JP2013160142A - Impeller structure of axial flow fan - Google Patents
Impeller structure of axial flow fan Download PDFInfo
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- JP2013160142A JP2013160142A JP2012022954A JP2012022954A JP2013160142A JP 2013160142 A JP2013160142 A JP 2013160142A JP 2012022954 A JP2012022954 A JP 2012022954A JP 2012022954 A JP2012022954 A JP 2012022954A JP 2013160142 A JP2013160142 A JP 2013160142A
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- 230000003746 surface roughness Effects 0.000 claims description 14
- 239000011347 resin Substances 0.000 claims description 8
- 229920005989 resin Polymers 0.000 claims description 8
- 238000010422 painting Methods 0.000 claims description 3
- 238000007747 plating Methods 0.000 claims description 3
- 238000007740 vapor deposition Methods 0.000 claims description 3
- 230000003068 static effect Effects 0.000 abstract description 7
- 230000000694 effects Effects 0.000 description 3
- 238000000034 method Methods 0.000 description 3
- 238000000465 moulding Methods 0.000 description 3
- 230000006866 deterioration Effects 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 230000001174 ascending effect Effects 0.000 description 1
- 238000007664 blowing Methods 0.000 description 1
- 239000011248 coating agent Substances 0.000 description 1
- 238000000576 coating method Methods 0.000 description 1
- 238000011038 discontinuous diafiltration by volume reduction Methods 0.000 description 1
- 239000004744 fabric Substances 0.000 description 1
- 238000009499 grossing Methods 0.000 description 1
- 238000001746 injection moulding Methods 0.000 description 1
- 239000002184 metal Substances 0.000 description 1
- 238000001000 micrograph Methods 0.000 description 1
- 230000002093 peripheral effect Effects 0.000 description 1
- 238000005498 polishing Methods 0.000 description 1
- 238000000926 separation method Methods 0.000 description 1
Abstract
Description
本発明は軸流ファンに関し、特にインペラの表面形状に関する。 The present invention relates to an axial fan, and more particularly to a surface shape of an impeller.
ファンモータの基本構造は、インペラを有するモータと、このモータを支持するハウジング（ケーシング）からなり、インペラは樹脂成形によって形成されるものが多い。成形品の表面の状態は軸流ファンの風量、騒音などの特性に大きな影響を及ぼす。例えば、インペラの回転によって生じる空気流がブレード面より離脱してしまい、その離脱領域には渦状の気流が起き、これにより騒音を増加させ、騒音レベル、トルク、風量―静圧特性ならびに静圧効率特性の悪化を招く問題がある。これに対し、インペラ表面またはハウジング内周面を通過する空気流の状態に着目し、インペラ又はハウジングの表面凹凸の高低差を小さくし、表面を滑らかにすることにより特性を向上させる方法が開示されている（例えば、特許文献１参照）。 The basic structure of a fan motor consists of a motor having an impeller and a housing (casing) that supports the motor, and the impeller is often formed by resin molding. The surface condition of the molded product has a great influence on the characteristics of the axial flow fan, such as air flow and noise. For example, the air flow generated by the rotation of the impeller is detached from the blade surface, and a vortex-like air current is generated in the separation region, thereby increasing noise, noise level, torque, air volume-static pressure characteristics, and static pressure efficiency. There is a problem that causes deterioration of characteristics. On the other hand, paying attention to the state of the air flow passing through the impeller surface or the inner peripheral surface of the housing, a method for improving the characteristics by reducing the level difference of the surface unevenness of the impeller or the housing and smoothing the surface is disclosed. (For example, refer to Patent Document 1).
また、複数枚の羽根を放射状に設けて形成されるプロペラフアンにおいて、羽根の負圧面全体を表面粗さ１００Ｓ以上１０００Ｓ以下の粗面とすることにより、騒音を低下できることが開示されている（例えば、特許文献２参照）。 Further, it is disclosed that in a propeller fan formed by providing a plurality of blades radially, noise can be reduced by making the entire suction surface of the blades a rough surface having a surface roughness of 100S to 1000S (for example, , See Patent Document 2).
