JPH08240197A - Axial fan - Google Patents
Axial fanInfo
- Publication number
- JPH08240197A JPH08240197A JP7044482A JP4448295A JPH08240197A JP H08240197 A JPH08240197 A JP H08240197A JP 7044482 A JP7044482 A JP 7044482A JP 4448295 A JP4448295 A JP 4448295A JP H08240197 A JPH08240197 A JP H08240197A
- Authority
- JP
- Japan
- Prior art keywords
- blade
- small
- axial
- recesses
- range
- 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.)
- Pending
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
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/26—Rotors specially for elastic fluids
- F04D29/32—Rotors specially for elastic fluids for axial flow pumps
- F04D29/38—Blades
- F04D29/384—Blades characterised by form
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
- F05D2240/00—Components
- F05D2240/20—Rotors
- F05D2240/30—Characteristics of rotor blades, i.e. of any element transforming dynamic fluid energy to or from rotational energy and being attached to a rotor
- F05D2240/306—Characteristics of rotor blades, i.e. of any element transforming dynamic fluid energy to or from rotational energy and being attached to a rotor related to the suction side of a rotor blade
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
(57)【要約】
【目的】 羽根負圧面における前縁側において顕著に生
ずる境界層剥離を効果的に防止して軸流ファンの運転騒
音を低減させる。
【構成】 回転中心となるハブ１の外周に複数枚の羽根
２,２・・を備えてなる軸流ファンにおいて、前記各羽
根２の負圧面２aにおける前縁部に、回転方向の幅が小
さい多数の小凹部（例えば、ディンプルあるいは三角
溝）３,３・・を形成するとともに、該各小凹部３にお
ける回転方向幅を、前記羽根２の周速と小凹部３の回転
方向幅とで定義されるレイノルズ数Ｒｅが１５００〜３
０００の範囲となるように設定している。
(57) [Abstract] [Purpose] Effectively prevent boundary layer separation that occurs remarkably on the leading edge side of the blade suction surface, and reduce the operating noise of the axial fan. In an axial flow fan having a plurality of blades 2, 2, ... On the outer periphery of a hub 1 which is the center of rotation, a width in the rotational direction is small at the front edge portion of the negative pressure surface 2a of each blade 2. A large number of small recesses (for example, dimples or triangular grooves) 3 are formed, and the width of each small recess 3 in the rotational direction is defined by the peripheral speed of the blade 2 and the width of the small recess 3 in the rotational direction. Reynolds number Re of 1500-3
The range is set to 000.
Description
【０００１】[0001]
【産業上の利用分野】本願発明は、空気調和機用室外機
における送風装置として多用されている軸流ファンに関
するものである。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an axial fan that is widely used as a blower in an outdoor unit for an air conditioner.
【０００２】[0002]
【従来の技術】一般に、空気調和機用送風装置として多
用されている軸流ファンは、図１０に示すように、回転
中心となるハブ１の外周に複数枚の羽根２，２・・を備
えて構成されている。2. Description of the Related Art In general, an axial fan, which is widely used as an air conditioner blower, is provided with a plurality of blades 2, 2, ... Is configured.
【０００３】このような構成の軸流ファンを回転させる
と、図１１に示すように、羽根２の負圧面２a上を流れ
る空気流れＦに境界層が発達し、剥離流Ｅが生ずること
となって、空力性能の低下、運転騒音の増大を招くこと
になる。When the axial fan having such a structure is rotated, as shown in FIG. 11, a boundary layer develops in the air flow F flowing on the negative pressure surface 2a of the blade 2 to generate a separated flow E. As a result, aerodynamic performance is deteriorated and driving noise is increased.
【０００４】そこで、軸流ファンの羽根負圧面に多数の
ディンプルを形成することにより、上記境界層の発達を
抑制しようとしたものが既に提案されている(例えば、
特開昭６０ー３５１１９号公報参照)。Therefore, it has already been proposed to suppress the development of the boundary layer by forming a large number of dimples on the suction surface of the blade of the axial fan (for example,
(See JP-A-60-35119).
