JP2008303760A - Axial blower - Google Patents

Axial blower Download PDF

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JP2008303760A
JP2008303760A JP2007150358A JP2007150358A JP2008303760A JP 2008303760 A JP2008303760 A JP 2008303760A JP 2007150358 A JP2007150358 A JP 2007150358A JP 2007150358 A JP2007150358 A JP 2007150358A JP 2008303760 A JP2008303760 A JP 2008303760A
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rib
outer peripheral
peripheral edge
boss
axial
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Seiji Nakajima
誠治 中島
Shoji Yamada
彰二 山田
Koji Yoshikawa
浩司 吉川
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Mitsubishi Electric Corp
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Mitsubishi Electric Corp
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Abstract

<P>PROBLEM TO BE SOLVED: To obtain an axial blower capable of suppressing blowing noise small without deteriorating blowing performance. <P>SOLUTION: The axial blower is equipped with: an impeller including a boss 3 rotated around an axis, a plurality of blades 4 disposed on the outer peripheral face of the boss 3 and each having a shape surrounded by a base edge part 4a, an outer peripheral edge part 4b, a front edge part 4c, and a rear edge part 4d; a bell-mouth 6 disposed coaxially with the boss 3, and having a rotational direction front end side of the blade 4 projecting from an opening on one side and surrounding a rotational direction rear end side of the blade 4; and a rib 5 projecting from a negative pressure face 4e of the blade 4. In the rib 5, a rib front end 5a is connected to a portion of the front edge part 4c separated from a front end in the rotational direction of the outer peripheral edge part 4b or near thereto, and a rib rear end 5b is connected to a portion of the outer peripheral edge part 4b separated from a front end in the rotational direction of the outer peripheral edge part 4b. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

この発明は空気調和機や換気機器などに用いられる軸流送風機に関するものである。   The present invention relates to an axial blower used for an air conditioner, a ventilator or the like.

従来の送風機は、モータと、モータに取り付けられたハブ、及びハブの周囲に設けられた複数の羽根とで構成された羽根車と、羽根の吐出側の外周を囲むオリフィスと、オリフィスに囲まれていない羽根の外周端部の負圧面側に羽根の吸込み側から吐出側にかけて順次高さが高くなるように取り付けられた板状のリブと、で構成されている。そして、従来の送風機では、気流がオリフィスに囲まれていない羽根車の外周に吹き出したり、羽根車の翼間中央より吸い込まれたりすることがリブによって抑制され、送風性能の劣化と送風騒音の増加が抑えられていた(例えば、特許文献1参照)。   A conventional blower is surrounded by an impeller composed of a motor, a hub attached to the motor, and a plurality of blades provided around the hub, an orifice surrounding the outer periphery of the discharge side of the blade, and the orifice. And plate-like ribs that are attached to the suction surface side of the outer peripheral end of the non-blade so as to increase in height from the suction side to the discharge side of the vane. In the conventional blower, the air flow is blown out to the outer periphery of the impeller that is not surrounded by the orifice, or sucked from the center between the blades of the impeller, which is suppressed by the rib, and the deterioration of the blowing performance and the increase of the blowing noise (For example, refer to Patent Document 1).

特許第3205009号公報Japanese Patent No. 3205009

しかしながら、従来の送風機は、リブが回転軸から最も離れた羽根の外周端に取り付けられているため、リブの前端から羽根に流入する気流の相対速度が速くなり、リブで発生する送風騒音が大きくなるという問題がある。また、リブにおける羽根の吐出側の端部は、羽根の負圧面からステップ状に高さが高くなっており、この部分で気流が不連続となって剥離流れが生じるために送風騒音が増大するという問題がある。さらに、リブがオリフィスに囲まれていない領域の吸込み側から吐出側にかけて延在しているので、オリフィスの上方からモータ軸の方向に向かって羽根に吸込まれる気流の流れが阻害される。これにより、気流の流れが不安定となって送風騒音が増大するという問題がある。   However, in the conventional blower, since the rib is attached to the outer peripheral end of the blade farthest from the rotating shaft, the relative speed of the airflow flowing into the blade from the front end of the rib is increased, and the blowing noise generated by the rib is large. There is a problem of becoming. The end of the rib on the discharge side of the blade has a stepped height from the suction surface of the blade, and the airflow is discontinuous at this portion and a separation flow is generated, so that the blowing noise increases. There is a problem. Furthermore, since the rib extends from the suction side to the discharge side in a region not surrounded by the orifice, the flow of airflow sucked into the blades from above the orifice toward the motor shaft is obstructed. Thereby, there exists a problem that the flow of airflow becomes unstable and ventilation noise increases.

この発明は、上記の問題を解決するためになされたものであり、送風性能を低下(劣化)させることなく送風騒音を小さく抑えることのできる軸流送風機を得ることを目的とする。   This invention was made in order to solve said problem, and it aims at obtaining the axial flow fan which can suppress ventilation noise small, without reducing ventilation performance.

軸心まわりに回転されるボス、及びボスの外周面に配設されて、それぞれボスの外周面との接合部位となる付け根縁部、ボスの軸心を中心とする所定の半径の円に沿って所定の長さを有する外周縁部、付け根縁部及び外周縁部の回転方向の前端同士を接続する前縁部、及び付け根縁部及び外周縁部の回転方向の後端同士を接続する後縁部に囲まれた形状に形成された複数枚の翼を有する羽根車と、ボスと同軸に配置され、一側の開口から翼の回転方向前端側を突出させて、翼の回転方向後端側を囲繞するベルマウスと、ベルマウスの一側の開口から突出する翼の負圧面の部位に突設されたリブと、を備え、リブは、リブ前端を外周縁部の回転方向の前端から所定距離だけ離間した前縁部の部位、又はその近傍に連結され、リブ後端を外周縁部の回転方向の前端から所定距離だけ離間した外周縁部の部位に連結され、かつ、リブの突出端面のリブ後端側が、負圧面からの高さを漸次低くしてリブ後端で負圧面に一致する滑らかな連続する曲面に形成されていることを特徴とする。   A boss that is rotated around the axis, and a base edge that is disposed on the outer peripheral surface of the boss and serves as a joint portion with the outer peripheral surface of the boss, along a circle with a predetermined radius centered on the boss axis. After connecting the outer peripheral edge having a predetermined length, the base edge and the front edge of the outer peripheral edge in the rotational direction, and connecting the rear edge of the root edge and the outer peripheral edge in the rotational direction An impeller having a plurality of blades formed in a shape surrounded by an edge portion, and arranged coaxially with the boss, protruding from the opening on one side to the front end side in the rotation direction of the blade, and the rear end in the rotation direction of the blade A bell mouth surrounding the side, and a rib projecting from a suction surface portion of the wing projecting from an opening on one side of the bell mouth, wherein the rib has a front end of the rib from a front end in the rotation direction of the outer peripheral edge. Connected to the vicinity of the front edge part separated by a predetermined distance or the vicinity thereof, the rear end of the rib is the outer peripheral edge part It is connected to a part of the outer peripheral edge that is separated from the front end in the rotation direction by a predetermined distance, and the rib rear end side of the protruding end surface of the rib is gradually lowered from the suction surface to coincide with the suction surface at the rib rear end. It is characterized by being formed into a smooth continuous curved surface.

この発明によれば、軸流送風機の送風騒音を、送風性能を低下させることなく小さく抑えることができる。 According to this invention, the blowing noise of the axial-flow fan can be suppressed to a low level without reducing the blowing performance.

