JP3850061B2 - Cylindrical impeller - Google Patents

Cylindrical impeller Download PDF

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Publication number
JP3850061B2
JP3850061B2 JP04705796A JP4705796A JP3850061B2 JP 3850061 B2 JP3850061 B2 JP 3850061B2 JP 04705796 A JP04705796 A JP 04705796A JP 4705796 A JP4705796 A JP 4705796A JP 3850061 B2 JP3850061 B2 JP 3850061B2
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Prior art keywords
blade
cylindrical impeller
impeller
cylindrical
root portion
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JPH09242694A (en
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浩光 高田
和文 上甲
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Sanko Gosei Ltd
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Sanko Gosei Ltd
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D17/02—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps having non-centrifugal stages, e.g. centripetal
    • F04D17/04—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps having non-centrifugal stages, e.g. centripetal of transverse-flow type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/26—Rotors specially for elastic fluids
    • F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
    • F04D29/281—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for fans or blowers
    • F04D29/282—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for fans or blowers the leading edge of each vane being substantially parallel to the rotation axis
    • F04D29/283—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for fans or blowers the leading edge of each vane being substantially parallel to the rotation axis rotors of the squirrel-cage type

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Air-Conditioning Room Units, And Self-Contained Units In General (AREA)

Description

【０００１】
【発明の属する技術分野】
この発明は、空気調和機等に使用されるクロスフローファン等の送風用の筒状羽根車に関するものである。
【０００２】
【従来の技術】
従来、前記のような筒状羽根車として、支持板の一端面に軸方向に沿ってまっすぐに延出する多数の羽根を周方向に所定間隔で形成したエレメントを所定数連結したものが知られている。この筒状羽根車を以下、図面に基づき説明する。
図６において、１は合成樹脂の一体成形品からなるエレメントであり、環状または円板状の支持板２の一端面に、軸方向に延出する多数の羽根３を周方向に所定間隔を設けて一体に成形したものである。前記各羽根３は、エレメント１の半径方向に対して傾斜し、近似円弧状に湾曲した翼状の横断面形状に形成してある。また、羽根３が延出していない支持板２の反対側の端面には、別のエレメントをまっすぐにねじれないように連結するために、その羽根の先端部を嵌合固定する嵌合溝4が形成されている。
【０００３】
