JP2661986B2 - Centrifugal blower impeller - Google Patents
Centrifugal blower impellerInfo
- Publication number
- JP2661986B2 JP2661986B2 JP24822388A JP24822388A JP2661986B2 JP 2661986 B2 JP2661986 B2 JP 2661986B2 JP 24822388 A JP24822388 A JP 24822388A JP 24822388 A JP24822388 A JP 24822388A JP 2661986 B2 JP2661986 B2 JP 2661986B2
- Authority
- JP
- Japan
- Prior art keywords
- blade
- impeller
- plate
- diameter
- 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.)
- Expired - Fee Related
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、空気調和機などに用いられる遠心送風機の
特に羽根車に関するものである。Description: BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a centrifugal blower used for an air conditioner and the like, particularly to an impeller.
従来の技術 従来、遠心送風機の羽根車は低騒音化のため羽根板の
断面形状を翼形とし、さらに送風能力（風量）を大きく
するため、吸込口径を羽根入口径より大径とすることが
あった。2. Description of the Related Art Conventionally, the impeller of a centrifugal blower has a blade-shaped cross-sectional shape in order to reduce noise, and furthermore, in order to increase the blowing capacity (air volume), it is necessary to make the suction port diameter larger than the blade inlet diameter. there were.
以下図面を参照しながら上述した従来の遠心送風機の
羽根車の一例について説明する。Hereinafter, an example of the above-described conventional centrifugal blower impeller will be described with reference to the drawings.
第６図〜第８図は従来の遠心送風機の羽根車の構造を
示すものである。１は羽根車であり、２は主板３と一体
に成形した羽根板である。４は側板であり羽根板２に固
定されている。５は側板４に設けた吸込口である。羽根
車１を回転軸に対して直角な平面で切断した時の羽根板
２の断面形状は、主板３からの距離Ｈまでの断面では第
７図に示す翼形状となっている。又、羽根車１の吸込口
径Doは羽根入口径D1より大きくしてある。さらに吸込口
５の近傍では羽根板２の先端部を羽根車１の軸心に対し
て同心円状に切削した形状とすることによって羽根入口
径DiはD1より徐々に大きくなり、羽根板２の上端部で最
も羽根入口径Diが大きくなっている。6 to 8 show the structure of an impeller of a conventional centrifugal blower. 1 is an impeller, and 2 is an impeller integrally formed with the main plate 3. Reference numeral 4 denotes a side plate fixed to the blade plate 2. Reference numeral 5 denotes a suction port provided in the side plate 4. The sectional shape of the blade plate 2 when the impeller 1 is cut along a plane perpendicular to the rotation axis has a blade shape shown in FIG. 7 in a section up to a distance H from the main plate 3. Further, the suction diameter D o of the impeller 1 is made larger than the vane inlet diameter D 1. Gradually larger than D 1 vane inlet diameter D i by the cutting shape concentrically with respect to the axis of the distal end portion of the impeller 1 slats 2 in yet vicinity of the suction port 5, the vane 2 most blade inlet diameter D i at the upper end of is large.
以上のように構成された遠心送風機の羽根車につい
て、以下その動作を説明する。The operation of the impeller of the centrifugal blower configured as described above will be described below.
まず、モータ（図示せず）の回転とともに羽根車１が
回転すると、オリフィス（図示ぜず）を介して空気が羽
根車１内に流入し、静圧と動圧を付加されて羽根車１外
に吐出された送風作用を為す。又、吸込口径Doが羽根入
口径D1より大きくしてあるため、吸込口面積が大きくな
り吸込気流の流速が小さくなり、羽根車入口および羽根
車内部での流動抵抗（損失）が少くなり、圧力の低い動
作点では送風性能が向上する。First, when the impeller 1 rotates together with the rotation of the motor (not shown), air flows into the impeller 1 via an orifice (not shown), and static pressure and dynamic pressure are applied to the outside of the impeller 1. The air blown out is discharged. Further, since the suction diameter D o is is made larger than the vane inlet diameter D 1, a flow rate of greater becomes the suction air flow inlet area is reduced, the flow resistance (loss) of the internal impeller inlet and the impeller is less At the operating point where the pressure is low, the blowing performance is improved.