以下、この発明を実施するための最良の形態について、図面を参照して説明する。
図1はこの発明に係る軸流送風機の斜視図、図2はこの発明に係る軸流送風機の正面図、図3は図2のIII−III矢視要部断面図、図4はこの発明に係る軸流送風機のボスの軸心から翼の外周縁部までの距離と同じ半径を有し、翼及びリブを囲繞するようにボスの軸心と同軸に配置された円筒面に、ボスの軸心を中心とする径方向に翼、リブ、及びベルマウスを投影した後に円筒面を平面上に展開した側面図、図5はこの発明に係る軸流送風機において発生する翼端渦の流れを概念的に示す図である。図6はこの発明に係る軸流送風機におけるIb/Ifと比騒音差ΔKsとの関係を示す図、図7はこの発明に係る軸流送風機におけるt/laと比騒音差ΔKsとの関係を示す図、図8はこの発明の軸流送風機におけるRw/(Rw+Rr)と比騒音差ΔKsとの関係を示す図、図9は比較例の軸流送風機の斜視図、図10は比較例の軸流送風機において発生する翼端渦の流れを概念的に示す図である。
The best mode for carrying out the present invention will be described below with reference to the drawings.
1 is a perspective view of an axial blower according to the present invention, FIG. 2 is a front view of the axial blower according to the present invention, FIG. 3 is a sectional view taken along the line III-III in FIG. 2, and FIG. The axis of the boss has a radius that is the same as the distance from the axial center of the boss of the axial flow fan to the outer peripheral edge of the blade, and is arranged coaxially with the axial center of the boss so as to surround the blade and the rib. FIG. 5 is a side view in which a cylindrical surface is developed on a plane after projecting blades, ribs, and bellmouths in the radial direction centered on the center, and FIG. 5 is a conceptual view of the flow of blade tip vortices generated in the axial blower according to the present invention. FIG. FIG. 6 is a diagram showing the relationship between Ib / If and specific noise difference ΔKs in the axial fan according to the present invention, and FIG. 7 shows the relationship between t / la and specific noise difference ΔKs in the axial fan according to the present invention. 8 is a diagram showing the relationship between Rw / (Rw + Rr) and the specific noise difference ΔKs in the axial fan according to the present invention, FIG. 9 is a perspective view of the axial fan of the comparative example, and FIG. 10 is the axial flow of the comparative example. It is a figure which shows notionally the flow of the blade tip vortex which generate | occur | produces in an air blower.

図1〜図4において、軸流送風機1は、羽根車2、ベルマウス6、及びリブ5を備えている。
羽根車2は、ボス3、及びボス3の外周面に周方向に設けられた3枚の翼4を備えている。なお、図示しないモータの回転軸が、ボス3に同軸に配設されており、翼4はモータの駆動に連動してボス3の軸心まわりに回転するようになっている。
1 to 4, the axial blower 1 includes an impeller 2, a bell mouth 6, and a rib 5.
The impeller 2 includes a boss 3 and three blades 4 provided on the outer peripheral surface of the boss 3 in the circumferential direction. A rotating shaft of a motor (not shown) is disposed coaxially with the boss 3, and the blade 4 rotates around the axis of the boss 3 in conjunction with the driving of the motor.

そして、翼4は、図2に示されるように、ボス3の外周面との接合部位となる付け根縁部4a、ボス3の軸心を中心とする所定の半径の円に沿って所定の長さを有する外周縁部4b、付け根縁部4a及び外周縁部4bの回転方向前端同士を接続する前縁部4c、及び付け根縁部4a及び外周縁部4bの回転方向後端同士を接続する後縁部4dに囲まれた形状に形成されている。また、それぞれの翼4の主面のボス3の軸方向の高さ位置が、翼4の回転方向の後方に向かうほど、かつ、径方向の中心に向かうほど、ボス3の軸心方向の一方から他方に向かうように翼4の主面が傾斜されている。   As shown in FIG. 2, the wing 4 has a predetermined length along a circle having a predetermined radius centered on the base of the base 4 a and the boss 3, which is a joint portion with the outer peripheral surface of the boss 3. After connecting the front edge part 4c which connects the rotation direction front ends of the outer peripheral edge part 4b, the base edge part 4a, and the outer peripheral edge part 4b, and the rotation direction rear ends of the base edge part 4a and the outer peripheral edge part 4b. It is formed in a shape surrounded by the edge 4d. In addition, the axial height of the boss 3 on the main surface of each blade 4 increases in the axial direction of the boss 3 toward the rear in the rotational direction of the blade 4 and toward the center in the radial direction. The main surface of the wing 4 is inclined so as to face the other side.

ベルマウス6は、円筒形状を有し、羽根車2を囲繞するようにボス3と同軸に配置されている。このとき、図2において、翼4の外周縁部4bとベルマウス6の内周面との間は、ベルマウス6の径方向に所定の隙間を有している。また、図1、図3、及び図4において、翼4の回転方向の前端側が、ベルマウス6の一側の開口から突出され、また、翼4の回転方向の後端側がベルマウス6に囲繞されている。これにより、翼4が回転されたときには、翼4の主面のうちボス3の軸心方向(翼4の回転軸方向)の一側の面が負圧面4eとなり、ボス3の軸心方向の他側の面が正圧面4fとなる。即ち、翼4が回転されると、図3の白抜き矢印に示したように、空気がベルマウス6の他側の開口から送風されるようになっている。   The bell mouth 6 has a cylindrical shape and is arranged coaxially with the boss 3 so as to surround the impeller 2. At this time, in FIG. 2, there is a predetermined gap in the radial direction of the bell mouth 6 between the outer peripheral edge 4 b of the wing 4 and the inner peripheral surface of the bell mouth 6. 1, 3, and 4, the front end side in the rotational direction of the wing 4 protrudes from an opening on one side of the bell mouth 6, and the rear end side in the rotational direction of the wing 4 surrounds the bell mouth 6. Has been. As a result, when the blade 4 is rotated, the surface on one side of the main surface of the blade 4 in the axial direction of the boss 3 (the rotational axis direction of the blade 4) becomes the negative pressure surface 4e. The other surface is the positive pressure surface 4f. That is, when the wing 4 is rotated, air is blown from the opening on the other side of the bell mouth 6 as shown by the white arrow in FIG.

また、リブ5は板状部材であり、翼4の負圧面4eに対して上に凸になるように、かつ、概略垂直に突出するように負圧面4eに取り付けられている。このとき、リブ前端5aが、外周前縁端4g(外周縁部4bの回転方向の前端)から所定距離だけ離間した前縁部4cの部位に配置され、リブ後端5bが外周前縁端4gから所定距離だけ離間した外周縁部4bの部位に配置されている。即ち、リブ5は、リブ前端5aが外周縁部4bより内周側の前縁部4cの所定部位に一致させた状態で負圧面4eに連結されるように、かつ、リブ後端5bが外周前縁端4gから回転方向後端に所定距離だけ離間した外周縁部4bの部位に滑らかに一致させた状態で負圧面4eに連結されるように取り付けられている。   The rib 5 is a plate-like member, and is attached to the negative pressure surface 4e so as to protrude upward with respect to the negative pressure surface 4e of the blade 4 and to protrude substantially vertically. At this time, the rib front end 5a is disposed at a portion of the front edge 4c that is separated from the outer peripheral front edge 4g (the front end in the rotation direction of the outer peripheral edge 4b) by a predetermined distance, and the rib rear end 5b is the outer front edge 4g. Is disposed at a portion of the outer peripheral edge portion 4b that is separated by a predetermined distance. That is, the rib 5 is connected to the negative pressure surface 4e in a state where the rib front end 5a is aligned with a predetermined portion of the front edge portion 4c on the inner peripheral side from the outer peripheral edge portion 4b, and the rib rear end 5b is It is attached so as to be connected to the suction surface 4e in a state where it is smoothly aligned with a portion of the outer peripheral edge portion 4b spaced from the front edge 4g by a predetermined distance from the rear edge in the rotational direction.

また、負圧面4eから突出されたリブ5の突出側の端面(以降、突出端面5dと記載する)は、負圧面4eに一致するリブ前端5aから、負圧面4eからの高さを漸次高くして中間部5cで最も負圧面4eからの高さが高くなり、中間部5cからリブ後端5bに向かうにつれて負圧面4eからの高さを漸次低くしてリブ後端5bで負圧面4eに一致する滑らかな連続する曲面に形成されている。   Further, the end surface on the protruding side of the rib 5 protruding from the negative pressure surface 4e (hereinafter referred to as a protruding end surface 5d) gradually increases the height from the negative pressure surface 4e from the rib front end 5a coinciding with the negative pressure surface 4e. The height from the negative pressure surface 4e is highest at the intermediate portion 5c, and the height from the negative pressure surface 4e is gradually decreased toward the rib rear end 5b from the intermediate portion 5c to coincide with the negative pressure surface 4e at the rib rear end 5b. It is formed into a smooth continuous curved surface.

