JPS62284999A - Laminar flow rib structure of forward fan - Google Patents
Laminar flow rib structure of forward fanInfo
- Publication number
- JPS62284999A JPS62284999A JP12750186A JP12750186A JPS62284999A JP S62284999 A JPS62284999 A JP S62284999A JP 12750186 A JP12750186 A JP 12750186A JP 12750186 A JP12750186 A JP 12750186A JP S62284999 A JPS62284999 A JP S62284999A
- Authority
- JP
- Japan
- Prior art keywords
- blade
- rib
- rectifying rib
- forward fan
- rectifying
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
- 230000002093 peripheral effect Effects 0.000 claims abstract description 27
- 238000005259 measurement Methods 0.000 description 4
- 238000010586 diagram Methods 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 238000000926 separation method Methods 0.000 description 2
- 235000004035 Cryptotaenia japonica Nutrition 0.000 description 1
- 244000146493 Cryptotaenia japonica Species 0.000 description 1
- 239000012141 concentrate Substances 0.000 description 1
- 238000001816 cooling Methods 0.000 description 1
- 230000003292 diminished effect Effects 0.000 description 1
- 238000002474 experimental method Methods 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 238000005192 partition Methods 0.000 description 1
- 230000001105 regulatory effect Effects 0.000 description 1
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- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
Description
【発明の詳細な説明】
３、発明の詳細な説明
〔産業上の利用分野］
本発明は、ラジェータの冷却等に使用される前進ファン
の整流リブ構造に関するものである。Detailed Description of the Invention 3. Detailed Description of the Invention [Field of Industrial Application] The present invention relates to a rectifying rib structure of a forward fan used for cooling a radiator or the like.
［従来技術及び発明が解決しようとする問題点コ近年、
自動車においては、エンジンの高出力化、エンジンルー
ムの小型化等のため、ラジェータの放熱量が増大する傾
向にあり、そこでこれを冷却するファンについても高風
量化が推進されている。[Problems to be solved by prior art and inventions have recently been
In automobiles, the amount of heat dissipated from radiators tends to increase due to higher engine output, smaller engine compartments, etc., and therefore the fans that cool the radiators are also being made to have higher airflow.
この様な場合に用いられる前進ファンは、特にその性質
がブレード２の外周前端部から高速集中渦流を発生させ
、これが正圧面側から負正面側への空気の巻き込みを抑
える作用を果すため、騒音の発生が他の軸流ファンに比
して低いと言われている。しかるにこの前進ファンをそ
のまま用い、単に回転数を上げることで高風量化を試み
た場合に、第５図に示す如く、ラジェータ４を通過する
空気流がシュラウド５側に排出される際に、正圧面上の
空気流は、前進ファン１の高速回転によってより大きな
遠心力成分を与えられてブレードの外周端後縁部のＸ、
Ｙ部に集中し、これが正圧面側からシュラウドとブレー
ドとの隙間を通って負圧面側に流れてしまい、このこと
が、■ブレード（翼体）２の後端の空気流の剥離による
乱気流の発生、■ブレード２の外周端からの空気の回り
込みによる乱気流の発生となり、さらには■ブレード２
の前縁の失速による剥離での乱気流の発生等が主因とし
て挙げられ、特に■、■が騒音発生に大きな影響を与え
ているものと推察され、従来からこれら乱気流の発生に
対する種々の対策が採られているが、未だ充分に満足の
いくものが出現していないという実情にある。The forward fan used in such cases generates a high-speed concentrated vortex flow from the front end of the outer circumference of the blades 2, which acts to suppress the entrainment of air from the positive pressure side to the negative front side, which reduces noise. It is said that the occurrence of this is lower than that of other axial fans. However, when using this forward fan as is and attempting to increase the air volume by simply increasing the rotation speed, as shown in Figure 5, when the airflow passing through the radiator 4 is discharged to the shroud 5 side, the The air flow on the pressure surface is given a larger centrifugal force component by the high-speed rotation of the forward fan 1, and the X of the rear edge of the outer peripheral end of the blade is
It concentrates on the Y section and flows from the pressure side through the gap between the shroud and the blade to the suction side, which causes turbulence due to separation of the airflow at the rear end of the blade (wing body) 2. ■ turbulence occurs due to air wrapping around from the outer edge of blade 2, and ■ blade 2
The main cause is the occurrence of turbulence due to separation due to the stalling of the leading edge of the engine. In particular, it is assumed that ① and ② have a large influence on noise generation, and various countermeasures have been taken to prevent the occurrence of turbulence. However, the reality is that nothing that is fully satisfactory has yet emerged.
