JP2014167288A - Centrifugal air blower - Google Patents
Centrifugal air blower Download PDFInfo
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- JP2014167288A JP2014167288A JP2013040122A JP2013040122A JP2014167288A JP 2014167288 A JP2014167288 A JP 2014167288A JP 2013040122 A JP2013040122 A JP 2013040122A JP 2013040122 A JP2013040122 A JP 2013040122A JP 2014167288 A JP2014167288 A JP 2014167288A
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Abstract
Description
この発明は、各種送排気、塗装設備、集塵装置、工場等の換気設備として使用される遠心送風機に関する。 The present invention relates to a centrifugal blower used as a ventilating facility for various air supply / exhaust, painting facilities, dust collectors, factories and the like.
従来の遠心送風機として、羽根車の外周縁側から内周縁側に延びる羽根が、羽根車の円周に沿って等間隔に複数個列設され、各羽根が、半径方向における全長にわたって、主軸に沿う方向に延びているものが知られている（例えば、特許文献１）。 As a conventional centrifugal blower, a plurality of blades extending from the outer peripheral edge side to the inner peripheral edge side of the impeller are arranged at equal intervals along the circumference of the impeller, and each blade extends along the main axis over the entire length in the radial direction. The thing extended in the direction is known (for example, patent document 1).
しかしながら、特許文献１に開示される遠心送風機では、羽根の外周端部近傍で部分的に流体の流速が遅くなる等により、羽根車全体の流体の速度分布の均一性が十分に得られず、送風機の効率に関して改善の余地があった。 However, in the centrifugal blower disclosed in Patent Document 1, the fluid velocity distribution of the entire impeller cannot be sufficiently obtained due to, for example, the fluid flow velocity partially slowing in the vicinity of the outer peripheral end of the blade, There was room for improvement in terms of blower efficiency.
本発明は、上記の課題を解決するためにされたものであり、送風機の効率を向上させることができる遠心送風機を提供することにある。 This invention is made in order to solve said subject, and it is providing the centrifugal air blower which can improve the efficiency of an air blower.
上記目的を達成するための本発明の要旨構成は、次の通りである。 In order to achieve the above object, the gist of the present invention is as follows.
本発明の遠心送風機は、主軸と、前記主軸により軸支される羽根車と、を備えた遠心送風機において、
前記羽根車は、
前記主軸に軸支されるインペラハブと、
前記インペラハブから半径方向外側に延びるインペラディスクと、
前記主軸に沿う方向に前記インペラディスクと対向する円環状のシュラウドと、
前記インペラディスクと前記シュラウドとの間で、それぞれ前記羽根車の外周縁側から少なくとも該羽根車の外周縁と前記インペラハブとの間の半径方向の中間位置まで延びるとともに、前記羽根車の円周に沿って配列された複数個の羽根と、
を有し、
前記複数個の羽根は、それぞれ、少なくとも前記インペラディスク側の縁部が前記半径方向の中間位置から半径方向外側かつ回転方向後側に向けて延びるように形成された本体部と、前記本体部に対して回転方向前側に屈曲されて前記本体部から前記羽根車の外周縁側まで延びる外周端部とを含み、
少なくとも１個の前記羽根は、前記半径方向中間位置から半径方向内側かつ回転方向前側に向けて延びるとともに、半径方向内側に向かうにつれて前記主軸に沿う方向の長さが徐々に短くなる略三角形状の延長部を含み、
前記主軸の一端側から観たときに、前記複数個の羽根の各々の前記シュラウド側の縁部は、前記本体部及び前記外周端部の間の屈曲位置と前記羽根の内周縁との間の部分で、前記インペラディスク側の縁部よりも回転方向前側に位置しており、前記屈曲位置と前記羽根の外周縁との間の部分で、前記インペラディスク側の縁部上に沿って延びていることを特徴とするものである。
この発明によれば、羽根車全体の流体の速度分布の均一性を向上させて、送風機の効率を向上させることができる。
The centrifugal blower of the present invention is a centrifugal blower provided with a main shaft and an impeller supported by the main shaft.
The impeller is
An impeller hub supported on the main shaft;
An impeller disk extending radially outward from the impeller hub;
An annular shroud facing the impeller disk in a direction along the main axis;
The impeller disk and the shroud extend from the outer peripheral edge side of the impeller to at least a radial intermediate position between the outer peripheral edge of the impeller and the impeller hub, and along the circumference of the impeller. A plurality of blades arranged in a row,
Have
Each of the plurality of blades includes a main body portion formed such that at least an edge portion on the impeller disk side extends from an intermediate position in the radial direction toward a radially outer side and a rear side in the rotational direction, and the main body portion. An outer peripheral end portion that is bent toward the front side in the rotational direction and extends from the main body portion to the outer peripheral edge side of the impeller,
At least one of the blades has a substantially triangular shape that extends radially inward and forward in the rotational direction from the radially intermediate position, and gradually decreases in length along the main axis toward the radially inner side. Including extensions,
When viewed from one end side of the main shaft, the shroud side edge of each of the plurality of blades is between the bent position between the main body portion and the outer peripheral end portion and the inner peripheral edge of the blade. Is located on the front side in the rotational direction from the edge on the impeller disk side, and extends along the edge on the impeller disk side at a part between the bent position and the outer peripheral edge of the blade. It is characterized by being.