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、羽根板２の吸
込口５の近傍の回転断面形状は第８図に示すように羽根
板２の羽根入口側先端部2aが鋭角的な形状となるので、
流入気流Ｆがこの羽根入口側先端部2aで剥離して流入気
流が乱れやすく、この気流の乱れにより乱流音が増加し
送風騒音が増加するという課題を有していた。However, in the above-described configuration, the rotational cross-sectional shape in the vicinity of the suction port 5 of the blade plate 2 is such that the blade inlet-side tip 2a of the blade plate 2 has an acute angle as shown in FIG. The shape
The inflow airflow F is separated at the blade inlet side tip 2a and the inflow airflow is likely to be turbulent, and the turbulence noise increases due to the turbulence of the airflow, thereby increasing the blowing noise.
本発明は上記課題に鑑み、側板の吸込口内径を羽根入
口径より大きくしたうえで、羽根板の吸込口近傍での流
入気流の剥離の少ない低騒音な遠心送風機の羽根車を提
供するものである。In view of the above problems, the present invention provides an impeller of a low-noise centrifugal blower in which the suction port inner diameter of the side plate is made larger than the blade inlet diameter and the separation of the inflow airflow near the suction port of the blade plate is small. is there.
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の羽根
車は、複数の羽根板と前記羽根板を固定した主板と、前
記羽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、前記側板の吸込口径d0を羽根車外径d2に対して0.
75d2〜0.9d2とし、また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、主板から
所定の位置ｈまでは羽根板の各断面形状を略同一の翼形
状とし、さらに羽根入口径d1を0.675d2〜0.8d2とし、ま
た位置ｈから側板部にかけての羽根板の断面形状は主板
近傍の羽根板断面形状に内包される形状とし、かつ羽根
板の羽根入口径を徐々に拡大すると共に、羽根板の翼腹
面の板厚を徐々に薄くしかつ羽根板の先端形状をなめら
かな曲線状としたものである。Means for Solving the Problems In order to solve the above problems, an impeller of a centrifugal blower of the present invention comprises a plurality of blade plates and a main plate to which the blade plates are fixed, and a side plate fixed to an end surface of the blade plate opposite to the main plate side. constitutes an impeller in a, 0 suction diameter d 0 of the side plate relative to the impeller outer diameter d 2.
75d 2 to 0.9d 2, and in a cross-section when the blade is cut on each plane orthogonal to the rotation axis of the impeller, each cross-sectional shape of the blade from the main plate to a predetermined position h is substantially the same as that of the blade. a shape, further vanes inlet diameter d 1 and 0.675d 2 ~0.8d 2, also cross-sectional shape of the blade plate toward the side plate portion from the position h is a shape enclosed in the slats sectional shape in the vicinity of the main plate, and vane plate The blade entrance diameter of the blade is gradually increased, the thickness of the blade abdominal surface of the blade is gradually reduced, and the tip of the blade is formed into a smooth curved shape.
作用 本発明は上記した構成によって、吸込口近傍の羽根板
の吸込口部の回転断面形状が、各断面毎に翼形状とな
り、かつ、吸込口近傍の羽根入口角が側板に近い断面ほ
ど小さくなるため、羽根端部での流入気流の剥離が発生
せず、羽根板の翼腹面側での気流の乱れを防止し、乱流
音の発生が抑制される。Function The present invention has the above-described configuration, and the rotational cross-sectional shape of the suction port portion of the blade plate near the suction port becomes a blade shape for each cross section, and the blade entrance angle near the suction port becomes smaller as the cross section becomes closer to the side plate. Therefore, separation of the inflow airflow at the blade end does not occur, and the turbulence of the airflow on the blade abdomen side of the blade plate is prevented, and generation of turbulent noise is suppressed.
