JP2000120582A - Centrifugal blower - Google Patents
Centrifugal blowerInfo
- Publication number
- JP2000120582A JP2000120582A JP10293497A JP29349798A JP2000120582A JP 2000120582 A JP2000120582 A JP 2000120582A JP 10293497 A JP10293497 A JP 10293497A JP 29349798 A JP29349798 A JP 29349798A JP 2000120582 A JP2000120582 A JP 2000120582A
- Authority
- JP
- Japan
- Prior art keywords
- shroud
- centrifugal fan
- fan
- outer peripheral
- peripheral portion
- 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
- Air-Conditioning Room Units, And Self-Contained Units In General (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
Description
【０００１】[0001]
【発明の属する技術分野】本発明は、空気調和機器およ
び換気送風機器に使用される遠心送風機に関する。The present invention relates to a centrifugal blower used for an air conditioner and a ventilation blower.
【０００２】[0002]
【従来の技術】従来のこの種の遠心送風機を図１０を参
照しながら説明する。2. Description of the Related Art A conventional centrifugal blower of this type will be described with reference to FIG.
【０００３】図に示すように、遠心送風機１１０は、筐
体１１７と吸込グリル１１１と吐出口１１４を備え、筐
体１１７の内部にオリフィス１１２と遠心ファン１０１
を備えた構成としている。As shown in FIG. 1, a centrifugal blower 110 includes a housing 117, a suction grill 111, and a discharge port 114. An orifice 112 and a centrifugal fan 101 are provided inside the housing 117.
Is provided.
【０００４】また、遠心ファン１０１は主板１０２とシ
ュラウド１０３で挟むように複数のブレード１０４が取
り付けられており、シュラウド１０３は遠心ファン１０
１の吸込側１０６から吐出側１０５に向かって主板側に
傾斜し、主板１０２とシュラウド外周部１０７のシュラ
ウド外周端１２２との幅ＰＬｓは、ブレード１０４の入
口幅ＰＢｉより小さい構成としている。The centrifugal fan 101 has a plurality of blades 104 mounted so as to be sandwiched between a main plate 102 and a shroud 103.
1, the width PLs between the main plate 102 and the shroud outer peripheral end 122 of the shroud outer peripheral portion 107 is smaller than the inlet width PBi of the blade 104.
【０００５】[0005]
【発明が解決しようとする課題】このような従来の遠心
送風機では、遠心ファンからの吐出流れが送風機本体の
吐出口の方向ではなく半径方向に吐出し、さらに減速し
ないまま送風機本体の筐体側壁に衝突するため筐体内の
流れの乱れも大きく、騒音が増大しファン効率が低下す
るという課題があり、送風機本体の筐体側壁への衝突を
少なくするとともに、衝突速度を減速することで筐体内
の乱れを減少させ、騒音の発生を低減しファンの効率を
向上することが要求されている。In such a conventional centrifugal blower, the discharge flow from the centrifugal fan is discharged not in the direction of the discharge port of the blower body but in the radial direction, and further, without deceleration, the side wall of the housing of the blower body. There is a problem that the flow in the case is turbulent due to the collision, and the noise increases and the fan efficiency decreases.Therefore, the collision with the side wall of the blower body is reduced, and the collision speed is reduced by reducing the collision speed. It is required to reduce the disturbance of the fan, reduce the generation of noise, and improve the efficiency of the fan.
【０００６】本発明は、このような従来の課題を解決す
るものであり、騒音の発生を低減し、ファンの効率を向
上することができ消費電力が低くすることができる遠心
送風機を提供することを目的としている。The present invention has been made to solve the above-mentioned conventional problems, and provides a centrifugal blower capable of reducing noise generation, improving fan efficiency and reducing power consumption. It is an object.
【０００７】[0007]
【課題を解決するための手段】本発明の遠心送風機は上
記目的を達成するために第１の手段は、主板とシュラウ
ドで挟むように複数のブレードが取り付けられた遠心フ
ァンで、ファン外径Ｄに比し、シュラウドのシュラウド
吸込径Ｄｓｉが０．６０〜０．８５であり、遠心ファン
の吐出側に位置するシュラウド外周部が、遠心ファンの
吸込側に傾斜し、かつ任意の周方向断面Ｓｉの通風路面
積がシュラウド内周部のブレード流入部とシュラウドが
交わる位置のブレード入口周方向断面Ｓ１の通風路面積
より大きい遠心ファンとしたものである。In order to achieve the above object, a centrifugal fan according to the present invention comprises, as a first means, a centrifugal fan having a plurality of blades mounted so as to be sandwiched between a main plate and a shroud. , The shroud suction diameter Dsi of the shroud is 0.60 to 0.85, the outer periphery of the shroud located on the discharge side of the centrifugal fan is inclined toward the suction side of the centrifugal fan, and any circumferential cross section Si Is a centrifugal fan whose ventilation passage area is larger than the ventilation passage area of the blade inlet circumferential section S1 at the position where the shroud intersects the blade inflow portion on the inner peripheral portion of the shroud.
【０００８】また第２の手段は、主板と、シュラウド外
部とシュラウド内部の形状が異なる肉厚のあるシュラウ
ドで挟むように複数のブレードが取り付けられた遠心フ
ァンで、ファン外径Ｄに比し、シュラウドのシュラウド
吸込径Ｄｓｉが０．６０〜０．８５であり、遠心ファン
の吐出側に位置するシュラウド内部のシュラウド外周部
が、遠心ファンの吸込側に傾斜し、かつ任意の周方向断
面Ｓｉの通風路面積がシュラウド内周部のブレード流入
部とシュラウドが交わる位置のブレード入口周方向断面
Ｓ１の通風路面積より大きい遠心ファンとしたものであ
る。The second means is a centrifugal fan in which a plurality of blades are mounted so as to be sandwiched between a main plate and a thick shroud having different shapes inside and outside of the shroud. The shroud suction diameter Dsi of the shroud is 0.60 to 0.85, the outer peripheral portion of the shroud inside the shroud located on the discharge side of the centrifugal fan is inclined toward the suction side of the centrifugal fan, and has an arbitrary circumferential cross section Si. The centrifugal fan has a ventilation passage area larger than the ventilation passage area of the blade inlet circumferential section S1 at the position where the shroud intersects with the blade inflow portion on the inner peripheral portion of the shroud.
【０００９】また第３の手段は、遠心ファンの吐出側に
位置するシュラウド外周部が、遠心ファンの吸込側に傾
斜し、シュラウド外周部の傾斜角αが１゜〜６０゜の遠
心ファンとしたものである。The third means is a centrifugal fan in which the outer peripheral portion of the shroud located on the discharge side of the centrifugal fan is inclined toward the suction side of the centrifugal fan, and the inclination angle α of the outer peripheral portion of the shroud is 1 ° to 60 °. Things.
【００１０】また第４の手段は、遠心ファンの吐出側に
位置するシュラウド外周部が、遠心ファンの吸込側に傾
斜し、シュラウド断面が略円弧形状の遠心ファンとした
ものである。A fourth means is a centrifugal fan in which the outer peripheral portion of the shroud located on the discharge side of the centrifugal fan is inclined toward the suction side of the centrifugal fan and the cross section of the shroud is substantially arc-shaped.
【００１１】また第５の手段は、遠心ファンの吐出側に
位置するシュラウド外周部が、遠心ファンの吸込側に傾
斜し、シュラウド断面が略円弧形状であり、ファン外径
Ｄに比しシュラウド断面半径Ｒが０．０１Ｄ〜０．２５
Ｄの遠心ファンとしたものである。A fifth means is that the outer periphery of the shroud located on the discharge side of the centrifugal fan is inclined toward the suction side of the centrifugal fan, the shroud has a substantially arc-shaped cross section, and the shroud cross section is smaller than the fan outer diameter D. Radius R is 0.01D to 0.25
D is a centrifugal fan.
【００１２】また第６の手段は、遠心ファンの吐出側に
位置するシュラウド外周部が、遠心ファンの吸込側に傾
斜し、かつ遠心ファンのブレードの任意の幅Ｂが最小と
なる位置をブレード幅最小径Ｄ１とし、ファン外径Ｄに
比しブレード幅最小径Ｄ１が０．７Ｄ〜０．９８Ｄの遠
心ファンとしたものである。The sixth means is that the shroud outer peripheral portion located on the discharge side of the centrifugal fan is inclined toward the suction side of the centrifugal fan, and the position where the arbitrary width B of the blade of the centrifugal fan is minimized is defined as the blade width. The centrifugal fan has a minimum diameter D1 and a blade width minimum diameter D1 of 0.7D to 0.98D compared to the fan outer diameter D.
【００１３】また第７の手段は、遠心ファンの吐出側に
位置するシュラウド外周部を含むシュラウド外径Ｄｓｏ
がファン外径Ｄより大きい遠心ファンとしたものであ
る。A seventh means is a shroud outer diameter Dso including a shroud outer peripheral portion located on the discharge side of the centrifugal fan.
Is a centrifugal fan larger than the fan outer diameter D.
