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JP2006258107A - Axial blower - Google Patents

Axial blower Download PDF

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JP2006258107A
JP2006258107A JP2006182113A JP2006182113A JP2006258107A JP 2006258107 A JP2006258107 A JP 2006258107A JP 2006182113 A JP2006182113 A JP 2006182113A JP 2006182113 A JP2006182113 A JP 2006182113A JP 2006258107 A JP2006258107 A JP 2006258107A
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blade
line segment
center
trailing edge
derived
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Mitsuyoshi Ishijima
嶋 満 義 石
Akihiro Takeuchi
内 章 洋 竹
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Carrier Japan Corp
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Toshiba Carrier Corp
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Abstract

【課題】回転数を上昇させて送風量の増加を図った場合でも、電動機の負荷を低く抑えることのできる軸流送風機を提供する。
【解決手段】ハブの周囲に複数の翼を一体的に形成してなる軸流送風機において、回転中の空気流出部に当たる翼後縁部と翼外周部とが交わる角部を空気の流出方向に凸状に膨出する膨出部を形成すると共に、回転軸の中心から翼の最外周までの半径をRとしたとき、前記膨出部を0.6R〜Rの範囲に形成し、前記膨出部から回転軸方向に連なる翼後縁部は風が流入する方向へ湾曲し、回転軸の中心をOとし、この中心Oから導出して前記翼後縁部の湾奥部(Q)と接触する線分をKm、中心Oから導出して前記膨出部の先端部(T)と接触する線分をKn、中心Oから導出して回転中の空気流入部に当たる翼前縁部の外周端(S)と接触する線分をKfとし、線分Kmと線分Knとの間の中心角をα1、線分Knと線分Kfとの間の中心角をα2とした場合、α1=0.05×α2〜0.15×α2としたことを特徴とする。
【選択図】図1
An axial flow blower that can keep the load on an electric motor low even when the rotational speed is increased to increase the amount of blown air.
In an axial blower in which a plurality of blades are integrally formed around a hub, a corner portion where a blade trailing edge and a blade outer peripheral portion that are in contact with a rotating air outflow portion intersect in an air outflow direction. A bulging portion that bulges in a convex shape is formed, and when the radius from the center of the rotating shaft to the outermost periphery of the blade is R, the bulging portion is formed in a range of 0.6R to R, and The trailing edge of the blade that extends from the exit portion in the direction of the rotation axis is curved in the direction in which the wind flows, and the center of the rotation shaft is defined as O. The outer periphery of the leading edge of the blade that is derived from Km, the center O, and is in contact with the tip (T) of the bulging part, and is derived from Kn, the center O and hits the rotating air inflow part. The line segment in contact with the end (S) is defined as Kf, the central angle between the line segment Km and the line segment Kn is α1, and the center between the line segment Kn and the line segment Kf. The case of the [alpha] 2, characterized in that the α1 = 0.05 × α2~0.15 × α2.
[Selection] Figure 1

Description

本発明は、空気調和機の室外機等に使用される軸流送風機に関する。   The present invention relates to an axial blower used for an outdoor unit or the like of an air conditioner.

この種の軸流送風機として、図13や図14に示す構成のものが知られている。このうち、図13に示した軸流送風機10Aは、ハブ11と複数の翼12(ここでは、1個のみを示す)とが一体的に成形される。この軸流送風機10Aが矢印X方向に回転するものとして、翼12の空気流出部に当たる翼後縁部21は略直線状に形成されていたため、風量の増加を図る場合、送風機を駆動する電動機の負荷が大きくなったり、送風音が増大したりするという問題があった。   As this type of axial blower, a configuration shown in FIGS. 13 and 14 is known. Among these, in the axial flow fan 10A shown in FIG. 13, the hub 11 and the plurality of blades 12 (only one is shown here) are integrally formed. As this axial blower 10A rotates in the direction of arrow X, the blade trailing edge 21 that hits the air outflow portion of the blade 12 was formed in a substantially straight line. Therefore, when increasing the air volume, the motor that drives the blower There has been a problem that the load increases and the blowing sound increases.