また、リブ後端5bにおけるボス3の軸心方向(即ち、ベルマウス6の軸方向)の高さ位置は、ベルマウス6の一側の開口からボス3の軸心方向の一側に向かって所定の距離だけ離間した場所にある。   Further, the height position of the boss 3 in the axial direction of the boss 3 (that is, the axial direction of the bell mouth 6) at the rib rear end 5 b is from the opening on one side of the bell mouth 6 toward one side in the axial direction of the boss 3. It is in a place separated by a predetermined distance.

次いで、翼端渦について図5を参照しつつ詳細に説明する。
上記のように構成された軸流送風機1では、翼4が回転されると、翼端渦7と呼ばれる渦状の空気の流れが、翼4の負圧面4e側と前述の正圧面4f側との圧力差に起因して、負圧面4eの前縁部4cの外周縁部4b側にまず発生する。発生された翼端渦7は、負圧面4e上を前縁部4cから後縁部4dに向かうように、外周縁部4bに沿って移動しながら漸次発達する。しかしながら、翼端渦7は、負圧面4e上を周方向に移動してリブ5に到達し、さらに、リブ5の壁面に沿って径方向の外方に向かうように移動方向を変え、ついには外周縁部4bから径方向の外方に離脱する。即ち、翼端渦7は、大きく発達する前に負圧面4eから離脱される。
Next, the blade tip vortex will be described in detail with reference to FIG.
In the axial blower 1 configured as described above, when the blade 4 is rotated, a spiral air flow called a blade tip vortex 7 is generated between the suction surface 4e side of the blade 4 and the above-described pressure surface 4f side. Due to the pressure difference, it first occurs on the outer peripheral edge 4b side of the front edge 4c of the negative pressure surface 4e. The generated blade tip vortex 7 gradually develops while moving along the outer peripheral edge 4b from the front edge 4c toward the rear edge 4d on the suction surface 4e. However, the blade tip vortex 7 moves in the circumferential direction on the suction surface 4e to reach the rib 5, and further changes the moving direction so as to go radially outward along the wall surface of the rib 5, and finally Detach from the outer peripheral edge 4b outward in the radial direction. That is, the blade tip vortex 7 is detached from the suction surface 4e before it greatly develops.

なお、図示しないが、翼端渦は、リブ5の配置位置より後縁部4d側かつ外周縁部4b側の負圧面4eの部位でも発生してベルマウス6内に向かうが、リブ5の配置位置から後縁部4dまでの距離が短くなっているので、翼端渦は大きく発達することがなくベルマウス6に流出入する気流を大きく乱すことがない。   Although not shown in the figure, the blade tip vortex is also generated at the portion of the negative pressure surface 4e on the rear edge 4d side and the outer peripheral edge 4b side from the position where the rib 5 is disposed and is directed into the bell mouth 6, but the rib 5 is disposed. Since the distance from the position to the trailing edge 4d is shortened, the blade tip vortex does not develop greatly, and the airflow flowing into and out of the bell mouth 6 is not greatly disturbed.

この発明の軸流送風機1によれば、リブ前端5aの位置は、前縁部4cのうち、外周前縁端4gから所定距離だけ離間した部位に配置されている。従って、翼4の回転軸からのリブ前端5aまでの距離が、翼4の回転軸から外周縁部4bまでの距離に比べて短くなっている。従って、軸流送風機1のリブ前端5aから翼4に流入する気流のリブ5に対する相対速度は、外周端部(縁部)に沿って取り付けられていた従来の軸流送風機のリブの前端から羽根(翼)に流入する気流のリブに対する相対速度に比べて遅くなる。即ち、軸流送風機1のリブ5で発生する送風騒音を小さく抑えることができる。   According to the axial blower 1 of the present invention, the position of the rib front end 5a is disposed in a portion of the front edge portion 4c that is separated from the outer peripheral front edge end 4g by a predetermined distance. Therefore, the distance from the rotating shaft of the blade 4 to the rib front end 5a is shorter than the distance from the rotating shaft of the blade 4 to the outer peripheral edge 4b. Therefore, the relative velocity of the airflow flowing into the blade 4 from the rib front end 5a of the axial blower 1 with respect to the rib 5 is reduced from the front end of the rib of the conventional axial blower attached along the outer peripheral end (edge). It becomes slower than the relative velocity of the airflow flowing into the (wing) with respect to the rib. That is, the blowing noise generated at the rib 5 of the axial blower 1 can be reduced.

また、前述したように、従来の軸流送風機では、リブにおける翼の反回転方向側の端部(リブの後端)が、翼の負圧面からステップ状に高さが高くなっていた。この場合、リブの後端では、ステップ状に高くなっていたリブの壁が突然なくなるので、気流の不連続が生じて激しく渦が放出されるため、送風騒音を増大させる要因となっていた。   Further, as described above, in the conventional axial blower, the height of the end portion of the rib on the side opposite to the rotation direction of the blade (the rear end of the rib) is increased stepwise from the suction surface of the blade. In this case, at the rear end of the rib, the rib wall that has been raised stepwise suddenly disappears, causing a discontinuity in the air flow and violent vortices, which increases the blowing noise.

一方、軸流送風機1では、リブ5の突出端面5dは、負圧面4eに一致するリブ前端5aから漸次高さを高くして、中間部5cで負圧面4eからの高さが最も高くなり、中間部5cからリブ後端5bに向かうにつれて負圧面4eからの高さを漸次低くしてリブ後端5bで負圧面4eに一致する滑らかな連続する曲面に形成されている。従って、リブ5の負圧面4eに対する高さはステップ状に変化することがないので、気流はリブ5の壁面に沿って流れるときも不連続になることが極力抑制され、渦放出が発生することを回避できる。即ち、軸流送風機1の送風騒音を、送風性能を低下させることなく小さく抑えることができる。   On the other hand, in the axial blower 1, the protruding end surface 5d of the rib 5 gradually increases in height from the rib front end 5a coinciding with the negative pressure surface 4e, and the height from the negative pressure surface 4e becomes the highest at the intermediate portion 5c, The height from the suction surface 4e is gradually lowered from the intermediate portion 5c toward the rib rear end 5b, and the rib rear end 5b is formed into a smooth continuous curved surface that matches the suction surface 4e. Therefore, since the height of the rib 5 with respect to the suction surface 4e does not change in a step shape, the airflow is suppressed from being discontinuous as much as possible when flowing along the wall surface of the rib 5, and vortex shedding occurs. Can be avoided. That is, the blowing noise of the axial blower 1 can be suppressed to a low level without reducing the blowing performance.

また、負圧面4eの前縁部4cの外周縁部4b側に発生した翼端渦7は、大きく発達する前に、外周縁部4bのリブ後端5bの配置部位で負圧面4eから離脱されるので、翼端渦7による気流の乱れを抑えることができる。即ち、軸流送風機1の送風騒音を、送風性能を低下させることなく小さく抑えることができる。さらに、リブ5が、ベルマウス6から突出された翼4の負圧面4eに突設され、リブ後端5bのボス3の軸心方向の高さ位置が、ベルマウス6の一端面から所定の距離だけ離反された場所にある。従って、気流の横吸い流れがリブ5の配設によって阻害されることなく確保されるので、気流の乱れを誘発することがなく、軸流送風機1の送風騒音を、送風性能を低下させることなく小さく抑えることができる。   Further, the blade tip vortex 7 generated on the outer peripheral edge 4b side of the front edge portion 4c of the negative pressure surface 4e is separated from the negative pressure surface 4e at the arrangement portion of the rib rear end 5b of the outer peripheral edge portion 4b before it greatly develops. Therefore, the turbulence of the airflow due to the blade tip vortex 7 can be suppressed. That is, the blowing noise of the axial blower 1 can be suppressed to a low level without reducing the blowing performance. Furthermore, the rib 5 projects from the suction surface 4 e of the wing 4 projecting from the bell mouth 6, and the height position of the rib rear end 5 b in the axial direction of the boss 3 is predetermined from one end surface of the bell mouth 6. It is in a place separated by a distance. Accordingly, since the lateral suction flow of the air current is ensured without being obstructed by the arrangement of the rib 5, the air current is not disturbed, and the air blowing noise of the axial blower 1 is reduced without reducing the air blowing performance. It can be kept small.