［問題を解決するための手段］
本発明は、上記の如き実情に鑑みこれらの欠点を一掃す
ることができる前進ファンの整流リブ構造を提供するこ
とを目的として創案されたものであって、ボス部から複
数枚のブレードが放射状に突出してなるａ進ファンにお
いて、前記ブレードの外周端部に整流リブを弦長略全域
に亘って突設するに、該整流リブは、一枚がブレードの
少なくとも負圧側の面に突設され、かつブレードの外周
端縁形状に略平行で、ブレード外周端縁からの距離およ
び整流リブの高さは前進ファンの直径に対してそれぞれ
１８２〜５％の範囲に設定されていることを特徴とする
ものである。[Means for Solving the Problems] In view of the above-mentioned circumstances, the present invention was devised for the purpose of providing a rectifying rib structure for a forward fan that can eliminate these drawbacks. In an a-adic fan in which a plurality of blades protrude radially from a section, a rectifying rib is provided at the outer circumferential end of the blade so as to protrude over substantially the entire chord length. The ribs protrude from the negative pressure side surface and are approximately parallel to the shape of the outer peripheral edge of the blade, and the distance from the outer peripheral edge of the blade and the height of the rectifying rib are each in the range of 182 to 5% of the diameter of the forward fan. It is characterized by being set.
さらに前記整流リブは、その上端縁形状が、ブレード外
周端縁の曲率に略一致した形状になっていることが好ま
しく、また整流リブのブレード外周端縁からの突設位置
と、整流リブの高さとが略等しくなるように設定されて
いることが好ましいものである。Further, it is preferable that the upper edge shape of the rectifying rib has a shape that substantially matches the curvature of the outer peripheral edge of the blade, and the position of the rectifying rib protruding from the outer peripheral edge of the blade, and the height of the rectifying rib. It is preferable that the values are set to be approximately equal.
そして本発明は、この構成によって、乱気流の発生を効
果的に押えて、静粛な状態で高風量化を果すことができ
るようにしたものである。With this configuration, the present invention can effectively suppress the occurrence of turbulence and achieve a high air volume in a quiet state.
［実施例］
次に、本発明の一実施例を図面に基づいて説明する。図
面において、１は前進型の前進ファンであって、該前進
ファン１は、四枚のブレード２をボス部１ａから放射状
に突出することによって構成されるものであるが、ブレ
ード２の外周端部に本発明の整流リブ３が突設されてい
る。そして本発明では、上述した整流リブ３の設定条件
を求めるために次の１〜６の検討を試みている。[Example] Next, an example of the present invention will be described based on the drawings. In the drawings, reference numeral 1 denotes a forward-moving forward fan, and the forward fan 1 is constructed by four blades 2 protruding radially from a boss portion 1a. A rectifying rib 3 of the present invention is provided in a protruding manner. In the present invention, the following studies 1 to 6 are attempted in order to determine the setting conditions for the above-mentioned rectifying ribs 3.