【００１４】また第８の手段は、主板とシュラウドで挟
むように複数のブレードが取り付けられた遠心ファン
で、ファン外径Ｄに比し、前記シュラウドのシュラウド
吸込径Ｄｓｉが０．６０〜０．８５であり、遠心ファン
の吐出側に位置するシュラウド外周部が、遠心ファンの
吸込側に傾斜し、かつシュラウド外周部がファン外径Ｄ
より外周側に位置しており、主板とシュラウド外周部の
シュラウド外周端との幅Ｌｓが、ブレードの入口幅Ｂｉ
より大きい遠心ファンとしたものである。An eighth means is a centrifugal fan in which a plurality of blades are mounted so as to be sandwiched between the main plate and the shroud. The shroud has a shroud suction diameter Dsi of 0.60-0. 85, the outer peripheral portion of the shroud located on the discharge side of the centrifugal fan is inclined toward the suction side of the centrifugal fan, and the outer peripheral portion of the shroud has a fan outer diameter D.
The width Ls between the main plate and the outer peripheral end of the shroud at the outer peripheral portion of the shroud is equal to the inlet width Bi of the blade.
A larger centrifugal fan.
【００１５】そして本発明によれば騒音の発生が低くで
き、ファンの効率を向上することができ消費電力を低く
することができる遠心送風機が得られる。According to the present invention, there is provided a centrifugal blower capable of reducing noise, improving fan efficiency and reducing power consumption.
【００１６】[0016]
【発明の実施の形態】本発明は、主板とシュラウドで挟
むように複数のブレードが取り付けられた遠心ファン
で、ファン外径Ｄに比し、前記シュラウドのシュラウド
吸込径Ｄｓｉが０．６０〜０．８５であり、前記遠心フ
ァンの吐出側に位置するシュラウド外周部が、前記遠心
ファンの吸込側に傾斜し、かつ任意の周方向断面Ｓｉの
通風路面積がシュラウド内周部のブレード流入部と前記
シュラウドが交わる位置のブレード入口周方向断面Ｓ１
の通風路面積より大きい前記遠心ファンを有する遠心送
風機としたものであり、シュラウド外周部を吸込側に傾
斜することで、遠心ファンの吐出流れを送風機本体の吐
出口の方向に向けるとともに、遠心ファンのシュラウド
外周部より流れの吐出速度を減速することができ、送風
機本体の筐体側壁への衝突を少なくするとともに、衝突
速度を減速することで筐体内の乱れを減少させ、騒音の
発生を低減できるとともに、同一回転時での風量−静圧
特性が増大しファン効率の向上ができるという作用を有
する。DESCRIPTION OF THE PREFERRED EMBODIMENTS The present invention is a centrifugal fan having a plurality of blades mounted so as to be sandwiched between a main plate and a shroud. The shroud has a shroud suction diameter Dsi of 0.60 to 0, as compared with the fan outer diameter D. 85, the outer peripheral portion of the shroud located on the discharge side of the centrifugal fan is inclined toward the suction side of the centrifugal fan, and the ventilation passage area of any circumferential cross section Si is equal to the blade inflow portion of the inner peripheral portion of the shroud. Blade inlet circumferential section S1 at the position where the shroud intersects
A centrifugal blower having the centrifugal fan larger than the ventilation path area of the centrifugal fan, wherein the outer circumferential portion of the shroud is inclined toward the suction side so that the discharge flow of the centrifugal fan is directed toward the discharge port of the blower body, and the centrifugal fan is Can reduce the flow discharge speed from the outer periphery of the shroud, reduce the collision of the blower body with the housing side wall, and reduce the collision speed by reducing the collision speed to reduce noise generation. In addition to this, there is an effect that the air volume-static pressure characteristics at the same rotation can be increased and the fan efficiency can be improved.
【００１７】また、主板と、シュラウド外部とシュラウ
ド内部の形状が異なる肉厚のあるシュラウドで挟むよう
に複数のブレードが取り付けられた遠心ファンで、ファ
ン外径Ｄに比し、前記シュラウドのシュラウド吸込径Ｄ
ｓｉが０．６０〜０．８５であり、前記遠心ファンの吐
出側に位置する前記シュラウド内部のシュラウド外周部
が、前記遠心ファンの吸込側に傾斜し、かつ任意の周方
向断面Ｓｉの通風路面積がシュラウド内周部のブレード
流入部と前記シュラウドが交わる位置のブレード入口周
方向断面Ｓ１の通風路面積より大きい前記遠心ファンを
有する遠心送風機としたものであり、肉厚によりシュラ
ウド内部のシュラウド外周部を吸込側に傾斜すること
で、遠心ファンの吐出流れを送風機本体の吐出口の方向
に向けるとともに、遠心ファンのシュラウド外周部より
流れの吐出速度を減速することができ、送風機本体の筐
体側壁への衝突を少なくするとともに、衝突速度を減速
することで筐体内の乱れを減少させ、騒音の発生を低減
できるとともに、同一回転時での風量−静圧特性が増大
しファン効率の向上ができるという作用を有する。Also, a centrifugal fan in which a plurality of blades are attached so as to be sandwiched between a main plate and a thick shroud having different shapes inside and outside of the shroud. Diameter D
si is 0.60 to 0.85, the outer peripheral portion of the shroud inside the shroud located on the discharge side of the centrifugal fan is inclined toward the suction side of the centrifugal fan, and the ventilation path has any circumferential cross section Si. A centrifugal blower having the centrifugal fan whose area is larger than a ventilation passage area of a blade inlet circumferential cross section S1 at a position where the shroud intersects the blade inflow portion of the inner peripheral portion of the shroud. By inclining the part toward the suction side, the discharge flow of the centrifugal fan can be directed toward the discharge port of the blower main body, and the discharge speed of the flow can be reduced from the outer periphery of the shroud of the centrifugal fan. By reducing collisions on the side walls and reducing the collision speed, turbulence in the housing can be reduced and noise generation can be reduced. Air volume at the time of rotation - static pressure characteristics is increased such an action can improve the fan efficiency.
【００１８】また、遠心ファンの吐出側に位置するシュ
ラウド外周部が、前記遠心ファンの吸込側に傾斜し、前
記シュラウド外周部の傾斜角αが１゜〜６０゜の前記遠
心ファンを有する遠心送風機としたものであり、シュラ
ウド外周部の傾斜角αが１゜〜６０゜の範囲で一定にす
ることで、製作が容易で低コスト化が図れ、遠心ファン
の吐出流れを送風機本体の吐出口の方向に向けるととも
に、遠心ファンのシュラウド外周部より流れの吐出速度
を減速することができ、送風機本体の筐体側壁への衝突
を少なくするとともに、衝突速度を減速することで筐体
内の乱れを減少させ、騒音の発生を低減できるととも
に、同一回転時での風量−静圧特性が増大しファン効率
の向上ができるという作用を有する。A centrifugal blower having the centrifugal fan, wherein the outer peripheral portion of the shroud located on the discharge side of the centrifugal fan is inclined toward the suction side of the centrifugal fan, and the inclination angle α of the outer peripheral portion of the shroud is 1 ° to 60 °. By making the inclination angle α of the outer peripheral portion of the shroud constant in the range of 1 ° to 60 °, it is easy to manufacture and reduce the cost, and the discharge flow of the centrifugal fan is reduced by the discharge port of the blower body. Direction, and the flow discharge speed can be reduced from the outer periphery of the shroud of the centrifugal fan.This reduces collision with the side wall of the blower body and reduces turbulence in the housing by reducing the collision speed. As a result, the generation of noise can be reduced, and the air flow-static pressure characteristics during the same rotation can be increased, thereby improving the fan efficiency.
【００１９】また、遠心ファンの吐出側に位置するシュ
ラウド外周部が、前記遠心ファンの吸込側に傾斜し、シ
ュラウド断面が略円弧形状の前記遠心ファンを有する遠
心送風機としたものであり、シュラウド外周部を吸込側
に傾斜し、シュラウド断面が略円弧形状とすることで、
遠心ファンの吐出流れがシュラウド外周部の形状に沿う
スムースな流れとなり、送風機本体の吐出口の方向に向
けるとともに、遠心ファンのシュラウド外周部より流れ
の吐出速度を減速することができ、送風機本体の筐体側
壁への衝突を少なくするとともに、衝突速度を減速する
ことで筐体内の乱れを減少させ、騒音の発生を低減でき
るとともに、同一回転時での風量−静圧特性が増大しフ
ァン効率の向上ができるという作用を有する。Also, the outer peripheral portion of the shroud located on the discharge side of the centrifugal fan is inclined toward the suction side of the centrifugal fan, and the centrifugal fan having the centrifugal fan having a substantially arc-shaped cross section is provided. By inclining the part to the suction side and making the shroud section approximately arc-shaped,
The discharge flow of the centrifugal fan becomes a smooth flow along the shape of the outer peripheral portion of the shroud, and can be directed toward the discharge port of the blower main body, and the discharge speed of the flow can be reduced from the outer peripheral portion of the shroud of the centrifugal fan. In addition to reducing collisions on the side wall of the housing, reducing the collision speed reduces turbulence in the housing, reducing noise generation and increasing airflow-static pressure characteristics during the same rotation, resulting in higher fan efficiency. It has the effect of being able to improve.