次いで、リブ5を取り付けたことを特徴とする本発明の効果を試験により確認したので、以下にその内容を具体的に説明する。試験は比較例の軸流送風機を用意し、軸流送風機1の比騒音(後述)と比較例の軸流送風機11の比騒音を各種条件で測定し、それぞれの結果を対比することにより行った。
比較例の軸流送風機11は図9に示されるように、リブ5が省略されている点を除いて軸流送風機1と同様に構成されている。
Next, since the effect of the present invention characterized by attaching the rib 5 was confirmed by a test, the contents thereof will be specifically described below. The test was performed by preparing an axial blower of a comparative example, measuring specific noise (described later) of the axial blower 1 and specific noise of the axial blower 11 of the comparative example under various conditions, and comparing the results. .
As shown in FIG. 9, the axial blower 11 of the comparative example is configured in the same manner as the axial blower 1 except that the rib 5 is omitted.

まず、軸流送風機1における翼前後端距離If、翼内包部距離Ib、リブ最大高さt、翼前後端長la、リブ前後端長Rw、及びリブ−ベルマウス間長Rrについてそれぞれ図4を参照しつつ説明する。   First, FIG. 4 shows the blade front-and-rear end distance If, the blade inner portion distance Ib, the rib maximum height t, the blade front-and-rear end length la, the rib front-and-rear end length Rw, and the rib-bell mouth length Rr in the axial blower 1. This will be described with reference to FIG.

翼前後端距離Ifは、翼4の回転軸方向における翼4の外周前縁端4gと外周後縁端4h(外周縁部4bの回転方向の後端)との間の距離であり、翼内包部距離Ibは、ボス3の軸心方向における翼4の外周後縁端4hとベルマウス6の一端面との間の距離である。また、リブ最大高さtは、翼4の負圧面4eの法線方向におけるリブ5の翼4の負圧面4eからの最大の高さであり、翼前後端長laは、ボス3の軸心から翼4の外周縁部4bまでの距離と同じ半径を有し、翼4及びリブ5を囲繞するようにボス3の軸心と同軸に配置された円筒面に、ボス3の軸心を中心とする径方向に翼4、リブ5、及びベルマウス6を投影した後に円筒面を平面上に展開した側面図において,翼4の外周前縁端4gと外周後縁端4hを結ぶ直線の長さである。また、図2にも示されるように、リブ前後端長Rwは、リブ前端5aからリブ後端5bに至るまでの翼4の負圧面4e上での長さであり、リブ−ベルマウス間長Rrはリブ後端5bが位置する翼4の外周縁部4bの部位から、ボス3の軸心方向の高さ位置がベルマウス6の一端面と同じである外周縁部4bの部位までの外周縁部4bに沿った(周方向の)長さである。なお、翼前後端距離If及び翼内包部距離Ibは比較例の軸流送風機11においても同様に定義される。以降、翼前後端距離If、翼内包部距離Ib、リブ最大高さt、翼前後端長la、リブ前後端長Rw、及びリブ−ベルマウス間長Rrは符号のみを記載して説明する。   The blade front and rear end distance If is the distance between the outer peripheral front edge 4g and the outer peripheral rear edge 4h (the rear end in the rotational direction of the outer peripheral edge 4b) of the blade 4 in the rotational axis direction of the blade 4, The partial distance Ib is a distance between the outer peripheral trailing edge 4 h of the wing 4 and one end face of the bell mouth 6 in the axial direction of the boss 3. The rib maximum height t is the maximum height of the rib 5 from the suction surface 4e of the blade 4 in the normal direction of the suction surface 4e of the blade 4, and the blade front and rear end length la is the axis of the boss 3. The center of the axis of the boss 3 is centered on a cylindrical surface having the same radius as the distance from the outer peripheral edge 4b of the wing 4 and arranged coaxially with the axis of the boss 3 so as to surround the wing 4 and the rib 5. The length of the straight line connecting the outer peripheral leading edge 4g and the outer trailing edge 4h of the blade 4 in a side view in which the cylindrical surface is developed on a plane after projecting the blade 4, the rib 5 and the bell mouth 6 in the radial direction That's it. Also, as shown in FIG. 2, the rib front and rear end length Rw is the length on the suction surface 4e of the blade 4 from the rib front end 5a to the rib rear end 5b, and is the rib-bell mouth length. Rr is an outer region from the outer peripheral edge portion 4b of the wing 4 where the rib rear end 5b is located to the outer peripheral edge portion 4b where the axial position of the boss 3 is the same as the one end surface of the bell mouth 6. It is the length (in the circumferential direction) along the peripheral edge 4b. The blade front and rear end distance If and the blade inner blade portion distance Ib are similarly defined in the axial flow fan 11 of the comparative example. Hereinafter, the blade front / rear end distance If, the blade inner portion distance Ib, the rib maximum height t, the blade front / rear end length la, the rib front / rear end length Rw, and the rib-bell mouth length Rr will be described by describing only the reference numerals.

そして、軸流送風機1と比較例の軸流送風機11に対して次の評価を行った。
まず、軸流送風機1の比騒音Ksと比較例の軸流送風機11の比騒音KsをそれぞれIb/Ifをパラメータとして測定した。比騒音Ksは、軸流送風機から吹き出される気流が単位風量で単位圧力であるときの送風騒音の大きさを表すものであり、比騒音Ksの値が大きいほど軸流送風機の送風騒音が大きいことを意味する。比騒音Ksは以下の式(1)により表される。
Ks=SPL−10log(Ps2.5Q)・・・(1)
ここで、SPLは騒音レベル、Psは静圧、Qは風量をそれぞれ示している。
なお、騒音レベルSPLの測定はJIS8346に準拠している。
And the following evaluation was performed with respect to the axial-flow fan 1 and the axial-flow fan 11 of a comparative example.
First, the specific noise Ks of the axial fan 1 and the specific noise Ks of the axial fan 11 of the comparative example were measured using Ib / If as a parameter. The specific noise Ks represents the magnitude of the blowing noise when the airflow blown from the axial blower is unit pressure and unit pressure. The larger the specific noise Ks, the larger the blowing noise of the axial blower. Means that. The specific noise Ks is expressed by the following equation (1).
Ks = SPL-10 log (Ps 2.5 Q) (1)
Here, SPL represents the noise level, Ps represents the static pressure, and Q represents the air volume.
The measurement of the noise level SPL conforms to JIS8346.

比騒音Ksの測定結果から得られた軸流送風機1の比騒音差ΔKsとIb/Ifとの関係を図6に実線で示す。
ここで、比騒音差ΔKsは、軸流送風機1で観測された比騒音Ksと比較例の軸流送風機11が最も低騒音となるIb/Ifの値での比騒音Ksとの差として表したものである。
なお、図6中、点線は比較例の軸流送風機11で観測された比騒音Ksと比較例の軸流送風機11が最も低騒音となるIb/Ifの値での比騒音Ksとの差を比騒音差ΔKsとして示している。即ち、比較例の軸流送風機11の比騒音差ΔKsは、比較例の軸流送風機11が最も低騒音となるIb/Ifの値での比騒音Ksを0[dBA]として規格化したものと同一である。
The relationship between the specific noise difference ΔKs of the axial fan 1 obtained from the measurement result of the specific noise Ks and Ib / If is shown by a solid line in FIG.
Here, the specific noise difference ΔKs is expressed as a difference between the specific noise Ks observed in the axial blower 1 and the specific noise Ks at the value of Ib / If at which the axial blower 11 of the comparative example has the lowest noise. Is.
In FIG. 6, the dotted line shows the difference between the specific noise Ks observed in the axial flow fan 11 of the comparative example and the specific noise Ks at the Ib / If value at which the axial flow fan 11 of the comparative example produces the lowest noise. It is shown as a specific noise difference ΔKs. That is, the specific noise difference ΔKs of the axial flow fan 11 of the comparative example is normalized by setting the specific noise Ks at the value of Ib / If at which the axial flow fan 11 of the comparative example has the lowest noise as 0 [dBA]. Are the same.