軸流ファンにおいては、インペラの正圧面と負圧面で空気流の状態が異なる。このため、騒音を低減したり、送風効率を高めるためには、インペラの正圧面と負圧面の表面形状を、それぞれの空気流に応じて別個に制御する必要がある。 In the axial fan, the airflow state differs between the pressure surface and the suction surface of the impeller. For this reason, in order to reduce noise or increase the blowing efficiency, it is necessary to control the surface shapes of the pressure surface and the suction surface of the impeller separately according to the respective air flows.
特許文献１に開示されている方法では、インペラ表面の表面凹凸高低差を３μｍ未満としているが、インペラの正圧面と負圧面で区別はしておらず一様の表面粗さとしているため、効果が不十分であるという問題があった。また、特許文献２に開示されている方法では、羽根の負圧面のみを表面粗さ１００Ｓ以上１０００Ｓ以下の粗面としており、正圧面の表面粗さについては考慮していないので、やはり効果が不十分であるという問題があった。さらに、表面粗さの定義のみでは様々な表面形状が存在するため、効果的な形状を一義的に規定することができず、特性が得られないばかりか騒音が増大する、効果のバラツキが大きく再現性にも乏しい、騒音低減の効果は得られても風量低下や消費電力増大などの特性劣化を伴う等、問題があった。 In the method disclosed in Patent Document 1, the surface unevenness height difference of the impeller surface is set to less than 3 μm. However, since the pressure surface and the suction surface of the impeller are not distinguished from each other, the surface roughness is uniform. There was a problem that was insufficient. In addition, in the method disclosed in Patent Document 2, only the suction surface of the blade is a rough surface having a surface roughness of 100S or more and 1000S or less, and the surface roughness of the pressure surface is not taken into consideration, so that the effect is still ineffective. There was a problem that it was enough. Furthermore, since there are various surface shapes only by the definition of the surface roughness, the effective shape cannot be uniquely defined, and not only the characteristics cannot be obtained, but also the noise increases, and the effect varies greatly. There are problems such as poor reproducibility, noise reduction effect, and characteristic deterioration such as air volume reduction and power consumption increase.
本発明は、上記の問題に鑑みなされたもので、インペラの表面粗さを正圧面と負圧面で個々に制御することにより、騒音の発生を低減し、Ｐ−Ｑ（静圧−風量）特性を改善し、さらに消費電力を低減した軸流ファンを提供することを目的とする。 The present invention has been made in view of the above problems, and by controlling the surface roughness of the impeller individually on the pressure surface and the suction surface, the generation of noise is reduced, and the PQ (static pressure-air volume) characteristics. An object of the present invention is to provide an axial fan with improved power consumption and reduced power consumption.
上記課題を解決するために、本発明の軸流ファンの特徴は、モータと、そのモータによって回転するインペラとを備え、そのインペラの正圧面の表面粗さをそのインペラの負圧面４の表面粗さより大きくすることを要旨とする。 In order to solve the above-mentioned problems, the axial fan according to the present invention includes a motor and an impeller that is rotated by the motor, and the surface roughness of the pressure surface of the impeller is set to the surface roughness of the suction surface 4 of the impeller. The main point is to make it larger.