【０００５】[0005]
【発明が解決しようとする課題】ところで、上記公知例
におけるように羽根負圧面にディンプルを形成する理由
は、ディンプル内に空気の二次流れを生じさせることに
よって、境界層の発達を抑制しようとすることにある
が、ディンプルの形成位置、形状あるいは大きさによっ
ては、その効果が十分でない場合が生ずる。The reason for forming dimples on the blade suction surface as in the above-mentioned known example is to suppress the development of the boundary layer by causing a secondary flow of air in the dimples. However, depending on the position, shape or size of the dimples, the effect may not be sufficient.
【０００６】一方、この種軸流ファンにおいては、羽根
前縁側での境界層剥離により翼面上での大きな圧力変動
を引き起こし、これがファン騒音の主要な音源となって
いるという事実がある。ところが、羽根前縁側（例え
ば、図１１におけるＡ〜Ｂ間）における境界層は極めて
薄いので、ディンプルの大きさによっては渦生成機能が
十分に発揮できないという問題が存する。On the other hand, in this kind of axial flow fan, there is a fact that boundary layer separation on the blade leading edge side causes a large pressure fluctuation on the blade surface, which is a main source of fan noise. However, since the boundary layer on the blade leading edge side (for example, between A and B in FIG. 11) is extremely thin, there is a problem that the vortex generation function cannot be sufficiently exerted depending on the size of the dimple.
【０００７】本願発明は、上記の点に鑑みてなされたも
ので、羽根負圧面における前縁側において顕著に生ずる
境界層剥離を効果的に防止して軸流ファンの運転騒音を
低減させることを目的とするものである。The present invention has been made in view of the above points, and it is an object of the present invention to effectively prevent the boundary layer separation that remarkably occurs on the leading edge side of the blade suction surface to reduce the operating noise of the axial fan. It is what
【０００８】[0008]
【課題を解決するための手段】本願発明の基本構成で
は、上記課題を解決するための手段として、回転中心と
なるハブ１の外周に複数枚の羽根２,２・・を備えてな
る軸流ファンにおいて、前記各羽根２の負圧面２aにお
ける前縁部に、回転方向の幅が小さい多数の小凹部（例
えば、ディンプルあるいは三角溝）３,３・・を形成す
るとともに、該各小凹部３における回転方向幅を、前記
羽根２の周速と小凹部３の回転方向幅とで定義されるレ
イノルズ数Ｒｅが１５００〜３０００の範囲となるよう
に設定している。In the basic configuration of the present invention, as a means for solving the above-mentioned problems, an axial flow having a plurality of blades 2, 2, ... In the fan, a large number of small recesses (for example, dimples or triangular grooves) 3, 3 ... Having a small width in the rotational direction are formed in the front edge portion of the negative pressure surface 2a of each blade 2, and each small recess 3 is formed. The width in the rotation direction is set so that the Reynolds number Re defined by the peripheral speed of the blade 2 and the width of the small recess 3 in the rotation direction is in the range of 1500 to 3000.
【０００９】本願発明の基本構成において、前記羽根２
の負圧面２ａにおける小凹部３，３・・の非形成部分
に、該小凹部３より回転方向幅が大きい大凹部（例え
ば、ディンプルあるいは三角溝）４，４・・を形成する
のが羽根２の後縁側において生ずるであろう境界層剥離
をも効果的に抑制し得る点で好ましい。In the basic structure of the present invention, the blade 2
The blades 2 are formed with large concave portions (for example, dimples or triangular grooves) 4, 4 ... having a larger width in the rotation direction than the small concave portions 3 in the portions where the small concave portions 3, 3 ... Are not formed on the negative pressure surface 2a. It is preferable in that boundary layer separation that may occur on the trailing edge side can be effectively suppressed.
【００１０】また、前記小凹部３，３・・の形成範囲
を、周方向に関しては前縁２ｂから０．０３Ｌ〜０．０
７Ｌ（ここで、Ｌ：平均半径での翼弦長）の範囲に、半
径方向に関しては羽根平均半径位置を基準として、ハブ
側およびチップ側にそれぞれ０．３Ｂ〜０．５Ｂ（ここ
で、Ｂ：羽根スパン長さ）の範囲に設定するのが最も境
界層剥離が顕著な領域での剥離防止を効果的に行い得る
点で好ましい。ここで、羽根ハブ側半径をＲ1、羽根チ
ップ側半径をＲ2とした場合、羽根平均半径Ｒは（Ｒ1＋
Ｒ2）／２、羽根スパン長さＢは（Ｒ2−Ｒ1）である。The range of formation of the small recesses 3, 3, ... Is 0.03L to 0.0 from the front edge 2b in the circumferential direction.