ここでこれらの検討をするに際し、実際に用いた前進フ
ァンの全体直径は３００＋＋＋ｍ、ボス部１ａの直径は
８０ｍｍ、ブレード２の全長は１１０ｍｍ、ブレード２
の捻れ幅Ｘは３５．５ｍｍ、さらにブレード２の捻れ中
心Ｙが前縁から１６．５ｍｍのものを標準型の前進ファ
ン１とし、このものに整流リブ３を後述する種々の条件
で突設したもの（検討例Ａ−Ｍ）について、基準風量（
Ｑ ） １２２０ｍ”／ｈを得るための前進ファン１の
回転数（ｒｐｍ）と、そのときの騒音（ｄ８）とを測定
し、その結果を図表に示した。尚、この標準型のものに
ついては、前記基準風量を得るには、 ２０２０ｒｐ＋
ｍの回転数が必要で、そのときの騒音は６３ｄＢである
ことが観測されている。以下、検討事項について述べる
・
検討１（整流リブの突出面の検討）
ここでは整流リブ３をブレード２の正圧、負圧の何れの
側の面に設けたら良いかの検討をする。When conducting these studies here, the overall diameter of the forward fan actually used was 300 +++ m, the diameter of the boss portion 1a was 80 mm, the total length of the blade 2 was 110 mm, and the blade 2 was
The standard forward fan 1 is one in which the torsion width X is 35.5 mm and the torsion center Y of the blade 2 is 16.5 mm from the front edge, and rectifying ribs 3 are protruded on this fan under various conditions described below. (Study examples A-M), the standard air volume (
Q) The number of revolutions (rpm) of the forward fan 1 to obtain 1220 m''/h and the noise (d8) at that time were measured, and the results are shown in a chart.For this standard type, , to obtain the reference air volume, 2020rp+
It has been observed that a rotation speed of m is required, and the noise at that time is 63 dB. The matters to be considered will be described below. Study 1 (Study of the protruding surface of the rectifying rib) Here, we will examine whether the rectifying rib 3 should be provided on the positive pressure or negative pressure side of the blade 2.
ここで用いる各検討例の前進ファン１は、前記標準型の
もののブレード２に、その外周端縁から１０１１Ｉｆｆ
ｌの位置に、ブレード２の外周縁形状に略平行で、中央
部位の高さく最大高さＨ）が１０ｍｍのものとし、かつ
上端縁の形状はブレード２の外周端縁の曲率と同じ形状
に設定した整流リブ３を突設した。そしてこの整流リブ
３を負圧面側に設けたもの（検討例Ａ）、正圧面側に設
けたもの（検討例Ｂ）、及び両面側に設けたもの（検討
例Ｃ）についてそれぞれ基準風量を得るための回転数と
その際の騒音を測定し、この結果を図表に示す。これに
よると、何れの検討例のものも基準風量を得る際の騒音
は、標準型のものに比して低減していることが認められ
るが、特に負正面のみに設けたもの、及び両面に設けた
ものについて顕著であり、このことから、少なくとも負
圧面側に整流リブ３を設けたものであることが必要であ
る。The forward fan 1 of each study example used here has a blade 2 of the standard type with a distance of 1011Iff from its outer peripheral edge.
At position l, the blade should be approximately parallel to the shape of the outer peripheral edge of the blade 2, the height of the central part (maximum height H) should be 10 mm, and the shape of the upper edge should be the same as the curvature of the outer peripheral edge of the blade 2. The set rectifying rib 3 was provided protrudingly. Then, obtain the standard air volume for each of the rectifying ribs 3 provided on the negative pressure side (example A), on the positive pressure side (example B), and on both sides (example C). The number of rotations and the noise generated at that time were measured, and the results are shown in a chart. According to this, it is recognized that the noise when obtaining the reference air volume for all of the studied examples is reduced compared to the standard type, but especially for those installed only on the negative front and on both sides. This is particularly noticeable in the case where the rectifying rib 3 is provided at least on the negative pressure side.