本発明の軸流ファンにおいては、インペラの正圧面及びインペラの負圧面が、ミクロ的には曲率半径で規定できる丸みを帯びた粗さ形状を有し、インペラの正圧面の算術平均粗さＲａが１〜１００μｍの範囲に、曲率半径ＲａｄＣｒｖが１，０００〜１０，０００μｍの範囲にあるとともに、インペラの負圧面の算術平均粗さＲａ＜０．５μｍ、曲率半径ＲａｄＣｒｖ＞１０，０００μｍであることが好ましい。 In the axial fan of the present invention, the pressure surface of the impeller and the suction surface of the impeller have a rounded roughness shape that can be microscopically defined by the radius of curvature, and the arithmetic average roughness Ra of the pressure surface of the impeller. Is in the range of 1 to 100 μm, the radius of curvature RadCrv is in the range of 1,000 to 10,000 μm, the arithmetic mean roughness Ra <0.5 μm of the impeller suction surface, and the radius of curvature RadCrv> 10,000 μm. Is preferred.
インペラの正圧面及びインペラの負圧面の粗さ形状は、カッター等の鋭利な刃物で形成される矩形をなした粗面ではなく、紙やすり等の研磨材が塗布された布紙で形成される丸みを帯びた粗面であるのが好ましい。 The roughness of the pressure surface of the impeller and the suction surface of the impeller is not a rectangular rough surface formed by a sharp blade such as a cutter, but is formed of cloth paper coated with an abrasive such as sandpaper. It is preferably a rounded rough surface.
さらに、本発明の軸流ファンにおいては、インペラの正圧面及び前記インペラの負圧面は、蒸着、塗装又はメッキのいずれかによって形成された被膜を有する構成でもよい。 Furthermore, in the axial fan of the present invention, the pressure surface of the impeller and the negative pressure surface of the impeller may have a coating formed by any one of vapor deposition, painting, or plating.
本発明によれば、インペラの表面粗さを正圧面と負圧面で個々に制御することにより、騒音の発生を低減し、Ｐ−Ｑ（静圧−風量）特性を改善し、さらに消費電力を低減した軸流ファンを提供することができる。 According to the present invention, the surface roughness of the impeller is individually controlled on the pressure surface and the suction surface, thereby reducing noise generation, improving the PQ (static pressure-air volume) characteristics, and further reducing power consumption. A reduced axial fan can be provided.
以下、添付図面を参照して、本発明を実施するための形態（以下、実施形態という。）について詳細に説明する。 DESCRIPTION OF EMBODIMENTS Hereinafter, embodiments for carrying out the present invention (hereinafter referred to as embodiments) will be described in detail with reference to the accompanying drawings.
図１は、本発明の実施形態に係る軸流ファンの外観図である。 FIG. 1 is an external view of an axial fan according to an embodiment of the present invention.
本発明の実施形態に係る軸流ファン１は、モータ駆動部２の周囲に中心対称に複数枚のインペラ３を備えており、軸流ファン１が矢印の方向に回転するとインペラ３の紙面の表側が負圧面４となり、インペラ３の紙面の裏側が正圧面５（図示せず）となる。インペラ３の枚数は、特に限定しない。軸流ファン１は、内部に空気流路を設けたハウジング（図示せず）に収納することができる。 An axial fan 1 according to an embodiment of the present invention includes a plurality of impellers 3 symmetrically about a motor drive unit 2. When the axial fan 1 rotates in the direction of an arrow, the front side of the surface of the impeller 3 is illustrated. Becomes the negative pressure surface 4, and the back side of the paper surface of the impeller 3 becomes the positive pressure surface 5 (not shown). The number of impellers 3 is not particularly limited. The axial fan 1 can be housed in a housing (not shown) having an air flow path therein.
モータ駆動部２とインペラ３を含む軸流ファン１は、樹脂を用いて射出成形等により一体成形することができるが、モータ駆動部２とインペラ３をそれぞれ樹脂又は金属で個別に製作して軸流ファン１に組み立ててもよい。 The axial fan 1 including the motor drive unit 2 and the impeller 3 can be integrally formed by injection molding or the like using resin. However, the motor drive unit 2 and the impeller 3 are individually manufactured from resin or metal, respectively. You may assemble to the flow fan 1.