【００２０】また、遠心ファンの吐出側に位置するシュ
ラウド外周部が、前記遠心ファンの吸込側に傾斜し、シ
ュラウド断面が略円弧形状であり、ファン外径Ｄに比し
シュラウド断面半径Ｒが０．０１Ｄ〜０．２５Ｄの前記
遠心ファンを有する遠心送風機としたものであり、シュ
ラウド断面が略円弧形状で、ファン外径Ｄに比しシュラ
ウド断面半径Ｒを０．０１Ｄ〜０．２５Ｄとすること
で、遠心ファンの吐出流れがシュラウド外周部の形状に
沿うスムースな流れとなり、確実に送風機本体の吐出口
の方向に向けるとともに、遠心ファンのシュラウド外周
部より流れの吐出速度を減速することができ、送風機本
体の筐体側壁への衝突を少なくするとともに、衝突速度
を減速することで筐体内の乱れを減少させ、騒音の発生
を低減できるとともに、同一回転時での風量−静圧特性
が増大しファン効率の向上ができるという作用を有す
る。Further, the outer peripheral portion of the shroud located on the discharge side of the centrifugal fan is inclined toward the suction side of the centrifugal fan, the cross section of the shroud is substantially arc-shaped, and the shroud cross-sectional radius R is smaller than the fan outer diameter D by 0. A centrifugal blower having the centrifugal fan of 0.01D to 0.25D, wherein the shroud has a substantially arc-shaped cross section and a shroud cross-sectional radius R of 0.01D to 0.25D as compared with the fan outer diameter D. Therefore, the discharge flow of the centrifugal fan becomes a smooth flow along the shape of the outer peripheral portion of the shroud, and can be surely directed toward the discharge port of the blower main body, and the discharge speed of the flow can be reduced from the outer peripheral portion of the shroud of the centrifugal fan. In addition to reducing the collision of the blower main body with the side wall of the housing and reducing the collision speed, the turbulence in the housing can be reduced and the noise generation can be reduced. , The same air volume at the time of rotation - has the effect of static pressure characteristics is increased can improve fan efficiency.
【００２１】また、遠心ファンの吐出側に位置するシュ
ラウド外周部が、前記遠心ファンの吸込側に傾斜し、か
つ前記遠心ファンのブレードの任意の幅Ｂが最小となる
位置をブレード幅最小径Ｄ１とし、ファン外径Ｄに比し
前記ブレード幅最小径Ｄ１が０．７Ｄ〜０．９８Ｄの前
記遠心ファンを有する遠心送風機としたものであり、ブ
レード幅最小径Ｄ１を０．７Ｄ〜０．８Ｄとすること
で、遠心ファンの内部のシュラウド側の内部流れと、シ
ュラウド外周部の吐出流れが形状に沿うスムースな流れ
となり、確実に送風機本体の吐出口の方向に向けるとと
もに、遠心ファンのシュラウド外周部より流れの吐出速
度を減速することができ、送風機本体の筐体側壁への衝
突を少なくするとともに、衝突速度を減速することで筐
体内の乱れを減少させ、騒音の発生を低減できるととも
に、同一回転時での風量−静圧特性が増大しファン効率
の向上ができるという作用を有する。Further, the outer peripheral portion of the shroud located on the discharge side of the centrifugal fan is inclined toward the suction side of the centrifugal fan, and the position where the arbitrary width B of the blade of the centrifugal fan is minimum is defined as the minimum blade width diameter D1. And a centrifugal blower having the centrifugal fan with the minimum blade width D1 of 0.7D to 0.98D as compared to the fan outer diameter D, and the minimum blade width D1 of 0.7D to 0.8D. As a result, the internal flow on the shroud side inside the centrifugal fan and the discharge flow on the outer peripheral portion of the shroud become a smooth flow along the shape, and are surely directed toward the discharge port of the blower main body, and The discharge speed of the flow can be reduced from the part, the collision with the side wall of the blower main body is reduced, and the turbulence in the housing is reduced by reducing the collision speed. , It is possible to reduce the generation of noise, air volume at the time the same rotation - has the effect of static pressure characteristics is increased can improve fan efficiency.
【００２２】また、遠心ファンの吐出側に位置するシュ
ラウド外周部を含むシュラウド外径Ｄｓｏがファン外径
Ｄより大きい前記遠心ファンを有する遠心送風機とした
ものであり、シュラウド外径Ｄｓｏをファン外径Ｄより
大きくし、シュラウド外周部を延長することで、吐出流
れがシュラウド外周部の形状に沿うスムースな流れを持
続し、確実に送風機本体の吐出口の方向に向けるととも
に、遠心ファンのシュラウド外周部より流れの吐出速度
を減速することができ、送風機本体の筐体側壁への衝突
を少なくするとともに、衝突速度を減速することで筐体
内の乱れを減少させ、騒音の発生を低減できるととも
に、同一回転時での風量−静圧特性が増大しファン効率
の向上ができるという作用を有する。Further, the centrifugal blower having the centrifugal fan whose shroud outer diameter Dso including the outer peripheral portion of the shroud located on the discharge side of the centrifugal fan is larger than the fan outer diameter D, wherein the shroud outer diameter Dso is the fan outer diameter D, and by extending the outer periphery of the shroud, the discharge flow maintains a smooth flow along the shape of the outer periphery of the shroud, and is surely directed toward the discharge port of the blower body, and the outer periphery of the shroud of the centrifugal fan. It is possible to reduce the discharge speed of the flow, reduce the collision of the blower main body with the side wall of the housing, and reduce the turbulence in the housing by reducing the collision speed, thereby reducing the generation of noise and the same. This has the effect of increasing the air flow-static pressure characteristics during rotation and improving the fan efficiency.
【００２３】また、主板とシュラウドで挟むように複数
のブレードが取り付けられた遠心ファンで、ファン外径
Ｄに比し、前記シュラウドのシュラウド吸込径Ｄｓｉが
０．６０〜０．８５であり、前記遠心ファンの吐出側に
位置するシュラウド外周部が、前記遠心ファンの吸込側
に傾斜し、かつ前記シュラウド外周部が前記ファン外径
Ｄより外周側に位置しており、前記主板とシュラウド外
周部のシュラウド外周端との幅Ｌｓが、前記ブレードの
入口幅Ｂｉより大きい前記遠心ファンを有する遠心送風
機としたものであり、シュラウド外周部がファン外径Ｄ
より外周側に位置し、主板２とシュラウド外周部のシュ
ラウド外周端との幅Ｌｓが、前記ブレードの入口幅Ｂｉ
より大きくすることで、吐出流れがシュラウド外周部の
形状に沿うスムースな流れで、送風機本体の吐出口付近
まで確実に導かれ、かつ遠心ファンの内部より流れは減
速し、さらにシュラウド外周部より流れの吐出速度を減
速することができ、送風機本体の筐体側壁への衝突を少
なくするとともに、衝突速度を減速することで筐体内の
乱れを減少させ、騒音の発生を低減できるとともに、同
一回転時での風量−静圧特性が増大しファン効率の向上
ができるという作用を有する。Also, the centrifugal fan has a plurality of blades mounted so as to be sandwiched between the main plate and the shroud. The shroud has a shroud suction diameter Dsi of 0.60 to 0.85 as compared with the fan outer diameter D. The outer peripheral portion of the shroud located on the discharge side of the centrifugal fan is inclined toward the suction side of the centrifugal fan, and the outer peripheral portion of the shroud is located on the outer peripheral side from the outer diameter D of the fan, and the outer peripheral portion of the main plate and the outer peripheral portion of the shroud are formed. A centrifugal blower having the centrifugal fan whose width Ls with respect to the outer peripheral end of the shroud is larger than the inlet width Bi of the blade, wherein the outer peripheral portion of the shroud has a fan outer diameter D
The width Ls between the main plate 2 and the outer periphery of the shroud at the outer periphery of the shroud is located closer to the outer periphery than the entrance width Bi of the blade.
By making it larger, the discharge flow is guided smoothly to the vicinity of the discharge port of the blower main body, and the flow is decelerated from the inside of the centrifugal fan, and further flows from the outer periphery of the shroud. Discharge speed can be reduced to reduce the collision of the blower body with the side wall of the housing, and reduce the collision speed to reduce turbulence in the housing, reduce noise and reduce This has the effect of increasing the air flow-static pressure characteristics at, and improving the fan efficiency.
【００２４】以下、本発明の実施例について図面を参照
しながら説明する。Hereinafter, embodiments of the present invention will be described with reference to the drawings.
【００２５】[0025]
【実施例】（実施例１）図１または図２に示すように、
主板２とシュラウド３で挟むように複数のブレード４が
取り付けられた遠心ファン１で、ファン外径Ｄに比し、
シュラウド３のシュラウド吸込径Ｄｓｉが０．６０〜
０．８５であり、遠心ファン１の吐出側５に位置するシ
ュラウド外周部７が、遠心ファン１の吸込側６に傾斜
し、かつ任意の周方向断面Ｓｉの通風路面積がシュラウ
ド内周部８のブレード流入部９とシュラウド３が交わる
位置のブレード入口周方向断面Ｓ１の通風路面積より大
きい遠心ファン１を有する構成にされている。(Embodiment 1) As shown in FIG. 1 or FIG.
A centrifugal fan 1 having a plurality of blades 4 attached so as to be sandwiched between a main plate 2 and a shroud 3.
Shroud 3 shroud suction diameter Dsi is 0.60
0.85, the outer peripheral portion 7 of the shroud located on the discharge side 5 of the centrifugal fan 1 is inclined toward the suction side 6 of the centrifugal fan 1, and the ventilation passage area of any circumferential cross section Si is changed to the inner peripheral portion 8 of the shroud 8. The centrifugal fan 1 is larger than the ventilation passage area of the blade inlet circumferential section S1 at the position where the blade inflow portion 9 and the shroud 3 intersect.