図７に示すように、前段のエレメント１の羽根３の先端部を次段のエレメント１の支持板２上に嵌合し保持させて接着または超音波溶着によって固定し、前記操作を繰り返して所定個数のエレメント１を軸方向にねじれないように連結し、先端のエレメント１に羽根３を嵌合、支持する端板２ａを設けることにより、筒状羽根車５を構成している。
【０００４】
また、図８は、従来の筒状羽根車の要部を羽根先端部１１から軸方向に沿って羽根３の根元部１２を見た拡大図である。羽根３は、筒状羽根車５の中心から半径Ｒ１の位置に半径方向に対する取り付け傾斜角度θ１で根元部１２を配置してある。羽根３の先端部１１は、軸方向にまっすぐに延出し、抜き勾配分だけ根元部１２より小さい。
【０００５】
そして、図９に示すように、空気調和機の送風装置として前段の筒状羽根車５をケーシングを形成するスタビライザ６とリアガイダ７の間に配置する。筒状羽根車５が、矢印８の時計方向に回転することにより、矢印９の方向から空気が流入し、矢印１０の方向に空気が流出するようにしている。
【０００６】
【発明が解決しようとする課題】
前記のエレメント１を配置して筒状羽根車５を構成した場合には、エレメント１の羽根３の枚数zと１分間当たりの回転数nからなる（n×z）／６０Ｈｚの周波数の音とその整数倍の周波数の音が発生するという問題があった。この音は、羽根ピッチ音やｎｚ音と呼ばれており、聴覚的に笛を吹くような耳ざわりな音である。
【０００７】
以下、この耳ざわりな音をｎｚ音と呼ぶことにする。
このｎｚ音は、エレメン１の羽根３、羽根３の取り付けピッチ、スタビライザ６、リアガイダ７の形状とそれらの位置関係により変化する。たとえば、送風効率を上げるために筒状羽根車５とスタビライザ６の間隔ｄを狭くすると、ｎｚ音が大きくなる。このように、送風効率を上げようとすると、ｎｚ音も大きくなってしまい、送風効率を極限まで上げられないという問題があった。
【０００８】
また、筒状羽根車のエレメント１は、一般に合成樹脂の成形品であるが、金型から成形品であるエレメント１を取り出すために、羽根３には抜き勾配が必要となる。これにより、羽根３の根元部１２の断面形状に対して先端部１１の断面形状が小さくなってしまい、送風効率が羽根３の根元部１２と先端部１１とで異なり、送風効率を極限まで上げられないという問題があった。
【０００９】
この発明は、前述のような問題を解決するもので、羽根３の根元部１２と羽根先端部１１での送風効率の差を少なくして、送風効率を向上させると共に、ｎｚ音のない筒状羽根車を提供することを目的とする。
【００１０】
【課題を解決するための手段】
この発明は上記の目的を達成するためになされたもので、環状または円板状の支持板の端面に、軸方向に沿って延出する多数の羽根を周方向に所定間隔で形成した筒状羽根車において、前記羽根の根元部を筒状羽根車の中心Ｏから半径Ｒ１の位置に、筒状羽根車の半径方向に対して取り付け傾斜角度θ 1 で配置し、前記羽根の先端部を筒状羽根車の中心Ｏから異なる半径Ｒ２の位置に、筒状羽根車の半径方向に対して前記取り付け傾斜角度θ１と異なる取り付け傾斜角度θ４で軸方向に所定距離だけ前記根元部から延出した位置に配置し、これらの配置によって、前記羽根の筒状羽根車半径方向に対する取り付け傾斜角度と筒状羽根車の中心Ｏからの取り付け位置とを根元部から先端部にかけて徐々に変化させ、前記羽根の前縁に後倒れになる外周側稜線を構成すると共に前記羽根を外倒れに構成したことを特徴とする。
【００１１】
【発明の実施の形態】
以下、この発明の実施の形態について図面を参照して説明する。
図1は、この発明に係る筒状羽根車のエレメント１の斜視図であり、図２は、図１に示したエレメント１を複数個軸方向に連結して先端部に端板２ａを設けた筒状羽根車５である。この筒状羽根車５は、各エレメント１に設けた各羽根３以外は、図６、図７に示した従来のものと同様である。
【００１２】
図３は、この発明の参考例１に係る筒状羽根車の羽根３の先端部１１側から軸方向に沿って羽根３の根元部１２を見た拡大図である。
図３に示すように、参考例 1 に示す羽根３の根元部１２は、筒状羽根車の中心Ｏから半径Ｒ１の位置に、半径方向に対する取り付け傾斜角度θ１で配置してあり、羽根３の先端部１１は、筒状羽根車の中心Ｏから同じ半径Ｒ１の位置に、半径方向に対する取り付け傾斜角度θ２で軸方向に所定距離だけ羽根３の根元部１２から延出した位置に配置してある。これらの配置によって、羽根３の筒状羽根車半径方向に対する取り付け傾斜角度を、根元から先端にかけて徐々に変化させ、羽根３の前縁に後倒れになる外周側稜線１３を構成してある。
【００１３】
なお、図３では１枚の羽根３を示して説明したが、筒状羽根車の各羽根のすべてを、前述した羽根と同様に半径方向に対する傾斜角度を根元から先端にかけて徐々に変化させてある。
【００１４】
前記のような羽根３の構成にすることにより、抜き勾配によって生じる羽根３の根元部１２と先端部１１の断面形状の差による送風効率の差を少なくできる。
【００１５】
また、羽根３の外周側稜線１３とケーシングを構成しているスタビライザ６との間隔ｄ１，ｄ２は、羽根３の根元部１２の位置でｄ１＝Ｒ０−Ｒ１であり、先端部１１でｄ２＝Ｒ０−Ｒ１であるからｄ１とｄ２は共に同じ間隔である。しかし、羽根３が矢印８に示す時計方向に回転することにより、羽根３の外周側稜線１３は、ケーシングを構成しているスタビライザ６に対して、間隔を一定に保ったまま、一直線上ではなく徐々に変化する位置関係を構成する。このため、羽根３への風の流入９と流出１０がなめらかに変化する。これにより、ｎｚ音をなくすことができる。