In the range of 7L (where L is the chord length at the average radius), 0.3B to 0.5B (here, B on the hub side and the tip side, respectively, with reference to the blade average radial position in the radial direction. It is preferable to set it in the range of (blade span length) from the viewpoint of effectively preventing separation in the region where boundary layer separation is most noticeable. Here, when the blade hub-side radius is R 1 and the blade tip-side radius is R 2 , the blade average radius R is (R 1 +
R 2 ) / 2, and the blade span length B is (R 2 −R 1 ).
【００１１】[0011]
【作用】本願発明の基本構成では、上記手段によって次
のような作用が得られる。In the basic configuration of the present invention, the following actions can be obtained by the above means.
【００１２】即ち、小凹部（例えば、ディンプルあるい
は三角溝）３の大きさが、羽根２の前縁側において二次
流れを生じさせるに最適な範囲とされているため、羽根
負圧面２aにおける前縁部での境界層発達が効果的に抑
制されることとなる。なお、Ｒｅ＜１５００の場合に
は、小凹部３内への空気流入が難しくなって二次流れが
期待できなくなり、Ｒｅ＞３０００の場合には、回転方
向の幅が大きくなり過ぎて小凹部３での二次流れが期待
できなくなる。That is, since the size of the small concave portion (for example, dimple or triangular groove) 3 is set to the optimum range for producing the secondary flow on the leading edge side of the blade 2, the leading edge of the blade negative pressure surface 2a. Boundary layer development in the area will be effectively suppressed. In the case of Re <1500, it becomes difficult for the air to flow into the small recesses 3 and a secondary flow cannot be expected. In the case of Re> 3000, the width in the rotational direction becomes too large and the small recesses 3 are not formed. The secondary flow in can not be expected.
【００１３】本願発明の基本構成において、前記羽根２
の負圧面２ａにおける小凹部３，３・・の非形成部分
に、該小凹部３より回転方向幅が大きい大凹部（例え
ば、ディンプルあるいは三角溝）４，４・・を形成した
場合、羽根２の後縁側において生ずるであろう境界層剥
離をも大凹部４において生ずる二次流れにより効果的に
抑制される。In the basic structure of the present invention, the blade 2
When the large recesses (for example, dimples or triangular grooves) 4, 4 ... having a larger width in the rotation direction than the small recesses 3 are formed in the portions where the small recesses 3, 3 ,. Boundary layer separation that may occur on the trailing edge side is effectively suppressed by the secondary flow generated in the large recess 4.
【００１４】また、前記小凹部３，３・・の形成範囲
を、周方向に関しては前縁２ｂから０．０３Ｌ〜０．０
７Ｌ（ここで、Ｌ：平均半径での翼弦長）の範囲に、半
径方向に関しては羽根平均半径位置を基準として、ハブ
側およびチップ側にそれぞれ０．３Ｂ〜０．５Ｂ（ここ
で、Ｂ：羽根スパン長さ）の範囲に設定した場合、最も
境界層剥離が顕著な領域での剥離防止が効果的に達成で
きる。The range of formation of the small recesses 3, 3 ... Is 0.03L to 0.0 from the front edge 2b in the circumferential direction.
In the range of 7L (where L is the chord length at the average radius), 0.3B to 0.5B (here, B on the hub side and the tip side, respectively, with reference to the blade average radial position in the radial direction. : Blade span length), it is possible to effectively achieve separation prevention in the region where boundary layer separation is most prominent.
【００１５】[0015]
【発明の効果】本願発明によれば、回転中心となるハブ
１の外周に複数枚の羽根２,２・・を備えてなる軸流フ
ァンにおいて、羽根負圧面２ａの前縁部に形成された小
凹部（例えば、ディンプルあるいは三角溝）３の大きさ
を、羽根２の前縁側において二次流れを生じさせるに最
適な範囲となしているので、羽根負圧面２aにおける前
縁部での境界層発達が効果的に抑制されることとなり、
軸流ファンの運転騒音低減に大いに寄与するという優れ
た効果がある。According to the present invention, in the axial fan having a plurality of blades 2, 2, ... On the outer periphery of the hub 1 which is the center of rotation, it is formed at the front edge of the blade negative pressure surface 2a. Since the size of the small recesses (for example, dimples or triangular grooves) 3 is set to the optimum range for producing the secondary flow on the leading edge side of the blade 2, the boundary layer at the leading edge portion of the blade suction surface 2a. Development is effectively suppressed,
It has an excellent effect that it greatly contributes to the reduction of the operating noise of the axial fan.