According to this invention, the uniformity of the velocity distribution of the fluid of the whole impeller can be improved, and the efficiency of a fan can be improved.
また、本発明の遠心送風機においては、前記複数個の羽根の全てが、それぞれ前記延長部を含むことが好ましい。
この構成によれば、送風機の効率をさらに向上させることができる。
In the centrifugal blower of the present invention, it is preferable that all of the plurality of blades include the extension portion.
According to this configuration, the efficiency of the blower can be further improved.
また、本発明の遠心送風機において、前記複数個の羽根の各々は、前記屈曲位置と前記羽根の内周縁との間の部分で、前記主軸に沿う方向に対して回転方向前側に傾斜しており、その傾斜角度が、前記内周縁から前記屈曲位置に向かって徐々に小さくなることが好ましい。
この構成によれば、送風機の効率をさらに向上させることができる。
In the centrifugal blower of the present invention, each of the plurality of blades is inclined to the front side in the rotational direction with respect to the direction along the main axis at a portion between the bent position and the inner peripheral edge of the blade. It is preferable that the inclination angle gradually decreases from the inner peripheral edge toward the bent position.
According to this configuration, the efficiency of the blower can be further improved.
本発明によれば、送風機の効率を向上させることができる遠心送風機を提供することができる。 ADVANTAGE OF THE INVENTION According to this invention, the centrifugal air blower which can improve the efficiency of an air blower can be provided.
以下、本発明の実施形態につき、図面を参照して詳細に例示説明する。 Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings.
本発明の一実施形態を、図１〜図３を参照して説明する。図１は、本発明の一実施形態に係る遠心送風機（以降、単に「送風機」とも称す。）の羽根車１を示す斜視図である。図２は、遠心送風機の主軸の一端側から観たときの、図１の羽根車１の平面図である。図３は、図２の羽根車１のＡ−Ａ断面図である。本実施形態に係る遠心送風機は、主軸（図示せず）と、この主軸により軸支される羽根車１とを備える。そして、この羽根車１は、主軸に軸支されるインペラハブ５と、インペラハブ５から半径方向外側に延びる円環状のインペラディスク４と、主軸に沿う方向ＡＤにインペラディスク４と対向する円環状のシュラウド３と、インペラディスク４とシュラウド３との間で、羽根車１の円周に沿って、好ましくは図の例のように等間隔に、配列された複数個（図の例では、１１個）の板状の羽根２と、を有する。このように構成された羽根車１が、主軸の回転により回転されると、流体が、シュラウド３の中央の開口から羽根車１内へ入り込み、遠心力の作用によりシュラウド３とインペラディスク４との間で羽根２に案内されながら半径方向外側へ流れて、羽根車１の外周縁１２側から抜け出る。 An embodiment of the present invention will be described with reference to FIGS. FIG. 1 is a perspective view showing an impeller 1 of a centrifugal blower (hereinafter also simply referred to as “blower”) according to an embodiment of the present invention. FIG. 2 is a plan view of the impeller 1 of FIG. 1 when viewed from one end side of the main shaft of the centrifugal blower. 3 is a cross-sectional view taken along the line AA of the impeller 1 of FIG. The centrifugal blower according to the present embodiment includes a main shaft (not shown) and an impeller 1 that is supported by the main shaft. The impeller 1 includes an impeller hub 5 supported by the main shaft, an annular impeller disc 4 extending radially outward from the impeller hub 5, and an annular shroud facing the impeller disc 4 in a direction AD along the main shaft. 3 and a plurality (11 in the example shown in the figure) arranged at equal intervals along the circumference of the impeller 1 between the impeller disk 4 and the shroud 3, preferably as shown in the figure. Plate-like blade 2. When the impeller 1 configured in this way is rotated by the rotation of the main shaft, the fluid enters the impeller 1 from the opening at the center of the shroud 3, and the shroud 3 and the impeller disc 4 are brought into contact by the action of centrifugal force. The air flows outward in the radial direction while being guided by the blades 2, and exits from the outer peripheral edge 12 side of the impeller 1.