インペラ３の表面は、成形した樹脂のままでもよく、耐摩耗性等の観点から蒸着、塗装又はメッキ等による被膜を形成してもよい。樹脂の成形金型の表面は研磨面である。本実施形態においては、樹脂の成形によって製作したインペラ３をそのまま用いて、インペラ３の正圧面５と負圧面４に別々に所定の表面形状を形成し、これを複数枚モータ駆動部２に取り付けて軸流ファン１を構成した。 The surface of the impeller 3 may be a molded resin or may be formed with a film by vapor deposition, painting, plating, or the like from the viewpoint of wear resistance. The surface of the resin mold is a polished surface. In the present embodiment, the impeller 3 manufactured by resin molding is used as it is, and a predetermined surface shape is separately formed on the positive pressure surface 5 and the negative pressure surface 4 of the impeller 3, and this is attached to the plurality of motor drive units 2. Thus, an axial fan 1 was constructed.
表面形状は、表面粗さ（算術平均粗さＲａ）、形状、曲率半径ＲａｄＣｒｖで規定した。 The surface shape was defined by the surface roughness (arithmetic mean roughness Ra), shape, and radius of curvature RadCrv.
表面粗さは、ＪＩＳＢ０６０１−２００１で規定される算術平均粗さＲａを用いた。 As the surface roughness, arithmetic average roughness Ra defined by JISB0601-2001 was used.
ＪＩＳＢ０６０１−２００１の規定によれば、算術平均粗さＲａが同じであっても、表面の粗面形状により粗面の凸凹の高低差は異なってくる。算術平均粗さを１Ｒａとすると、図２（ａ）に示したように、表面が矩形粗面の場合、粗面の高低差は２Ｒａに相当する。同様に、図２（ｂ）に示したように、表面が丸みを帯びた粗面の場合、粗面の高低差は２．５Ｒａに相当する。同様に、図２（ｃ）に示したように、表面が鋸歯状粗面の場合、粗面の高低差は４Ｒａに相当する。 According to the provisions of JIS B0601-2001, even if the arithmetic average roughness Ra is the same, the level difference of the roughness of the rough surface varies depending on the rough surface shape. Assuming that the arithmetic average roughness is 1 Ra, as shown in FIG. 2A, when the surface is a rectangular rough surface, the height difference of the rough surface corresponds to 2 Ra. Similarly, as shown in FIG. 2B, when the surface is a rounded rough surface, the difference in height of the rough surface corresponds to 2.5 Ra. Similarly, as shown in FIG. 2C, when the surface is a serrated rough surface, the height difference of the rough surface corresponds to 4Ra.
曲率半径は、図３に示したＲａｄＣｒｖで定義した。図に示した三角形に関するピタゴラスの定理（１）式から、粗面の凹部の曲率半径ＲａｄＣｒｖは、（２）式で表される。
（ＲａｄＣｒｖ−ｓ）２＋（２／ｄ）２＝ＲａｄＣｒｖ２ （１）
ＲａｄＣｒｖ＝（ｓ２＋（ｄ／２）２）／２ｓ
（２）
The radius of curvature was defined by RadCrv shown in FIG. From the Pythagorean theorem (1) relating to the triangle shown in the figure, the curvature radius RadCrv of the concave portion of the rough surface is expressed by the following equation (2).
(RadCrv−s) 2 + (2 / d) 2 = RadCrv 2 (1)
RadCrv = (s 2 + (d / 2) 2 ) / 2s
(2)
本発明の実施例においては、樹脂の成形によって製作したインペラ３の正圧面５と負圧面４に、以下の（Ａ）、（Ｂ）、（Ｃ）の３種類の表面形状を形成してから複数枚のインペラ３をモータ駆動部２に取り付けて軸流ファン１を構成した。この軸流ファン１を駆動して、騒音値（ｄＢＡ）、消費電力（Ｗ）、静圧（Ｐａ）を測定し、インペラ３の正圧面５の表面形状と負圧面４の表面形状の組合せによる比較を行った。 In the embodiment of the present invention, the following three types of surface shapes (A), (B), and (C) are formed on the pressure surface 5 and the suction surface 4 of the impeller 3 manufactured by resin molding. A plurality of impellers 3 were attached to the motor drive unit 2 to constitute the axial fan 1. The axial fan 1 is driven to measure the noise value (dBA), power consumption (W), and static pressure (Pa), and the combination of the surface shape of the pressure surface 5 and the surface shape of the suction surface 4 of the impeller 3. A comparison was made.