一方、図14に示した軸流送風機10Bの翼後縁部21は略円弧状に湾曲しており、翼後縁部21と翼外周部22とが交わる角部が凸状に膨出する膨出部23になっている。しかし、膨出部23を形成する範囲が、回転軸の中心Oから翼外周部22までの半径をrとしたとき、0.5rを超える広い領域に存在するため、前述したと同様に送風機の回転数を上昇させて風量の増大を図った場合、翼後縁部21における流れ損失が増大し、送風機駆動用電動機の負荷が大きくなったり、送風音が増大したりするという問題があった。   On the other hand, the blade trailing edge portion 21 of the axial blower 10B shown in FIG. 14 is curved in a substantially arc shape, and a corner portion where the blade trailing edge portion 21 and the blade outer peripheral portion 22 intersect is bulged in a convex shape. It is the exit 23. However, since the range in which the bulging portion 23 is formed exists in a wide region exceeding 0.5r, where r is the radius from the center O of the rotating shaft to the blade outer peripheral portion 22, When the rotational speed is increased to increase the air volume, there is a problem that the flow loss at the blade trailing edge portion 21 increases, the load on the blower driving motor increases, and the blowing sound increases.

本発明は、上記の問題点を解決するためになされたもので、その目的は回転数を上昇させて送風量の増加を図った場合でも、電動機の負荷を低く抑えることのできる軸流送風機を提供するにある。   The present invention has been made to solve the above-described problems, and an object of the present invention is to provide an axial blower that can keep the load on the motor low even when the rotational speed is increased to increase the amount of air flow. In offer.

本発明の他の目的は、翼後縁部に発生する渦を抑制し、送風騒音の増加を抑えることのできる軸流送風機を提供するにある。   Another object of the present invention is to provide an axial blower capable of suppressing vortices generated at the blade trailing edge and suppressing an increase in blowing noise.

本発明のもう一つ他の目的は、成形性やコスト低減に優れた軸流送風機を提供するにある。   Another object of the present invention is to provide an axial blower excellent in formability and cost reduction.

請求項1に係る発明は、ハブの周囲に複数の翼を一体的に形成してなる軸流送風機において、
回転中の空気流出部に当たる翼後縁部と翼外周部とが交わる角部を空気の流出方向に凸状に膨出する膨出部を形成すると共に、回転軸の中心から翼の最外周までの半径をRとしたとき、前記膨出部を0.6R〜Rの範囲に形成し、
前記膨出部から回転軸方向に連なる翼後縁部は風が流入する方向へ湾曲し、
回転軸の中心をOとし、この中心Oから導出して前記翼後縁部の湾奥部(Q)と接触する線分をKm、中心Oから導出して前記膨出部の先端部(T)と接触する線分をKn、中心Oから導出して回転中の空気流入部に当たる翼前縁部の外周端(S)と接触する線分をKfとし、線分Kmと線分Knとの間の中心角をα1、線分Knと線分Kfとの間の中心角をα2とした場合、α1=0.05×α2〜0.15×α2としたことを特徴とする。
The invention according to claim 1 is an axial blower in which a plurality of blades are integrally formed around a hub.
From the center of the rotating shaft to the outermost periphery of the wing, it forms a bulge that bulges in the air outflow direction at the corner where the blade trailing edge that hits the rotating air outflow portion and the blade outer periphery intersect When the radius of R is R, the bulging portion is formed in the range of 0.6R to R,
The blade trailing edge that continues from the bulge to the rotational axis is curved in the direction in which the wind flows,
The center of the rotation axis is defined as O, the line segment derived from the center O and contacting the bay depth (Q) of the trailing edge of the blade is derived from Km, the center O and the tip of the bulging portion (T ) Is a line segment that comes into contact with the outer peripheral edge (S) of the blade leading edge that is derived from the center O and hits the rotating air inflow portion, and Kf is a line segment that comes into contact with the rotating air inflow portion. When the central angle between them is α1, and the central angle between the line segment Kn and the line segment Kf is α2, α1 = 0.05 × α2 to 0.15 × α2.

請求項2に係る発明は、一つの翼の外周縁の弧長をCLとしたとき、前記翼後縁部の湾曲部の弧長を0.4〜0.6CLの範囲としたことを特徴とする。   The invention according to claim 2 is characterized in that when the arc length of the outer peripheral edge of one wing is CL, the arc length of the curved portion of the wing trailing edge is in a range of 0.4 to 0.6 CL. To do.