複数個の羽根２は、それぞれ、羽根車１の外周縁１２側（図の例では、羽根車１の外周縁１２よりも半径方向内側の位置）から、少なくとも羽根車１の外周縁１２とインペラハブ５との間の半径方向の中間位置７（図の例では、シュラウド３の内周縁よりも半径方向内側の位置）まで、延びている。そして、複数個の羽根２は、それぞれ、少なくともインペラディスク４側の縁部３２が羽根車１の外周縁１２とインペラハブ５との間の半径方向の中間位置７から半径方向外側かつ回転方向ＲＤの後側に向けて延びるように形成された本体部２１と、本体部２１に対して回転方向ＲＤの前側に屈曲されて本体部２１から羽根車１の外周縁１２側まで延びるように形成された外周端部２２と、を含む。
ここで、「羽根車１の外周縁１２」は、互いに外径が略同じとなるインペラディスク４及びシュラウド３の外周縁により規定されるものとする。
「羽根車１の外周縁１２とインペラハブ５との間の半径方向の中間位置７」とは、羽根車１の外周縁１２及びインペラハブ５との間の半径方向のちょうど中央位置よりも、半径方向内側又は半径方向外側の位置とすることができる。
図の例では、羽根２の外周縁１１が、羽根車１の外周縁１２よりも半径方向内側に位置しているが、羽根車１の外周縁１２と同じ半径方向位置にあってもよいし、羽根車１の外周縁１２よりも半径方向外側に位置していてもよい。
また、「本体部２１に対して回転方向ＲＤの前側に屈曲される」とは、図２に示すように、羽根２のインペラディスク４側の縁部３２のうち外周端部２２に沿う部分が、羽根２の本体部２１及び外周端部２２の間の屈曲位置９（すなわち曲率が変化する変曲点の位置）での該縁部３２に対する接線Ｌ５よりも、回転方向ＲＤの前側に向かって延びていることをいう。
Each of the plurality of blades 2 includes at least the outer peripheral edge 12 of the impeller 1 and the impeller hub from the outer peripheral edge 12 side of the impeller 1 (in the illustrated example, a position radially inward of the outer peripheral edge 12 of the impeller 1). It extends to an intermediate position 7 in the radial direction with respect to 5 (in the example shown in the figure, a position radially inward of the inner peripheral edge of the shroud 3). Each of the plurality of blades 2 has at least an edge portion 32 on the impeller disk 4 side at a radially outer side and a rotational direction RD from a radial intermediate position 7 between the outer peripheral edge 12 of the impeller 1 and the impeller hub 5. The main body 21 formed to extend toward the rear side, and the main body 21 is formed to be bent toward the front side in the rotation direction RD with respect to the main body 21 and extend from the main body 21 to the outer peripheral edge 12 side of the impeller 1. Peripheral end 22.
Here, “the outer peripheral edge 12 of the impeller 1” is defined by the outer peripheral edges of the impeller disk 4 and the shroud 3 that have substantially the same outer diameter.
The “radial intermediate position 7 between the outer peripheral edge 12 of the impeller 1 and the impeller hub 5” is a radial direction rather than the central position in the radial direction between the outer peripheral edge 12 of the impeller 1 and the impeller hub 5. The position may be inside or radially outside.
In the illustrated example, the outer peripheral edge 11 of the blade 2 is located radially inward of the outer peripheral edge 12 of the impeller 1, but may be at the same radial position as the outer peripheral edge 12 of the impeller 1. The outer peripheral edge 12 of the impeller 1 may be located on the radially outer side.
In addition, “bent to the front side in the rotational direction RD with respect to the main body portion 21” means that the portion along the outer peripheral end portion 22 of the edge portion 32 on the impeller disc 4 side of the blade 2 is shown in FIG. 2. The tangent L5 to the edge 32 at the bending position 9 (that is, the position of the inflection point at which the curvature changes) between the main body 21 and the outer peripheral end 22 of the blade 2 is toward the front side in the rotational direction RD. It means extending.
なお、図の例では、図２の平面図で示すように、羽根２のインペラディスク４側の縁部３２は、本体部２１に沿う部分で、回転方向ＲＤの前側に凸に湾曲（曲率半径Ｒ１）している。
また、図の例では、図２の平面図で示すように、羽根２のインペラディスク４側の縁部３２は、外周端部２２に沿う部分で、回転方向ＲＤの後側に凸に湾曲（曲率半径Ｒ２）しているとともに、半径方向内側から半径方向外側に向かうにつれて、羽根２の外周縁１１に到るまで、回転方向ＲＤの後側に向かって延びている。
ここで、羽根２の出口角β２は、３５〜８０度であることが好ましい（図の例では、６５度）。羽根２の出口角β２は、図２に示すように、羽根２のインペラディスク４側の縁部３２の、羽根２の外周縁１１での接線と、羽根車１の中心点を中心として羽根２の外周縁１１を通る円の、該羽根２の外周縁１１での接線との、なす角度である。
In the example of the figure, as shown in the plan view of FIG. 2, the edge portion 32 on the impeller disk 4 side of the blade 2 is a portion along the main body portion 21, and is curved convexly toward the front side in the rotational direction RD (the radius of curvature). R1).