実 施 例 以下本発明の一実施例の遠心送風機の羽根車について
図面を参照しながら説明する。第１図〜第３図は本発明
の一実施例における遠心送風機の羽根車の構造を示すも
のである。６は羽根車であり、７は主板８と一体に成形
した羽根板である。９は側板であり羽根板７に固定され
ている。10は側板９に設けた羽根車６の吸込口である。
側板９の吸込口径d0は羽根車６の外径d2に対して0.825d
2としてある。また、羽根車６の回転軸に直交する各平
面で羽根板７を切断した時の断面において、主板８から
所定の距離ｈ′の位置ｈまでは羽根板７の各断面形状は
第２図に示す略同一の翼形状とし、さらに羽根入口径d1
は0.725としてある。また位置ｈから側板９にかけての
羽根板７の断面形状は主板８近傍の羽根板７断面形状に
内包される形状とし、羽根板７の翼腹面12の板厚を徐々
に薄くしかつ羽根板の先端形状をなめらかな曲線状とし
てある。Embodiment Hereinafter, an impeller of a centrifugal blower according to an embodiment of the present invention will be described with reference to the drawings. 1 to 3 show the structure of an impeller of a centrifugal blower according to one embodiment of the present invention. Reference numeral 6 denotes an impeller, and 7 denotes an impeller integrally formed with the main plate 8. Reference numeral 9 denotes a side plate fixed to the blade plate 7. Reference numeral 10 denotes a suction port of the impeller 6 provided on the side plate 9.
Suction diameter d 0 of the side plate 9 0.825D is the outer diameter d 2 of the impeller 6
There are two . Further, in a cross section when the blade plate 7 is cut on each plane orthogonal to the rotation axis of the impeller 6, each cross sectional shape of the blade plate 7 up to a position h at a predetermined distance h 'from the main plate 8 is shown in FIG. And the blade inlet diameter d 1
Is set to 0.725. The cross-sectional shape of the blade plate 7 from the position h to the side plate 9 is a shape included in the cross-sectional shape of the blade plate 7 in the vicinity of the main plate 8, the thickness of the blade vent surface 12 of the blade plate 7 is gradually reduced, and The shape of the tip is a smooth curve.
以上のように構成された遠心送風機の羽根車について
以下その動作を説明する。まず、モータ（図示せず）の
回転とともに羽根車６が回転するとオリフィス（図示せ
ず）を介して空気が羽根車６内に流入し、静圧と動圧を
付加され羽根車６外に吐出され送風作用を為す。The operation of the impeller of the centrifugal blower configured as described above will be described below. First, when the impeller 6 rotates together with the rotation of the motor (not shown), air flows into the impeller 6 through an orifice (not shown), and a static pressure and a dynamic pressure are applied to discharge the air outside the impeller 6. It performs a blowing action.
又、主板から距離ｈまでの羽根入口径d1を羽根車外径
d2に対して0.725d2とし、側板９の吸込口径d0を0.825d2
としてあるから、吸込口径d0は羽根入口径d1より大きく
なっており、吸込口面積が大きくなるため吸込気流の流
速が小さくなり、羽根車入口および羽根車内部での流動
抵抗（損失）が少くなり、圧力の小さな動作点では送風
性能が向上する。In addition, the blade inlet diameter d 1 from the main plate to the distance h is the outer diameter of the impeller.
and 0.725D 2 relative to d 2, 0.825d suction diameter d 0 of the side plate 9 2
Therefore, the suction port diameter d 0 is larger than the blade inlet diameter d 1 , and the suction port area is large, so that the flow velocity of the suction air flow is small, and the flow resistance (loss) at the impeller inlet and inside the impeller is low. It becomes less, and the blowing performance is improved at the operating point where the pressure is small.