請求項3に係る発明は、前記翼後縁部の径方向内側の湾曲部の始点をUとし、回転軸の中心Oから導出して前記翼後縁部の湾奥部(Q)と接触する線分をKmとし、点Uから線分Kmに下ろした垂線の脚の長さをL1とし、前記膨出部の先端部(T)から線分Kmに下ろした垂線の脚の長さをL2としたとき、L2=0.5×L1〜0.7×L1としたことを特徴とする。   In the invention according to claim 3, the starting point of the radially inner curved portion of the blade trailing edge is defined as U, and is derived from the center O of the rotating shaft and is in contact with the bay inner portion (Q) of the blade trailing edge. The length of the leg of the perpendicular line dropped from the point U to the line segment Km is L1, and the length of the leg of the perpendicular line lowered from the tip (T) of the bulging portion to the line segment Km is L2. L2 = 0.5 × L1 to 0.7 × L1.

以上の説明によって明らかなように、本発明によれば、回転数を上昇させて送風量の増加を図った場合でも、電動機の負荷を低く抑えることのできる軸流送風機が得られる。   As is apparent from the above description, according to the present invention, an axial blower capable of keeping the load on the motor low can be obtained even when the rotational speed is increased to increase the amount of blown air.

以下、本発明を図面に示す好適な実施形態に基づいて詳細に説明する。図1は本発明に係る軸流送風機の全体的な構成を示した、軸方向で見る平面図である。この軸流送風機1はハブ11と3枚の翼12とが一体的に成形され、矢印X方向に回転するものとする。図2は図1に示した軸流送風機1の一つの翼12を拡大して示したもので、矢印X方向に回転する翼12の空気流出部に当たる翼後縁部21と、翼外周部22とが交わる部分を空気が流れる方向に凸状に膨出させて膨出部23を形成している。この場合、膨出部23は回転軸の中心Oから翼外周部22までの半径をRとしたとき、膨出部23は翼後縁部21のうち、0.6RからRに至る範囲に形成されている。   Hereinafter, the present invention will be described in detail based on preferred embodiments shown in the drawings. FIG. 1 is a plan view showing an overall configuration of an axial blower according to the present invention as viewed in the axial direction. In the axial blower 1, a hub 11 and three blades 12 are integrally formed and rotate in the direction of arrow X. FIG. 2 is an enlarged view of one blade 12 of the axial blower 1 shown in FIG. 1, and a blade trailing edge portion 21 corresponding to an air outflow portion of the blade 12 rotating in the arrow X direction, and a blade outer peripheral portion 22. The bulging portion 23 is formed by bulging a portion where the crosses with the projection in the direction in which the air flows. In this case, when the radius from the center O of the rotating shaft to the blade outer peripheral portion R is R, the bulge portion 23 is formed in the range from 0.6R to R in the blade trailing edge portion 21. Has been.

図3は膨出部23の形成範囲と、送風量及び電動機の入力との関係を示す線図であり、膨出部23を翼後縁部21のうち、0.6RからRに至る範囲に形成することにより、翼後縁部21の付近の流れ損失を抑制し、電動機に与える負荷を小さくできる。従って、翼外周部22の周速増大を図って送風量を増大させながら、電動機に与える負荷を小さくできるため、空気調和機等の省エネ性能を向上させることができる。    FIG. 3 is a diagram showing the relationship between the formation range of the bulging portion 23, the air flow rate and the input of the electric motor. The bulging portion 23 is in the range from 0.6 R to R in the blade trailing edge portion 21. By forming, the flow loss near the blade trailing edge 21 can be suppressed, and the load applied to the electric motor can be reduced. Therefore, since the load applied to the electric motor can be reduced while increasing the air flow rate by increasing the peripheral speed of the blade outer peripheral portion 22, the energy saving performance of the air conditioner or the like can be improved.