図6に示されるように、比騒音差ΔKsは、Ib/Ifを0.15近傍から0.5まで連続して変化させたときには、下に凸の形状で連続して変化する特性を有し、Ib/Ifがおおよそ0.3の値のときに最小値となった。そして、同じIb/Ifの値であれば、軸流送風機1の比騒音差ΔKsは比較例の軸流送風機11の比騒音差ΔKsより小さい値となった。また、Ib/Ifが、0.23<Ib/If<0.42の範囲にある場合、軸流送風機1の比騒音差ΔKsは0[dBA]より小さくなった。   As shown in FIG. 6, the specific noise difference ΔKs has a characteristic of continuously changing in a downwardly convex shape when Ib / If is continuously changed from near 0.15 to 0.5. When Ib / If is approximately 0.3, the minimum value is obtained. And if it was the same value of Ib / If, the specific noise difference (DELTA) Ks of the axial flow fan 1 became a value smaller than the specific noise difference (DELTA) Ks of the axial flow fan 11 of a comparative example. In addition, when Ib / If is in the range of 0.23 <Ib / If <0.42, the specific noise difference ΔKs of the axial blower 1 is smaller than 0 [dBA].

次いで、上記結果を考察する。
上述したように、負圧面4eの前縁部4cの外周縁部4b側に発生した翼端渦7は大きく発達する前に、負圧面4eから離脱されるので、翼端渦7による気流の乱れが抑制され、軸流送風機1の比騒音Ksが小さく抑えられる。
The above results are then considered.
As described above, since the blade tip vortex 7 generated on the outer peripheral edge 4b side of the leading edge 4c of the suction surface 4e is separated from the suction surface 4e before it develops greatly, the turbulence of the air flow due to the blade tip vortex 7 Is suppressed, and the specific noise Ks of the axial blower 1 is reduced.

一方、比較例の軸流送風機11では、図10に示されるように、リブ5が配設されていないので負圧面4eにおける前縁部4cの外周縁部4b側で発生した翼端渦12は、翼4の外周縁部4bから離脱されることなく、前縁部4cから後縁部4dに向かって周方向に負圧面4e上を移動しつつ漸次発達する。即ち、発達した翼端渦12がベルマウス6に流出入する気流を乱すので、比較例の軸流送風機11の比騒音Ksが増大される。
従って、同じIb/Ifの値であれば、軸流送風機1の比騒音差ΔKsは比較例の軸流送風機11の比騒音差ΔKsより小さい値となる。
On the other hand, in the axial blower 11 of the comparative example, as shown in FIG. 10, since the rib 5 is not provided, the blade tip vortex 12 generated on the outer peripheral edge 4b side of the front edge 4c on the negative pressure surface 4e is The blade 4 gradually develops while moving on the suction surface 4e in the circumferential direction from the front edge 4c toward the rear edge 4d without being separated from the outer peripheral edge 4b of the blade 4. That is, since the developed blade tip vortex 12 disturbs the airflow flowing into and out of the bell mouth 6, the specific noise Ks of the axial blower 11 of the comparative example is increased.
Therefore, if the Ib / If values are the same, the specific noise difference ΔKs of the axial flow fan 1 is smaller than the specific noise difference ΔKs of the axial flow fan 11 of the comparative example.

また、軸流送風機1の送風騒音が、最も小さくなるIb/Ifの値から、徐々にIb/Ibを小さくしていくと、言い換えればベルマウス6に囲繞される翼4の領域の割合を徐々に小さくしていくと、十分な静圧上昇が得られなくなり、送風性能が低下して、比騒音差ΔKsは増大する。   Further, when Ib / Ib is gradually reduced from the value of Ib / If at which the blowing noise of the axial flow fan 1 becomes the smallest, in other words, the ratio of the region of the blade 4 surrounded by the bell mouth 6 is gradually increased. If it is made smaller, a sufficient increase in static pressure cannot be obtained, the blowing performance is lowered, and the specific noise difference ΔKs increases.

なお、軸流送風機1の送風性能が低下するとは、軸流送風機1で観測された比騒音Ksが最も小さくなる条件に対してのものである。軸流送風機1の比騒音差ΔKsが、比較例の軸流送風機11の比騒音差ΔKsより小さいことからもわかるように、軸流送風機1の送風性能は、Ib/Ifが同じ値であれば、比較例の軸流送風機11の送風性能より向上されている。   In addition, that the ventilation performance of the axial-flow fan 1 is reduced is that the specific noise Ks observed in the axial-flow fan 1 is minimized. As can be seen from the fact that the specific noise difference ΔKs of the axial flow fan 1 is smaller than the specific noise difference ΔKs of the axial flow fan 11 of the comparative example, the blowing performance of the axial flow fan 1 is equal to Ib / If. The air blowing performance of the axial blower 11 of the comparative example is improved.

そして、Ib/If=0.23となったところで、軸流送風機1の比騒音Ksは、比較例の軸流送風機11において最も低騒音となるIb/Ifの値での比騒音Ksと同じになり、Ib/Ifを0.23よりさらに小さくすると比較例の軸流送風機11の比騒音Ksの最小値より軸流送風機1の比騒音Ksが大きくなるので、比騒音差ΔKsが0[dBA]より大きくなる。   When Ib / If = 0.23, the specific noise Ks of the axial flow fan 1 is the same as the specific noise Ks at the value of Ib / If at which the axial flow fan 11 of the comparative example has the lowest noise. Thus, when Ib / If is made smaller than 0.23, the specific noise Ks of the axial fan 1 becomes larger than the minimum value of the specific noise Ks of the axial fan 11 of the comparative example, so that the specific noise difference ΔKs is 0 [dBA]. Become bigger.

また、軸流送風機1の送風騒音が最も小さくなるIb/Ifの値から、Ib/Ifの値を大きくしていくと、言い換えればベルマウス6に囲繞される翼の領域の割合を大きくしていくと、軸流送風機1の送風性能は、リブ5によって正圧面4fから負圧面4eに巻き上がろうとする気流の流れが阻害されることに起因する圧力損失が増大するために徐々に低下する。即ち、比騒音Ksが増大する。そして、Ib/If=0.42となったところで、軸流送風機1の比騒音Ksが比較例の軸流送風機11において最も低騒音となる条件での比騒音Ksと同じになり、Ib/Ifを0.42よりさらに大きくすると比較例の軸流送風機11の比騒音Ksの最小値より軸流送風機1の比騒音Ksが大きくなり、比騒音差ΔKsが0[dBA]より大きくなる。   Further, when the value of Ib / If is increased from the value of Ib / If where the blowing noise of the axial blower 1 is minimized, in other words, the ratio of the region of the wing surrounded by the bell mouth 6 is increased. Then, the air blowing performance of the axial blower 1 gradually decreases due to an increase in pressure loss due to the flow of air flowing to the negative pressure surface 4e from the positive pressure surface 4f being hindered by the ribs 5. . That is, the specific noise Ks increases. When Ib / If = 0.42, the specific noise Ks of the axial blower 1 is the same as the specific noise Ks under the condition that the lowest noise is obtained in the axial blower 11 of the comparative example, and Ib / If Is made larger than 0.42, the specific noise Ks of the axial fan 1 becomes larger than the minimum value of the specific noise Ks of the axial fan 11 of the comparative example, and the specific noise difference ΔKs becomes larger than 0 [dBA].