【００２６】上記構成により、遠心ファン１が回転する
とき、送風機本体１０の吸込グリル１１を通りオリフィ
ス１２より流入した空気は、遠心ファン１のブレード流
入部９を通りブレード流出部１３より吐出され、更に送
風機本体１０の吐出口１４より吐出される。そこで、遠
心ファン１より吐出する吐出流れ１５の大半が送風機本
体１０の筐体側壁１６に衝突しようとするが、シュラウ
ド外周部７が吸込側６に傾斜しているので、遠心ファン
１の吐出流れ１５を送風機本体１０の吐出口１４の方向
に向けるとともに、遠心ファン１のシュラウド外周部７
より流れの吐出速度を減速することができ、送風機本体
１０の筐体側壁１６への衝突を少なくするとともに、衝
突速度を減速することで筐体１７内の乱れを減少させ、
騒音の発生を低減できるとともに、同一回転時での風量
−静圧特性が増大しファン効率の向上ができる。With the above configuration, when the centrifugal fan 1 rotates, the air flowing from the orifice 12 through the suction grill 11 of the blower body 10 is discharged from the blade outlet 13 through the blade inlet 9 of the centrifugal fan 1, Further, it is discharged from the discharge port 14 of the blower main body 10. Therefore, most of the discharge flow 15 discharged from the centrifugal fan 1 attempts to collide with the housing side wall 16 of the blower main body 10, but since the shroud outer peripheral portion 7 is inclined to the suction side 6, the discharge flow of the centrifugal fan 1 is 15 in the direction of the discharge port 14 of the blower main body 10 and the outer peripheral portion 7 of the shroud of the centrifugal fan 1.
It is possible to further reduce the discharge speed of the flow, reduce the collision of the blower main body 10 with the housing side wall 16, and reduce the turbulence in the housing 17 by reducing the collision speed,
The generation of noise can be reduced, and the air flow-static pressure characteristics at the same rotation can be increased, and the fan efficiency can be improved.
【００２７】なお、実施例では、遠心ファン１の吸込側
６に吸込グリル１１とオリフィス１２を設置している
が、無くてもよく、その作用効果に差異を生じない。In the embodiment, the suction grill 11 and the orifice 12 are provided on the suction side 6 of the centrifugal fan 1, but they may not be provided, so that there is no difference in operation and effect.
【００２８】また、遠心ファン１の吸込側６または吐出
側５に熱交換器を設置してもよく、その作用効果に差異
を生じない。Further, a heat exchanger may be installed on the suction side 6 or the discharge side 5 of the centrifugal fan 1, so that there is no difference in operation and effect.
【００２９】また、送風機本体１０の吸込部となる吸込
グリル１１と、吐出部となる吐出口１４が略同一平面上
でかつ、同一方向に設置しているが、その必要はなく、
その作用効果に差異を生じない。The suction grill 11 serving as a suction portion of the blower main body 10 and the discharge port 14 serving as a discharge portion are provided on substantially the same plane and in the same direction, but this is not necessary.
There is no difference in the effects.
【００３０】（実施例２）図２または図３に示すよう
に、主板２と、シュラウド外部１８とシュラウド内部１
９の形状が異なる肉厚２０のあるシュラウド３で挟むよ
うに複数のブレード４が取り付けられた遠心ファン１
で、ファン外径Ｄに比し、シュラウド３のシュラウド吸
込径Ｄｓｉが０．６０〜０．８５であり、遠心ファン１
の吐出側５に位置するシュラウド内部１９のシュラウド
外周部７が、遠心ファン１の吸込側６に傾斜し、かつ任
意の周方向断面Ｓｉの通風路面積がシュラウド内周部８
のブレード流入部９とシュラウド３が交わる位置のブレ
ード入口周方向断面Ｓ１の通風路面積より大きい遠心フ
ァン１を有する構成にされている。(Embodiment 2) As shown in FIG. 2 or 3, the main plate 2, the shroud exterior 18 and the shroud interior 1
9 is a centrifugal fan 1 having a plurality of blades 4 attached between shrouds 3 having different thicknesses 20
In comparison with the fan outer diameter D, the shroud suction diameter Dsi of the shroud 3 is 0.60 to 0.85, and the centrifugal fan 1
The outer peripheral portion 7 of the shroud inside 19 located on the discharge side 5 of the centrifugal fan is inclined toward the suction side 6 of the centrifugal fan 1, and the area of the ventilation passage having an arbitrary circumferential cross section Si is changed to the inner peripheral portion 8 of the shroud 8.
The centrifugal fan 1 is larger than the ventilation passage area of the blade inlet circumferential section S1 at the position where the blade inflow portion 9 and the shroud 3 intersect.
【００３１】上記構成により、遠心ファン１が回転する
とき、送風機本体１０の吸込グリル１１を通りオリフィ
ス１２より流入した空気は、遠心ファン１のブレード流
入部９を通りブレード流出部１３より吐出され、更に送
風機本体１０の吐出口１４より吐出される。そこで、遠
心ファン１より吐出する吐出流れ１５の大半が送風機本
体１０の筐体側壁１６に衝突しようとするが、肉厚２０
によりシュラウド３内部のシュラウド外周部７が吸込側
６に傾斜しているので、遠心ファン１の吐出流れ１５を
送風機本体１０の吐出口１４の方向に向けるとともに、
遠心ファン１のシュラウド外周部７より流れの吐出速度
を減速することができ、送風機本体１０の筐体側壁１６
への衝突を少なくするとともに、衝突速度を減速するこ
とで筐体１７内の乱れを減少させ、騒音の発生を低減で
きるとともに、同一回転時での風量−静圧特性が増大し
ファン効率の向上ができる。With the above configuration, when the centrifugal fan 1 rotates, the air that has flowed in from the orifice 12 through the suction grill 11 of the blower main body 10 is discharged from the blade outflow portion 13 through the blade inflow portion 9 of the centrifugal fan 1, Further, it is discharged from the discharge port 14 of the blower main body 10. Therefore, most of the discharge flow 15 discharged from the centrifugal fan 1 attempts to collide with the housing side wall 16 of the blower main body 10,
As a result, the shroud outer peripheral portion 7 inside the shroud 3 is inclined toward the suction side 6, so that the discharge flow 15 of the centrifugal fan 1 is directed toward the discharge port 14 of the blower main body 10, and
The discharge speed of the flow can be reduced from the shroud outer peripheral portion 7 of the centrifugal fan 1, and the housing side wall 16 of the blower main body 10 can be reduced.
In addition to reducing collisions, the turbulence in the housing 17 can be reduced by reducing the collision speed, noise can be reduced, and the air flow-static pressure characteristics during the same rotation increase, thereby improving fan efficiency. Can be.
【００３２】なお、実施例では、遠心ファン１の吸込側
６に吸込グリル１１とオリフィス１２を設置している
が、無くてもよく、その作用効果に差異を生じない。In the embodiment, the suction grill 11 and the orifice 12 are provided on the suction side 6 of the centrifugal fan 1, but they may not be provided, and no difference occurs in the operation and effect.
【００３３】また、遠心ファン１の吸込側６または吐出
側５に熱交換器を設置してもよく、その作用効果に差異
を生じない。Further, a heat exchanger may be provided on the suction side 6 or the discharge side 5 of the centrifugal fan 1, so that there is no difference in operation and effect.
【００３４】また、送風機本体１０の吸込部となる吸込
グリル１１と、吐出部となる吐出口１４が略同一平面上
でかつ、同一方向に設置しているが、その必要はなく、
その作用効果に差異を生じない。The suction grill 11 serving as a suction portion of the blower main body 10 and the discharge port 14 serving as a discharge portion are provided on substantially the same plane and in the same direction.
There is no difference in the effects.
【００３５】また、肉厚２０によりシュラウド３内部の
シュラウド外周部７が吸込側６に傾斜しているが、薄肉
または板金のシュラウド３に肉厚２０の部材を取り付け
てもよく、その作用効果に差異を生じない。Although the shroud outer peripheral portion 7 inside the shroud 3 is inclined toward the suction side 6 due to the wall thickness 20, a member having a wall thickness of 20 may be attached to the shroud 3 made of thin or sheet metal. Make no difference.
【００３６】（実施例３）図２または図４に示すよう
に、遠心ファン１の吐出側５に位置するシュラウド外周
部７が、遠心ファン１の吸込側６に傾斜し、シュラウド
外周部７の傾斜角αが１゜〜６０゜の遠心ファン１を有
する構成にされている。(Embodiment 3) As shown in FIG. 2 or FIG. 4, the outer peripheral portion 7 of the shroud located on the discharge side 5 of the centrifugal fan 1 is inclined toward the suction side 6 of the centrifugal fan 1, and the outer peripheral portion 7 of the shroud 7 The centrifugal fan 1 has an inclination angle α of 1 ° to 60 °.
