JPH084698A - Axial flow fan - Google Patents
Axial flow fanInfo
- Publication number
- JPH084698A JPH084698A JP13340394A JP13340394A JPH084698A JP H084698 A JPH084698 A JP H084698A JP 13340394 A JP13340394 A JP 13340394A JP 13340394 A JP13340394 A JP 13340394A JP H084698 A JPH084698 A JP H084698A
- Authority
- JP
- Japan
- Prior art keywords
- fan
- casing
- motor
- wall
- gap
- 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
Landscapes
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
Description
【０００１】[0001]
【産業上の利用分野】本発明は、毛髪乾燥用ドライヤー
等に用いられる軸流ファンの構造に関し、特に軸流ファ
ンの低騒音化を図る構造に関するものである。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a structure of an axial fan used for a hair dryer and the like, and more particularly to a structure for reducing the noise of the axial fan.
【０００２】[0002]
【従来の技術】従来の軸流ファンの場合、ケーシングと
ファンとの間の隙間で発生する騒音の主な原因のひとつ
として、ファンの外周部から発生する渦による乱流騒音
がある。その対策として、ファンとファン周りのケーシ
ングの内壁との間の隙間を可能な限り小さくする手法が
とられてきた。2. Description of the Related Art In the case of a conventional axial fan, one of the main causes of noise generated in the gap between the casing and the fan is turbulent noise due to vortices generated from the outer peripheral portion of the fan. As a countermeasure, a method has been adopted in which the gap between the fan and the inner wall of the casing around the fan is made as small as possible.
【０００３】[0003]
【発明が解決しようとする課題】しかしながら、ファン
１の羽根２の形状は図５、図６に示すように低騒音化の
ために回転方向（図６の矢印Ａ方向）に前進（吸い込み
口側を前とし、吐風口側を後としている）してあること
が多く、そのためファン１は回転時、特に５０００ｒｐ
ｍを超えるような高速回転時において、遠心力にて羽根
２の外周部２ｂの前縁部２ａ側が外方に広がる。However, as shown in FIGS. 5 and 6, the shape of the blades 2 of the fan 1 is forward (in the suction port side) in the rotational direction (direction of arrow A in FIG. 6) for noise reduction. Is set to the front, and the air outlet side is set to the rear). Therefore, the fan 1 rotates at 5000 rpm in particular.
When rotating at a high speed exceeding m, centrifugal force causes the outer peripheral portion 2b of the blade 2 to spread outward on the front edge 2a side.
【０００４】そこで、図７（ａ）に示すように、ケーシ
ング３の内壁とファン１の羽根２の外周部２ｂとの間の
隙間Ｓを静止時に一定にした場合、この隙間Ｓが小さ過
ぎると、ファン１の回転時に図７（ｂ）に示すように羽
根２の外周部２ｂの前縁部２ａ側が遠心力にて広がり、
ファン１の回転時に羽根２とケーシング３の内壁との接
触が発生しやすくなるという問題がある。Therefore, as shown in FIG. 7 (a), when the gap S between the inner wall of the casing 3 and the outer peripheral portion 2b of the blade 2 of the fan 1 is kept constant at rest, if the gap S is too small. When the fan 1 rotates, as shown in FIG. 7B, the front edge portion 2a side of the outer peripheral portion 2b of the blade 2 spreads by centrifugal force,
There is a problem that contact between the blades 2 and the inner wall of the casing 3 tends to occur when the fan 1 rotates.
【０００５】またファン１の回転時に羽根２の外周部２
ｂの前縁部２ａ側がケーシング３の内壁に接触しないよ
うに隙間Ｓを大きくした場合、ファン１の回転時に羽根
２の外周部２ｂの後縁部２ｃ側が殆ど広がらないため、
静止時にファン１の羽根２の外周部２ｂとケーシング３
の内壁との間に隙間Ｓが一定になる仕様にしたとき、羽
根２の外周部２ｂの後縁部２ｃ側において必要以上に隙
間Ｓが大きくなり、騒音レベルが大きくなるという問題
がある。Further, when the fan 1 rotates, the outer peripheral portion 2 of the blade 2
When the gap S is made large so that the front edge 2a side of b does not contact the inner wall of the casing 3, the outer edge 2b side of the outer peripheral portion 2b of the blade 2 hardly expands when the fan 1 rotates.