検討２ （！ｌ！流リブの数の検討）
次に整流リブ３の数について検討するが、これには、前
記検討例Ａのブレード２に、さらにその軸芯側にｉｏａ
ｍだけずれた位置に同じような整流リブ３をもう一枚突
設して都合二枚にしたもの（検討例Ｄ）を用いて同じく
測定し、その結果を図表に示す。これによると、整流リ
ブ３が二枚になったものは、基準風量を得るためには高
速回転が必要となり、従って整流リブ３の数が増加する
ことは効率的に好ましくなく、また騒音については、検
討例Ａのものよりも若干悪くなっているが、標準型のも
のよりは良いことが認められる。而して整流リブ３は、
検討例Ａの如く一枚のものが好ましいことになり、効率
の点をあまり考慮に入れなければ二枚程度でも良いが、
これをさらに増やした場合には騒音の増加が推察され好
ましいとは言えない。Study 2 (!l! Study on the number of flow ribs) Next, the number of flow straightening ribs 3 will be studied.
The same measurement was carried out using another similar rectifying rib 3 protruding from a position shifted by m (study example D), and the results are shown in the chart. According to this, the one with two rectifying ribs 3 requires high speed rotation to obtain the standard air volume, so increasing the number of rectifying ribs 3 is not preferable in terms of efficiency, and also reduces noise. Although it is slightly worse than that of Study Example A, it is recognized that it is better than that of the standard type. Therefore, the rectifying rib 3 is
It is preferable to use one sheet as in study example A, and if you do not take efficiency into consideration too much, two sheets may be sufficient.
If this number is further increased, it is assumed that the noise will increase, which is not desirable.
検討３ （′！Ｉｉ流リブの突出角度の検討）ここでは
、整流リブ３がブレード２の外周端縁に対してどのよう
な角度に設定したものが良いかを検討する。そこで整流
リブ３の突設角度を、前端がブレード２の外周端に一致
したもの（検討例Ｅ）、後端がブレード２の外周端に一
致したもの（検討例Ｆ）とそれぞれ傾斜状にし、他は検
討例Ａと同じ条件としたものについてそれぞれ測定し、
この結果を図表に示す、これによると、検討例Ｅ。Study 3 (Study of protruding angle of '!Ii flow ribs) Here, we will study what angle the rectifying ribs 3 should be set to with respect to the outer peripheral edge of the blade 2. Therefore, the protruding angle of the straightening rib 3 is made slanted so that the front end coincides with the outer peripheral edge of the blade 2 (example E), and the rear end coincides with the outer peripheral edge of the blade 2 (example F), respectively. Other measurements were made under the same conditions as Study Example A.
The results are shown in a diagram, according to which study example E is shown.
Ｆのものは、騒音について何れもｉＲ準型のものに近似
し、この結果整流リブ３の突出角度は、検討例Ａのよう
にブレード２の外周端縁に略平行であるものが最も好ま
しいと言える。The noise of F type is similar to that of the iR quasi-type, and as a result, it is most preferable that the protruding angle of the rectifying rib 3 is approximately parallel to the outer peripheral edge of the blade 2, as in study example A. I can say it.
検討４ （！１１流リブの高さの検討）次に、整流リブ
３の高さについて検討するに、整流リブ３のリブ高さの
みを、前記検討例Ａの１０ａｍとしたものよりも低い５
１ｎＩ１１としたもの（検討例Ｇ）、高い１５ｍｎ＋と
じたもの（検討例Ｈ）について測定し、その結果を図表
に示す。これによると、リブ高さは、検討例Ａの１０１
としたものが最低の騒音で、これよりも大きいか小さく
なると何れも騒音が大きくなっていることが認められ、
従ってこのことから、リブ高さは、ブレード２の外周端
からの距離と略同じ高さにすることが好ましいと。Study 4 (!11 Study on the height of the flow ribs) Next, when considering the height of the flow straightening ribs 3, only the rib height of the flow straightening ribs 3 was set to 5.
Measurements were carried out for those with 1nI11 (Study Example G) and those with high 15m+ binding (Study Example H), and the results are shown in the graph. According to this, the rib height is 101 in study example A.