さらに、羽根板７の吸込口10の近傍の回転断面形状
は、羽根板の先端の形状がなめらかな曲線状としてあ
り、しかも翼腹面12の板厚を薄くしているため羽根入口
角θ１は吸込口10に近づく程小さくなるため、流入気流
Ｇは羽根板７に沿って流れ、気流の剥離が生じにくく、
乱流音の発生を抑制し、送風騒音が低くなる。Further, the rotary cross-sectional shape of the blade plate 7 in the vicinity of the suction port 10 is such that the shape of the tip of the blade plate is a smooth curve, and the blade thickness of the blade abdominal surface 12 is thin, so that the blade inlet angle θ 1 is Since it becomes smaller as approaching the suction port 10, the inflow airflow G flows along the blade plate 7, and the separation of the airflow hardly occurs.
The generation of turbulent noise is suppressed, and the blowing noise is reduced.
尚、送風騒音のレベルは第４図，第５図に示すよう
に、主板から距離ｈまでの羽根入口径d1および側板の吸
込口径d0によって変化するが、d0/d2を0.75〜0.9とし、
d1/d2を0.675〜0.8とすることによりほぼ最適化するこ
とができ、実用上十分低騒音な遠心送風機の羽根車とす
ることができる。The level fourth view of the blower noise, as shown in FIG. 5, but varies with the blade inlet diameter d 1 and the side plate suction diameter d 0 of the main plate up to a distance h, and d 0 / d 2 0.75~ 0.9,
By setting d 1 / d 2 to be 0.675 to 0.8, it can be almost optimized, and the impeller of the centrifugal blower can be made practically low in noise.
発明の効果 以上のように、本発明の遠心送風機は、複数の羽根板
と前記羽根板を固定した主板と、前記羽根板の反主板側
端面に固定した側板とで羽根車を構成し、前記側板の吸
込口径d0を羽根車外径d2に対して0.75d2〜0.9d2とし、
また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、主板から所定の位置ｈまでは
羽根板の各断面形状を略同一の翼形状とし、さらに羽根
入口径d1を0.675d2〜0.8d2とし、また位置ｈから側板部
にかけての羽根板の断面形状は主板近傍の羽根板断面形
状に内包される形状とし、かつ羽根板の羽根入口径を徐
々に拡大すると共に、羽根板の翼腹面の板厚を徐々に薄
くし、かつ羽根板の先端形状をなめらかな曲線状とする
ことにより、低静圧条件において、送風性能を向上させ
ると共に、吸込口近傍の羽根板の腹面部での流入気流の
剥離を防止し、気流の乱れに起因する送風騒音を低減す
ることができる。Effect of the Invention As described above, the centrifugal blower of the present invention comprises an impeller including a plurality of blade plates and a main plate to which the blade plates are fixed, and a side plate fixed to an end surface of the blade plate opposite to the main plate, and 0.75d 2 ~0.9d 2 suction diameter d 0 of the side plate relative to the impeller outer diameter d 2,
Further, in a cross section when the blade plate is cut on each plane orthogonal to the rotation axis of the impeller, each cross section of the blade plate has substantially the same blade shape from the main plate to a predetermined position h, and further, a blade inlet diameter d. 1 and 0.675d 2 ~0.8d 2, also cross-sectional shape of the blade plate toward the side plate portion from the position h is a shape enclosed in the slats sectional shape in the vicinity of the main plate and the blade inlet diameter slats progressively larger At the same time, by gradually reducing the thickness of the wing abdominal surface of the wing plate and making the tip shape of the wing plate a smooth curve, under low static pressure conditions, the air blowing performance is improved and the vicinity of the suction port is improved. Separation of the inflow airflow at the abdominal surface of the blade can be prevented, and blowing noise caused by turbulence of the airflow can be reduced.
