-end shape of the blade is included in the front-end shape of the blade cross-sectional shape 12a near the main plate 10, the blowing performance is improved and the blowing noise is improved. And the mechanical strength of the impeller 8 can be improved, and the movable plate can be used to integrally mold the blade plate 12 and the main plate 10 with resin.
Thus, it is possible to improve the assembling accuracy and the productivity, and the practical effect is large.
【００３７】[0037]
【発明の効果】以上説明したように本発明の遠心送風機
は、主板と複数の羽根板と吸込口を有する側板から成る
羽根車と、側板の吸込口に挿入した吸込リングとを有
し、前記羽根車の回転軸に直交する羽根断面において、
主板近傍羽根断面の羽根出口角β2hに対して側板に接す
る羽根断面の羽根出口角β2sをβ2h＋５゜≦β2s≦β2h
＋１５゜として主板から側板までの羽根の断面形状を連
続的に変化させ、かつ主板近傍羽根断面から側板に接す
る羽根断面までの羽根取付角の平均値γo を４３゜≦γ
o ≦４６゜とすることにより、羽根車出口の気流速度分
布を均一化して送風性能を向上させると共に、側板側の
羽根板断面の後縁部の流れの剥離を抑制し、各羽根断面
において羽根圧力面および負圧面における気流の剥離を
抑制するため、送風性能の向上と送風騒音の低減を効果
的に実現することができる。As described above, the centrifugal blower of the present invention has an impeller comprising a main plate, a plurality of blade plates and a side plate having a suction port, and a suction ring inserted into the suction port of the side plate. In the blade section orthogonal to the rotation axis of the impeller,
The blade outlet angle β2s of the blade section in contact with the side plate is β2h + 5 ° ≦ β2s ≦ β2h with respect to the blade outlet angle β2h of the blade section near the main plate.
+ 15 °, the cross-sectional shape of the blade from the main plate to the side plate is continuously changed, and the average value γo of the blade mounting angle from the cross section of the blade near the main plate to the cross section of the blade in contact with the side plate is 43 ° ≦ γ
By setting o ≤ 46 °, the airflow velocity distribution at the outlet of the impeller is made uniform to improve the air blowing performance, and the separation of the flow at the trailing edge of the cross section of the blade on the side plate side is suppressed. Since the separation of the airflow on the pressure surface and the negative pressure surface is suppressed, it is possible to effectively improve the blowing performance and reduce the blowing noise.
【００３８】また、他の本発明の遠心送風機はさらに羽
根車の回転軸に直交する各羽根断面において、各断面形
状を翼形に形成したうえ、各羽根入口部断面を主板部の
羽根入口断面に内包させることにより、送風性能を向上
し送風騒音が低減すると共に、羽根車の機械的強度を向
上させることができ、かつ羽根板と主板の樹脂一体成形
を可能とし、羽根車の組立精度向上と生産性の向上をも
実現することができる。Further, in another centrifugal blower of the present invention, in each blade cross section orthogonal to the rotation axis of the impeller, each cross section is formed into an airfoil shape, and each blade inlet section is cut into the blade inlet cross section of the main plate. In addition to improving the ventilation performance and reducing the ventilation noise, the mechanical strength of the impeller can be improved and the impeller and main plate can be integrally molded with resin to improve the assembly accuracy of the impeller. And an improvement in productivity can also be realized.
【図１】本発明の第１の実施例の遠心送風機の縦断面図FIG. 1 is a longitudinal sectional view of a centrifugal blower according to a first embodiment of the present invention.
【図２】同実施例の遠心送風機の羽根車の斜視図FIG. 2 is a perspective view of an impeller of the centrifugal blower of the embodiment.
【図３】同実施例の遠心送風機の羽根車の要部縦断面図FIG. 3 is a longitudinal sectional view of a main part of an impeller of the centrifugal blower of the embodiment.
【図４】図３のＤ−Ｄ線断面図FIG. 4 is a sectional view taken along line DD of FIG. 3;
【図５】図３のＣ−Ｃ線断面図FIG. 5 is a sectional view taken along line CC of FIG. 3;
【図６】同実施例の遠心式送風機の羽根車出口の気流速
度分布を示す模式図FIG. 6 is a schematic diagram showing an airflow velocity distribution at an impeller outlet of the centrifugal blower of the embodiment.
【図７】同実施例の遠心式送風機の羽根車の設計値αと
送風騒音との関係を示す特性図FIG. 7 is a characteristic diagram showing a relationship between a design value α of the impeller of the centrifugal blower of the embodiment and blowing noise.
【図８】同実施例の遠心式送風機の羽根車の設計値γo
と送風騒音との関係を示す特性図FIG. 8 is a design value γo of the impeller of the centrifugal blower of the embodiment.
Diagram showing the relationship between airflow and blast noise
【図９】本発明の第２の実施例の遠心送風機の羽根車の
要部横断面図FIG. 9 is a cross-sectional view of a main part of an impeller of a centrifugal blower according to a second embodiment of the present invention.
【図１０】同実施例の羽根板を成形する金型の構造を示
す模式図FIG. 10 is a schematic view showing the structure of a mold for molding the blade plate of the embodiment.