【００１６】
図４は、この発明の参考例２に係る筒状羽根車の羽根３の先端部１１側から軸方向に沿って羽根３の根元部１２を見た拡大図である。
図４に示すように、参考例２に示す羽根３の根元部１２は、筒状羽根車の中心Ｏから半径Ｒ１の位置に、半径方向に対する取り付け傾斜角度θ１で配置してあり、羽根３の先端部１１は、筒状羽根車の中心Ｏから異なる半径Ｒ２の位置に、半径方向に対する異なる取り付け傾斜角度θ３で軸方向に所定距離だけ根元部１２から延出した位置に配置してある。これらの配置によって、羽根３の筒状羽根車中心Ｏからの取り付け位置を、根元から先端にかけて徐々に変化させ、羽根３を外倒れに構成してある。
【００１７】
なお、図4では、1枚の羽根３のみを示して説明したが、筒状羽根車の各羽根のすべてを、前述した羽根と同様に、取り付け位置を根元から先端にかけて徐々に変化させてあり、また、羽根以外の構成は前述した図６，図７に示した従来のものと同様である。
【００１８】
前記のような羽根３の構成にすることにより、抜き勾配によって生じる羽根３の根元部１２と先端部１１の断面形状の差による送風効率の差を少なくできる。
また、羽根３の外周側稜線１３とケーシングを構成しているスタビライザ６との間隔ｄ１，ｄ２は、羽根３の根元部１２の位置でｄ１＝Ｒ０−Ｒ１であり、羽根３の先端部１１でｄ２＝Ｒ０−Ｒ２である。そして、羽根３の外周側稜線１３は、ケーシングを構成しているスタビライザ6との位置関係では一直線上に並ぶが、羽根３の根元部１２から先端部１１にかけて間隔が徐々に変化する位置関係を構成するため、羽根３が矢印８に示す時計方向に回転することにより、羽根３への風の流入９と流出１０がなめらかに変化する。これにより、ｎｚ音をなくすことができる。
【００１９】
次に、図５により、この発明の実施の形態について説明する。
図５は、この発明の実施の形態に係る筒状羽根車の羽根３の先端部１１側から軸方向に沿って羽根３の根元部１２を見た拡大図である。
図５において、この実施の形態に示す羽根３の根元部１２は、筒状羽根車の中心Ｏから半径Ｒ１の位置に、半径方向に対する取り付け傾斜角度θ1で配置してあり、羽根３の先端部１１は、筒状羽根車の中心Ｏから異なる半径Ｒ２の位置に、半径方向に対する異なる取り付け傾斜角度θ４で軸方向に所定距離だけ根元部１２から延出した位置に配置してある。これらの配置によって、羽根３の筒状羽根車半径方向に対する取り付け傾斜角度と、筒状羽根車の中心Ｏからの取り付け位置とを根元部から先端部にかけて徐々に変化させ、羽根３の前縁に後倒れになる外周側稜線１３を構成すると共に、羽根３を外倒れに構成してある。
なお、この実施の形態における羽根の構成は、図３，図４に示した参考例１，２の羽根の構成を、併せて具備させた構成である。
【００２０】
なお、図５では1枚の羽根３のみを示して説明したが、筒状羽根車のすべての羽根を、同様に取り付け傾斜角度と取り付け位置とを根元部から先端部にかけて徐々に変化させてあり、また、羽根以外の構成は前述した図６，図７に示した従来のものと同様である。
【００２１】
前記のような羽根３の構成にすることにより、抜き勾配によって生じる羽根３の根元部１２と先端部１１との断面形状の差による送風効率の差を少なくできる。また、羽根３の外周側稜線1 3とケーシングを構成しているスタビライザ6との間隔は、根元部１２の位置でｄ１＝Ｒ０−Ｒ１であり、羽根３の先端部１１でｄ２＝Ｒ０−Ｒ１である。しかし、羽根３の外周側稜線１３は、ケーシングを構成しているスタビライザ６との位置関係が一直線上になく、羽根３が矢印８に示す時計方向に回転することにより間隔が徐々に変化する位置関係を構成するため、羽根３への風の流入９と流出１０がなめらかに変化する。これにより、ｎｚ音をなくすことができる。
【００２２】
この発明において、前記各実施形態のものは複数のエレメントを軸方向に連結して筒状羽根車を構成したが、１個のエレメントの羽根の先端部に端板を装着して筒状羽根車を構成してもよい。
【００２３】
【発明の効果】
以上説明したように、この発明に係る筒状羽根車は、環状または円板状の支持板の端面に、軸方向に沿って延出する多数の羽根を周方向に所定間隔で形成した筒状羽根車において、前記羽根の根元部を筒状羽根車の中心Ｏから半径Ｒ１の位置に、筒状羽根車の半径方向に対して取り付け傾斜角度θ 1 で配置し、前記羽根の先端部を筒状羽根車の中心Ｏから異なる半径Ｒ２の位置に、筒状羽根車の半径方向に対して前記取り付け傾斜角度θ１と異なる取り付け傾斜角度θ４で軸方向に所定距離だけ前記根元部から延出した位置に配置し、これらの配置によって、前記羽根の筒状羽根車半径方向に対する取り付け傾斜角度と筒状羽根車の中心Ｏからの取り付け位置とを根元部から先端部にかけて徐々に変化させ、前記羽根の前縁に後倒れになる外周側稜線を構成すると共に前記羽根を外倒れに構成したので、抜き勾配によって生じる羽根の根元部と羽根の先端部との断面形状の差による送風効率の差を少なくして、送風効率を向上させることができるとともに羽根への空気の流入と流出がなめらかに変化する。これにより、耳ざわりなｎｚ音をなくすことができる。
【図面の簡単な説明】