【００３７】上記構成により、遠心ファン１が回転する
とき、送風機本体１０の吸込グリル１１を通りオリフィ
ス１２より流入した空気は、遠心ファン１のブレード流
入部９を通りブレード流出部１３より吐出され、更に送
風機本体１０の吐出口１４より吐出される。そこで、遠
心ファン１より吐出する吐出流れ１５の大半が送風機本
体１０の筐体側壁１６に衝突しようとするが、シュラウ
ド外周部７が吸込側６に傾斜し、シュラウド外周部７の
傾斜角αが１゜〜６０゜の範囲で一定にしているので、
製作が容易で低コスト化が図れ、遠心ファン１の吐出流
れ１５を送風機本体１０の吐出口１４の方向に向けると
ともに、遠心ファン１のシュラウド外周部７より流れの
吐出速度を減速することができ、送風機本体１０の筐体
側壁１６への衝突を少なくするとともに、衝突速度を減
速することで筐体１７内の乱れを減少させ、騒音の発生
を低減できるとともに、同一回転時での風量−静圧特性
が増大しファン効率の向上ができる。With the above configuration, when the centrifugal fan 1 rotates, the air flowing from the orifice 12 through the suction grill 11 of the blower body 10 is discharged from the blade outlet 13 through the blade inlet 9 of the centrifugal fan 1, Further, it is discharged from the discharge port 14 of the blower main body 10. Therefore, most of the discharge flow 15 discharged from the centrifugal fan 1 attempts to collide with the housing side wall 16 of the blower main body 10, but the shroud outer peripheral portion 7 inclines to the suction side 6, and the inclination angle α of the shroud outer peripheral portion 7 becomes smaller. Because it is constant in the range of 1 ゜ to 60 ゜,
The discharge flow 15 of the centrifugal fan 1 can be directed toward the discharge port 14 of the blower main body 10 and the discharge speed of the flow from the outer peripheral portion 7 of the shroud of the centrifugal fan 1 can be reduced. In addition to reducing the collision of the blower main body 10 with the housing side wall 16 and reducing the collision speed, the turbulence in the housing 17 can be reduced and the generation of noise can be reduced. The pressure characteristics are increased, and the fan efficiency can be improved.
【００３８】なお、実施例では、遠心ファン１の吸込側
６に吸込グリル１１とオリフィス１２を設置している
が、無くてもよく、その作用効果に差異を生じない。In the embodiment, the suction grill 11 and the orifice 12 are provided on the suction side 6 of the centrifugal fan 1, but they may be omitted, so that there is no difference in the operation and effect.
【００３９】また、遠心ファン１の吸込側６または吐出
側５に熱交換器を設置してもよく、その作用効果に差異
を生じない。Further, a heat exchanger may be provided on the suction side 6 or the discharge side 5 of the centrifugal fan 1, so that there is no difference in operation and effect.
【００４０】また、送風機本体１０の吸込部となる吸込
グリル１１と、吐出部となる吐出口１４が略同一平面上
でかつ、同一方向に設置しているが、その必要はなく、
その作用効果に差異を生じない。The suction grill 11 serving as a suction portion of the blower main body 10 and the discharge port 14 serving as a discharge portion are provided on substantially the same plane and in the same direction.
There is no difference in the effects.
【００４１】（実施例４）図２または図５に示すよう
に、遠心ファン１の吐出側５に位置するシュラウド外周
部７が、遠心ファン１の吸込側６に傾斜し、シュラウド
３断面が略円弧形状の遠心ファン１を有する構成にされ
ている。(Embodiment 4) As shown in FIG. 2 or FIG. 5, the outer peripheral portion 7 of the shroud located on the discharge side 5 of the centrifugal fan 1 is inclined to the suction side 6 of the centrifugal fan 1, and the cross section of the shroud 3 is substantially formed. It has a configuration having an arc-shaped centrifugal fan 1.
【００４２】上記構成により、遠心ファン１が回転する
とき、送風機本体１０の吸込グリル１１を通りオリフィ
ス１２より流入した空気は、遠心ファン１のブレード流
入部９を通りブレード流出部１３より吐出され、更に送
風機本体１０の吐出口１４より吐出される。そこで、遠
心ファン１より吐出する吐出流れ１５の大半が送風機本
体１０の筐体側壁１６に衝突しようとするが、シュラウ
ド外周部７が吸込側６に傾斜し、シュラウド３断面を略
円弧形状とすることで、遠心ファン１の吐出流れ１５が
シュラウド外周部７の形状に沿うスムースな流れとな
り、送風機本体１０の吐出口１４の方向に向けるととも
に、遠心ファン１のシュラウド外周部７より流れの吐出
速度を減速することができ、送風機本体１０の筐体側壁
１６への衝突を少なくするとともに、衝突速度を減速す
ることで筐体１７内の乱れを減少させ、騒音の発生を低
減できるとともに、同一回転時での風量−静圧特性が増
大しファン効率の向上ができる。With the above configuration, when the centrifugal fan 1 rotates, the air that has flowed in from the orifice 12 through the suction grill 11 of the blower main body 10 is discharged from the blade outflow portion 13 through the blade inflow portion 9 of the centrifugal fan 1, Further, it is discharged from the discharge port 14 of the blower main body 10. Therefore, most of the discharge flow 15 discharged from the centrifugal fan 1 attempts to collide with the housing side wall 16 of the blower main body 10, but the shroud outer peripheral portion 7 is inclined to the suction side 6, and the cross section of the shroud 3 has a substantially arc shape. As a result, the discharge flow 15 of the centrifugal fan 1 becomes a smooth flow along the shape of the shroud outer peripheral portion 7, and is directed toward the discharge port 14 of the blower main body 10, and the discharge speed of the flow from the shroud outer peripheral portion 7 of the centrifugal fan 1. Can be reduced, the collision of the blower main body 10 with the housing side wall 16 can be reduced, and the collision speed can be reduced to reduce the turbulence in the housing 17 and reduce the generation of noise. The air flow-static pressure characteristics at the time are increased, and the fan efficiency can be improved.
【００４３】なお、実施例では、遠心ファン１の吸込側
６に吸込グリル１１とオリフィス１２を設置している
が、無くてもよく、その作用効果に差異を生じない。In the embodiment, the suction grill 11 and the orifice 12 are provided on the suction side 6 of the centrifugal fan 1, but they may be omitted, and the operation and effect do not differ.
【００４４】また、送風機本体１０の吸込部となる吸込
グリル１１と、吐出部となる吐出口１４が略同一平面上
でかつ、同一方向に設置しているが、その必要はなく、
その作用効果に差異を生じない。The suction grill 11 serving as a suction portion of the blower main body 10 and the discharge port 14 serving as a discharge portion are arranged on substantially the same plane and in the same direction.
There is no difference in the effects.
【００４５】（実施例５）図２または図６に示すよう
に、遠心ファン１の吐出側５に位置するシュラウド外周
部７が、遠心ファン１の吸込側６に傾斜し、シュラウド
３断面が略円弧形状であり、ファン外径Ｄに比しシュラ
ウド断面半径Ｒが０．０１Ｄ〜０．２５Ｄの遠心ファン
１を有する構成にされている。Embodiment 5 As shown in FIG. 2 or FIG. 6, the outer peripheral portion 7 of the shroud located on the discharge side 5 of the centrifugal fan 1 is inclined toward the suction side 6 of the centrifugal fan 1, and the cross section of the shroud 3 is substantially formed. The centrifugal fan 1 has an arc shape and has a shroud sectional radius R of 0.01D to 0.25D as compared with the fan outer diameter D.
【００４６】上記構成により、遠心ファン１が回転する
とき、送風機本体１０の吸込グリル１１を通りオリフィ
ス１２より流入した空気は、遠心ファン１のブレード流
入部９を通りブレード流出部１３より吐出され、更に送
風機本体１０の吐出口１４より吐出される。そこで、遠
心ファン１より吐出する吐出流れ１５の大半が送風機本
体１０の筐体側壁１６に衝突しようとするが、シュラウ
ド外周部７が吸込側６に傾斜し、シュラウド３断面が略
円弧形状で、ファン外径Ｄに比しシュラウド断面半径Ｒ
を０．０１Ｄ〜０．２５Ｄとすることで、遠心ファン１
の吐出流れ１５がシュラウド外周部７の形状に沿うスム
ースな流れとなり、確実に送風機本体１０の吐出口１４
の方向に向けるとともに、遠心ファン１のシュラウド外
周部７より流れの吐出速度を減速することができ、送風
機本体１０の筐体側壁１６への衝突を少なくするととも
に、衝突速度を減速することで筐体１７内の乱れを減少
させ、騒音の発生を低減できるとともに、同一回転時で
の風量−静圧特性が増大しファン効率の向上ができる。With the above configuration, when the centrifugal fan 1 rotates, the air that has flowed in from the orifice 12 through the suction grill 11 of the blower main body 10 is discharged from the blade outflow portion 13 through the blade inflow portion 9 of the centrifugal fan 1, Further, it is discharged from the discharge port 14 of the blower main body 10. Therefore, most of the discharge flow 15 discharged from the centrifugal fan 1 tries to collide with the housing side wall 16 of the blower main body 10, but the shroud outer peripheral portion 7 is inclined to the suction side 6, and the cross section of the shroud 3 has a substantially arc shape. Shroud section radius R compared to fan outer diameter D
Is set to 0.01D to 0.25D, the centrifugal fan 1
Discharge flow 15 of the blower body 10 becomes a smooth flow along the shape of the shroud outer peripheral portion 7, and the discharge port 14
, The discharge speed of the flow from the outer peripheral portion 7 of the shroud of the centrifugal fan 1 can be reduced, the collision of the blower main body 10 with the housing side wall 16 is reduced, and the collision speed is reduced to reduce the housing speed. The turbulence in the body 17 can be reduced to reduce the generation of noise, and the air flow-static pressure characteristics at the same rotation can be increased to improve the fan efficiency.
【００４７】なお、実施例では、遠心ファン１の吸込側
６に吸込グリル１１とオリフィス１２を設置している
が、無くてもよく、その作用効果に差異を生じない。In the embodiment, the suction grill 11 and the orifice 12 are provided on the suction side 6 of the centrifugal fan 1, but they may not be provided, so that there is no difference in operation and effect.