【図１１】従来の遠心送風機の縦断面図FIG. 11 is a longitudinal sectional view of a conventional centrifugal blower.
【図１２】同従来例の遠心送風機の羽根車の要部縦断面
図FIG. 12 is a longitudinal sectional view of an essential part of an impeller of the conventional centrifugal blower.
【図１３】図１２のＡ−Ａ線断面図FIG. 13 is a sectional view taken along line AA of FIG.
【図１４】同従来例の遠心送風機の羽根車出口の気流速
度分布を示す模式図FIG. 14 is a schematic diagram showing an airflow velocity distribution at an impeller outlet of the conventional centrifugal blower.
８ 羽根車 ９ 羽根板 １０ 主板 １１ 側板 １２ 羽根板 β2s 羽根出口角 β2h 羽根出口角 γs 羽根取付角 γh 羽根取付角 8 impeller 9 blade plate 10 main plate 11 side plate 12 blade plate β2s blade outlet angle β2h blade outlet angle γs blade mounting angle γh blade mounting angle
───────────────────────────────────────────────────── フロントページの続き (56)参考文献 特開 昭61−31698（ＪＰ，Ａ) 特開 平２−248693（ＪＰ，Ａ) 特開 平２−70997（ＪＰ，Ａ) 特開 平６−299994（ＪＰ，Ａ) 特開 平５−312189（ＪＰ，Ａ) (58)調査した分野(Int.Cl.6，ＤＢ名) F04D 29/18 - 29/38 ──────────────────────────────────────────────────続 き Continuation of front page (56) References JP-A-61-31698 (JP, A) JP-A-2-2488693 (JP, A) JP-A-2-70997 (JP, A) JP-A-6-296 299994 (JP, A) JP-A-5-312189 (JP, A) (58) Fields investigated (Int. Cl. 6 , DB name) F04D 29/18-29/38
Claims (2)
板から成る羽根車と、側板の吸込口に挿入した吸込リン
グとを有し、前記羽根車の回転軸に直交する羽根断面に
おいて、主板近傍羽根断面の羽根出口角β2hに対して側
板に接する羽根断面の羽根出口角β2sをβ2h＋５゜≦β
2s≦β2h＋１５゜として主板から側板までの羽根の断面
形状を連続的に変化させ、かつ主板近傍羽根断面から側
板に接する羽根断面までの羽根取付角の平均値γo を４
３゜≦γo ≦４６゜とした遠心式送風機。1. An impeller comprising a main plate, a plurality of impeller plates, and a side plate having a suction port, and a suction ring inserted into a suction port of the side plate, wherein in a cross section of the blade perpendicular to a rotation axis of the impeller, The blade exit angle β2s of the blade section in contact with the side plate is β2h + 5 ° ≦ β with respect to the blade exit angle β2h of the blade section near the main plate.
The cross-sectional shape of the blade from the main plate to the side plate is continuously changed as 2s ≦ β2h + 15 °, and the average value γo of the blade mounting angle from the cross section of the blade near the main plate to the cross section of the blade in contact with the side plate is 4
Centrifugal blower with 3 ゜ ≦ γo ≦ 46 ゜.
おいて、各羽根板断面形状を翼形に形成したうえ、各羽
根入口部断面を主板部の羽根入口断面に内包させた請求
項１記載の遠心送風機。2. In each blade cross section orthogonal to the rotation axis of the impeller, each blade plate cross-sectional shape is formed into an airfoil shape, and each blade inlet section is included in the blade inlet cross section of the main plate section. The centrifugal blower as described.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP4564695A JP2871515B2 (en) | 1995-03-06 | 1995-03-06 | Centrifugal blower |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP4564695A JP2871515B2 (en) | 1995-03-06 | 1995-03-06 | Centrifugal blower |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH08247091A JPH08247091A (en) | 1996-09-24 |
| JP2871515B2 true JP2871515B2 (en) | 1999-03-17 |
Family
ID=12725147
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP4564695A Expired - Fee Related JP2871515B2 (en) | 1995-03-06 | 1995-03-06 | Centrifugal blower |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2871515B2 (en) |
Families Citing this family (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2001087162A (en) * | 1999-09-27 | 2001-04-03 | Toto Ltd | Human body dryer and method for designing the dryer |
| JP3949663B2 (en) * | 2004-01-29 | 2007-07-25 | 三相電機株式会社 | Centrifugal impeller |
| CN102330706A (en) * | 2010-07-13 | 2012-01-25 | 珠海格力电器股份有限公司 | Centrifugal wind wheel |
| CN104863892A (en) * | 2014-02-20 | 2015-08-26 | 顾发华 | Impeller with high outlet flow field uniformity and centrifugal compressor |
| CN106122088B (en) * | 2016-08-17 | 2019-04-02 | 芜湖美智空调设备有限公司 | Centrifugal wind wheel and cabinet air-conditioner |
-
1995
- 1995-03-06 JP JP4564695A patent/JP2871515B2/en not_active Expired - Fee Related
Also Published As
| Publication number | Publication date |
|---|---|
| JPH08247091A (en) | 1996-09-24 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| LAPS | Cancellation because of no payment of annual fees |