図4は図2に示した翼後縁部21及び膨出部23の輪郭形状を説明するためのもので、先ず、膨出部23は翼外周部22に連なり、径方向外側に比較的大きな曲率半径で内側に入りこむ円弧31と、最も小さな曲率半径で空気の流出方向に凸状をなす円弧32と、この円弧32よりも大きな曲率半径で空気の流出方向に凹状をなす円弧33とを順次連ねた形状を有している。また、膨出部23よりも径方向内側の翼後縁部21は曲率半径が比較的大きく、空気の流出方向に凹状をなす円弧34と、この円弧34よりも小さい曲率半径で、空気の流出方向に凹状をなす円弧35とを順に連ねた形状を有している。   FIG. 4 is for explaining the outline shape of the blade trailing edge portion 21 and the bulging portion 23 shown in FIG. 2. First, the bulging portion 23 is connected to the blade outer peripheral portion 22 and is relatively large radially outward. An arc 31 that enters inward with a radius of curvature, an arc 32 that is convex in the direction of air outflow with the smallest radius of curvature, and an arc 33 that is concave in the direction of air outflow with a radius of curvature larger than the arc 32 are sequentially formed. It has a continuous shape. Further, the blade trailing edge portion 21 radially inward of the bulging portion 23 has a relatively large radius of curvature, and has an arc 34 that is concave in the air outflow direction, and an air outflow with a radius of curvature smaller than the arc 34. It has a shape in which a circular arc 35 having a concave shape in the direction is connected in order.

このように、膨出部23を3つ以上の異なる円弧を連ねた形状にすることにより、渦の発生を抑制し、騒音を低減することができる。また、膨出部23の径方向内側の部位を2つの円弧を連ねた形状とすることにより、1つの円弧で形成した場合と比較して翼面積を増大させることができ、送風量を増大させることができる。   In this way, by forming the bulging portion 23 into a shape in which three or more different arcs are connected, generation of vortices can be suppressed and noise can be reduced. Further, by forming the radially inner portion of the bulging portion 23 into a shape in which two arcs are connected, the blade area can be increased compared to the case where the arcs are formed by one arc, and the amount of blown air is increased. be able to.

図5は翼12の翼外周部22の弧長CLと翼後縁部21の湾曲部の弧長LWとの関係を示したもので、翼後縁部21における湾曲部の弧長LWを、0.4CL〜0.6CLの範囲となるように設定している。   FIG. 5 shows the relationship between the arc length CL of the blade outer peripheral portion 22 of the blade 12 and the arc length LW of the curved portion of the blade trailing edge portion 21. It is set to be in the range of 0.4 CL to 0.6 CL.

図6は弧長CLに対する湾曲部LWの比率と送風量及び電動機入力との関係を示した線図であり、弧長CLに対して湾曲部の弧長LWを40%〜60%の範囲に設定することにより、送風量を一定量に確保しながら、電動機に与える負荷を小さく抑えることができる。   FIG. 6 is a diagram showing the relationship between the ratio of the curved portion LW to the arc length CL, the air flow rate, and the motor input. The arc length LW of the curved portion is in the range of 40% to 60% with respect to the arc length CL. By setting, the load applied to the electric motor can be suppressed to a small value while ensuring a constant air flow rate.

図7は膨出部23が翼12の周方向に占有する割合を説明する図であり、回転軸の中心をOとし、この中心Oから導出して翼後縁部21の湾奥部Qと接触する線分をKm、中心Oから導出して膨出部23の先端部Tと接触する線分をKn、中心Oから導出して回転中の空気流入部に当たる翼前縁部の外周端Sと接触する線分をKfとし、線分Kmと線分Knとの間の中心角をα1、線分Knと線分Kfとの間の中心角をα2とした場合、α1=0.05×α2〜0.15×α2としたことを示している。   FIG. 7 is a diagram for explaining the proportion of the bulging portion 23 occupied in the circumferential direction of the wing 12, where the center of the rotation axis is O, and the bay depth portion Q of the wing trailing edge 21 is derived from this center O. The line segment in contact is derived from Km, the center O and the line segment in contact with the tip T of the bulging portion 23 is derived from Kn, the center O, and the outer peripheral edge S of the leading edge of the blade impinging on the rotating air inflow portion. When the line segment in contact with the line segment is Kf, the central angle between the line segment Km and the line segment Kn is α1, and the central angle between the line segment Kn and the line segment Kf is α2, α1 = 0.05 × It shows that α2 to 0.15 × α2.

図8はα1/α2と送風量及び電動機入力との関係を示す線図であり、送風機の回転数を上昇させ、送風量の増加を図った場合においても、送風騒音を上昇させることなく、電動機に与える負荷を小さく抑えることができる。   FIG. 8 is a diagram showing the relationship between α1 / α2 and the amount of blown air and the motor input. Even when the number of rotations of the blower is increased to increase the amount of blown air, the motor is not increased without increasing the blowing noise. It is possible to reduce the load applied to the battery.