It is recognized that the noise level above is the lowest level, and the noise becomes louder when the noise level is higher or lower than this level.
Therefore, from this, it is preferable that the rib height be approximately the same as the distance from the outer peripheral end of the blade 2.
あるいは１０ｍｍ前後にすることが好ましいと言うこと
ができる。Alternatively, it can be said that it is preferable to set it to around 10 mm.
検討５（？！流リブの突出位置の検討）ここでは、整流
リブ３をブレード２の外周端縁からどれくらいのところ
に突設したら良いかを検討する。そこで整流リブ３の突
設位置のみを、ブレード外周端位［（つまり０ｍｍ位置
）に突設したもの（検討例Ｉ）、５ｍｍ位置に突設した
もの（検討例Ｊ ） 、１５ｍｍ５ｍｍ位置したもの（
検討例Ｋ）として検討例Ａと異ならしめたものを設定し
、これらについて測定し、その結果を図表に示す。これ
によると、検討例工のものは殆ど騒音の低減は認められ
ず、検討例Ａのものにおいて最低値を示すことが認めら
れ、このことから、整流リブ３の突設位置は、ブレード
２の直径に対して３〜５％程度の位置に設けたものが、
あるいは１０ｍ１１前後に設けたものが騒音低減に好ま
しいと言える。Study 5 (Study on the protruding position of the flow ribs) Here, we will study how far from the outer peripheral edge of the blade 2 the flow regulating ribs 3 should protrude. Therefore, the protruding position of the rectifying rib 3 was changed to one in which the straightening rib 3 protruded only at the blade outer circumferential end position [(i.e., 0 mm position) (examination example I), one in which it was protruded at the 5 mm position (examination example J), and one in which the rectifying rib 3 was protruded at the blade outer circumferential end (i.e., the 0 mm position), one in which it was protruded at the 5 mm position (examination example J), and one in which the rectifying rib 3 was protruded at the blade outer circumferential end (i.e., 0 mm position), and one in which it was protruded at the 5 mm position (example J).
A study example K) different from study example A was set up and measured, and the results are shown in a chart. According to this, almost no noise reduction was observed in the study example A, and the lowest value was observed in the study example A. From this, the protruding position of the rectifying rib 3 is determined by the blade 2. The one provided at a position of about 3 to 5% of the diameter,
Alternatively, it can be said that one installed around 10m11 is preferable for noise reduction.
検討例６（９１流リブの形状の検討）
ここでは整流リブ３がどのような形状であることが最も
良いかを検討する。そこで前記検討例Ａの整流リブ３を
、前進ファン１の回転方向手前側の部位を切欠いた楔形
状のものとし、その切欠位置を、整流リブ３のリブ幅の
略１／３までとしたもの（検討例Ｌ）、後端部までとし
たもの（検討例Ｍ）について測定し、その結果を図表６
に示す。Study Example 6 (Study of Shape of 91st Flow Rib) Here, we will study what shape is best for the flow straightening rib 3. Therefore, the rectifying rib 3 of the study example A was made into a wedge shape with a notch on the front side in the rotational direction of the forward fan 1, and the notch position was set to approximately 1/3 of the rib width of the rectifying rib 3. (Study example L) and the one up to the rear end (Study example M), and the results are shown in Figure 6.
Shown below.
これによると、リブ形状については検討例Ａのものが騒
音について最良であり、前端部が切欠かれているほど騒
音が大きくなることが認められ、従って、整流リブ３の
上端縁形状は、ブレード２の外周端縁形状に近い形状に
なっていた方が騒音低減に効果があると言える。According to this, regarding the rib shape, Study Example A is the best in terms of noise, and it is recognized that the more the front end is notched, the louder the noise is.Therefore, the shape of the upper edge of the rectifying rib 3 is It can be said that having a shape similar to the shape of the outer peripheral edge is more effective in reducing noise.