【００４８】また、遠心ファン１の吸込側６または吐出
側５に熱交換器を設置してもよく、その作用効果に差異
を生じない。Further, a heat exchanger may be provided on the suction side 6 or the discharge side 5 of the centrifugal fan 1, so that there is no difference in operation and effect.
【００４９】また、送風機本体１０の吸込部となる吸込
グリル１１と、吐出部となる吐出口１４が略同一平面上
でかつ、同一方向に設置しているが、その必要はなく、
その作用効果に差異を生じない。The suction grill 11 serving as a suction portion of the blower main body 10 and the discharge port 14 serving as a discharge portion are provided on substantially the same plane and in the same direction.
There is no difference in the effects.
【００５０】（実施例６）図２または図７に示すよう
に、遠心ファン１の吐出側５に位置するシュラウド外周
部７が、遠心ファン１の吸込側６に傾斜し、かつ遠心フ
ァン１のブレード４の任意の幅Ｂが最小となる位置をブ
レード幅最小径Ｄ１とし、ファン外径Ｄに比しブレード
幅最小径Ｄ１が０．７Ｄ〜０．９８Ｄの遠心ファン１を
有する構成にされている。(Embodiment 6) As shown in FIG. 2 or FIG. 7, the outer peripheral portion 7 of the shroud located on the discharge side 5 of the centrifugal fan 1 is inclined to the suction side 6 of the centrifugal fan 1, and The position where the arbitrary width B of the blade 4 is minimum is defined as the blade width minimum diameter D1, and the centrifugal fan 1 has a blade width minimum diameter D1 of 0.7D to 0.98D compared to the fan outer diameter D. I have.
【００５１】上記構成により、遠心ファン１が回転する
とき、送風機本体１０の吸込グリル１１を通りオリフィ
ス１２より流入した空気は、遠心ファン１のブレード流
入部９を通りブレード流出部１３より吐出され、更に送
風機本体１０の吐出口１４より吐出される。そこで、遠
心ファン１より吐出する吐出流れ１５の大半が送風機本
体１０の筐体側壁１６に衝突しようとするが、シュラウ
ド外周部７が吸込側６に傾斜し、ブレード幅最小径Ｄ１
を０．７Ｄ〜０．９８Ｄとすることで、遠心ファン１の
内部のシュラウド３側の内部流れと、シュラウド外周部
７の吐出流れ１５が形状に沿うスムースな流れとなり、
確実に送風機本体１０の吐出口１４の方向に向けるとと
もに、遠心ファン１のシュラウド外周部７より流れの吐
出速度を減速することができ、送風機本体１０の筐体側
壁１６への衝突を少なくするとともに、衝突速度を減速
することで筐体１７内の乱れを減少させ、騒音の発生を
低減できるとともに、同一回転時での風量−静圧特性が
増大しファン効率の向上ができる。With the above configuration, when the centrifugal fan 1 rotates, the air that has flowed in from the orifice 12 through the suction grill 11 of the blower main body 10 is discharged from the blade outflow portion 13 through the blade inflow portion 9 of the centrifugal fan 1, Further, it is discharged from the discharge port 14 of the blower main body 10. Therefore, most of the discharge flow 15 discharged from the centrifugal fan 1 attempts to collide with the housing side wall 16 of the blower main body 10, but the shroud outer peripheral portion 7 is inclined to the suction side 6 and the blade width minimum diameter D1
Is set to 0.7D to 0.98D, the internal flow on the shroud 3 side inside the centrifugal fan 1 and the discharge flow 15 of the shroud outer peripheral portion 7 become a smooth flow along the shape,
The blower body 10 can be reliably directed toward the discharge port 14 of the blower body 10 and the discharge speed of the flow can be reduced from the outer peripheral portion 7 of the shroud of the centrifugal fan 1, thereby reducing the collision of the blower body 10 with the housing side wall 16. By reducing the collision speed, turbulence in the housing 17 can be reduced to reduce noise, and the air flow-static pressure characteristics at the same rotation can be increased, thereby improving fan efficiency.
【００５２】なお、実施例では、遠心ファン１の吸込側
６に吸込グリル１１とオリフィス１２を設置している
が、無くてもよく、その作用効果に差異を生じない。In the embodiment, the suction grill 11 and the orifice 12 are provided on the suction side 6 of the centrifugal fan 1, but they may be omitted, so that there is no difference in operation and effect.
【００５３】また、遠心ファン１の吸込側６または吐出
側５に熱交換器を設置してもよく、その作用効果に差異
を生じない。Further, a heat exchanger may be provided on the suction side 6 or the discharge side 5 of the centrifugal fan 1, so that there is no difference in operation and effect.
【００５４】また、送風機本体１０の吸込部となる吸込
グリル１１と、吐出部となる吐出口１４が略同一平面上
でかつ、同一方向に設置しているが、その必要はなく、
その作用効果に差異を生じない。The suction grill 11 serving as the suction portion of the blower main body 10 and the discharge port 14 serving as the discharge portion are disposed on substantially the same plane and in the same direction.
There is no difference in the effects.
【００５５】（実施例７）図２または図８に示すよう
に、遠心ファン１の吐出側５に位置するシュラウド外周
部７を含むシュラウド外径Ｄｓｏがファン外径Ｄより大
きい遠心ファン１を有する構成にされている。(Embodiment 7) As shown in FIG. 2 or FIG. 8, the centrifugal fan 1 having a shroud outer diameter Dso including the shroud outer peripheral portion 7 located on the discharge side 5 of the centrifugal fan 1 is larger than the fan outer diameter D. Is configured.
【００５６】上記構成により、遠心ファン１が回転する
とき、送風機本体１０の吸込グリル１１を通りオリフィ
ス１２より流入した空気は、遠心ファン１のブレード流
入部９を通りブレード流出部１３より吐出され、更に送
風機本体１０の吐出口１４より吐出される。そこで、遠
心ファン１より吐出する吐出流れ１５の大半が送風機本
体１０の筐体側壁１６に衝突しようとするが、シュラウ
ド外周部７が吸込側６に傾斜して、シュラウド外径Ｄｓ
ｏがブレード４の外径であるファン外径Ｄより大きく
し、シュラウド外周部７を延長することで、吐出流れ１
５がシュラウド外周部７の形状に沿うスムースな流れを
持続し、確実に送風機本体１０の吐出口１４の方向に向
けるとともに、遠心ファン１のシュラウド外周部７より
流れの吐出速度を減速することができ、送風機本体１０
の筐体側壁１６への衝突を少なくするとともに、衝突速
度を減速することで筐体１７内の乱れを減少させ、騒音
の発生を低減できるとともに、同一回転時での風量−静
圧特性が増大しファン効率の向上ができる。With the above configuration, when the centrifugal fan 1 rotates, the air that has flowed in from the orifice 12 through the suction grill 11 of the blower main body 10 is discharged from the blade outflow portion 13 through the blade inflow portion 9 of the centrifugal fan 1, Further, it is discharged from the discharge port 14 of the blower main body 10. Therefore, most of the discharge flow 15 discharged from the centrifugal fan 1 attempts to collide with the housing side wall 16 of the blower main body 10, but the shroud outer peripheral portion 7 is inclined to the suction side 6, and the shroud outer diameter Ds
o is larger than the fan outer diameter D which is the outer diameter of the blade 4 and the outer peripheral portion 7 of the shroud is extended, so that the discharge flow 1
5 can maintain a smooth flow along the shape of the shroud outer peripheral portion 7, reliably direct the flow toward the discharge port 14 of the blower main body 10, and reduce the discharge speed of the flow from the shroud outer peripheral portion 7 of the centrifugal fan 1. Yes, blower body 10
In addition to reducing the collision with the housing side wall 16 and reducing the collision speed, the turbulence in the housing 17 can be reduced, noise can be reduced, and the air flow-static pressure characteristic at the same rotation increases. Fan efficiency can be improved.
【００５７】なお、実施例では、遠心ファン１の吸込側
６に吸込グリル１１とオリフィス１２を設置している
が、無くてもよく、その作用効果に差異を生じない。In the embodiment, the suction grill 11 and the orifice 12 are provided on the suction side 6 of the centrifugal fan 1, but they may be omitted, and the operation and effect thereof do not differ.
【００５８】また、遠心ファン１の吸込側６または吐出
側５に熱交換器を設置してもよく、その作用効果に差異
を生じない。Further, a heat exchanger may be provided on the suction side 6 or the discharge side 5 of the centrifugal fan 1, so that there is no difference in operation and effect.
【００５９】また、送風機本体１０の吸込部となる吸込
グリル１１と、吐出部となる吐出口１４が略同一平面上
でかつ、同一方向に設置しているが、その必要はなく、
その作用効果に差異を生じない。The suction grill 11 serving as a suction portion of the blower main body 10 and the discharge port 14 serving as a discharge portion are provided on substantially the same plane and in the same direction, but this is not necessary.
There is no difference in the effects.
【００６０】また、シュラウド外径Ｄｓｏをファン外径
Ｄより大きくし、シュラウド外周部７を延長する形状と
しているが、シュラウド外周部７のファン外径Ｄより大
きいシュラウド延長部２１は、シュラウド３とは異なる
形状または肉厚または材質の別部材を取り付けてもよ
く、その作用効果に差異を生じない。Although the shroud outer diameter Dso is made larger than the fan outer diameter D and the shroud outer peripheral portion 7 is extended, the shroud extension 21 larger than the fan outer diameter D of the shroud outer peripheral portion 7 is May be attached with another member of different shape, thickness or material, so that there is no difference in operation and effect.