図9は翼後縁部21の湾曲部の径方向外側部位と、径方向内側部位の風流出方向への突出状態を示したもので、翼後縁部21の径方向内側の湾曲部の始点をUとし、回転軸の中心Oから導出して翼後縁部21の湾奥部Qと接触する線分をKmとし、点Uから線分Kmに下ろした垂線の脚の長さをL1とし、膨出部23の先端部Tから線分Kmに下ろした垂線の脚の長さをL2としたとき、L2=0.5×L1〜0.7×L1に設定している。   FIG. 9 shows a radially outward portion of the curved portion of the blade trailing edge 21 and a protruding state of the radially inner portion in the wind outflow direction. The starting point of the radially inner curved portion of the blade trailing edge 21 is shown in FIG. Is U, and the line segment that is derived from the center O of the rotating shaft and contacts the bay depth Q of the wing trailing edge 21 is Km, and the length of the leg of the perpendicular line from the point U to the line segment Km is L1. When the length of the leg of the perpendicular line dropped from the distal end T of the bulging portion 23 to the line segment Km is L2, L2 = 0.5 × L1 to 0.7 × L1 is set.

この構成によれば、図10に示したL1に対するL2の比率と送風量及び電動機入力との関係から明らかなように、送風量を低下させることなく、電動機に与える負荷を小さく抑えることができる。   According to this configuration, as is clear from the relationship between the ratio of L2 to L1 shown in FIG. 10, the air flow rate, and the motor input, the load applied to the motor can be kept small without reducing the air flow rate.

図11は翼12の翼外周部22の弧長と翼後縁部21の湾奥部に対応する部位の周方向の弧長との関係を表したもので、回転の中心から翼の外周までの半径をRとして、この外周の円弧長をCL、回転の中心から0.6×Rの半径を有する円弧のうち、空気流入部に当たる翼前縁部から空気流出部に当たる翼後縁部までの円弧長をYeとしたとき、Ye=0.4CL〜0.6CLに設定している。   FIG. 11 shows the relationship between the arc length of the blade outer peripheral portion 22 of the wing 12 and the arc length in the circumferential direction of the portion corresponding to the back of the bay of the wing trailing edge portion 21. The radius of the outer periphery is R, and the arc length of the outer periphery is CL, and the arc from the center of rotation to the blade trailing edge corresponding to the air outflow portion from the blade leading edge corresponding to the air inflow portion out of the arc having a radius of 0.6 × R. When the arc length is Ye, Ye = 0.4CL to 0.6CL is set.

図12は外周の円弧長CLに対する翼前縁部から翼後縁部までの円弧長Yeの比率と騒音値及び電動機入力との関係を示した線図であり、この線図から明らかなように、送風騒音を増大することなく、電動機の負荷を小さく抑えることができる。   FIG. 12 is a diagram showing the relationship between the ratio of the arc length Ye from the blade leading edge to the blade trailing edge with respect to the arc length CL of the outer periphery, the noise value, and the motor input. As is apparent from this diagram. The load on the motor can be kept small without increasing the blowing noise.