When stationary, the outer peripheral portion 2b of the blade 2 of the fan 1 and the casing 3
When the specification is such that the gap S between the inner wall and the inner wall of the blade is constant, the gap S becomes larger than necessary on the trailing edge portion 2c side of the outer peripheral portion 2b of the blade 2, resulting in a problem that the noise level increases.
【０００６】またこの種の軸流ファンに騒音を低減する
ものとして特公平５−１４１１８号公報に開示されるも
のが提供されているが、これは羽根の３次元的形状の設
計に工夫をして騒音を低減するものであって、構造的に
複雑なものである。本発明は上記問題点に鑑みてなされ
たものであって、本発明の目的とするところはファンの
羽根とその周りのケーシングの内壁との間の隙間を回転
時に一定にし、ファンの羽根とケーシングの内壁との接
触を避けつつ、軸流ファンの主な騒音源であるファン外
周部の乱流騒音を最大限に低減させることができる軸流
ファンを提供するにある。Further, an axial flow fan of this type is disclosed in Japanese Examined Patent Publication (Kokoku) No. 5-14118 as a device for reducing noise, which is devised in designing the three-dimensional shape of the blade. It reduces noise and is structurally complicated. The present invention has been made in view of the above problems, and an object of the present invention is to make a gap between a fan blade and an inner wall of a casing around the fan blade constant during rotation so that the fan blade and the casing. (EN) Provided is an axial flow fan capable of maximally reducing turbulent noise at the outer peripheral portion of the fan, which is a main noise source of the axial flow fan, while avoiding contact with the inner wall of the fan.
【０００７】[0007]
【課題を解決するための手段】上記目的を達成するため
本発明軸流ファンは、前側の一端に吸い込み口４を、後
側の他端に吐風口５を有する筒状のケーシング３内に、
ファン１と、ファン１を駆動するモータ６と、モータ６
の保持と風の整流を目的とした整流翼７とをモータ６や
整流翼７がファン１より吐風口５側である後側に位置す
るように配設した軸流ファンにおいて、ファン１が回転
してファン１の羽根２の外周部２ｂの前縁部２ａ側の径
が大きくなるように広がった状態で、ファン１とファン
１の周りのケーシング３の内壁との間の隙間Ｓを一定に
するために、ケーシング３の内壁を風上側の径が大きく
なるように傾斜させて成ることを特徴とする。To achieve the above object, an axial fan according to the present invention has a cylindrical casing 3 having a suction port 4 at one end on the front side and an air outlet 5 at the other end on the rear side.
Fan 1, motor 6 for driving fan 1, and motor 6
In an axial fan in which the motor 6 and the flow straightening vanes 7 for the purpose of holding the wind and for straightening the wind are arranged so that the motor 6 and the straightening vanes 7 are located on the rear side of the fan 1 on the side of the air outlet 5, Then, the gap S between the fan 1 and the inner wall of the casing 3 around the fan 1 is made constant in a state where the outer peripheral portion 2b of the blade 2 of the fan 1 is widened so that the diameter on the front edge portion 2a side becomes large. Therefore, the inner wall of the casing 3 is inclined so that the diameter on the windward side is increased.
【０００８】またファン１が回転してファン１の羽根２
の外周部２ｂの前縁部２ａ側の径が大きくなるように広
がった状態で、ファン１とファン１の周りのケーシング
３の内壁との間の隙間Ｓを一定にするために、ファン１
の外周を風上側の径が小さくなるように傾斜させて成る
ことを特徴とすることも好ましい。Further, the fan 1 rotates to rotate the blades 2 of the fan 1.
In order to make the gap S between the fan 1 and the inner wall of the casing 3 around the fan 1 constant in a state where the diameter of the outer peripheral portion 2b on the front edge 2a side is widened, the fan 1
It is also preferable that the outer periphery of the is inclined so that the diameter on the windward side becomes smaller.
【０００９】[0009]
【作用】上記構成によれば、ファン１が回転して羽根２
の外周部２ｂの前縁部２ａ側が広がった場合にも、ファ
ン１の羽根２とケーシング３の内壁との当たりを避けつ
つ、羽根２の外周部２ｂとケーシング３の内壁との間の
隙間を前縁部２ａ側から後縁部２ｃ側まで小さくでき、
ファン１外周部から発生する騒音を最大限低減できる。According to the above construction, the fan 1 rotates to rotate the blades 2
Even when the front edge portion 2a side of the outer peripheral portion 2b of the fan expands, the gap between the outer peripheral portion 2b of the blade 2 and the inner wall of the casing 3 is avoided while avoiding the contact between the blade 2 of the fan 1 and the inner wall of the casing 3. The size can be reduced from the front edge 2a side to the rear edge 2c side,
The noise generated from the outer peripheral portion of the fan 1 can be reduced to the maximum.