【図１】 この発明の実施の形態に係る筒状羽根車のエレメントを示した斜視図。
【図２】 この発明の実施の形態に係る筒状羽根車を示した一部切り欠き斜視図。
【図３】 この発明の参考例１における筒状羽根車の羽根の先端部から軸方向に沿って羽根の根元部を見た拡大図。
【図４】 この発明の参考例２における筒状羽根車の羽根の先端部から軸方向に沿って羽根の根元部を見た拡大図。
【図５】 この発明の実施の形態に係る筒状羽根車の羽根の先端部から軸方向に沿って羽根の根元部を見た拡大図。
【図６】 従来の筒状羽根車のエレメントを示した斜視図。
【図７】 図６に示したエレメントを連結した従来の筒状羽根車の一部切り欠き斜視図。
【図８】 図７に示した筒状羽根車の羽根の先端部から軸方向に沿って羽根の根元部を見た拡大図。
【図９】 空気調和機における筒状羽根車とケーシングとの位置関係を示す断面説明図。
【符号の説明】
１ エレメント
２ 支持板
３ 羽根
４ 嵌合溝
５ 筒状羽根車
６ スタビライザ、
７ リアガイダ
８ 筒状羽根車の回転方向
９ 流入方向
１０ 流出方向
１１ 羽根の先端部
１２ 羽根の根元部
１３ 羽根の外周側稜線[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a cylindrical impeller for blowing air such as a crossflow fan used in an air conditioner or the like.
[0002]
[Prior art]
Conventionally, as a cylindrical impeller as described above, a structure in which a predetermined number of elements each having a plurality of blades extending straight along the axial direction and formed at predetermined intervals in the circumferential direction is connected to one end surface of a support plate is known. ing. The cylindrical impeller will be described below with reference to the drawings.
In FIG. 6, reference numeral 1 denotes an element made of a synthetic resin integrally molded product. A large number of blades 3 extending in the axial direction are provided on one end surface of an annular or disk-shaped support plate 2 at a predetermined interval in the circumferential direction. Are integrally molded. Each blade 3 is formed in a wing-like cross-sectional shape that is inclined with respect to the radial direction of the element 1 and curved in an approximate arc shape. In addition, a fitting groove 4 for fitting and fixing the tip of the blade is connected to the opposite end surface of the support plate 2 where the blade 3 does not extend so as to prevent another element from being twisted straight. Is formed.
[0003]
As shown in FIG. 7, the tip of the blade 3 of the preceding element 1 is fitted and held on the support plate 2 of the succeeding element 1 and fixed by bonding or ultrasonic welding, and the above operation is repeated to obtain a predetermined value. A cylindrical impeller 5 is configured by connecting a number of elements 1 so as not to be twisted in the axial direction, and providing an end plate 2a for fitting and supporting the blade 3 to the element 1 at the tip.