翼4が0.23<Ib/If<0.42を満足するように形成されていれば、過度に静圧上昇を低下させることがなく、また、過度にリブ5によって正圧面4fから負圧面4eに巻き上がろうとする気流の流れを阻害することもない。従って、0.23<Ib/If<0.42であれば、軸流送風機1の送風性能の低下に対して、翼端渦7の発達を抑える効果が大きいので、比騒音差ΔKsが0[dBA]より小さくなる。   If the blade 4 is formed so as to satisfy 0.23 <Ib / If <0.42, the static pressure rise is not excessively reduced, and the rib 5 excessively reduces the pressure surface 4f to the suction surface. It does not hinder the flow of airflow that is going to wind up to 4e. Therefore, if 0.23 <Ib / If <0.42, the effect of suppressing the development of the blade tip vortex 7 is great against the deterioration of the blowing performance of the axial blower 1, so that the specific noise difference ΔKs is 0 [ dBA].

次いで、軸流送風機1の比騒音Ksをt/laをパラメータとして測定した。測定結果から得られたt/laと比騒音差ΔKsとの関係を図7に示す。
図7中、軸流送風機1の比騒音差ΔKsを実線で示し、また、比較例の軸流送風機11において、最も低騒音となる条件での比騒音差ΔKs(即ちΔKs=0[dBA])のみを点線で併記している。
図7に示されるように、比騒音差ΔKsは、t/laを0から連続して増大させるように変化させたときに、下に凸の形状で連続して変化する特性を有し、t/laがおおよそ0.16のときに最小値となる。また、0<t/la<0.025の範囲のときに、比騒音差ΔKsが0[dBA]より小さくなって、送風騒音を効果的に低減できる。
Next, the specific noise Ks of the axial fan 1 was measured using t / la as a parameter. FIG. 7 shows the relationship between t / la obtained from the measurement result and the specific noise difference ΔKs.
In FIG. 7, the specific noise difference ΔKs of the axial flow fan 1 is shown by a solid line, and in the axial flow fan 11 of the comparative example, the specific noise difference ΔKs (ie, ΔKs = 0 [dBA]) under the lowest noise condition. Are shown with dotted lines.
As shown in FIG. 7, the specific noise difference ΔKs has a characteristic of continuously changing in a downwardly convex shape when t / la is continuously increased from 0, and t The minimum value is obtained when / la is approximately 0.16. Further, when 0 <t / la <0.025, the specific noise difference ΔKs becomes smaller than 0 [dBA], and the blowing noise can be effectively reduced.

次いで、上記結果を考察する。
リブ5が、0<t/la<0.025を満足するように翼4に配設されている場合、laに対してtが適度な高さであり、リブ5を取り付けたことによって発生する壁面摩擦等による圧力損失は小さくなる。従って、軸流送風機1の送風性能の低下に対して、翼端渦7の発達を抑える効果が大きいので、比騒音差ΔKsが0[dBA]より小さくなる。
一方、t/la≧0.025では、laに対してリブの高さが高くなりすぎて、前記圧力損失が増大するために送風性能が低下し、比騒音差ΔKsが0[dBA]以上になる。
The above results are then considered.
When the rib 5 is disposed on the blade 4 so as to satisfy 0 <t / la <0.025, t is an appropriate height with respect to la, and is generated by attaching the rib 5. Pressure loss due to wall friction or the like is reduced. Therefore, since the effect of suppressing the development of the blade tip vortex 7 is great against the deterioration of the blowing performance of the axial blower 1, the specific noise difference ΔKs becomes smaller than 0 [dBA].
On the other hand, at t / la ≧ 0.025, the rib height becomes too high with respect to la, and the pressure loss increases, so the blowing performance decreases, and the specific noise difference ΔKs becomes 0 [dBA] or more. Become.

次いで、軸流送風機1の比騒音KsをRw/(Rw+Rr)をパラメータとして測定した。測定結果から得られたRw/(Rw+Rr)と比騒音差ΔKsとの関係を図8に示す。
図8中、軸流送風機1の比騒音差ΔKsを実線で示し、また、比較例の軸流送風機において、最も低騒音となる条件での比騒音差ΔKs(即ちΔKs=0[dBA])のみを点線で併記している。
Next, the specific noise Ks of the axial blower 1 was measured using Rw / (Rw + Rr) as a parameter. FIG. 8 shows the relationship between Rw / (Rw + Rr) obtained from the measurement results and the specific noise difference ΔKs.
In FIG. 8, the specific noise difference ΔKs of the axial flow fan 1 is shown by a solid line, and only the specific noise difference ΔKs (that is, ΔKs = 0 [dBA]) under the lowest noise condition in the axial flow fan of the comparative example. Are shown with dotted lines.

図8に示されるように、比騒音差ΔKsは、Rw/(Rw+Rr)を0から1まで連続して変化させたときに、下に凸の形状で連続して変化する特性を有し、Rw/(Rw+Rr)がおおよそ0.5のときに最小値となる。そして、Rw/(Rw+Rr)<0.88の範囲のときに、比騒音差ΔKsが0[dBA]より小さくなって、送風騒音を効果的に低減できる。   As shown in FIG. 8, the specific noise difference ΔKs has a characteristic of continuously changing in a downwardly convex shape when Rw / (Rw + Rr) is continuously changed from 0 to 1, and Rw The minimum value is obtained when / (Rw + Rr) is approximately 0.5. When Rw / (Rw + Rr) <0.88, the specific noise difference ΔKs becomes smaller than 0 [dBA], and the blowing noise can be effectively reduced.

次いで、上記結果について考察する。
Rw/(Rw+Rr)<0.88の場合、翼端渦7はベルマウス6から離れた位置で翼4の外周縁部4bから離脱される。従って、翼端渦7がベルマウス6に流出入する気流を乱すことなく、外周縁部4bから離脱されるので、比騒音差ΔKsは、Rw/(Rw+Rr)<0.88のときに0[dBA]より小さくなる。
Next, the above results will be considered.
When Rw / (Rw + Rr) <0.88, the blade tip vortex 7 is separated from the outer peripheral edge 4 b of the blade 4 at a position away from the bell mouth 6. Therefore, the blade tip vortex 7 is separated from the outer peripheral edge 4b without disturbing the airflow flowing into and out of the bell mouth 6, so that the specific noise difference ΔKs is 0 [Rw / (Rw + Rr) <0.88. dBA].

一方、リブ5が、Rw/(Rw+Rr)>0.88を満足するように翼4に配設されている場合、リブ後端5bとベルマウス6の一端との距離が短くなる。この場合、翼端渦7が離脱される翼4の外周縁部4bの部位がベルマウス6に近づくため、ベルマウス6に流出入する気流が翼端渦7に乱される。このため、Rw/(Rw+Rr)≧0.88となると、比騒音差が0[dBA]以上になる。
以上、図6〜図8に示された測定結果に基づいて説明したように、リブ5を配設したことによって、軸流送風機1の送風騒音が、軸流送風機1の送風性能を低下させることなしに、小さく抑えられることが確認された。
On the other hand, when the rib 5 is disposed on the wing 4 so as to satisfy Rw / (Rw + Rr)> 0.88, the distance between the rib rear end 5b and one end of the bell mouth 6 is shortened. In this case, since the portion of the outer peripheral edge 4 b of the blade 4 from which the blade tip vortex 7 is separated approaches the bell mouth 6, the airflow flowing into and out of the bell mouth 6 is disturbed by the blade tip vortex 7. For this reason, when Rw / (Rw + Rr) ≧ 0.88, the specific noise difference becomes 0 [dBA] or more.
As described above, as described based on the measurement results shown in FIG. 6 to FIG. 8, by providing the rib 5, the blowing noise of the axial blower 1 reduces the blowing performance of the axial blower 1. It was confirmed that it can be kept small.