【００６１】（実施例８）図２または図９に示すよう
に、主板２とシュラウド３で挟むように複数のブレード
４が取り付けられた遠心ファン１で、ファン外径Ｄに比
し、シュラウド３のシュラウド吸込径Ｄｓｉが０．６０
〜０．８５であり、遠心ファン１の吐出側５に位置する
シュラウド外周部７が、遠心ファン１の吸込側６に傾斜
し、かつシュラウド外周部７がファン外径Ｄより外周側
に位置しており、主板２とシュラウド外周部７のシュラ
ウド外周端２２との幅Ｌｓが、ブレード４の入口幅Ｂｉ
より大きい遠心ファン１を有する構成にされている。(Embodiment 8) As shown in FIG. 2 or FIG. 9, a centrifugal fan 1 in which a plurality of blades 4 are attached so as to be sandwiched between a main plate 2 and a shroud 3 is provided. Has a shroud suction diameter Dsi of 0.60
The outer peripheral portion 7 of the shroud located on the discharge side 5 of the centrifugal fan 1 is inclined toward the suction side 6 of the centrifugal fan 1 and the outer peripheral portion 7 of the shroud is located on the outer peripheral side of the fan outer diameter D. The width Ls between the main plate 2 and the shroud outer peripheral end 22 of the shroud outer peripheral portion 7 is equal to the inlet width Bi of the blade 4.
It is configured to have a larger centrifugal fan 1.
【００６２】上記構成により、遠心ファン１が回転する
とき、送風機本体１０の吸込グリル１１を通りオリフィ
ス１２より流入した空気は、遠心ファン１のブレード流
入部９を通りブレード流出部１３より吐出され、更に送
風機本体１０の吐出口１４より吐出される。そこで、遠
心ファン１より吐出する吐出流れ１５の大半が送風機本
体１０の筐体側壁１６に衝突しようとするが、シュラウ
ド外周部７が吸込側６に傾斜して、シュラウド外周部７
がブレード４の外径であるファン外径Ｄより外周側に位
置し、主板２とシュラウド外周部７のシュラウド外周端
２２との幅Ｌｓを、ブレード４の入口幅Ｂｉより大きく
することで、吐出流れ１５がシュラウド外周部７の形状
に沿うスムースな流れで、送風機本体１０の吐出口１４
付近まで確実に導かれ、かつ遠心ファン１の内部より流
れは減速し、さらにシュラウド外周部７より流れの吐出
速度を減速することができ、送風機本体１０の筐体側壁
１６への衝突を少なくするとともに、衝突速度を減速す
ることで筐体１７内の乱れを減少させ、騒音の発生を低
減できるとともに、同一回転時での風量−静圧特性が増
大しファン効率の向上ができる。With the above configuration, when the centrifugal fan 1 rotates, the air that has flowed in from the orifice 12 through the suction grill 11 of the blower main body 10 is discharged from the blade outflow portion 13 through the blade inflow portion 9 of the centrifugal fan 1, Further, it is discharged from the discharge port 14 of the blower main body 10. Therefore, most of the discharge flow 15 discharged from the centrifugal fan 1 attempts to collide with the housing side wall 16 of the blower main body 10, but the shroud outer peripheral portion 7 is inclined to the suction side 6, and the shroud outer peripheral portion 7 is inclined.
Is located on the outer peripheral side of the fan outer diameter D which is the outer diameter of the blade 4, and the width Ls between the main plate 2 and the shroud outer peripheral end 22 of the shroud outer peripheral portion 7 is made larger than the inlet width Bi of the blade 4 so that the discharge is performed. The flow 15 is a smooth flow along the shape of the outer peripheral portion 7 of the shroud, and the discharge port 14 of the blower main body 10 is formed.
The flow is reliably guided to the vicinity, the flow is reduced from the inside of the centrifugal fan 1, the discharge speed of the flow is further reduced from the outer peripheral portion 7 of the shroud, and the collision of the blower main body 10 with the housing side wall 16 is reduced. At the same time, by reducing the collision speed, the turbulence in the housing 17 can be reduced, noise can be reduced, and the air flow-static pressure characteristics at the same rotation can be increased to improve the fan efficiency.
【００６３】なお、実施例では、遠心ファン１の吸込側
６に吸込グリル１１とオリフィス１２を設置している
が、無くてもよく、その作用効果に差異を生じない。In the embodiment, the suction grill 11 and the orifice 12 are provided on the suction side 6 of the centrifugal fan 1, but they may be omitted, so that there is no difference in operation and effect.
【００６４】また、遠心ファン１の吸込側６または吐出
側５に熱交換器を設置してもよく、その作用効果に差異
を生じない。Further, a heat exchanger may be installed on the suction side 6 or the discharge side 5 of the centrifugal fan 1, so that there is no difference in operation and effect.
【００６５】また、送風機本体１０の吸込部となる吸込
グリル１１と、吐出部となる吐出口１４が略同一平面上
でかつ、同一方向に設置しているが、その必要はなく、
その作用効果に差異を生じない。The suction grille 11 serving as the suction portion of the blower main body 10 and the discharge port 14 serving as the discharge portion are provided on substantially the same plane and in the same direction, but this is not necessary.
There is no difference in the effects.
【００６６】また、シュラウド外周部７がファン外径Ｄ
より外周側に位置する形状としているが、シュラウド外
周部７は、シュラウド３とは異なる形状または肉厚また
は材質の別部材を取り付けてもよく、その作用効果に差
異を生じない。The shroud outer peripheral portion 7 has a fan outer diameter D.
Although the shape is located on the outer peripheral side, the shroud outer peripheral portion 7 may be attached with another member having a shape, thickness, or material different from that of the shroud 3, and there is no difference in the operation and effect.
【００６７】[0067]
【発明の効果】以上の実施例から明らかなように、本発
明によれば、騒音の発生を低減することができ、ファン
の効率を向上することができ消費電力を低くすることが
できる遠心送風機を提供できる。As is clear from the above embodiments, according to the present invention, the generation of noise can be reduced, the efficiency of the fan can be improved, and the power consumption can be reduced. Can be provided.
【図１】本発明の実施例１の遠心送風機を示す側断面図FIG. 1 is a side sectional view showing a centrifugal blower according to a first embodiment of the present invention.
【図２】同実施例１、２，３，４，５，６，７または８
の要部正面断面図FIG. 2 shows the first, second, third, fourth, fifth, sixth, seventh or eighth embodiment.
Main part front sectional view of
【図３】同実施例２の遠心送風機を示す側断面図FIG. 3 is a side sectional view showing a centrifugal blower according to the second embodiment.
【図４】同実施例３の遠心送風機を示す側断面図FIG. 4 is a side sectional view showing the centrifugal blower according to the third embodiment.
【図５】同実施例４の遠心送風機を示す側断面図FIG. 5 is a side sectional view showing the centrifugal blower according to the fourth embodiment.
【図６】同実施例５の遠心送風機を示す側断面図FIG. 6 is a side sectional view showing the centrifugal blower of the fifth embodiment.
【図７】同実施例６の遠心送風機を示す側断面図FIG. 7 is a side sectional view showing a centrifugal blower according to the sixth embodiment.
【図８】同実施例７の遠心送風機を示す側断面図FIG. 8 is a side sectional view showing the centrifugal blower of the seventh embodiment.
【図９】同実施例８の遠心送風機を示す側断面図FIG. 9 is a side sectional view showing the centrifugal blower according to the eighth embodiment.
【図１０】従来の遠心送風機を示す側断面図FIG. 10 is a side sectional view showing a conventional centrifugal blower.
１ 遠心ファン ２ 主板 ３ シュラウド ４ ブレード ５ 吐出側 ６ 吸込側 Ｄ ファン外径 Ｄｓｉ シュラウド吸込径 ７ シュラウド外周部 ８ シュラウド内周部 ９ ブレード流入部 １０ 送風機本体 １１ 吸込グリル １２ オリフィス １３ ブレード流出部 １４ 吐出口 １５ 吐出流れ １６ 筐体側壁 １７ 筐体 １８ シュラウド外部 １９ シュラウド内部 ２０ 肉厚 Ｓｉ 周方向断面 Ｓ１ ブレード入口周方向断面 α 傾斜角 Ｒ シュラウド断面半径 Ｄ１ ブレード幅最小径 Ｄｓｏ シュラウド外径 ２１ シュラウド延長部 ２２ シュラウド外周端 Ｌｓ 幅 Ｂｉ 入口幅 DESCRIPTION OF SYMBOLS 1 Centrifugal fan 2 Main plate 3 Shroud 4 Blade 5 Discharge side 6 Suction side D Fan outer diameter Dsi Shroud suction diameter 7 Shroud outer peripheral part 8 Shroud inner peripheral part 9 Blade inflow part 10 Blower main body 11 Suction grille 12 Orifice 13 Blade outflow part 14 Discharge Outlet 15 Discharge flow 16 Case side wall 17 Case 18 Shroud outside 19 Shroud inside 20 Wall thickness Si circumferential section S1 Blade inlet circumferential section α Slope angle R Shroud section radius D1 Blade width minimum diameter Dso Shroud outer diameter 21 Shroud extension 22 Outer edge of shroud Ls width Bi Inlet width
Claims (8)
レードが取り付けられた遠心ファンで、ファン外径Ｄに
比し、前記シュラウドのシュラウド吸込径Ｄｓｉが０．
６０〜０．８５であり、前記遠心ファンの吐出側に位置
するシュラウド外周部が、前記遠心ファンの吸込側に傾
斜し、かつ任意の周方向断面Ｓｉの通風路面積がシュラ
ウド内周部のブレード流入部と前記シュラウドが交わる
位置のブレード入口周方向断面Ｓ１の通風路面積より大
きい前記遠心ファンを有する遠心送風機。1. A centrifugal fan in which a plurality of blades are attached so as to be sandwiched between a main plate and a shroud, wherein the shroud has a shroud suction diameter Dsi of 0.
