JP2753182B2 - Axial fan - Google Patents
Axial fanInfo
- Publication number
- JP2753182B2 JP2753182B2 JP4259315A JP25931592A JP2753182B2 JP 2753182 B2 JP2753182 B2 JP 2753182B2 JP 4259315 A JP4259315 A JP 4259315A JP 25931592 A JP25931592 A JP 25931592A JP 2753182 B2 JP2753182 B2 JP 2753182B2
- Authority
- JP
- Japan
- Prior art keywords
- blade
- axial fan
- circumferential
- edge
- vicinity
- 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.)
- Expired - Fee Related
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
- F04D29/68—Combating cavitation, whirls, noise, vibration or the like; Balancing by influencing boundary layers
- F04D29/681—Combating cavitation, whirls, noise, vibration or the like; Balancing by influencing boundary layers especially adapted for elastic fluid pumps
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Description
【０００１】[0001]
【産業上の利用分野】本発明は、換気送風機器等に使用
される軸流ファンに関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an axial fan used for a ventilation blower or the like.
【０００２】[0002]
【従来の技術】近年、居住および非居住空間で使用され
る換気送風機器および空気調和機器に対する低騒音化の
要求が高まってきている。2. Description of the Related Art In recent years, there has been an increasing demand for ventilation and ventilation equipment and air conditioning equipment used in living and non-living spaces to reduce noise.
【０００３】従来、この種の軸流ファンは、図６および
図７に示すようにブレード１０１の周方向断面は軸流フ
ァン１０２のどの半径方向位置においても、一円弧翼ま
たは複数の円弧翼または薄肉翼型であり、半径方向位置
の変化により弦長１０３が異なるだけで、肉厚は弦長１
０３に比例して変化させ、最大肉厚部１０７は前縁１０
８より２０％〜５０％に設定する構成であった。Conventionally, as shown in FIGS. 6 and 7, a circumferential cross section of a blade 101 has a circular arc blade or a plurality of circular blades at any radial position of the axial fan 102 as shown in FIGS. It is a thin wing type. The chord length 103 differs only by the change of the radial position.
03, and the maximum thickness portion 107 is
The configuration is set to 20% to 50% from 8.
【０００４】[0004]
【発明が解決しようとする課題】このような従来の軸流
ファンでは、流れがブレード１０１の表面に沿えずに前
記ブレード１０１の後縁１０４において背面側１０５に
剥離流れ１０６を生じ騒音が大きくなる問題があった。In such a conventional axial flow fan, the flow does not follow the surface of the blade 101, and a separation flow 106 is generated on the rear side 105 of the trailing edge 104 of the blade 101 to increase noise. There was a problem.
【０００５】本発明は上記課題を解決するもので、家電
および設備機器に用いられている騒音の低い軸流ファン
を提供することを目的とする。An object of the present invention is to solve the above-mentioned problems and to provide an axial fan with low noise used for home appliances and equipment.
【０００６】[0006]
【課題を解決するための手段】本発明の軸流ファンは上
記目的を達成するために、第１の手段は、外径から羽根
ハブ近傍までの範囲全域にわたるブレード周方向断面の
後縁から背面側に、弦長に対し２％〜３０％の周方向長
さで、周方向断面で最も大きい肉厚平面部を段差状に設
けた構成とする。In order to achieve the above object, an axial fan according to the present invention has a first means in which a blade circumferential cross section extending from an outer diameter to a vicinity of a blade hub is provided from a rear edge to a rear surface. on the side, in chord length vs. 2% to 30% of the circumferential length, a set <br/> was Ke constituting the largest thickness flat portion in the circumferential direction section stepwise.
【０００７】また、第２の手段は、ブレード周方向断面
の背面側の、前縁から弦長の６０％〜９０％の範囲内に
最大肉厚頂点部を設け、この最大肉厚頂点部にブレード
の前縁側および後縁側から向かうにしたがって肉厚がな
めらかに増加する形状とした構成とする。The second means is a blade circumferential section.
Blade on the rear side, the front edge with the largest thickness vertex portion in the range of 6 0% to 90% of the chord length from the maximum thickness apex
Thickness increases from the leading and trailing edges of the
The configuration is such that the shape increases smoothly .
【０００８】[0008]
【作用】本発明は上記した第１および第２の手段の構成
によりブレード後端部より放出される渦は極めて少なく
渦による騒音を低減することができる。According to the present invention, the vortex emitted from the rear end of the blade is extremely small and the noise due to the vortex can be reduced by the above first and second means.
【０００９】[0009]
【実施例】以下、本発明の第１実施例について、図１か
ら図３を参照しながら説明する。DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Hereinafter, a first embodiment of the present invention will be described with reference to FIGS.
【００１０】図に示すように、１は送風機または換気扇
で軸流ファン２が本体３内部に取り付けられた電動機４
のシャフト５に係止されている。前記軸流ファン２のブ
レード６は外径から羽根ハブ７近傍の範囲全域にわたっ
て、前記ブレード６の周方向断面は図２のように後縁８
から背面側９に、弦長に対し２％〜３０％の周方向長さ
１で、周方向断面で最も大きい肉厚平面部１０が段差状
に設けられている。As shown in FIG. 1, reference numeral 1 denotes a blower or a ventilation fan, and an electric motor 4 having an axial fan 2 mounted inside a main body 3.