（Ａ）＃１５，０００のラッピングテープによる研磨面
（Ｂ）＃６０の紙やすりによる丸みを帯びた粗面
（Ｃ）カッターによる矩形粗面
(A) Polished surface by lapping tape of # 15,000 (B) Rounded rough surface by sandpaper of # 60 (C) Rectangular rough surface by cutter
図４は、上記（Ａ）、（Ｂ）、（Ｃ）の形状を有するインペラ３の表面の、顕微鏡写真と、表面形状測定器による算術平均粗さＲａ、曲率半径ＲａｄＣｒｖを示したものである。図４（ａ）は、（Ａ）＃１５，０００のラッピングテープによる研磨面を示したものであり、算術平均粗さＲａ＝０．２６μｍ、曲率半径ＲａｄＣｒｖ＝７４，０００μｍである。図４（ｂ）は、（Ｂ）＃６０の紙やすりによる丸みを帯びた粗面を示したものであり、算術平均粗さＲａ＝７．３μｍ、曲率半径ＲａｄＣｒｖ＝３，２００μｍである。図４（ｃ）は、（Ｃ）カッターによる矩形粗面を示したものであり、算術平均粗さＲａ＝８．２μｍ、曲率半径ＲａｄＣｒｖ＝７８０μｍである。 FIG. 4 shows a micrograph of the surface of the impeller 3 having the shapes (A), (B), and (C), and the arithmetic average roughness Ra and the radius of curvature RadCrv measured by a surface shape measuring instrument. . FIG. 4 (a) shows the polished surface of the wrapping tape of (A) # 15,000, with arithmetic average roughness Ra = 0.26 μm and curvature radius RadCrv = 74,000 μm. FIG. 4B shows a rounded rough surface by sandpaper of (B) # 60, with arithmetic average roughness Ra = 7.3 μm and curvature radius RadCrv = 3,200 μm. FIG. 4C shows a rectangular rough surface by a cutter (C), where the arithmetic average roughness Ra = 8.2 μm and the radius of curvature RadCrv = 780 μm.
図５は、本実施例における軸流ファン１のインペラ３の表面形状を模式的に説明する図である。例えば、図５（ａ）は、複数枚のインペラ３の負圧面４に上記（Ａ）の研磨面を形成したこと表し、図５（ｂ）は複数枚のインペラ３の正圧面５に上記（Ｂ）又は（Ｃ）の粗面を形成したこと表す。 FIG. 5 is a diagram schematically illustrating the surface shape of the impeller 3 of the axial fan 1 in the present embodiment. For example, FIG. 5A shows that the polishing surface (A) is formed on the suction surfaces 4 of the plurality of impellers 3, and FIG. 5B shows the above ( It represents that the rough surface of B) or (C) was formed.
図６は、インペラ３の（負圧面４の表面形状）／（正圧面５の表面形状）の組合せの異なる軸流ファン１の騒音量（ｄＢＡ）の最大風量（ｍ３／ｍｉｎ）依存性を示したものである。図中、（Ａ）、（Ｂ）、（Ｃ）は、上記表面形状を表す。現行品は、負圧面４の表面形状、正圧面５の表面形状とも、同じ滑らかな表面形状となっている。 FIG. 6 shows the maximum air volume (m 3 / min) dependence of the noise amount (dBA) of the axial fan 1 with different combinations of (surface shape of the suction surface 4) / (surface shape of the pressure surface 5) of the impeller 3. It is shown. In the figure, (A), (B), and (C) represent the surface shape. In the current product, the surface shape of the suction surface 4 and the surface shape of the pressure surface 5 are the same smooth surface shape.