[0004]
FIG. 8 is an enlarged view of the main part of a conventional cylindrical impeller as viewed from the blade tip 11 along the axial direction of the root 12 of the blade 3. In the blade 3, a root portion 12 is disposed at a mounting inclination angle θ <b> 1 with respect to the radial direction from the center of the cylindrical impeller 5 to a position of a radius R <b> 1. The tip portion 11 of the blade 3 extends straight in the axial direction and is smaller than the root portion 12 by the draft angle.
[0005]
And as shown in FIG. 9, the cylindrical impeller 5 of the front | former stage is arrange | positioned between the stabilizer 6 which forms a casing, and the rear guider 7 as a ventilation apparatus of an air conditioner. When the cylindrical impeller 5 rotates in the clockwise direction of the arrow 8, air flows in from the direction of the arrow 9 and air flows out in the direction of the arrow 10.
[0006]
[Problems to be solved by the invention]
In the case where the element 1 is arranged to form the cylindrical impeller 5, the number z of the blades 3 of the element 1 and the sound having a frequency of (n × z) / 60 Hz composed of the number of rotations n per minute There was a problem that sounds with an integer multiple of the frequency were generated. This sound is called a blade pitch sound or an nz sound, and is an acoustic sound that sounds like a whistle.
[0007]
Hereinafter, this unpleasant sound is referred to as nz sound.
This nz sound changes depending on the blades 3 of the element 1, the mounting pitch of the blades 3, the shapes of the stabilizers 6 and the rear guider 7, and their positional relationships. For example, if the interval d between the cylindrical impeller 5 and the stabilizer 6 is reduced in order to increase the air blowing efficiency, the nz sound increases. As described above, when the air blowing efficiency is increased, the nz sound increases, and there is a problem that the air blowing efficiency cannot be increased to the limit.
[0008]
The element 1 of the cylindrical impeller is generally a synthetic resin molded product. However, in order to take out the element 1 which is a molded product from the mold, the blade 3 needs a draft. As a result, the cross-sectional shape of the tip portion 11 becomes smaller than the cross-sectional shape of the root portion 12 of the blade 3, and the blowing efficiency is different between the root portion 12 and the tip portion 11 of the blade 3, and the blowing efficiency is increased to the limit. There was a problem that it was not possible.
[0009]
The present invention solves the above-described problems, and reduces the difference in the blowing efficiency between the root portion 12 and the blade tip portion 11 of the blade 3 to improve the blowing efficiency, and has a cylindrical shape without nz sound. The purpose is to provide an impeller.
[0010]
[Means for Solving the Problems]
The present invention has been made in order to achieve the above-mentioned object, and has a cylindrical shape in which a large number of blades extending in the axial direction are formed at predetermined intervals in the circumferential direction on the end face of an annular or disk-shaped support plate. In the impeller, the root portion of the blade is disposed at a radius R1 from the center O of the cylindrical impeller at a mounting inclination angle θ 1 with respect to the radial direction of the cylindrical impeller, and the tip portion of the blade is disposed in the cylinder A position extending from the root portion by a predetermined distance in the axial direction at a mounting inclination angle θ4 different from the mounting inclination angle θ1 with respect to the radial direction of the cylindrical impeller at a position of a different radius R2 from the center O of the cylindrical impeller With these arrangements, the mounting inclination angle of the blade with respect to the radial direction of the cylindrical impeller and the mounting position from the center O of the cylindrical impeller are gradually changed from the root portion to the tip portion, Fall to the front edge Characterized by being configured to collapse out of said blade as well as constituting a peripheral side edge line.
[0011]
DETAILED DESCRIPTION OF THE INVENTION
Embodiments of the present invention will be described below with reference to the drawings .
FIG. 1 is a perspective view of an element 1 of a cylindrical impeller according to the present invention. FIG. 2 is a diagram in which a plurality of elements 1 shown in FIG. This is a cylindrical impeller 5. The cylindrical impeller 5 is the same as the conventional one shown in FIGS. 6 and 7 except for each blade 3 provided in each element 1.