【００１６】[0016]
【実施例】以下、添付の図面を参照して、本願発明の幾
つかの好適な実施例を説明する。DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Some preferred embodiments of the present invention will be described below with reference to the accompanying drawings.
【００１７】実施例１ 図１および図２には、本願発明の実施例１にかかる軸流
ファンの要部が示されている。Embodiment 1 FIGS. 1 and 2 show the main part of an axial flow fan according to Embodiment 1 of the present invention.
【００１８】本実施例の軸流ファンは、空気調和機用室
外機の送風装置として多用されているものであり、図１
に示すように、回転中心となるハブ１の外周に４枚の羽
根２,２,２,２を備えた構成とされている。The axial fan according to the present embodiment is widely used as a blower for an outdoor unit for an air conditioner.
As shown in FIG. 3, the hub 1 serving as the center of rotation is provided with four blades 2, 2, 2, 2.
【００１９】そして、前記各羽根２の負圧面２aにおけ
る前縁部には、多数の小凹部である小ディンプル３,３
・・が形成されている。The front edge of the negative pressure surface 2a of each blade 2 has a large number of small dimples 3, 3 which are small recesses.
.. is formed.
【００２０】該小ディンプル３,３・・の形成によっ
て、図２に示すように、羽根負圧面２aにおける空気流
れＦにより各小ディンプル３内に二次流れが生じ、境界
層発達が効果的に抑制されることとなっており、剥離流
の発生も大幅に抑制されることとなる。By the formation of the small dimples 3, 3, ... As shown in FIG. 2, a secondary flow is generated in each small dimple 3 by the air flow F on the blade negative pressure surface 2a, and the boundary layer is effectively developed. It is supposed to be suppressed, and the generation of the separated flow will be greatly suppressed.
【００２１】ところで、前記各小ディンプル３における
回転方向幅（換言すれば、直径ｄ）は、前記羽根２の周
速と小ディンプル３の直径ｄとで定義されるレイノルズ
数Ｒｅが１５００〜３０００の範囲となるように設定さ
れ、また、前記小ディンプル３，３・・の形成範囲は、
周方向に関しては前縁２ｂから０．０３Ｌ〜０．０７Ｌ
（ここで、Ｌ：平均半径での翼弦長）の範囲に、半径方
向に関しては羽根平均半径位置を基準として、ハブ側お
よびチップ側にそれぞれ０．３Ｂ〜０．５Ｂ（ここで、
Ｂ：羽根スパン長さ）の範囲に設定されている。By the way, the width of each small dimple 3 in the rotational direction (in other words, the diameter d) is such that the Reynolds number Re defined by the peripheral speed of the blade 2 and the diameter d of the small dimple 3 is 1500 to 3000. And the formation range of the small dimples 3, 3 ...
Regarding the circumferential direction, 0.03L to 0.07L from the front edge 2b
Within the range of (where L is the chord length at the average radius), 0.3B to 0.5B (here, on the hub side and the tip side, respectively, with reference to the blade average radius position in the radial direction.
(B: blade span length).