［作用コ
そして以上の各検討１〜６の結果から考察するに、本発
明のように、整流リブ３は、一枚がブレード２の少なく
とも負圧側の面に突設され、かつブレード２の外周端縁
形状に略平行で、ブレード２の外周端縁からの距離およ
び整流リブ３の高さは前進ファン１の直径に対してそれ
ぞれ略２〜５％の範囲に設定されているものにおいて、
明らかに騒音の低減が認められる。これは、前述したよ
うに前進ファンが、プレート２の外周前端部から高速集
中渦流を発生させ、これが正圧面側から負圧面側への空
気の巻き込みを抑える作用を果すものであるが、ここに
上記整流リブ３を設けた場合に、負圧面に流れる高速集
中渦流が整流リブ３によって受けられる構造となるため
、その高速集中渦流による空気の巻き込み抑え作用が殆
ど減殺されることなく後端部においても有効に働き、し
かも負圧面側において整流リブ３が仕切り壁の作用をし
、正圧面側から実質的に負圧状態となっている整流リブ
３の内側までの距離が長くなることによって、ブレード
２の正圧面側から外周端縁を越えた負正面側への空気の
流れを阻止し、これによって乱気流の発生が抑えられる
ものと推察される。[Operations] Considering the results of each of the above studies 1 to 6, it is clear that according to the present invention, one of the rectifying ribs 3 is provided protruding from at least the negative pressure side surface of the blade 2, and The fan is substantially parallel to the edge shape, and the distance from the outer peripheral edge of the blade 2 and the height of the rectifying rib 3 are each set within a range of approximately 2 to 5% of the diameter of the forward fan 1.
A clear reduction in noise is observed. This is because, as mentioned above, the forward fan generates a high-speed concentrated vortex from the front end of the outer periphery of the plate 2, and this serves to suppress the entrainment of air from the pressure side to the negative pressure side. When the above-mentioned straightening rib 3 is provided, the structure is such that the high-speed concentrated vortex flowing on the negative pressure surface is received by the straightening rib 3, so that the effect of suppressing air entrainment due to the high-speed concentrated vortex is hardly diminished at the rear end. Moreover, the rectifying rib 3 acts as a partition wall on the negative pressure side, and the distance from the positive pressure side to the inside of the rectifying rib 3, which is in a substantially negative pressure state, becomes longer, so that the blade It is presumed that this prevents the flow of air from the positive pressure side of No. 2 to the negative front side beyond the outer peripheral edge, thereby suppressing the occurrence of turbulence.
そしてこの乱気流発生が抑えられている事実は、風洞実
験（タフト法）においても確認されており、本発明が理
論的にも正しいものであると推認できる。The fact that the generation of turbulence is suppressed has been confirmed in wind tunnel experiments (Taft method), and it can be inferred that the present invention is theoretically correct.
そしてこのものは、さらに検討４，５から判断して、前
進ファン１の直径と、整流リブ３のブレード外周端縁か
らの突設位置、および整流リブ３の高さとの比率は、そ
れぞれ３００に対して１０に近くなるほど好適なものと
なり、さらに、ブレード外周端縁からの突出位置と整流
リブ３の高さとが略等しくなるように設定することが条
件的に望ましいと言える。Further, judging from studies 4 and 5, the ratios of the diameter of the forward fan 1, the protruding position of the rectifying rib 3 from the outer peripheral edge of the blade, and the height of the rectifying rib 3 are 300, respectively. On the other hand, the closer it is to 10, the more preferable it is, and furthermore, it can be said that it is desirable to set the position so that the protruding position from the outer peripheral edge of the blade and the height of the rectifying rib 3 are approximately equal.
［効果コ
以上要するに、本発明は叙述の如く構成したものである
から、ブレードに設けた整流リブによって、ブレード外
周端縁部での正圧面側から負圧面側への空気の回り込み
による乱気流の発生を極力抑え得て、騒音の発生を効果
的に低減することができ、従って前進ファンにおいて、
近時要望されている高風量化を計ったとしても、騒音の
少ない静粛なものとすることができることになる。[Effects] In summary, since the present invention is constructed as described above, the rectifying rib provided on the blade prevents the generation of turbulent air due to the circulation of air from the pressure side to the suction side at the outer peripheral edge of the blade. can be suppressed as much as possible, and the generation of noise can be effectively reduced.