第１図は本発明の一実施例における遠心送風機の羽根車
の断面図、第２図は第１図のＣ−Ｃ部断面図、第３図は
第１図のＤ−Ｄ部断面図、第４図はd1/d2を変えたとき
の最高効率点での騒音値を示す実験結果による特性図、
第５図はd0/d2を変えたときの最高効率点での騒音値を
示す実験結果による特性図、第６図は従来の遠心送風機
の羽根車の断面図、第７図は第６図のＡ−Ａ部断面図、
第８図は第６図のＢ−Ｂ部断面図である。 ７……羽根板、８……主板、９……側板、10……吸込
口、11……翼背面、12……翼腹面。FIG. 1 is a sectional view of an impeller of a centrifugal blower according to an embodiment of the present invention, FIG. 2 is a sectional view taken along the line CC of FIG. 1, FIG. 3 is a sectional view taken along the line DD of FIG. FIG. 4 is a characteristic diagram based on an experimental result showing a noise value at the highest efficiency point when d 1 / d 2 is changed,
FIG. 5 is a characteristic diagram based on experimental results showing a noise value at the highest efficiency point when d 0 / d 2 is changed, FIG. 6 is a cross-sectional view of a conventional centrifugal fan impeller, and FIG. AA sectional view of the figure,
FIG. 8 is a sectional view taken along the line BB of FIG. 7 ... blade plate, 8 ... main plate, 9 ... side plate, 10 ... suction port, 11 ... wing back surface, 12 ... wing abdominal surface.
Claims (1)
と前記羽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、前記側板の吸込口径d0を羽根車外径d2に対し
て0.75d2〜0.9d2とし、また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、主板
から所定の位置ｈまでは羽根板の各断面形状を略同一の
翼形状とし、さらに羽根入口径d1を0.675d2〜0.8d2と
し、また位置ｈから側板部にかけての羽根板の断面形状
は主板近傍の羽根板断面形状に内包される形状とし、か
つ羽根板の羽根入口径を徐々に拡大すると共に、羽根板
の翼腹面の板厚を徐々に薄くし、かつ羽根板の先端形状
をなめらかな曲線状とした遠心送風機の羽根車。[Claim 1] constitute an impeller with a plurality of vanes and fixed side plate counter-main plate side end face of the main plate and the blade plate fixed to the blades, suction diameter d 0 of the impeller outer diameter d of the side plate 2 and 0.75 D 2 ～0.9D 2 against, and each cross-sectional shape of each in a cross section obtained by cutting the blade plate in the plane, from the main plate to a predetermined position h vane perpendicular to the rotation axis of the impeller shape and substantially the same airfoil shape, further vanes inlet diameter d 1 and 0.675d 2 ~0.8d 2, also cross-sectional shape of the blade plate toward the side plate portion from the position h is to be encapsulated in the slats sectional shape in the vicinity of the main plate The centrifugal impeller has a blade inlet diameter of the blade that is gradually enlarged, the thickness of the blade abdominal surface of the blade is gradually reduced, and the tip of the blade is formed into a smooth curved shape.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP24822388A JP2661986B2 (en) | 1988-09-30 | 1988-09-30 | Centrifugal blower impeller |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP24822388A JP2661986B2 (en) | 1988-09-30 | 1988-09-30 | Centrifugal blower impeller |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH0295797A JPH0295797A (en) | 1990-04-06 |
| JP2661986B2 true JP2661986B2 (en) | 1997-10-08 |
Family
ID=17175008
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP24822388A Expired - Fee Related JP2661986B2 (en) | 1988-09-30 | 1988-09-30 | Centrifugal blower impeller |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2661986B2 (en) |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR20010001065A (en) * | 1999-06-01 | 2001-01-05 | 구자홍 | Turbofan |
| JP3949663B2 (en) * | 2004-01-29 | 2007-07-25 | 三相電機株式会社 | Centrifugal impeller |
| JP5287772B2 (en) | 2010-03-16 | 2013-09-11 | 株式会社デンソー | Centrifugal multi-blade fan |
-
1988
- 1988-09-30 JP JP24822388A patent/JP2661986B2/en not_active Expired - Fee Related
Also Published As
| Publication number | Publication date |
|---|---|
| JPH0295797A (en) | 1990-04-06 |
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