In the example of the figure, as shown in the plan view of FIG. 2, the edge portion 32 on the impeller disk 4 side of the blade 2 is a portion along the outer peripheral end portion 22, and is curved convexly to the rear side in the rotational direction RD ( The radius of curvature R2) extends from the inner side in the radial direction toward the outer side in the radial direction and extends toward the rear side in the rotational direction RD until reaching the outer peripheral edge 11 of the blade 2.
Here, the exit angle β2 of the blade 2 is preferably 35 to 80 degrees (65 degrees in the example in the figure). As shown in FIG. 2, the exit angle β 2 of the blade 2 is determined by the blade 2 centering on the tangent line at the outer peripheral edge 11 of the blade 2 of the edge 32 on the impeller disk 4 side of the blade 2 and the center point of the impeller 1. The angle formed by the circle passing through the outer peripheral edge 11 and the tangent at the outer peripheral edge 11 of the blade 2.
さらに、複数個の羽根２のうち少なくとも１個（図の例では、全ての羽根２）が、羽根車１の外周縁１２とインペラハブ５との間の半径方向の中間位置７から半径方向内側かつ回転方向ＲＤの前側に向けて延びる延長部６を含む。延長部６は、該中間位置７から半径方向内側に向かうにつれて、主軸に沿う方向（すなわちインペラディスク４に対して垂直な方向）ＡＤの長さが徐々に短くなる略三角形状を有する。
ここで、「略三角形状」とは、図３に示すように、羽根２のシュラウド３側の縁部３１のうち延長部６に沿う部分が、周方向に沿って観たときに、半径方向外側から半径方向内側に向かうにつれてシュラウド３側からインペラディスク４側に向かって延びる傾斜形状に形成される場合に限られず、このような傾斜形状の代わりに、一箇所以上で半径方向内側及び／又は外側に凸に湾曲及び／又は屈曲して延びる形状に形成される場合も含む。
Furthermore, at least one of the plurality of blades 2 (all blades 2 in the illustrated example) is radially inward from the intermediate position 7 in the radial direction between the outer peripheral edge 12 of the impeller 1 and the impeller hub 5 and The extension part 6 extended toward the front side of the rotation direction RD is included. The extension 6 has a substantially triangular shape in which the length of the AD along the main axis (that is, the direction perpendicular to the impeller disk 4) gradually decreases from the intermediate position 7 toward the inside in the radial direction.
Here, as shown in FIG. 3, the “substantially triangular shape” means a radial direction when a portion along the extended portion 6 of the edge 31 on the shroud 3 side of the blade 2 is viewed along the circumferential direction. It is not limited to the case where it is formed in an inclined shape extending from the shroud 3 side toward the impeller disk 4 side from the outside toward the inside in the radial direction. Instead of such an inclined shape, at least one place in the radial direction inside and / or It includes the case where it is formed in a shape that is curved and / or bent to protrude outward.
なお、図の例では、延長部６を含む羽根２の内周縁１０が、インペラハブ５から半径方向外側に離れた位置にある。 In the example of the figure, the inner peripheral edge 10 of the blade 2 including the extension 6 is located at a position away from the impeller hub 5 radially outward.
また、図の例では、羽根２のインペラディスク４側の縁部３２は、延長部６に沿う部分で、回転方向ＲＤの前側に凸に湾曲（曲率半径Ｒ１）しており、本体部２１に沿う部分とともに一つの滑らかな湾曲形状（曲率半径Ｒ１）を形成している。言い換えれば、羽根２のインペラディスク４側の縁部３２が、延長部６及び本体部２１に沿う部分で形成する湾曲形状（曲率半径Ｒ１）は、回転方向ＲＤの前側に凸であるとともに、半径方向内側から半径方向外側に向かうにつれて回転方向ＲＤの後側に向かって延びている。
ここで、延長部６を含む羽根２の入口角β１は、１０〜５０度であることが好ましい（図の例では、３０度）。延長部６を含む羽根２の入口角β１は、羽根２のインペラディスク４側の縁部３２の、該羽根２の内周縁１０での接線と、羽根車１の中心点を中心として該羽根２の内周縁１０を通る円に対する、該羽根２の内周縁１０での接線との、なす角度である。
Further, in the example of the figure, the edge portion 32 on the impeller disk 4 side of the blade 2 is a portion along the extension portion 6 and is convexly curved (curvature radius R1) to the front side in the rotational direction RD. A smooth curved shape (curvature radius R1) is formed together with the portion along. In other words, the curved shape (curvature radius R1) formed by the edge portion 32 on the impeller disk 4 side of the blade 2 along the extension portion 6 and the main body portion 21 is convex to the front side in the rotational direction RD, and the radius It extends toward the rear side in the rotational direction RD from the inner side in the direction toward the outer side in the radial direction.