[0012]
FIG. 3 is an enlarged view of the root portion 12 of the blade 3 viewed along the axial direction from the tip 11 side of the blade 3 of the cylindrical impeller according to Reference Example 1 of the present invention .
As shown in FIG. 3, the base portion 12 of the blade 3 as in Reference Example 1, from the center O of the cylindrical impeller at a radius R1, Yes and placed in the mounting angle of inclination θ1 with respect to the radial direction, the blade 3 The tip portion 11 is disposed at a position of the same radius R1 from the center O of the cylindrical impeller at a position extending from the root portion 12 of the blade 3 by a predetermined distance in the axial direction at an attachment inclination angle θ2 with respect to the radial direction. is there. With these arrangements, the outer peripheral ridgeline 13 is configured such that the attachment inclination angle of the blade 3 with respect to the radial direction of the cylindrical impeller is gradually changed from the root to the tip, and the blade 3 falls backward at the front edge of the blade 3.
[0013]
In FIG. 3, the single blade 3 is shown and described, but all the blades of the cylindrical impeller are gradually changed from the root to the tip with respect to the radial direction in the same manner as the blades described above. .
[0014]
By using the configuration of the blade 3 as described above, the difference in the blowing efficiency due to the difference in the cross-sectional shape of the root portion 12 and the tip portion 11 of the blade 3 caused by the draft can be reduced.
[0015]
Further, the distances d1 and d2 between the outer peripheral ridge line 13 of the blade 3 and the stabilizer 6 constituting the casing are d1 = R0−R1 at the position of the root portion 12 of the blade 3 and d2 = R0 at the tip portion 11. Since -R1, both d1 and d2 are the same interval. However, when the blade 3 rotates in the clockwise direction indicated by the arrow 8, the outer peripheral side ridge line 13 of the blade 3 is not in a straight line with a constant distance from the stabilizer 6 constituting the casing. A gradually changing positional relationship is constructed. For this reason, the inflow 9 and the outflow 10 of the wind to the blade | wing 3 change smoothly. Thereby, nz sound can be eliminated.
[0016]
FIG. 4 is an enlarged view of the root portion 12 of the blade 3 viewed along the axial direction from the tip portion 11 side of the blade 3 of the cylindrical impeller according to Reference Example 2 of the present invention .
Figure 4 As shown in the root portion 12 of the blade 3 as in Reference Example 2, the position of the radius R1 from the center O of the cylindrical impeller, Yes and placed in the mounting angle of inclination θ1 with respect to the radial direction, the blade 3 The tip portion 11 is disposed at a position of a different radius R2 from the center O of the cylindrical impeller, at a position extending from the root portion 12 by a predetermined distance in the axial direction at a different mounting inclination angle θ3 with respect to the radial direction. With these arrangements, the attachment position of the blade 3 from the cylindrical impeller center O is gradually changed from the root to the tip, and the blade 3 is configured to fall outward.
[0017]
In FIG. 4, only one blade 3 is shown and described, but all the blades of the cylindrical impeller are gradually changed from the root to the tip in the same manner as the blades described above. The configuration other than the blades is the same as the conventional one shown in FIGS.
[0018]
By using the configuration of the blade 3 as described above, the difference in the blowing efficiency due to the difference in the cross-sectional shape of the root portion 12 and the tip portion 11 of the blade 3 caused by the draft can be reduced.
Further, the distances d1 and d2 between the outer peripheral side ridge line 13 of the blade 3 and the stabilizer 6 constituting the casing are d1 = R0−R1 at the position of the root portion 12 of the blade 3, and at the tip portion 11 of the blade 3. d2 = R0-R2. The ridge line 13 on the outer peripheral side of the blade 3 is aligned in a straight line with the stabilizer 6 constituting the casing, but has a positional relationship in which the interval gradually changes from the root portion 12 to the tip portion 11 of the blade 3. Since the blade 3 rotates in the clockwise direction indicated by the arrow 8, the wind inflow 9 and the outflow 10 smoothly change into the blade 3. Thereby, nz sound can be eliminated.
[0019]
Next, an embodiment of the present invention will be described with reference to FIG.
FIG. 5 is an enlarged view of the root portion 12 of the blade 3 viewed along the axial direction from the tip portion 11 side of the blade 3 of the cylindrical impeller according to the embodiment of the present invention .