【００２２】従って、小ディンプル３の大きさが、羽根
２の前縁側において二次流れを生じさせるに最適な範囲
とされ、羽根負圧面２aにおける前縁部での境界層発達
が効果的に抑制されることとなる。なお、Ｒｅ＜１５０
０の場合には、小凹部３内への空気流入が難しくなって
二次流れが期待できなくなり、Ｒｅ＞３０００の場合に
は、回転方向の幅が大きくなり過ぎて小凹部３での二次
流れが期待できなくなる。また、前記小ディンプル３，
３・・の形成範囲が、周方向に関しては前縁２ｂから
０．０３Ｌ〜０．０７Ｌ（ここで、Ｌ：平均半径での翼
弦長）の範囲に、半径方向に関しては羽根平均半径位置
を基準として、ハブ側およびチップ側にそれぞれ０．３
Ｂ〜０．５Ｂ（ここで、Ｂ：羽根スパン長さ）の範囲に
設定したことにより、最も境界層剥離が顕著な領域での
剥離防止が効果的に達成でき、軸流ファンの運転騒音低
減に大いに寄与するのである。Therefore, the size of the small dimples 3 is set to an optimum range for producing a secondary flow on the leading edge side of the blade 2, and the development of the boundary layer at the leading edge portion of the blade suction surface 2a is effectively suppressed. Will be done. Re <150
In the case of 0, the inflow of air into the small recess 3 becomes difficult, and the secondary flow cannot be expected. In the case of Re> 3000, the width in the rotational direction becomes too large and the secondary flow in the small recess 3 becomes too large. The flow cannot be expected. Also, the small dimples 3,
The formation range of 3 ... is in the range of 0.03L to 0.07L (where L is the chord length at the average radius) from the leading edge 2b in the circumferential direction, and the blade average radius position is in the radial direction. As a standard, 0.3 each on the hub side and the tip side
By setting in the range of B to 0.5B (here, B: blade span length), separation prevention can be effectively achieved in the region where boundary layer separation is most noticeable, and operation noise of the axial fan is reduced. Greatly contribute to.
【００２３】ちなみに、本実施例の軸流ファン（即ち、
前縁部にディンプルを形成したもの）と従来の軸流ファ
ン（即ち、小ディンプルを形成していないもの）とを用
いて、運転騒音および比騒音について比較したところ、
図４および図５に示す結果が得られた。ここで、両軸流
ファンは６６０ｒｐｍの回転数で運転された。By the way, the axial flow fan of this embodiment (that is,
When a dimple is formed on the front edge) and a conventional axial fan (that is, a small dimple is not formed) are used to compare the operating noise and the specific noise,
The results shown in FIGS. 4 and 5 were obtained. Here, the biaxial fan was operated at a rotation speed of 660 rpm.
【００２４】上記結果によれば、吹出空気流量が３０ｍ
3／ｍｉｎ近傍において運転騒音および比騒音の低減効
果が得られている。これは、羽根負圧面２ａの前縁部に
形成された小ディンプル３による境界層剥離防止効果が
得られた結果にほかならない。According to the above results, the flow rate of blown air is 30 m.
The effect of reducing operating noise and specific noise is obtained near 3 / min. This is nothing but the result that the boundary layer separation prevention effect is obtained by the small dimples 3 formed at the front edge portion of the blade negative pressure surface 2a.
【００２５】実施例２ 図６および図７には、本願発明の実施例２にかかる軸流
ファンが示されている。Embodiment 2 FIGS. 6 and 7 show an axial flow fan according to Embodiment 2 of the present invention.
【００２６】本実施例の場合、実施例１の軸流ファンに
おいて、羽根２の負圧面２ａにおける小ディンプル３，
３・・の非形成部分に、該各小ディンプル３より回転方
向幅（即ち、直径）が大きい大ディンプル４，４・・が
形成されている。この大ディンプル４，４・・の形成に
よって、羽根２の後縁側において生ずるであろう境界層
剥離をも大凹部４，４・・において生ずる二次流れによ
り効果的に抑制することができ、軸流ファンの運転騒音
低減に大いに寄与する。なお、本実施例の場合、各羽根
２における曲率半径が半径方向外側に向かうにしたがっ
て大きくなっているため、大ディンプル４，４・・の直
径も、半径方向外側に向かうにしたがって大きくされて
いる。その他の構成および作用効果は実施例１と同様な
ので重複を避けて説明を省略する。In the case of this embodiment, in the axial fan of the first embodiment, the small dimples 3 on the suction surface 2a of the blade 2 are small.
The large dimples 4, 4, ..., Which have a larger width (that is, the diameter) in the rotational direction than the respective small dimples 3, are formed in the portions where 3 ... By forming the large dimples 4, 4, ..., Boundary layer separation that may occur on the trailing edge side of the blade 2 can be effectively suppressed by the secondary flow generated in the large recesses 4, 4 ,. It greatly contributes to the reduction of operating noise of the flow fan. In the case of this embodiment, the radius of curvature of each blade 2 increases toward the outer side in the radial direction, so the diameters of the large dimples 4, 4, ... Also increase toward the outer side in the radial direction. . Other configurations, functions and effects are the same as those of the first embodiment, and the description will be omitted to avoid duplication.