The shaft 5 is locked. The blade 6 of the axial fan 2 extends over the entire range from the outer diameter to the vicinity of the blade hub 7.
Te, circumferential section of the blade 6 is rear edge 8 as shown in FIG. 2
From the rear side 9, the thickest flat portion 10 having a circumferential length 1 of 2% to 30% of the chord length and having the largest circumferential cross section is stepped.
It is provided in.
【００１１】上記構成により、電動機４によって軸流フ
ァン２が回転すると、吸込口１１より吸引された空気は
ブレード６の最大そり点１２の背面側９に剥離を生じよ
うとするが、前記肉厚平面部１０が設けられているので
剥離が小さくなり騒音の発生を低減することができる。With the above configuration, when the axial fan 2 is rotated by the electric motor 4, the air sucked from the suction port 11 tends to separate on the back side 9 of the maximum warp point 12 of the blade 6. Since the flat portion 10 is provided, peeling is reduced, and the generation of noise can be reduced.
【００１２】なお、図３に肉厚平面部１０の長さ１を変
えたときの騒音の変化を示す。これにより肉厚平面部１
０の長さの最適値を決定した。また、後縁８での乱れに
よる騒音は、風速が大きいほど大きく、発生音の大きさ
は周速の６乗に比例する。従って発生音の大きさは周速
の大きさで決まるが、周速により音の周波数も変わるの
で、各周波数について騒音の発生を低減することが効果
的であり、ある外径の羽根に対して、羽根ハブ７の径の
大きさによらず、羽根ハブ７近傍まで肉厚平面部１０を
つける必要があった。[0012] Incidentally, showing the change in the Noise when varying the length 1 of the thick planar portion 10 in Figure 3. Thereby, the thick plane portion 1
The optimal value for the length of 0 was determined. The noise due to the disturbance at the trailing edge 8 increases as the wind speed increases, and the magnitude of the generated sound is proportional to the sixth power of the peripheral speed. The size of the thus generated sound Ru Kima the size of the peripheral speed, but the change also the frequency of the sound by the peripheral speed
It is effective to reduce noise generation for each frequency
Therefore, it is necessary to attach the thick plane portion 10 to the vicinity of the blade hub 7 irrespective of the diameter of the blade hub 7 for the blade having a certain outer diameter.
【００１３】このように、本発明の第１実施例の軸流フ
ァンによれば、騒音の発生を低減することができる。As described above, according to the axial flow fan of the first embodiment of the present invention, generation of noise can be reduced.
【００１４】つぎに本発明の第２実施例について、図４
および図５を参照しながら説明する。Next, a second embodiment of the present invention will be described with reference to FIG.
This will be described with reference to FIG.
【００１５】なお、第１実施例と同一箇所には同一番号
を付し、詳細な説明は省略する。図に示すように、軸流
ファン２のブレード６は外径から羽根ハブ７近傍の範囲
全域にわたって、前記ブレード６の周方向断面の背面側
９に、その前縁１３から弦長に対し６０％〜９０％の範
囲内に最大肉厚頂点部１４が設けられており、この最大
肉厚頂点部１４にブレード６の前縁側および後縁側から
向かうにしたがって肉厚がなめらかに増加する形状とし
ている。 The same parts as those in the first embodiment are denoted by the same reference numerals, and detailed description is omitted. As shown in the figure, the blade 6 of the axial fan 2 has a range from the outer diameter to the vicinity of the blade hub 7.
Over the entire region, the back face side 9 of the circumferential cross-section of the blade 6, the maximum thickness apex portion 14 is provided on the front range of 60% to 90% relative to the chord length from the edge 13, the maximum
From the leading edge side and the trailing edge side of the blade 6
The shape is such that the wall thickness increases smoothly as you go
ing.
【００１６】上記構成により、電動機４によって軸流フ
ァン２が回転すると、吸込口１１より吸引された空気は
ブレード６の最大そり点１２の背面側９に剥離を生じよ
うとするが、前記肉厚頂点部１４が設けられているので
剥離が小さくなり騒音の発生を低減することができる。With the above configuration, when the axial fan 2 is rotated by the electric motor 4, the air sucked from the suction port 11 tends to separate on the back side 9 of the maximum warp point 12 of the blade 6. Since the apex portion 14 is provided, peeling is reduced, and generation of noise can be reduced.
【００１７】なお、図５に肉厚頂点部１４の位置を変え
たときの騒音の変化を示す。これにより肉厚頂点部１４
の位置の最適位置を決定した。また、上記第１実施例に
おける肉厚平面部の場合と同様の理由により、ある外径
の羽根に対して、羽根ハブ７の径の大きさによらず、羽
根ハブ７近傍まで肉厚頂点部１４をつける必要があっ
た。[0017] Incidentally, showing the change in the Noise when changing the position of the thick top portion 14 in FIG. 5. As a result, the thickness top 14
The optimal position of the position was determined. Also, in the first embodiment,
For the same reason as in the case of the thick plane portion, it is necessary to attach the thick top portion 14 to the vicinity of the blade hub 7 irrespective of the diameter of the blade hub 7 for the blade having a certain outer diameter. .