This means that even if the air volume is increased, which has been demanded recently, it will be quiet with less noise.
図面は、本発明に係る前進ファンの″Ｍｉ流リブ構造の
実施例を示したものであって、第１図は前進ファンの要
部正面図、第２図は同上要部側面図、第３図は整流リブ
の平面図、第４図は測定結果を示す図表、第５図Ａ、Ｂ
、Ｃは騒音発生のメカニズムを示す作用説明図である。
図中、１は前進ファン、２はブレード、３は整流リブで
ある。
特許出願人 株式会社三ツ葉電機製作所３ 、Ｙ
第３図
第５図
第４
図The drawings show an embodiment of the "Mi-style rib structure of the forward fan according to the present invention, and FIG. 1 is a front view of the main part of the forward fan, FIG. 2 is a side view of the main part of the same, and FIG. The figure is a plan view of the rectifying rib, Figure 4 is a chart showing the measurement results, and Figures 5A and B.
, C are action explanatory diagrams showing the mechanism of noise generation. In the figure, 1 is a forward fan, 2 is a blade, and 3 is a rectifying rib. Patent applicant: Mitsuba Electric Manufacturing Co., Ltd. 3, Y Figure 3 Figure 5 Figure 4
Claims (1)
る前進ファンにおいて、前記ブレードの外周端部に整流
リブを弦長略全域に亘つて突設するに、該整流リブは、
一枚がブレードの少なくとも負圧側の面に突設され、か
つブレードの外周端縁形状に略平行で、ブレード外周端
縁からの突出位置および整流リブの高さは前進ファンの
直径に対してそれぞれ略２〜５％の範囲に設定されてい
ることを特徴とする前進ファンの整流リブ構造。 ２）前記整流リブの上端縁形状は、ブレード外周端縁の
曲率に略一致した形状になつていることを特徴とする特
許請求の範囲第１項記載の前進ファンの整流リブ構造。 ３）前記整流リブのブレード外周端縁からの突出位置と
、整流リブの高さとが略等しくなるように設定されてい
ることを特徴とする特許請求の範囲第１項記載の前進フ
ァンの整流リブ構造。[Scope of Claims] 1) In a forward fan having a plurality of blades protruding radially from a boss portion, a rectifying rib is provided at an outer circumferential end of the blade so as to protrude over substantially the entire chord length. teeth,
One piece protrudes from at least the negative pressure side surface of the blade, and is approximately parallel to the shape of the outer peripheral edge of the blade, and the protruding position from the outer peripheral edge of the blade and the height of the rectifying rib are respectively relative to the diameter of the forward fan. A rectifying rib structure of a forward fan, characterized in that the rectifying rib structure is set in a range of approximately 2 to 5%. 2) The rectifying rib structure for a forward fan according to claim 1, wherein the upper edge shape of the rectifying rib has a shape that substantially matches the curvature of the outer peripheral edge of the blade. 3) The rectifying rib of the forward fan according to claim 1, wherein the protruding position of the rectifying rib from the outer circumferential edge of the blade is set to be approximately equal to the height of the rectifying rib. structure.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP61127501A JPH071040B2 (en) | 1986-06-02 | 1986-06-02 | Forward fan straightening rib structure |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP61127501A JPH071040B2 (en) | 1986-06-02 | 1986-06-02 | Forward fan straightening rib structure |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS62284999A true JPS62284999A (en) | 1987-12-10 |
| JPH071040B2 JPH071040B2 (en) | 1995-01-11 |
Family
ID=14961532
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP61127501A Expired - Lifetime JPH071040B2 (en) | 1986-06-02 | 1986-06-02 | Forward fan straightening rib structure |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH071040B2 (en) |
Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH10252692A (en) * | 1997-03-12 | 1998-09-22 | Hitachi Ltd | Air-conditioning propeller fan |
| JP2005194923A (en) * | 2004-01-06 | 2005-07-21 | Ishikawajima Harima Heavy Ind Co Ltd | Compressor moving blade |
| JP2010065706A (en) * | 2009-12-25 | 2010-03-25 | Sony Corp | Axial flow fan device and electronic apparatus |
| JP2010101326A (en) * | 2009-12-25 | 2010-05-06 | Sony Corp | Axial flow fan device, housing, and electronic appliance |
| US8068339B2 (en) | 2007-04-17 | 2011-11-29 | Sony Corporation | Axial fan apparatus, housing, and electronic apparatus |
| EP1750014A3 (en) * | 2005-08-03 | 2013-03-13 | Mitsubishi Heavy Industries, Ltd. | Axial fan for heat exchanger of in-vehicle air conditioner |
| WO2015030048A1 (en) * | 2013-09-02 | 2015-03-05 | 三菱電機株式会社 | Propeller fan, air-blowing device, and outdoor unit |
| JP2017067059A (en) * | 2015-10-03 | 2017-04-06 | 遊生 井手 | Wing of wind mill |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105170697A (en) * | 2015-10-20 | 2015-12-23 | 江苏华久辐条制造有限公司 | Take-up device for spoke wire drawing machine |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5418711U (en) * | 1977-07-08 | 1979-02-06 | ||
| JPS59126100A (en) * | 1983-01-05 | 1984-07-20 | Natl Aerospace Lab | Rotary blade |
-
1986
- 1986-06-02 JP JP61127501A patent/JPH071040B2/en not_active Expired - Lifetime
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5418711U (en) * | 1977-07-08 | 1979-02-06 | ||
| JPS59126100A (en) * | 1983-01-05 | 1984-07-20 | Natl Aerospace Lab | Rotary blade |
Cited By (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH10252692A (en) * | 1997-03-12 | 1998-09-22 | Hitachi Ltd | Air-conditioning propeller fan |
| JP2005194923A (en) * | 2004-01-06 | 2005-07-21 | Ishikawajima Harima Heavy Ind Co Ltd | Compressor moving blade |
| JP4617674B2 (en) * | 2004-01-06 | 2011-01-26 | 株式会社Ｉｈｉ | Compressor blade |
| EP1750014A3 (en) * | 2005-08-03 | 2013-03-13 | Mitsubishi Heavy Industries, Ltd. | Axial fan for heat exchanger of in-vehicle air conditioner |
| EP2696079A1 (en) * | 2005-08-03 | 2014-02-12 | Mitsubishi Heavy Industries, Ltd. | Propeller fan for heat exchanger of in-vehicle air conditioner |
| US8068339B2 (en) | 2007-04-17 | 2011-11-29 | Sony Corporation | Axial fan apparatus, housing, and electronic apparatus |
| CN102278324A (en) * | 2007-04-17 | 2011-12-14 | 索尼株式会社 | Axial fan apparatus and electronic apparatus |
| JP2010065706A (en) * | 2009-12-25 | 2010-03-25 | Sony Corp | Axial flow fan device and electronic apparatus |
| JP2010101326A (en) * | 2009-12-25 | 2010-05-06 | Sony Corp | Axial flow fan device, housing, and electronic appliance |
| WO2015030048A1 (en) * | 2013-09-02 | 2015-03-05 | 三菱電機株式会社 | Propeller fan, air-blowing device, and outdoor unit |
| JP2017067059A (en) * | 2015-10-03 | 2017-04-06 | 遊生 井手 | Wing of wind mill |
Also Published As
| Publication number | Publication date |
|---|---|
| JPH071040B2 (en) | 1995-01-11 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| EXPY | Cancellation because of completion of term |