表１は、図６の結果を騒音量が低い順に並べたものである。 Table 1 arranges the results of FIG. 6 in ascending order of noise level.
図６、表１から、騒音値に関しては、正圧面を粗面化、すなわち正圧面を荒らした方が良好であることがわかる。軸流ファン１の騒音量（ｄＢＡ）は、（Ｂ）／（Ｂ）の組合せで最も少なく、（Ａ）／（Ｂ）の組合せがこれに近くなっており、これらは、現行品の騒音量（ｄＢＡ）よりも顕著に少なくなっている。 From FIG. 6 and Table 1, it can be seen that regarding the noise value, it is better to roughen the pressure surface, that is, to roughen the pressure surface. The noise amount (dBA) of the axial fan 1 is the smallest in the combination of (B) / (B), and the combination of (A) / (B) is close to this, which is the noise amount of the current product. It is significantly less than (dBA).
図７は、インペラ３の（負圧面４の表面形状）／（正圧面５の表面形状）の組合せの異なる軸流ファン１の電力量（Ｗ）の最大風量（ｍ３／ｍｉｎ）依存性を示したものである。図中、（Ａ）、（Ｂ）、（Ｃ）は、上記表面形状を表す。現行品は、負圧面４の表面形状、正圧面５の表面形状とも、同じ滑らかな表面形状となっている。 FIG. 7 shows the maximum air volume (m 3 / min) dependence of the electric energy (W) of the axial fan 1 with different combinations of (surface shape of the suction surface 4) / (surface shape of the pressure surface 5) of the impeller 3. It is shown. In the figure, (A), (B), and (C) represent the surface shape. In the current product, the surface shape of the suction surface 4 and the surface shape of the pressure surface 5 are the same smooth surface shape.
表２は、図７の結果を消費電力が低い順に並べたものである。 Table 2 lists the results of FIG. 7 in order of increasing power consumption.
図７、表２から、消費電力に関しては、負圧面を研磨面にした方が良好であることがわかる。軸流ファン１の電力量（Ｗ）は、（Ａ）／（Ｂ）の組合せで最も小さく、これは、現行品の電力量（Ｗ）よりも顕著に小さくなっている。 From FIG. 7 and Table 2, it can be seen that the power consumption is better when the negative pressure surface is a polished surface. The electric energy (W) of the axial fan 1 is the smallest in the combination (A) / (B), which is significantly smaller than the electric energy (W) of the current product.
図６、表１、図７、表２に示した結果から、（Ａ）／（Ｂ）の組合せ、すなわち、インペラ３の負圧面４の表面形状を（Ａ）研磨面とし、正圧面５の表面形状を（Ｂ）丸みを帯びた粗面とした場合に、騒音、電力量とも顕著に低減された軸流ファン１が得られることが明らかとなった。ここで、上記のように、（Ａ）研磨面は算術平均粗さＲａ＝０．２６μｍ、曲率半径ＲａｄＣｒｖ＝７４，０００μｍを有し、（Ｂ）丸みを帯びた粗面は算術平均粗さＲａ＝７．３μｍ、曲率半径ＲａｄＣｒｖ＝３，２００μｍを有する。 From the results shown in FIGS. 6, 1, 7, and 2, the combination of (A) / (B), that is, the surface shape of the suction surface 4 of the impeller 3 is (A) the polished surface, and the pressure surface 5 When the surface shape is (B) a rounded rough surface, it has been clarified that the axial fan 1 with significantly reduced noise and electric power can be obtained. Here, as described above, (A) the polished surface has an arithmetic average roughness Ra = 0.26 μm and a radius of curvature RadCrv = 74,000 μm, and (B) the rounded rough surface has an arithmetic average roughness Ra. = 7.3 μm, radius of curvature RadCrv = 3,200 μm.