本発明に係る軸流送風機の全体的な構成を示した、軸方向で見る平面図。The top view seen in the axial direction which showed the whole structure of the axial blower which concerns on this invention. 図1に示した軸流送風機1の一つの翼を拡大して示した図。The figure which expanded and showed one wing | blade of the axial-flow fan 1 shown in FIG. 膨出部の形成範囲と、送風量及び電動機の入力との関係を示す線図。The diagram which shows the relationship between the formation range of a bulging part, the ventilation volume, and the input of an electric motor. 図2に示した翼後縁部及び膨出部の輪郭形状を説明するたの図。The figure for demonstrating the outline shape of the wing | wing trailing edge part and bulging part which were shown in FIG. 翼外周部の弧長と翼後縁部2湾曲部の弧長との関係を示し平面図。The top view which shows the relationship between the arc length of a blade outer peripheral part, and the arc length of a blade trailing edge 2 curved part. 弧長と送風量及び電動機入力との関係を示した線図。The diagram which showed the relationship between arc length, ventilation volume, and motor input. 膨出部が翼の周方向に占有する割合を説明するための図。The figure for demonstrating the ratio which a bulging part occupies for the circumferential direction of a wing | blade. 膨出部が翼の周方向に占有する割合と送風量及び電動機入力との関係を示す線図。The diagram which shows the relationship between the ratio which a bulging part occupies to the circumferential direction of a wing | blade, ventilation volume, and an electric motor input. 翼後縁部の湾曲部の径方向外側部位と、径方向内側部位の風流出方向への突出状態を示した図。The figure which showed the protrusion state to the wind outflow direction of the radial direction outer side part and radial direction inner side part of the curved part of a blade trailing edge part. 図9に示した径方向外側部位と風流出方向の突出部との比率と送風量及び電動機入力との関係を示した線図。The diagram which showed the relationship between the ratio of the radial direction outer side site | part shown in FIG. 9, and the protrusion part of a wind outflow direction, ventilation volume, and an electric motor input. 翼外周部の弧長と翼後縁部の湾奥部に対応する部位の周方向の弧長との関係を表した図。The figure showing the relationship between the arc length of a wing | blade outer peripheral part and the arc length of the circumferential direction of the site | part corresponding to the bay depth part of a wing | wing trailing edge part. 外周の円弧長に対する翼前縁部から翼後縁部までの円弧長の比率と騒音値及び電動機入力との関係を示した線図。The diagram which showed the relationship between the ratio of the circular arc length from a blade front edge part to a blade rear edge part with respect to the circular arc length of an outer periphery, a noise value, and an electric motor input. 従来の軸流送風機の構成を示すために、軸方向から見た平面図。The top view seen from the axial direction in order to show the structure of the conventional axial blower. 従来の軸流送風機の他の構成を示すために、軸方向から見た平面図。The top view seen from the axial direction in order to show other composition of the conventional axial blower.

符号の説明Explanation of symbols

1 軸流送風機
11 ハブ
12 翼
21 翼後縁部
22 翼外周部
23 膨出部
31〜34 円弧
DESCRIPTION OF SYMBOLS 1 Axial flow fan 11 Hub 12 Wing | blade 21 Wing | blade trailing edge part 22 Wing | blade outer peripheral part 23 The swelling part 31-34 Arc

Claims (3)