なお、上記実施の形態では、リブ5は、その突出端面5dが、負圧面4eに一致するリブ前端5aから漸次高さを高くして、中間部5cで負圧面4eからの高さが最も高くなり、中間部5cからリブ後端5bに向かうにつれて負圧面4eからの高さを漸次低くしてリブ後端5bで負圧面4eに一致する滑らかな連続する曲面に形成されるものとして説明したが、リブ5の形状はこのものに限定されない。   In the above-described embodiment, the rib 5 has a protruding end surface 5d that gradually increases in height from the rib front end 5a that coincides with the negative pressure surface 4e, and the intermediate portion 5c has the highest height from the negative pressure surface 4e. The height from the suction surface 4e is gradually lowered from the intermediate portion 5c toward the rib rear end 5b, and the rib rear end 5b is described as being formed into a smooth continuous curved surface that matches the suction surface 4e. The shape of the rib 5 is not limited to this.

リブ5は、リブ前端5aが外周縁部4bより内周側の前縁部4cの所定部位に一致させた状態で負圧面4eに連結されるように、かつ、リブ後端5bが外周前縁端4gから回転方向後端に所定距離だけ離間した外周縁部4bの部位に滑らかに一致させた状態で負圧面4eに連結されるように取り付けられていれば、リブ前端5a側およびリブ後端5b側の突出端面5dの形状は必ずしも滑らかな曲面に形成されていなくてもよい。即ち、リブ前端5aが外周縁部4bより内周側の前縁部4cの所定部位に一致させた状態で負圧面4eに連結されるように、かつ、リブ後端5bが外周前縁端4gから回転方向後端に所定距離だけ離間した外周縁部4bの部位に滑らかに一致させた状態で負圧面4eに連結されるように取り付けられていれば、リブ前端5aから翼4に流入する気流のリブ5に対する相対速度を遅くでき、かつ、翼端渦7は大きく発達する前に離脱される。即ち、軸流送風機1の送風騒音を小さく抑えることができる。このとき、突出端面5dのリブ前端5a側およびリブ後端5b側が滑らかな曲面に形成されていない場合は、気流が乱されて、送風騒音を低下させる効果が薄れるが、リブ前端5aが外周縁部4bより内周側の前縁部4cの所定部位に一致させた状態で負圧面4eに連結されるように、かつ、リブ後端5bが外周前縁端4gから回転方向後端に所定距離だけ離間した外周縁部4bの部位に滑らかに一致させた状態で負圧面4eに連結されるように取り付けたことによる送風騒音の低減効果をすべて打ち消すものではない。   The rib 5 is connected to the negative pressure surface 4e in a state where the rib front end 5a is aligned with a predetermined portion of the front edge portion 4c on the inner peripheral side from the outer peripheral edge portion 4b, and the rib rear end 5b is the outer peripheral front edge. The rib front end 5a side and the rib rear end can be connected to the negative pressure surface 4e in a state of being smoothly aligned with the portion of the outer peripheral edge 4b spaced from the end 4g by a predetermined distance from the rotation direction rear end. The shape of the protruding end surface 5d on the 5b side does not necessarily have to be a smooth curved surface. That is, the rib front end 5a is connected to the suction surface 4e in a state where the rib front end 5a is aligned with a predetermined portion of the front edge portion 4c on the inner peripheral side from the outer peripheral edge portion 4b, and the rib rear end 5b is connected to the outer peripheral front edge end 4g. Air flow from the rib front end 5a to the blade 4 as long as it is attached to the suction surface 4e in a state of being smoothly aligned with the portion of the outer peripheral edge 4b that is separated from the rear end in the rotation direction by a predetermined distance. The relative velocity with respect to the rib 5 can be reduced, and the tip vortex 7 is separated before it is greatly developed. That is, the blowing noise of the axial blower 1 can be reduced. At this time, when the rib front end 5a side and the rib rear end 5b side of the projecting end surface 5d are not formed into smooth curved surfaces, the airflow is disturbed and the effect of reducing the blowing noise is diminished, but the rib front end 5a is the outer peripheral edge. The rib rear end 5b is connected from the outer peripheral front edge 4g to the rear end in the rotational direction by a predetermined distance so as to be connected to the suction surface 4e in a state of being aligned with a predetermined portion of the front edge 4c on the inner peripheral side from the portion 4b. It does not counteract all the effects of reducing the blowing noise caused by being attached so as to be connected to the suction surface 4e in a state of being smoothly aligned with the part of the outer peripheral edge 4b that is spaced apart.

また、リブ5は、リブ前端5aを外周縁部4bより内周側の前縁部4cの所定部位に一致させた状態で、かつ、リブ後端5bを、外周前縁端4gを除く外周縁部4bの部位に一致させた状態で負圧面4eと連結されるものとして説明したが、リブ前端5aの配置位置は上記のものに限定されない。リブ前端5aが外周縁部4bより内周側の前縁部4cの所定部位近傍の負圧面4e上に連結されている場合でも、リブ5の配設による送風騒音を低減させる効果が得られる。   The rib 5 has a rib front end 5a aligned with a predetermined portion of the front edge 4c on the inner peripheral side from the outer peripheral edge 4b, and the rib rear end 5b has an outer peripheral edge excluding the outer peripheral front edge 4g. Although described as being connected to the suction surface 4e in a state of being matched with the portion 4b, the arrangement position of the rib front end 5a is not limited to the above. Even when the rib front end 5a is connected to the negative pressure surface 4e near the predetermined portion of the front edge portion 4c on the inner peripheral side from the outer peripheral edge portion 4b, the effect of reducing the blowing noise due to the arrangement of the rib 5 can be obtained.

翼先端付近で発生する翼端渦7は勢力が小さいため、この領域では必ずしもリブ5により翼端渦7を径方向外方へ移動させる必要はない。ただし、中程度に翼端渦7が発達するとリブをもってしても翼端渦7を径方向外方へ移動させることが困難となるので、リブ前端5aが外周縁部4bより内周側の前縁部4cの所定部位近傍の負圧面4e上に連結される必要がある。   Since the blade tip vortex 7 generated near the blade tip has a small force, it is not always necessary to move the blade tip vortex 7 radially outward by the rib 5 in this region. However, if the blade tip vortex 7 is moderately developed, it is difficult to move the blade tip vortex 7 radially outward even if it has a rib. Therefore, the rib front end 5a is located in front of the outer peripheral edge 4b on the inner peripheral side. It is necessary to be connected on the negative pressure surface 4e in the vicinity of a predetermined portion of the edge 4c.

この発明に係る軸流送風機の斜視図である。It is a perspective view of the axial blower concerning this invention. この発明に係る軸流送風機の正面図である。1 is a front view of an axial blower according to the present invention. 図2のIII−III矢視要部断面図である。FIG. 3 is a cross-sectional view taken along the line III-III in FIG. 2. この発明に係る軸流送風機のボスの軸心から翼の外周縁部までの距離と同じ半径を有し、翼及びリブを囲繞するようにボスの軸心と同軸に配置された円筒面に、ボスの軸心を中心とする径方向に翼、リブ、及びベルマウスを投影した後に円筒面を平面上に展開した側面図である。A cylindrical surface having the same radius as the distance from the boss axis of the axial fan according to the present invention to the outer peripheral edge of the wing, and arranged coaxially with the boss axis so as to surround the wing and the rib, It is the side view which developed the cylindrical surface on the plane after projecting a wing, a rib, and a bell mouth in the diameter direction centering on the axis of a boss. この発明に係る軸流送風機において発生する翼端渦の流れを概念的に示す図である。It is a figure which shows notionally the flow of the blade tip vortex which generate | occur | produces in the axial-flow fan which concerns on this invention. この発明に係る軸流送風機におけるIb/Ifと比騒音差ΔKsとの関係を示す図である。It is a figure which shows the relationship between Ib / If and specific noise difference (DELTA) Ks in the axial blower which concerns on this invention. この発明に係る軸流送風機におけるt/laと比騒音差ΔKsとの関係を示す図である。It is a figure which shows the relationship between t / la and the specific noise difference (DELTA) Ks in the axial-flow fan which concerns on this invention. この発明の軸流送風機におけるRw/(Rw+Rr)と比騒音差ΔKsとの関係を示す図である。It is a figure which shows the relationship between Rw / (Rw + Rr) and specific noise difference (DELTA) Ks in the axial-flow fan of this invention. 比較例の軸流送風機の正面図である。It is a front view of the axial-flow fan of a comparative example. 比較例の軸流送風機において発生する翼端渦の流れを概念的に示す図である。It is a figure which shows notionally the flow of the blade tip vortex which generate | occur | produces in the axial-flow fan of a comparative example.