Here, the inlet angle β1 of the blade 2 including the extension 6 is preferably 10 to 50 degrees (30 degrees in the example in the figure). The inlet angle β1 of the blade 2 including the extension 6 is such that the edge 2 on the impeller disk 4 side of the blade 2 is tangent to the inner peripheral edge 10 of the blade 2 and the center point of the impeller 1 is the blade 2 The angle formed by the tangent at the inner peripheral edge 10 of the blade 2 with respect to a circle passing through the inner peripheral edge 10 of the blade 2.
図の例では、全ての羽根２がそれぞれ延長部６を含むように構成したので、送風機１の効率を大きく向上させることができる。ただし、この構成以外にも、延長部６を含まない（すなわち本体部２１及び外周端部２２のみを含む）１個以上（例えば３個）の羽根２と、延長部６を含む１個以上（例えば１個）の羽根２とを交互に、羽根車１の円周に沿って配列した場合でも、送風機１の効率を十分好適なものとすることができる。 In the example shown in the figure, since all the blades 2 are configured to include the extension portions 6 respectively, the efficiency of the blower 1 can be greatly improved. However, in addition to this configuration, the extension portion 6 is not included (that is, only the main body portion 21 and the outer peripheral end portion 22 are included), and one or more (for example, three) blades 2 and one or more including the extension portion 6 ( For example, even when the blades 2 are alternately arranged along the circumference of the impeller 1, the efficiency of the blower 1 can be made sufficiently favorable.
複数個の羽根２は、それぞれ、本体部２１及び外周端部２２の間の屈曲位置９と羽根２の内周縁１０との間の部分で、回転方向ＲＤの前側に向けて倒れるように形成されており、さらに、該屈曲位置９と羽根２の外周縁１１との間の部分で、主軸に沿う方向ＡＤに延びている。即ち、図２に示すように、主軸の一端側から観たとき、複数個の羽根２の各々のシュラウド３側の縁部３１は、本体部２１及び外周端部２２の間の屈曲位置９と内周縁１０との間の部分で、インペラディスク４側の縁部３２よりも回転方向ＲＤの前側に位置しており、さらに、該屈曲位置９と羽根２の外周縁１１との間の部分で、インペラディスク４側の縁部３２上に沿って延びている。
このように、羽根２を、屈曲位置９と羽根２の外周縁１１との間の部分のみで、主軸に沿う方向ＡＤに延在させることにより、羽根２の外周端部２２の近傍を流れる流体の速度分布の均一性を向上させることにより、送風機１の効率のさらなる向上及び騒音のさらなる低下を達成することができる。
Each of the plurality of blades 2 is formed to fall toward the front side in the rotational direction RD at a portion between the bending position 9 between the main body portion 21 and the outer peripheral end portion 22 and the inner peripheral edge 10 of the blade 2. Furthermore, it extends in the direction AD along the main axis at a portion between the bent position 9 and the outer peripheral edge 11 of the blade 2. That is, as shown in FIG. 2, when viewed from one end side of the main shaft, the edge 31 on the shroud 3 side of each of the plurality of blades 2 has a bent position 9 between the main body portion 21 and the outer peripheral end portion 22. It is located at the front side in the rotational direction RD from the edge 32 on the impeller disk 4 side at the portion between the inner peripheral edge 10 and at the portion between the bent position 9 and the outer peripheral edge 11 of the blade 2. , And extends along the edge 32 on the impeller disk 4 side.
In this manner, the fluid flowing in the vicinity of the outer peripheral end 22 of the blade 2 by extending the blade 2 in the direction AD along the main axis only at the portion between the bending position 9 and the outer peripheral edge 11 of the blade 2. By improving the uniformity of the speed distribution, it is possible to further improve the efficiency of the blower 1 and further reduce the noise.