In FIG. 5 , the root portion 12 of the blade 3 shown in this embodiment is disposed at a radius R1 from the center O of the cylindrical impeller at an attachment inclination angle θ1 with respect to the radial direction. 11 is arranged at a position of a different radius R2 from the center O of the cylindrical impeller at a position extending from the root portion 12 by a predetermined distance in the axial direction at a different mounting inclination angle θ4 with respect to the radial direction. With these arrangements, the mounting inclination angle of the blade 3 with respect to the radial direction of the cylindrical impeller and the mounting position from the center O of the cylindrical impeller are gradually changed from the root portion to the tip portion, and the blade 3 has a leading edge. The outer peripheral side ridgeline 13 that falls backward is configured, and the blade 3 is configured to fall outward.
In addition, the structure of the blade | wing in this embodiment is the structure which comprised the structure of the blade | wing of the reference examples 1 and 2 shown in FIG. 3, FIG. 4 collectively.
[0020]
In FIG. 5, only one blade 3 is shown and described. However, for all the blades of the cylindrical impeller, the attachment inclination angle and the attachment position are gradually changed from the root portion to the tip portion. The configuration other than the blades is the same as the conventional one shown in FIGS.
[0021]
By using the configuration of the blade 3 as described above, the difference in blowing efficiency due to the difference in cross-sectional shape between the root portion 12 and the tip portion 11 of the blade 3 caused by the draft angle can be reduced. Further, the distance between the outer peripheral side ridge line 13 of the blade 3 and the stabilizer 6 constituting the casing is d1 = R0−R1 at the position of the root portion 12, and d2 = R0−R1 at the tip portion 11 of the blade 3. It is. However, the ridge line 13 on the outer peripheral side of the blade 3 is not in a straight line with the stabilizer 6 constituting the casing, and the interval gradually changes as the blade 3 rotates in the clockwise direction indicated by the arrow 8. In order to constitute the relationship, the inflow 9 and the outflow 10 of the wind into the blade 3 change smoothly. Thereby, nz sound can be eliminated.
[0022]
In the present invention, in each of the above embodiments, a plurality of elements are connected in the axial direction to form a cylindrical impeller. However, an end plate is attached to the tip of the blade of one element to form a cylindrical impeller. May be configured.
[0023]
【The invention's effect】
As described above, the cylindrical impeller according to the present invention has a cylindrical shape in which a large number of blades extending along the axial direction are formed at predetermined intervals in the circumferential direction on the end face of an annular or disk-shaped support plate. In the impeller, the root portion of the blade is disposed at a radius R1 from the center O of the cylindrical impeller at a mounting inclination angle θ 1 with respect to the radial direction of the cylindrical impeller, and the tip portion of the blade is disposed in the cylinder A position extending from the root portion by a predetermined distance in the axial direction at a mounting inclination angle θ4 different from the mounting inclination angle θ1 with respect to the radial direction of the cylindrical impeller at a position of a different radius R2 from the center O of the cylindrical impeller With these arrangements, the mounting inclination angle of the blade with respect to the radial direction of the cylindrical impeller and the mounting position from the center O of the cylindrical impeller are gradually changed from the root portion to the tip portion, The outer circumference that falls back to the front edge Since the wing line is configured to fall outward while configuring the ridgeline, the difference in the blowing efficiency due to the difference in cross-sectional shape between the root part of the blade and the tip part of the blade caused by the draft is reduced, and the blowing efficiency is improved. And the inflow and outflow of air into the blades change smoothly. As a result, it is possible to eliminate an unpleasant nz sound.
[Brief description of the drawings]
FIG. 1 is a perspective view showing an element of a cylindrical impeller according to an embodiment of the present invention.
FIG. 2 is a partially cutaway perspective view showing a cylindrical impeller according to an embodiment of the present invention.
FIG. 3 is an enlarged view of the root portion of the blade along the axial direction from the tip portion of the blade of the cylindrical impeller in Reference Example 1 of the present invention .
FIG. 4 is an enlarged view of a root portion of a blade as viewed along the axial direction from a tip portion of the blade of the cylindrical impeller in Reference Example 2 of the present invention.