図８は、インペラ３の（負圧面４の表面形状）／（正圧面５の表面形状）の組合せの異なる軸流ファン１のＰ−Ｑ特性、すなわち静圧（Ｐａ）と風量（Ｑ）の関係を示したものである。図中、（Ａ）、（Ｂ）、（Ｃ）は、上記表面形状を表す。現行品は、負圧面４の表面形状、正圧面５の表面形状とも、同じ滑らかな表面形状となっている。 FIG. 8 shows the PQ characteristics of the axial fan 1 having different combinations of (surface shape of the suction surface 4) / (surface shape of the pressure surface 5) of the impeller 3, that is, static pressure (Pa) and air flow (Q). It shows the relationship. In the figure, (A), (B), and (C) represent the surface shape. In the current product, the surface shape of the suction surface 4 and the surface shape of the pressure surface 5 are the same smooth surface shape.
図８から、（Ａ）／（Ｂ）の組合せで、現行品よりも顕著に高い風量が得られることがわかる From FIG. 8, it can be seen that the combination of (A) / (B) provides a significantly higher air volume than the current product.
以上、実施形態を用いて本発明を説明したが、本発明の技術的範囲は上記実施形態に記載の範囲には限定されないことは言うまでもない。また、その他、本発明はその要旨を逸脱しない範囲で種々変形して実施可能である。 As mentioned above, although this invention was demonstrated using embodiment, it cannot be overemphasized that the technical scope of this invention is not limited to the range as described in the said embodiment. In addition, the present invention can be variously modified and implemented without departing from the scope of the invention.
１ 軸流ファン
２ モータ駆動部
３ インペラ
４ 負圧面
５ 正圧面
DESCRIPTION OF SYMBOLS 1 Axial fan 2 Motor drive part 3 Impeller 4 Negative pressure surface 5 Positive pressure surface
Claims (5)
前記インペラの正圧面の表面粗さを前記インペラの負圧面の表面粗さより大きくすることを特徴とするインペラ。 In an axial fan including a motor and an impeller rotated by the motor,
The impeller characterized in that the surface roughness of the pressure surface of the impeller is larger than the surface roughness of the suction surface of the impeller.
前記インペラの正圧面の算術平均粗さＲａが１〜１００μｍの範囲に、曲率半径ＲａｄＣｒｖが１，０００〜１０，０００μｍの範囲にあるとともに、
前記インペラの負圧面の算術平均粗さＲａ＜０．５μｍ、曲率半径ＲａｄＣｒｖ＞１０，０００μｍであることを特徴とする請求項1に記載のインペラ。 The pressure surface of the impeller and the suction surface of the impeller have a rounded roughness shape that can be microscopically defined by a curvature radius,
The arithmetic mean roughness Ra of the pressure surface of the impeller is in the range of 1 to 100 μm, the radius of curvature RadCrv is in the range of 1,000 to 10,000 μm,
2. The impeller according to claim 1, wherein an arithmetic mean roughness Ra <0.5 μm and a curvature radius RadCrv> 10,000 μm of the suction surface of the impeller.
ことを特徴とする請求項１又は２に記載のインペラ。 The impeller according to claim 1 or 2, wherein the pressure surface of the impeller and the suction surface of the impeller are integrally molded with resin.
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| JP2014218517A (en) * | 2002-12-09 | 2014-11-20 | アブラクシスバイオサイエンス リミテッド ライアビリティー カンパニー | Amine derivative compounds for treatment of eye diseases and disorders |
| JP2019206958A (en) * | 2018-05-30 | 2019-12-05 | 三菱重工サーマルシステムズ株式会社 | Propeller fan and outdoor unit for air conditioner including the same |
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