さらに、図の例において、複数個の羽根２の各々は、本体部２１及び外周端部２２の間の屈曲位置９と羽根２の内周縁１０との間の部分で、主軸に沿う方向ＡＤに対して回転方向ＲＤの前側に傾斜（すなわち平坦面状に延在）しており、その傾斜角度θが、羽根２の内周縁１０近傍で最も大きく、屈曲位置９に向かうにつれて徐々に小さくなって、屈曲位置９で０度となる。
なお、羽根２の内周縁１０近傍での傾斜角度θは、図の例では１７度であるが、７〜２５度であることが好ましい。
ここで、「傾斜角度θ」とは、図１の要部拡大図で示すように、羽根２のインペラディスク４側の縁部３２上に位置する任意の点Ｐで、該縁部３２の接線Ｌ１を引いて、該接線Ｌ１に対して垂直な平面Ｓ内で観たとき、点Ｐから主軸に沿う方向ＡＤに延びる直線Ｌ３と、羽根２に沿う直線Ｌ４とのなす角度をいうものとする。
Further, in the illustrated example, each of the plurality of blades 2 is a portion between the bending position 9 between the main body portion 21 and the outer peripheral end portion 22 and the inner peripheral edge 10 of the blade 2 in the direction AD along the main axis. On the other hand, it is inclined to the front side in the rotational direction RD (that is, extending in a flat surface shape), and its inclination angle θ is the largest in the vicinity of the inner peripheral edge 10 of the blade 2 and gradually decreases toward the bending position 9. Then, it becomes 0 degree at the bending position 9.
In addition, although the inclination | tilt angle (theta) in the inner periphery 10 vicinity of the blade | wing 2 is 17 degree | times in the example of a figure, it is preferable that it is 7-25 degree | times.
Here, the “inclination angle θ” is an tangent to the edge 32 at an arbitrary point P located on the edge 32 on the impeller disk 4 side of the blade 2 as shown in the enlarged view of the main part of FIG. When L1 is drawn and viewed in a plane S perpendicular to the tangent L1, the angle formed by the straight line L3 extending from the point P in the direction AD along the main axis and the straight line L4 along the blade 2 is defined. .
なお、図示はしないが、主軸の一端側から観たとき、複数個の羽根２の各々のシュラウド３側の縁部３１が、本体部２１及び外周端部２２の間の屈曲位置９と内周縁１０との間の部分で、インペラディスク４側の縁部３２よりも回転方向ＲＤの前側に位置している限り、羽根２の、シュラウド３側の縁部３１とインペラディスク４側の縁部３２との間を延びる部分は、例えば半径方向及び／又は主軸に沿う方向ＡＤの一箇所以上で回転方向ＲＤの前側及び／又は後側に凸に湾曲及び／又は屈曲して延びる等、任意の形状を有することができる。 Although not shown, when viewed from one end side of the main shaft, the edge 31 on the shroud 3 side of each of the plurality of blades 2 has a bent position 9 between the main body 21 and the outer peripheral end 22 and the inner peripheral edge. 10, the edge 31 on the shroud 3 side and the edge 32 on the impeller disk 4 side of the blade 2, as long as it is located in front of the edge 32 on the impeller disk 4 side in the rotational direction RD. The portion extending between the first and second portions may have an arbitrary shape such as extending in the radial direction and / or the direction AD along the main axis so as to be convex and curved and / or bent toward the front side and / or the rear side of the rotational direction RD. Can have.
図４は、実施例に係る送風機の作動時の図３のＡ−Ａ断面における流体の相対速度ベクトル図である。図５は、実施例に係る送風機の作動時の図２の平面図における流体の相対速度ベクトル図である。図６は、比較例に係る送風機の羽根車を示す斜視図であり、図７は、図６の比較例に係る送風機の作動時の図３のＡ−Ａ断面に相当する断面における流体の相対速度ベクトル図である。図８は、比較例に係る送風機の作動時の図２に相当する平面図における流体の相対速度ベクトル図である。
なお、図４と図５に示す羽根車は、図１に示す構成を有するものである。図６に示す羽根車は、合計１２個の羽根を有し、延長部を含まない３個の羽根と、延長部を含む１個の羽根とが、交互に羽根車の円周方向に配列されている。また、図６に示す羽根車は、全ての羽根が、その半径方向における全長にわたって、主軸に沿う方向（インペラディスクに対して垂直な方向）に延びており、これゆえに、主軸の一端側から観たときに、羽根の半径方向における全長にわたって、羽根のシュラウド側の縁部が、インペラディスク側の縁部上に沿って延びている。なお、図４と図５、及び図７と図８は、同じ回転数で作動した場合を示している。図７の比較例に係る送風機では、主に屈曲位置９から羽根の外周縁１１において、速度分布が不均一になっている部分（図７の丸で囲った部分）が観られる。具体的に、この比較例の送風機の羽根車では、羽根の内周縁と屈曲位置との間の部分で、主軸に沿う方向に延びている（すなわち羽根車の回転方向の前側に向けて倒れるように形成されていない）ことから、羽根の屈曲位置から羽根の外周縁までの部分の近傍において、主軸に沿う方向の速度分布が不均一となっている。このような速度分布の不均一性は、送風機の効率の低下をもたらすものである。一方、図４の実施例に係る送風機では、屈曲位置９から羽根の外周縁１１までの部分の近傍において、主軸に沿う方向ＡＤの速度分布が、図７の場合よりも、より均一となっていることがわかる。さらに、図８の比較例に係る送風機では、主に羽根の外周端部近傍で流速が遅く速度分布の均一性が損なわれている部分（図８の丸で囲った部分）が観られるが、図５の実施例に係る送風機では、羽根の外周端部近傍での流速が回復し、羽根車全体の速度分布の均一性が大きく向上していることがわかる。
FIG. 4 is a relative velocity vector diagram of the fluid in the AA cross section of FIG. 3 when the blower according to the embodiment is operated. FIG. 5 is a relative velocity vector diagram of the fluid in the plan view of FIG. 2 when the blower according to the embodiment is operating. 6 is a perspective view showing an impeller of a blower according to a comparative example, and FIG. 7 is a diagram of relative fluid in a cross section corresponding to the AA cross section of FIG. 3 when the blower according to the comparative example of FIG. 6 is operated. It is a velocity vector diagram. FIG. 8 is a relative velocity vector diagram of the fluid in the plan view corresponding to FIG. 2 when the blower according to the comparative example is operated.