符号の説明Explanation of symbols

2 羽根車、3 ボス、4 翼、4a 付け根縁部、4b 外周縁部、4c 前縁部、4d 後縁部、4e 負圧面、4f 正圧面、5 リブ、5a リブ前端、5b リブ後端、5c 中間部、5d 突出端面、6 ベルマウス。   2 impeller, 3 boss, 4 blades, 4a root edge portion, 4b outer peripheral edge portion, 4c front edge portion, 4d rear edge portion, 4e negative pressure surface, 4f positive pressure surface, 5 rib, 5a rib front end, 5b rib rear end, 5c middle part, 5d protruding end face, 6 bell mouth.

Claims (5)

軸心まわりに回転されるボス、及び該ボスの外周面に配設されて、それぞれ上記ボスの外周面との接合部位となる付け根縁部、上記ボスの軸心を中心とする所定の半径の円に沿って所定の長さを有する外周縁部、上記付け根縁部及び上記外周縁部の回転方向の前端同士を接続する前縁部、及び上記付け根縁部及び上記外周縁部の回転方向の後端同士を接続する後縁部に囲まれた形状に形成された複数枚の翼を有する羽根車と、
上記ボスと同軸に配置され、一側の開口から上記翼の回転方向前端側を突出させて、上記翼の回転方向後端側を囲繞するベルマウスと、
上記ベルマウスの一側の開口から突出する上記翼の負圧面の部位に突設されたリブと、を備え、
上記リブは、リブ前端を上記外周縁部の回転方向の前端から所定距離だけ離間した上記前縁部の部位、又はその近傍に連結され、リブ後端を上記外周縁部の回転方向の前端から所定距離だけ離間した外周縁部の部位に滑らかに連結されていることを特徴とする軸流送風機。
A boss rotated around an axis, and a base edge portion disposed on an outer peripheral surface of the boss, each serving as a joint portion with the outer peripheral surface of the boss, and having a predetermined radius centered on the axis of the boss An outer peripheral edge having a predetermined length along the circle, a front edge connecting the root edges and the front edges in the rotation direction of the outer peripheral edges, and a rotation direction of the root edges and the outer peripheral edges. An impeller having a plurality of blades formed in a shape surrounded by a rear edge portion connecting the rear ends;
A bell mouth that is arranged coaxially with the boss, protrudes from the opening on one side of the wing in the rotation direction front end side, and surrounds the wing rotation direction rear end side;
A rib projecting from a portion of the suction surface of the wing projecting from an opening on one side of the bell mouth,
The rib is connected to a portion of the front edge portion where the rib front end is separated from the front end in the rotation direction of the outer peripheral edge portion by a predetermined distance or in the vicinity thereof, and the rib rear end is connected to the front end in the rotation direction of the outer peripheral edge portion. An axial blower characterized in that it is smoothly connected to a portion of the outer peripheral edge separated by a predetermined distance.
上記リブの上記突出端面は、上記リブ前端と上記リブ後端との間に上記負圧面からの高さが最も大きくなる中間部を有し、かつ上記負圧面に一致する上記リブ前端から上記リブ後端に至るまで滑らかな連続する曲面に形成されていることを特徴とする請求項1記載の軸流送風機。   The protruding end surface of the rib has an intermediate portion between the rib front end and the rib rear end that has the largest height from the suction surface, and from the rib front end that coincides with the suction surface to the rib 2. The axial flow fan according to claim 1, wherein the blower is formed in a smooth continuous curved surface up to the rear end. 上記ボスの軸心方向における上記外周縁部の回転方向の前端と後端との間の距離(If)と、上記ボスの軸心方向における外周縁部の回転方向の後端と上記ベルマウスの一側の開口面との間の距離(Ib)が、0.23<Ib/If<0.42を満足するように構成されていることを特徴とする請求項1または請求項2記載の軸流送風機。   The distance (If) between the front end and the rear end in the rotational direction of the outer peripheral edge in the axial direction of the boss, the rear end in the rotational direction of the outer peripheral edge in the axial direction of the boss, and the bell mouth 3. The shaft according to claim 1, wherein the distance (Ib) between the opening surface on one side is configured to satisfy 0.23 <Ib / If <0.42. Current blower. 上記リブ前端から上記リブ後端に至るまでの上記翼の負圧面上での長さ(Rw)と、上記リブ後端が配置された上記翼の上記外周縁部の部位から、上記ボスの軸心方向の高さ位置が上記ベルマウスの上記一側の開口と同じである上記外周縁部の部位までの該外周縁部に沿った長さ(Rr)とが、Rw/(Rw+Rr)<0.88を満足するように構成されていることを特徴とする請求項1乃至請求項3のいずれか1項に記載の軸流送風機。   From the front end of the rib to the rear end of the rib, the length (Rw) on the suction surface of the blade, and from the portion of the outer peripheral edge of the blade where the rear end of the rib is disposed, the axis of the boss The length (Rr) along the outer peripheral edge to the outer peripheral edge where the height in the heart direction is the same as the opening on the one side of the bell mouth is Rw / (Rw + Rr) <0. The axial flow blower according to any one of claims 1 to 3, wherein the axial flow blower is configured to satisfy. 上記ボスの軸心から上記翼の上記外周縁部までの距離と同じ半径を有し、上記翼及び上記リブを囲繞するように上記ボスの軸心と同軸に配置された円筒面に、上記ボスの軸心を中心とする径方向に上記翼、及び上記リブを投影した後に上記円筒面を平面上に展開した側面図において、上記負圧面の法線方向における上記リブの上記負圧面からの最大の高さ(t)と、上記外周縁部の回転方向の前端と上記外周縁部の回転方向の後端とを結ぶ直線の距離(la)とが、0<t/la<0.025を満足するように構成されていることを特徴とする請求項1乃至請求項4のいずれか1項に記載の軸流送風機。   The boss has a radius that is the same as the distance from the axial center of the boss to the outer peripheral edge of the wing, and is disposed on a cylindrical surface that is coaxial with the boss axial center so as to surround the wing and the rib. In the side view in which the cylindrical surface is developed on a plane after projecting the blade and the rib in the radial direction centered on the axial center of the axis, the maximum of the rib from the suction surface in the normal direction of the suction surface And the distance (la) of the straight line connecting the front end in the rotational direction of the outer peripheral edge and the rear end in the rotational direction of the outer peripheral edge satisfies 0 <t / la <0.025. It is comprised so that it may be satisfied, The axial-flow fan of any one of Claim 1 thru | or 4 characterized by the above-mentioned.
JP2007150358A 2007-06-06 2007-06-06 Axial blower Pending JP2008303760A (en)

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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104343729A (en) * 2013-07-31 2015-02-11 日本电产株式会社 Impeller and air blower
CN106640742A (en) * 2016-12-06 2017-05-10 西华大学 Spiral axial-flow type oil-gas multiphase pump impeller
JP7195490B1 (en) 2022-04-01 2022-12-23 三菱電機株式会社 Axial impeller and axial fan

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104343729A (en) * 2013-07-31 2015-02-11 日本电产株式会社 Impeller and air blower
CN106640742A (en) * 2016-12-06 2017-05-10 西华大学 Spiral axial-flow type oil-gas multiphase pump impeller
CN106640742B (en) * 2016-12-06 2022-10-11 西华大学 Spiral axial-flow type oil-gas mixed transportation pump impeller
JP7195490B1 (en) 2022-04-01 2022-12-23 三菱電機株式会社 Axial impeller and axial fan

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