ハブの周囲に複数の翼を一体的に形成してなる軸流送風機において、
回転中の空気流出部に当たる翼後縁部と翼外周部とが交わる角部を空気の流出方向に凸状に膨出する膨出部を形成すると共に、回転軸の中心から翼の最外周までの半径をRとしたとき、前記膨出部を0.6R〜Rの範囲に形成し、
前記膨出部から回転軸方向に連なる翼後縁部は風が流入する方向へ湾曲し、
回転軸の中心をOとし、この中心Oから導出して前記翼後縁部の湾奥部(Q)と接触する線分をKm、中心Oから導出して前記膨出部の先端部(T)と接触する線分をKn、中心Oから導出して回転中の空気流入部に当たる翼前縁部の外周端(S)と接触する線分をKfとし、線分Kmと線分Knとの間の中心角をα1、線分Knと線分Kfとの間の中心角をα2とした場合、α1=0.05×α2〜0.15×α2としたことを特徴とする軸流送風機。
In the axial blower formed by integrally forming a plurality of blades around the hub,
From the center of the rotating shaft to the outermost periphery of the wing, it forms a bulge that bulges in the air outflow direction at the corner where the blade trailing edge that hits the rotating air outflow portion and the blade outer periphery intersect When the radius of R is R, the bulging portion is formed in the range of 0.6R to R,
The blade trailing edge that continues from the bulge to the rotational axis is curved in the direction in which the wind flows,
The center of the rotation axis is defined as O, the line segment derived from the center O and contacting the bay depth (Q) of the trailing edge of the blade is derived from Km, the center O and the tip of the bulging portion (T ) Is a line segment that comes into contact with the outer peripheral edge (S) of the blade leading edge that is derived from the center O and hits the rotating air inflow portion, and Kf is a line segment that comes into contact with the rotating air inflow portion. An axial blower characterized in that α1 = 0.05 × α2 to 0.15 × α2 where α1 is the central angle between them and α2 is the central angle between the line Kn and the line Kf.
一つの翼の外周縁の弧長をCLとしたとき、前記翼後縁部の湾曲部の弧長を0.4〜0.6CLの範囲としたことを特徴とする請求項1に記載の軸流送風機。   The shaft according to claim 1, wherein when the arc length of the outer peripheral edge of one blade is CL, the arc length of the curved portion of the trailing edge of the blade is in a range of 0.4 to 0.6CL. Current blower. 前記翼後縁部の径方向内側の湾曲部の始点をUとし、回転軸の中心Oから導出して前記翼後縁部の湾奥部(Q)と接触する線分をKmとし、点Uから線分Kmに下ろした垂線の脚の長さをL1とし、前記膨出部の先端部(T)から線分Kmに下ろした垂線の脚の長さをL2としたとき、L2=0.5×L1〜0.7×L1としたことを特徴とする請求項1に記載の軸流送風機。   The starting point of the curved portion radially inward of the blade trailing edge is set as U, the line segment derived from the center O of the rotating shaft and in contact with the bay depth (Q) of the blade trailing edge is set as Km, and the point U L2 is the length of the leg of the perpendicular line that is lowered to the line segment Km from L1 and L2 is the length of the leg of the perpendicular line that is lowered from the tip (T) of the bulging part to the line segment Km. The axial blower according to claim 1, wherein the axial flow blower is 5 x L1 to 0.7 x L1.
JP2006182113A 2006-06-30 2006-06-30 Axial blower Pending JP2006258107A (en)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2010047001A1 (en) * 2008-10-22 2010-04-29 シャープ株式会社 Propeller fan, fluid feeder and mold
JP2010101223A (en) * 2008-10-22 2010-05-06 Sharp Corp Propeller fan, fluid feeding device, and molding die
AU2011202590B2 (en) * 2008-10-22 2013-01-10 Sharp Kabushiki Kaisha Propeller fan, fluid feeder and molding die
WO2014102970A1 (en) * 2012-12-27 2014-07-03 三菱電機株式会社 Propeller fan, air blowing equipment, outdoor unit
CN115111194A (en) * 2022-06-27 2022-09-27 约克广州空调冷冻设备有限公司 Blade and axial flow impeller using same

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JPS60114300U (en) * 1984-12-13 1985-08-02 トリン コーポレーシヨン axial flow wheel
JPH02253000A (en) * 1989-03-27 1990-10-11 Mitsubishi Heavy Ind Ltd Low-noise blade
JPH06249196A (en) * 1993-03-02 1994-09-06 Matsushita Electric Ind Co Ltd Impeller of axial blower

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Publication number Priority date Publication date Assignee Title
JPS5181006A (en) * 1975-01-14 1976-07-15 Matsushita Seiko Kk SOFUKINO HANEGURUMA
JPS59173598A (en) * 1983-03-23 1984-10-01 Nippon Denso Co Ltd Axial fan
JPS60114300U (en) * 1984-12-13 1985-08-02 トリン コーポレーシヨン axial flow wheel
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Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2010047001A1 (en) * 2008-10-22 2010-04-29 シャープ株式会社 Propeller fan, fluid feeder and mold
JP2010101223A (en) * 2008-10-22 2010-05-06 Sharp Corp Propeller fan, fluid feeding device, and molding die
CN102197228A (en) * 2008-10-22 2011-09-21 夏普株式会社 Propeller fan, fluid feeder and mold
AU2008363120B2 (en) * 2008-10-22 2012-08-16 Sharp Kabushiki Kaisha Propeller fan, fluid feeder and mold
AU2011202590B2 (en) * 2008-10-22 2013-01-10 Sharp Kabushiki Kaisha Propeller fan, fluid feeder and molding die
CN102197228B (en) * 2008-10-22 2014-05-14 夏普株式会社 Propeller fan, fluid feeder and mold
WO2014102970A1 (en) * 2012-12-27 2014-07-03 三菱電機株式会社 Propeller fan, air blowing equipment, outdoor unit
CN115111194A (en) * 2022-06-27 2022-09-27 约克广州空调冷冻设备有限公司 Blade and axial flow impeller using same
CN115111194B (en) * 2022-06-27 2024-05-10 约克广州空调冷冻设备有限公司 Blade and axial flow impeller using same

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