The impeller shown in FIGS. 4 and 5 has the configuration shown in FIG. The impeller shown in FIG. 6 has a total of twelve blades, and three blades not including an extension portion and one blade including an extension portion are alternately arranged in the circumferential direction of the impeller. ing. Further, in the impeller shown in FIG. 6, all the blades extend in the direction along the main axis (direction perpendicular to the impeller disk) over the entire length in the radial direction. In this case, the shroud side edge of the blade extends along the impeller disk side edge over the entire length of the blade in the radial direction. FIGS. 4 and 5 and FIGS. 7 and 8 show the case of operation at the same rotational speed. In the blower according to the comparative example of FIG. 7, a portion where the velocity distribution is not uniform (a portion surrounded by a circle in FIG. 7) is observed mainly from the bent position 9 to the outer peripheral edge 11 of the blade. Specifically, in the impeller of the blower of this comparative example, it extends in a direction along the main axis at a portion between the inner peripheral edge of the blade and the bending position (that is, it falls down toward the front side in the rotation direction of the impeller). Therefore, the velocity distribution in the direction along the main axis is non-uniform in the vicinity of the portion from the bent position of the blade to the outer peripheral edge of the blade. Such non-uniformity of the speed distribution causes a reduction in the efficiency of the blower. On the other hand, in the blower according to the embodiment of FIG. 4, in the vicinity of the portion from the bending position 9 to the outer peripheral edge 11 of the blade, the speed distribution in the direction AD along the main axis becomes more uniform than in the case of FIG. I understand that. Furthermore, in the blower according to the comparative example of FIG. 8, the portion where the flow velocity is slow and the uniformity of the velocity distribution is impaired mainly in the vicinity of the outer peripheral end portion of the blade (the circled portion in FIG. 8) is observed. In the blower according to the example of FIG. 5, it can be seen that the flow velocity in the vicinity of the outer peripheral end of the blade is recovered, and the uniformity of the velocity distribution of the entire impeller is greatly improved.
図９は、上述した実施例及び比較例に係る送風機について、風量Ｑと効率η及び圧力Ｐのそれぞれとの関係を示すグラフである。実施例の送風機によれば、比較例に係る送風機と比べて、送風機の効率ηの最大値を向上させることができる。また、実施例に係る送風機は、比較例に係る送風機と比べて、騒音が大きく低減された。 FIG. 9 is a graph showing the relationship between the air volume Q, the efficiency η, and the pressure P for the blowers according to the above-described examples and comparative examples. According to the air blower of an Example, the maximum value of the efficiency (eta) of an air blower can be improved compared with the air blower which concerns on a comparative example. Moreover, the noise of the blower according to the example was greatly reduced as compared with the blower according to the comparative example.
なお、上述した羽根車１は、送風機以外にも、遠心ポンプ等、他の回転体にも用いることができる。 In addition, the impeller 1 mentioned above can be used also for other rotary bodies, such as a centrifugal pump, besides a blower.
本発明に係る送風機は、各種送排気、塗装設備、集塵装置、工場等の換気設備として、広い用途に適用することができる。 The blower according to the present invention can be applied to a wide range of uses as ventilation equipment for various types of exhaust and exhaust, painting equipment, dust collectors, factories, and the like.