【００２７】実施例３ 図８および図９には、本願発明の実施例３にかかる軸流
ファンが示されている。Embodiment 3 FIGS. 8 and 9 show an axial flow fan according to Embodiment 3 of the present invention.
【００２８】本実施例の場合、羽根負圧面２ａの前縁部
に形成される小凹部３，３・・として、実施例１におけ
る小ディンプルに代えて回転方向に直交する方向に長さ
を有する小三角溝を採用している。なお、実施例２にお
けると同様に小三角溝３，３・・が形成されていない部
分に該各小三角溝３より回転方向溝幅が大きな大三角溝
４，４・・を形成する場合もある。その他の構成および
作用効果は実施例１と同様なので重複を避けて説明を省
略する。In the case of this embodiment, the small recesses 3, 3 ... Formed at the front edge of the blade negative pressure surface 2a have a length in the direction orthogonal to the rotation direction in place of the small dimples in the first embodiment. Uses a small triangular groove. In the same manner as in the second embodiment, the large triangular grooves 4, 4, ... Which have a larger groove width in the rotational direction than the small triangular grooves 3 may be formed in the portions where the small triangular grooves 3, 3 ,. is there. Other configurations, functions and effects are the same as those of the first embodiment, and the description will be omitted to avoid duplication.
【００２９】本願発明は、上記各実施例の構成に限定さ
れるものではなく、発明の要旨を逸脱しない範囲におい
て適宜設計変更可能なことは勿論である。The invention of the present application is not limited to the configuration of each of the above-described embodiments, and it goes without saying that the design can be appropriately changed without departing from the scope of the invention.
【図１】本願発明の実施例１にかかる軸流ファンにおけ
る羽根の一つを負圧面側から見た正面図である。FIG. 1 is a front view of one of the blades of an axial flow fan according to a first embodiment of the present invention as viewed from a suction surface side.
【図２】本願発明の実施例１にかかる軸流ファンにおけ
る羽根の部分拡大断面図である。FIG. 2 is a partially enlarged cross-sectional view of blades in the axial flow fan according to the first embodiment of the present invention.
【図３】本願発明の実施例１にかかる軸流ファンにおけ
るディンプル部分の拡大断面図である。FIG. 3 is an enlarged sectional view of a dimple portion in the axial fan according to the first embodiment of the present invention.
【図４】本願発明の実施例１にかかる軸流ファンと従来
例とにおける吹出空気流量と運転騒音との関係を示す特
性図である。FIG. 4 is a characteristic diagram showing the relationship between the blown air flow rate and the operating noise in the axial flow fan according to the first embodiment of the present invention and the conventional example.
【図５】本願発明の実施例１にかかる軸流ファンと従来
例とにおける吹出空気流量と比騒音との関係を示す特性
図である。FIG. 5 is a characteristic diagram showing the relationship between the blown air flow rate and the specific noise in the axial flow fan according to the first embodiment of the present invention and the conventional example.
【図６】本願発明の実施例２にかかる軸流ファンにおけ
る羽根の一つを負圧面側から見た正面図である。FIG. 6 is a front view of one of the blades of the axial flow fan according to the second embodiment of the present invention as viewed from the suction surface side.
【図７】本願発明の実施例２にかかる軸流ファンにおけ
る羽根の部分拡大断面図である。FIG. 7 is a partially enlarged cross-sectional view of blades of an axial flow fan according to a second embodiment of the present invention.
【図８】本願発明の実施例３にかかる軸流ファンにおけ
る羽根の一つを負圧面側から見た正面図である。FIG. 8 is a front view of one of the blades of the axial flow fan according to the third embodiment of the present invention as viewed from the suction surface side.
【図９】本願発明の実施例３にかかる軸流ファンにおけ
る羽根の部分拡大断面図である。FIG. 9 is a partial enlarged cross-sectional view of blades in an axial flow fan according to a third embodiment of the present invention.
【図１０】従来の軸流ファンを負圧面側から見た正面図
である。FIG. 10 is a front view of a conventional axial flow fan as viewed from the suction surface side.
【図１１】従来の軸流ファンにおける羽根の部分拡大断
面図である。FIG. 11 is a partially enlarged cross-sectional view of blades in a conventional axial flow fan.