FIG. 5 is an enlarged view of the root portion of the blade along the axial direction from the tip portion of the blade of the cylindrical impeller according to the embodiment of the present invention.
FIG. 6 is a perspective view showing an element of a conventional cylindrical impeller.
7 is a partially cutaway perspective view of a conventional cylindrical impeller to which the elements shown in FIG. 6 are connected. FIG.
8 is an enlarged view of the blade root portion seen from the tip of the blade of the cylindrical impeller shown in FIG. 7 along the axial direction.
FIG. 9 is an explanatory cross-sectional view showing the positional relationship between a cylindrical impeller and a casing in an air conditioner.
[Explanation of symbols]
1 element 2 support plate 3 blade 4 fitting groove 5 cylindrical impeller 6 stabilizer,
7 Rear guider 8 Rotating direction of cylindrical impeller 9 Inflow direction 10 Outflow direction 11 Blade tip 12 Blade root 13 Blade outer edge

Claims (1)

環状または円板状の支持板の端面に、軸方向に沿って延出する多数の羽根を周方向に所定間隔で形成した筒状羽根車において、前記羽根の根元部を筒状羽根車の中心Ｏから半径Ｒ１の位置に、筒状羽根車の半径方向に対して取り付け傾斜角度θ 1 で配置し、前記羽根の先端部を筒状羽根車の中心Ｏから異なる半径Ｒ２の位置に、筒状羽根車の半径方向に対して前記取り付け傾斜角度θ１と異なる取り付け傾斜角度θ４で軸方向に所定距離だけ前記根元部から延出した位置に配置し、これらの配置によって、前記羽根の筒状羽根車半径方向に対する取り付け傾斜角度と筒状羽根車の中心Ｏからの取り付け位置とを根元部から先端部にかけて徐々に変化させ、前記羽根の前縁に後倒れになる外周側稜線を構成すると共に前記羽根を外倒れに構成したことを特徴とする筒状羽根車。A cylindrical impeller in which a large number of blades extending in the axial direction are formed at predetermined intervals in the circumferential direction on an end surface of an annular or disk-shaped support plate, and the root portion of the blade is the center of the cylindrical impeller It is arranged at a position of radius R1 from O with a mounting inclination angle θ 1 with respect to the radial direction of the cylindrical impeller, and the tip of the blade is cylindrical at a position of different radius R2 from the center O of the cylindrical impeller. Arranged at a position extending from the root portion by a predetermined distance in the axial direction at an attachment inclination angle θ4 different from the attachment inclination angle θ1 with respect to the radial direction of the impeller, and by these arrangements, the cylindrical impeller of the blade The mounting inclination angle with respect to the radial direction and the mounting position from the center O of the cylindrical impeller are gradually changed from the root portion to the tip portion, and an outer peripheral side ridge line that falls backward is formed on the front edge of the blade and the blade It was constructed to fall outside Cylindrical impeller characterized and.
JP04705796A 1996-03-05 1996-03-05 Cylindrical impeller Expired - Fee Related JP3850061B2 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP04705796A JP3850061B2 (en) 1996-03-05 1996-03-05 Cylindrical impeller

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Application Number Priority Date Filing Date Title
JP04705796A JP3850061B2 (en) 1996-03-05 1996-03-05 Cylindrical impeller

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JPH09242694A JPH09242694A (en) 1997-09-16
JP3850061B2 true JP3850061B2 (en) 2006-11-29

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Publication number Priority date Publication date Assignee Title
JP2010209849A (en) * 2009-03-11 2010-09-24 Sharp Corp Cross-flow fan and method of manufacturing the cross-flow fan
JP5041446B2 (en) * 2010-02-16 2012-10-03 シャープ株式会社 Cross-flow fan, blower and impeller molding machine
JP5030115B2 (en) * 2010-02-16 2012-09-19 シャープ株式会社 Cross-flow fan, blower and impeller molding machine
JP6431663B2 (en) * 2013-09-30 2018-11-28 日清紡メカトロニクス株式会社 Blower impeller
JP2017214937A (en) * 2017-09-19 2017-12-07 日清紡メカトロニクス株式会社 Cross flow fan
CN112412832B (en) * 2020-10-28 2022-07-19 青岛海尔空调器有限总公司 Cross-flow fan and air conditioner

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