１：羽根車、 ２：羽根、 ３：シュラウド、 ４：インペラディスク、 ５：インペラハブ、 ６：延長部、 ７：中間位置、 ９：屈曲位置、 １０：羽根の内周縁、 １１：羽根の外周縁、 １２：羽根車の外周縁、 ２１：本体部、 ２２：外周端部、 ３１：羽根の、シュラウド側の縁部、 ３２：羽根の、インペラディスク側の縁部 1: impeller, 2: blade, 3: shroud, 4: impeller disc, 5: impeller hub, 6: extension, 7: intermediate position, 9: bent position, 10: inner peripheral edge of blade, 11: outer peripheral edge of blade 12: Outer peripheral edge of impeller, 21: Main body, 22: Outer peripheral edge, 31: Edge of blade on shroud side, 32: Edge of blade on impeller disk side
Claims (3)
前記羽根車は、
前記主軸に軸支されるインペラハブと、
前記インペラハブから半径方向外側に延びるインペラディスクと、
前記主軸に沿う方向に前記インペラディスクと対向する円環状のシュラウドと、
前記インペラディスクと前記シュラウドとの間で、それぞれ前記羽根車の外周縁側から少なくとも該羽根車の外周縁と前記インペラハブとの間の半径方向の中間位置まで延びるとともに、前記羽根車の円周に沿って配列された複数個の羽根と、
を有し、
前記複数個の羽根は、それぞれ、少なくとも前記インペラディスク側の縁部が前記半径方向の中間位置から半径方向外側かつ回転方向後側に向けて延びるように形成された本体部と、前記本体部に対して回転方向前側に屈曲されて前記本体部から前記羽根車の外周縁側まで延びる外周端部とを含み、
少なくとも１個の前記羽根は、前記半径方向の中間位置から半径方向内側かつ回転方向前側に向けて延びるとともに、半径方向内側に向かうにつれて前記主軸に沿う方向の長さが徐々に短くなる略三角形状の延長部を含み、
前記主軸の一端側から観たときに、前記複数個の羽根の各々の前記シュラウド側の縁部は、前記本体部及び前記外周端部の間の屈曲位置と前記羽根の内周縁との間の部分で、前記インペラディスク側の縁部よりも回転方向前側に位置しており、前記屈曲位置と前記羽根の外周縁との間の部分で、前記インペラディスク側の縁部上に沿って延びていることを特徴とする、遠心送風機。 In a centrifugal blower comprising a main shaft and an impeller supported by the main shaft,
The impeller is
An impeller hub supported on the main shaft;
An impeller disk extending radially outward from the impeller hub;
An annular shroud facing the impeller disk in a direction along the main axis;
The impeller disk and the shroud extend from the outer peripheral edge side of the impeller to at least a radial intermediate position between the outer peripheral edge of the impeller and the impeller hub, and along the circumference of the impeller. A plurality of blades arranged in a row,
Have
Each of the plurality of blades includes a main body portion formed such that at least an edge portion on the impeller disk side extends from an intermediate position in the radial direction toward a radially outer side and a rear side in the rotational direction, and the main body portion. An outer peripheral end portion that is bent toward the front side in the rotational direction and extends from the main body portion to the outer peripheral edge side of the impeller,
At least one of the blades has a substantially triangular shape extending from the intermediate position in the radial direction toward the radially inner side and the front side in the rotational direction, and gradually decreasing in the direction along the main axis toward the radially inner side. Including an extension of
When viewed from one end side of the main shaft, the shroud side edge of each of the plurality of blades is between the bent position between the main body portion and the outer peripheral end portion and the inner peripheral edge of the blade. Is located on the front side in the rotational direction from the edge on the impeller disk side, and extends along the edge on the impeller disk side at a part between the bent position and the outer peripheral edge of the blade. A centrifugal blower characterized in that
Each of the plurality of blades is a portion between the bent position and the inner peripheral edge of the blade, and is inclined forward in the rotational direction with respect to the direction along the main axis. The centrifugal blower according to claim 1, wherein the centrifugal blower gradually decreases toward the bent position.
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| CN110307178A (en) * | 2019-06-27 | 2019-10-08 | 上海马陆日用友捷汽车电气有限公司 | A kind of low-noise impeller |
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| CN108266403A (en) * | 2017-01-03 | 2018-07-10 | 珠海格力电器股份有限公司 | Centrifugal blower and its impeller assembly |
| CN107676303A (en) * | 2017-09-11 | 2018-02-09 | 佛山市美家生活电器有限公司 | The spiral case blower fan of smoke exhaust ventilator |
| TWI662195B (en) * | 2018-01-29 | 2019-06-11 | 王勝豊 | Blade structure and impeller composed of blade structure |
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| CN105275873A (en) * | 2015-10-27 | 2016-01-27 | 上海华鼓鼓风机有限公司 | Three-dimensional flow closed type casting impeller used for low-speed running air blower |
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