【００１８】このように、本発明の第２実施例の軸流フ
ァンによれば、騒音の発生を低減することができるAs described above, the axial fan according to the second embodiment of the present invention can reduce the generation of noise.
【００１９】[0019]
【発明の効果】以上の実施例から明らかなように、本発
明によれば、換気扇または送風機において軸流ファンの
ブレード後端部での空気の流れの剥離を減少させ騒音を
減少させることのできる軸流ファンが提供できる。As apparent from the above embodiment according to the present invention, according to the present invention, it can reduce the noise to reduce the separation of the air flow in the blade trailing edge portion of the axial fan in the ventilation fan or blower An axial fan can be provided.
【図１】本発明の第１実施例の軸流ファンの断面図FIG. 1 is a sectional view of an axial fan according to a first embodiment of the present invention.
【図２】同ブレード断面図FIG. 2 is a sectional view of the blade.
【図３】同肉厚平面部の長さと性能との関連を示す図FIG. 3 is a diagram showing the relationship between the length of the thick flat portion and the performance.
【図４】本発明の第２実施例のブレード断面図FIG. 4 is a sectional view of a blade according to a second embodiment of the present invention.
【図５】同肉厚頂点部の位置と性能との関連を示す図FIG. 5 is a diagram showing the relationship between the position of the top portion of the thickness and the performance.
【図６】従来の軸流ファンの断面図FIG. 6 is a sectional view of a conventional axial fan.
【図７】同ブレード断面図FIG. 7 is a sectional view of the blade.
２ 軸流ファン ６ ブレード ７ 羽根ハブ ８ 後縁 ９ 背面側 １０ 肉厚平面部 １３ 前縁 １４ 最大肉厚頂点部 2 Axial fan 6 Blade 7 Blade hub 8 Trailing edge 9 Back side 10 Thick plane 13 Front edge 14 Maximum thickness top
───────────────────────────────────────────────────── フロントページの続き (56)参考文献 実開 昭56−34097（ＪＰ，Ｕ) (58)調査した分野(Int.Cl.6，ＤＢ名) F04D 29/18 - 29/38──────────────────────────────────────────────────続 き Continuation of the front page (56) References JP-A-56-34097 (JP, U) (58) Field surveyed (Int. Cl. 6 , DB name) F04D 29/18-29/38
Claims (2)
わたるブレード周方向断面の後縁から背面側に、弦長に
対し２％〜３０％の周方向長さで、周方向断面で最も大
きい肉厚平面部を段差状に設けた軸流ファン。1. The entire area from the outer diameter to the vicinity of the blade hub.
To the rear side from the rear edge of Wataru blade circumferential section, in chord length <br/> vs. 2% to 30% of the circumferential length, provided the largest thickness flat portion in the circumferential direction section stepwise Axial fan.
わたるブレード周方向断面の背面側の、前縁から弦長の
６０％〜９０％の範囲内に最大肉厚頂点部を設け、この
最大肉厚頂点部にブレードの前縁側および後縁側から向
かうにしたがって肉厚がなめらかに増加する形状とした
軸流ファン。2. The entire area from the outer diameter to the vicinity of the blade hub.
Wataru blade circumferential sectional rear side, with the largest thickness apex before the range of chord length of 60% to 90% from the edge, the
From the leading edge and trailing edge of the blade to the maximum thickness peak
Axial fan with a shape whose wall thickness increases smoothly .
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP4259315A JP2753182B2 (en) | 1992-09-29 | 1992-09-29 | Axial fan |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP4259315A JP2753182B2 (en) | 1992-09-29 | 1992-09-29 | Axial fan |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH06108997A JPH06108997A (en) | 1994-04-19 |
| JP2753182B2 true JP2753182B2 (en) | 1998-05-18 |
Family
ID=17332375
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP4259315A Expired - Fee Related JP2753182B2 (en) | 1992-09-29 | 1992-09-29 | Axial fan |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2753182B2 (en) |
Families Citing this family (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE69820853T2 (en) * | 1998-03-23 | 2004-11-18 | Spal S.R.L., Correggio | Axial |
| EP0945625B1 (en) * | 1998-03-23 | 2004-03-03 | SPAL S.r.l. | Axial flow fan |
| US6544010B1 (en) * | 2000-06-09 | 2003-04-08 | Lg Electronics Co., Ltd. | Axial flow fan with brushless direct current motor |
| JP4745626B2 (en) * | 2004-06-29 | 2011-08-10 | ループウイング株式会社 | Axial flow blower |
| CN108180169A (en) * | 2018-02-09 | 2018-06-19 | 广东美的厨房电器制造有限公司 | Fan and micro-wave oven |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5634097U (en) * | 1979-08-23 | 1981-04-03 |
-
1992
- 1992-09-29 JP JP4259315A patent/JP2753182B2/en not_active Expired - Fee Related
Also Published As
| Publication number | Publication date |
|---|---|
| JPH06108997A (en) | 1994-04-19 |
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