１はハブ、２は羽根、２aは負圧面、２ｂは前縁、３は
小凹部（ディンプルあるいは三角溝）、４は大凹部（デ
ィンプルあるいは三角溝）。1 is a hub, 2 is a blade, 2a is a negative pressure surface, 2b is a front edge, 3 is a small recess (dimple or triangular groove), and 4 is a large recess (dimple or triangular groove).
Claims (5)
の羽根(２),(２)・・を備えてなる軸流ファンであっ
て、前記各羽根(２)の負圧面(２a)における前縁部に
は、回転方向の幅が小さい多数の小凹部(３),(３)・・
を形成するとともに、該各小凹部(３)における回転方向
幅を、前記羽根（２）の周速と小凹部(３)の回転方向幅
とで定義されるレイノルズ数Ｒｅが１５００〜３０００
の範囲となるように設定したことを特徴とする軸流ファ
ン。1. An axial fan comprising a plurality of blades (2), (2), ... Around the outer periphery of a hub (1) which is the center of rotation, the negative pressure surface ( 2a) has a large number of small recesses (3), (3) ...
And the Reynolds number Re defined by the circumferential speed of the blades (2) and the width of the small recesses (3) in the rotation direction is 1500 to 3000.
Axial fan, which is set to be within the range.
小凹部（３），（３）・・の非形成部分には、該各小凹
部（３）より回転方向幅が大きい大凹部（４），（４）
・・を形成したことを特徴とする前記請求項１記載の軸
流ファン。2. A large recess having a rotation direction width larger than that of each of the small recesses (3), (3), ... In the non-forming portion of the negative pressure surface (2a) of the blade (2). (4), (4)
The axial flow fan according to claim 1, characterized in that.
（４）をディンプルにより構成したことを特徴とする前
記請求項１および請求項２のいずれか一項記載の軸流フ
ァン。3. The axial fan according to claim 1, wherein each of the small recesses (3) and each of the large recesses (4) are constituted by dimples.
（４）を回転方向に直交する方向に長さを有する三角溝
により構成したことを特徴とする前記請求項１および請
求項２のいずれか一項記載の軸流ファン。4. The small recesses (3) and the large recesses (4) are constituted by triangular grooves each having a length in a direction orthogonal to the rotation direction. The axial fan according to any one of claims.
囲を、周方向に関しては前縁（２ｂ）から０．０３Ｌ〜
０．０７Ｌ（ここで、Ｌ：平均半径での翼弦長）の範囲
に、半径方向に関しては羽根平均半径位置を基準とし
て、ハブ側およびチップ側にそれぞれ０．３Ｂ〜０．５
Ｂ（ここで、Ｂ：羽根スパン長さ）の範囲に設定したこ
とを特徴とする前記請求項１ないし請求項４のいずれか
一項記載の軸流ファン。5. The formation range of the small recesses (3), (3), ... Is 0.03L to the circumferential direction from the front edge (2b).
Within the range of 0.07L (where L is the chord length at the average radius), 0.3B to 0.5 on the hub side and the tip side, respectively, with reference to the blade average radial position in the radial direction.