60 to 0.85, the outer peripheral portion of the shroud located on the discharge side of the centrifugal fan is inclined toward the suction side of the centrifugal fan, and the air passage area of any circumferential cross section Si is the blade of the inner peripheral portion of the shroud. A centrifugal blower having the centrifugal fan larger than a ventilation passage area of a blade inlet circumferential cross section S1 at a position where an inflow portion and the shroud intersect.
部の形状が異なる肉厚のあるシュラウドで挟むように複
数のブレードが取り付けられた遠心ファンで、ファン外
径Ｄに比し、前記シュラウドのシュラウド吸込径Ｄｓｉ
が０．６０〜０．８５であり、前記遠心ファンの吐出側
に位置する前記シュラウド内部のシュラウド外周部が、
前記遠心ファンの吸込側に傾斜し、かつ任意の周方向断
面Ｓｉの通風路面積がシュラウド内周部のブレード流入
部と前記シュラウドが交わる位置のブレード入口周方向
断面Ｓ１の通風路面積より大きい前記遠心ファンを有す
る遠心送風機。2. A centrifugal fan in which a plurality of blades are mounted so as to be sandwiched between a main plate and a thick shroud having different shapes inside and outside of the shroud, and the shroud suction of the shroud is smaller than a fan outer diameter D. Diameter Dsi
Is 0.60 to 0.85, and the outer peripheral portion of the shroud inside the shroud located on the discharge side of the centrifugal fan is:
The air passage area of the circumferential cross section Si inclined to the suction side of the centrifugal fan is larger than the air passage area of the blade inlet circumferential cross section S1 at the position where the shroud intersects the blade inflow portion of the shroud inner periphery. Centrifugal blower with centrifugal fan.
ド外周部が、前記遠心ファンの吸込側に傾斜し、前記シ
ュラウド外周部の傾斜角αが１゜〜６０゜の前記遠心フ
ァンを有する請求項１または２記載の遠心送風機。3. A shroud outer peripheral portion located on a discharge side of the centrifugal fan is inclined toward a suction side of the centrifugal fan, and the shroud outer peripheral portion has the centrifugal fan having an inclination angle α of 1 ° to 60 °. 3. The centrifugal blower according to 1 or 2.
ド外周部が、前記遠心ファンの吸込側に傾斜し、シュラ
ウド断面が略円弧形状の前記遠心ファンを有する請求項
１、２または３記載の遠心送風機。4. The centrifugal fan according to claim 1, wherein the outer peripheral portion of the shroud located on the discharge side of the centrifugal fan is inclined toward the suction side of the centrifugal fan, and the centrifugal fan has a substantially arc-shaped cross section. Blower.
ド外周部が、前記遠心ファンの吸込側に傾斜し、シュラ
ウド断面が略円弧形状であり、ファン外径Ｄに比しシュ
ラウド断面半径Ｒが０．０１Ｄ〜０．２５Ｄの前記遠心
ファンを有する請求項１、２、３または４記載の遠心送
風機。5. A shroud outer peripheral portion located on the discharge side of the centrifugal fan is inclined toward the suction side of the centrifugal fan, has a substantially arc-shaped cross-section, and has a shroud cross-sectional radius R of 0 compared to the fan outer diameter D. The centrifugal blower according to claim 1, 2, 3, or 4, comprising the centrifugal fan of 0.01D to 0.25D.
ド外周部が、前記遠心ファンの吸込側に傾斜し、かつ前
記遠心ファンのブレードの任意の幅Ｂが最小となる位置
をブレード幅最小径Ｄ１とし、ファン外径Ｄに比し前記
ブレード幅最小径Ｄ１が０．７Ｄ〜０．９８Ｄの前記遠
心ファンを有する請求項１、２、３、４または５記載の
遠心送風機。6. A shroud outer peripheral portion located on a discharge side of the centrifugal fan is inclined toward a suction side of the centrifugal fan, and a position where an arbitrary width B of the blade of the centrifugal fan is minimum is defined as a blade width minimum diameter D1. The centrifugal blower according to claim 1, 2, 3, 4, or 5, wherein the centrifugal fan has a blade width minimum diameter D1 of 0.7D to 0.98D as compared with a fan outer diameter D.
ド外周部を含むシュラウド外径Ｄｓｏがファン外径Ｄよ
り大きい前記遠心ファンを有する請求項１、２、３、
４、５または６記載の遠心送風機。7. The centrifugal fan according to claim 1, wherein the outer diameter Dso of the shroud including the outer peripheral portion of the shroud located on the discharge side of the centrifugal fan is larger than the outer diameter D of the fan.
The centrifugal blower according to 4, 5, or 6.
レードが取り付けられた遠心ファンで、ファン外径Ｄに
比し、前記シュラウドのシュラウド吸込径Ｄｓｉが０．
６０〜０．８５であり、前記遠心ファンの吐出側に位置
するシュラウド外周部が、前記遠心ファンの吸込側に傾
斜し、かつ前記シュラウド外周部が前記ファン外径Ｄよ
り外周側に位置しており、前記主板とシュラウド外周部
のシュラウド外周端との幅Ｌｓが、前記ブレードの入口
幅Ｂｉより大きい前記遠心ファンを有する遠心送風機。8. A centrifugal fan in which a plurality of blades are attached so as to be sandwiched between a main plate and a shroud, wherein the shroud has a shroud suction diameter Dsi of 0.1 mm as compared with a fan outer diameter D.
60 to 0.85, the outer peripheral portion of the shroud located on the discharge side of the centrifugal fan is inclined toward the suction side of the centrifugal fan, and the outer peripheral portion of the shroud is located on the outer peripheral side of the outer diameter D of the fan. And a centrifugal blower having the centrifugal fan, wherein a width Ls between the main plate and a shroud outer peripheral end of a shroud outer peripheral portion is larger than an inlet width Bi of the blade.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP10293497A JP2000120582A (en) | 1998-10-15 | 1998-10-15 | Centrifugal blower |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP10293497A JP2000120582A (en) | 1998-10-15 | 1998-10-15 | Centrifugal blower |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JP2000120582A true JP2000120582A (en) | 2000-04-25 |
Family
ID=17795513
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP10293497A Pending JP2000120582A (en) | 1998-10-15 | 1998-10-15 | Centrifugal blower |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2000120582A (en) |
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2009013926A (en) * | 2007-07-06 | 2009-01-22 | Daikin Ind Ltd | Centrifugal fan and air conditioner using the same |
| WO2010035584A1 (en) * | 2008-09-29 | 2010-04-01 | ダイキン工業株式会社 | Indoor unit for floor mounted air conditioner |
| WO2011121773A1 (en) * | 2010-03-31 | 2011-10-06 | 三菱電機株式会社 | Multi-blade blower |
| CN104165147A (en) * | 2013-05-20 | 2014-11-26 | 海尔集团公司 | Centrifugal fan system, and air cooling refrigerator using same |
| WO2015111210A1 (en) | 2014-01-27 | 2015-07-30 | 三菱電機株式会社 | Centrifugal fan and air conditioning device |
| JP2017036723A (en) * | 2015-08-07 | 2017-02-16 | 日本電産株式会社 | Impeller and centrifugal fan |
| JP2019078196A (en) * | 2017-10-23 | 2019-05-23 | フルタ電機株式会社 | Impeller for heating cooker, dryer or air blower |
-
1998
- 1998-10-15 JP JP10293497A patent/JP2000120582A/en active Pending
Cited By (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2009013926A (en) * | 2007-07-06 | 2009-01-22 | Daikin Ind Ltd | Centrifugal fan and air conditioner using the same |
| WO2010035584A1 (en) * | 2008-09-29 | 2010-04-01 | ダイキン工業株式会社 | Indoor unit for floor mounted air conditioner |
| JP2010078274A (en) * | 2008-09-29 | 2010-04-08 | Daikin Ind Ltd | Indoor unit for floor setting type air conditioner |
| JP4502057B2 (en) * | 2008-09-29 | 2010-07-14 | ダイキン工業株式会社 | Indoor unit of floor type air conditioner |
| WO2011121773A1 (en) * | 2010-03-31 | 2011-10-06 | 三菱電機株式会社 | Multi-blade blower |
| CN104165147A (en) * | 2013-05-20 | 2014-11-26 | 海尔集团公司 | Centrifugal fan system, and air cooling refrigerator using same |
| WO2015111210A1 (en) | 2014-01-27 | 2015-07-30 | 三菱電機株式会社 | Centrifugal fan and air conditioning device |
| JP2017036723A (en) * | 2015-08-07 | 2017-02-16 | 日本電産株式会社 | Impeller and centrifugal fan |
| JP2019078196A (en) * | 2017-10-23 | 2019-05-23 | フルタ電機株式会社 | Impeller for heating cooker, dryer or air blower |
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