The axial fan according to any one of claims 1 to 4, wherein the axial flow fan is set in a range of B (where B: blade span length).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP7044482A JPH08240197A (en) | 1995-03-03 | 1995-03-03 | Axial fan |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP7044482A JPH08240197A (en) | 1995-03-03 | 1995-03-03 | Axial fan |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH08240197A true JPH08240197A (en) | 1996-09-17 |
Family
ID=12692768
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP7044482A Pending JPH08240197A (en) | 1995-03-03 | 1995-03-03 | Axial fan |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH08240197A (en) |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2000345995A (en) * | 1999-06-03 | 2000-12-12 | Daikin Ind Ltd | fan |
| JP2002317797A (en) * | 2001-04-19 | 2002-10-31 | Ishikawajima Harima Heavy Ind Co Ltd | Compressor blade and its pressure loss reduction method |
| JP2002317795A (en) * | 2001-02-15 | 2002-10-31 | Ebara Corp | Flow separation control structure for blade of pump impeller |
| WO2010104083A1 (en) * | 2009-03-10 | 2010-09-16 | ダイキン工業株式会社 | Crossflow fan and air conditioner provided with same |
| CN103511340A (en) * | 2012-06-28 | 2014-01-15 | 珠海格力电器股份有限公司 | Axial flow fan blade and air conditioner comprising same |
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| JPWO2019030868A1 (en) * | 2017-08-09 | 2020-03-19 | 三菱電機株式会社 | Propeller fan, blower and refrigeration cycle device |
| CN112855610A (en) * | 2021-03-26 | 2021-05-28 | 珠海格力电器股份有限公司 | Axial flow fan blade, axial flow fan and air conditioner outdoor unit |
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-
1995
- 1995-03-03 JP JP7044482A patent/JPH08240197A/en active Pending
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|---|---|---|---|---|
| JP2000345995A (en) * | 1999-06-03 | 2000-12-12 | Daikin Ind Ltd | fan |
| JP2002317795A (en) * | 2001-02-15 | 2002-10-31 | Ebara Corp | Flow separation control structure for blade of pump impeller |
| JP2002317797A (en) * | 2001-04-19 | 2002-10-31 | Ishikawajima Harima Heavy Ind Co Ltd | Compressor blade and its pressure loss reduction method |
| US9046110B2 (en) | 2009-03-10 | 2015-06-02 | Daikin Industries, Ltd. | Crossflow fan and air conditioner provided with same |
| JP2010236540A (en) * | 2009-03-10 | 2010-10-21 | Daikin Ind Ltd | Cross flow fan and air conditioner equipped with the same |
| CN102341601A (en) * | 2009-03-10 | 2012-02-01 | 大金工业株式会社 | Crossflow fan and air conditioner provided with same |
| AU2010222097B2 (en) * | 2009-03-10 | 2012-10-11 | Daikin Industries, Ltd. | Crossflow fan and air conditioner provided with same |
| WO2010104083A1 (en) * | 2009-03-10 | 2010-09-16 | ダイキン工業株式会社 | Crossflow fan and air conditioner provided with same |
| CN103511340A (en) * | 2012-06-28 | 2014-01-15 | 珠海格力电器股份有限公司 | Axial flow fan blade and air conditioner comprising same |
| CN103573703A (en) * | 2012-07-31 | 2014-02-12 | 珠海格力电器股份有限公司 | Axial flow fan blade |
| CN103573703B (en) * | 2012-07-31 | 2016-03-09 | 珠海格力电器股份有限公司 | Axial flow fan blade |
| CN103711712A (en) * | 2012-09-28 | 2014-04-09 | 大金工业株式会社 | Blower |
| US10662975B2 (en) | 2015-04-08 | 2020-05-26 | Horton, Inc. | Fan blade surface features |
| US10539157B2 (en) | 2015-04-08 | 2020-01-21 | Horton, Inc. | Fan blade surface features |
| JPWO2019030868A1 (en) * | 2017-08-09 | 2020-03-19 | 三菱電機株式会社 | Propeller fan, blower and refrigeration cycle device |
| CN109386425A (en) * | 2017-08-09 | 2019-02-26 | 新疆工程学院 | The pneumatic equipment bladess and wind energy conversion system of a kind of linear micro- cavernous structure of blade inlet edge |
| WO2020028010A1 (en) * | 2018-08-02 | 2020-02-06 | Horton, Inc. | Low solidity vehicle cooling fan |
| EP3830424A4 (en) * | 2018-08-02 | 2022-06-08 | Horton, Inc. | LOW FULLNESS VEHICLE COOLING FAN |
| US11767761B2 (en) | 2018-08-02 | 2023-09-26 | Horton, Inc. | Low solidity vehicle cooling fan |
| CN114483644A (en) * | 2020-11-12 | 2022-05-13 | 佛山市顺德区美的洗涤电器制造有限公司 | Centrifugal impeller, centrifugal fan and range hood |
| CN114483644B (en) * | 2020-11-12 | 2024-03-26 | 佛山市顺德区美的洗涤电器制造有限公司 | Centrifugal impeller, centrifugal fan and fume absorbing equipment |
| CN112855610A (en) * | 2021-03-26 | 2021-05-28 | 珠海格力电器股份有限公司 | Axial flow fan blade, axial flow fan and air conditioner outdoor unit |
| CN116733774A (en) * | 2022-03-02 | 2023-09-12 | 广州雷辰机电技术有限公司 | Impeller, fan and dust collector |
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