【００１０】[0010]
【実施例】図３に示すように軸流ファンのケーシング３
は円筒状をしており、ケーシング３の前側の一端の開口
部を吸い込み口４とし、後側の他端の開口部を吐風口５
としてある。吸い込み口４にベルマウス状のフランジ１
０を設けてある。ケーシング３内はファン１と、ファン
１を駆動するモータ６と、モータ６の固定とファン１か
ら出る風の整流の機能を有する整流翼７を配置してあ
る。モータ６の出力軸８はファン１の軸部９に結合して
あり、モータ６を回転駆動することによりファン１を回
転駆動できるようになっている。ファン１には複数枚の
羽根２を設けてある。モータ６は整流翼７に固定してあ
り、整流翼７はケーシング３に固定してある。EXAMPLE As shown in FIG. 3, an axial fan casing 3
Has a cylindrical shape, and an opening at one end on the front side of the casing 3 serves as a suction port 4, and an opening at the other end on the rear side serves as an outlet 5.
There is. Bellmouth-shaped flange 1 on the suction port 4
0 is set. Inside the casing 3, there are arranged a fan 1, a motor 6 for driving the fan 1, and a rectifying blade 7 having a function of fixing the motor 6 and rectifying the air discharged from the fan 1. The output shaft 8 of the motor 6 is connected to the shaft portion 9 of the fan 1, and the fan 1 can be rotationally driven by rotationally driving the motor 6. The fan 1 is provided with a plurality of blades 2. The motor 6 is fixed to the straightening vanes 7, and the straightening vanes 7 are fixed to the casing 3.
【００１１】ところで、ファン１とファン１周りのケー
シング３の内壁との隙間は小さいことが望ましいが、ケ
ーシング３が外力を受けたときの変形量を確保しなけれ
ばならない。この変形量は軸流ファンの使用状態によっ
て異なるが、本実施例において、ファン１をプラスチッ
ク製の外径６０ｍｍとし、ケーシング３も厚さ２ｍｍの
プラスチック製とし、吸い込み口４にベルマウス状のフ
ランジ１０を設けて、８Ｋｇ・ｆの外力に耐えることを
条件とした場合、約０．６ｍｍの隙間Ｓが必要である。
また図５、図６のようにファン１の羽根２の形状が回転
方向に前進している場合、本実施例において、１０００
０ｒｐｍの回転時に、羽根２の外周部２ｂの前縁部２ａ
側の外径が０．８ｍｍ広がる。羽根２の外周部２ｂの後
縁部２ｃ側は殆ど広がらない。By the way, it is desirable that the gap between the fan 1 and the inner wall of the casing 3 around the fan 1 is small, but it is necessary to secure a deformation amount when the casing 3 receives an external force. The amount of this deformation varies depending on the usage of the axial fan, but in the present embodiment, the fan 1 has a plastic outer diameter of 60 mm, the casing 3 also has a thickness of 2 mm, and the suction port 4 has a bell mouth-shaped flange. When 10 is provided and it is required to withstand an external force of 8 kg · f, a gap S of about 0.6 mm is required.
Further, when the shape of the blades 2 of the fan 1 is advanced in the rotation direction as shown in FIGS.
The front edge portion 2a of the outer peripheral portion 2b of the blade 2 when rotating at 0 rpm
The outer diameter on the side expands by 0.8 mm. The outer peripheral portion 2b of the blade 2 hardly spreads on the rear edge 2c side.
【００１２】これらのことを考慮し、図１に示す実施例
ではファン１の羽根２の外周部２ｂの後縁部２ｃ側の隙
間Ｓを０．６ｍｍ、羽根２の外周部２ｂの前縁部２ａ側
の隙間Ｓが１．０ｍｍになるようにケーシング３の内壁
を傾斜させている。つまり、ケーシング３の内壁を後側
から前側に向けて径が大きくなるテーパー筒状にしてい
る。図１（ａ）はファン１が静止時の状態であり、図１
（ｂ）はファン１が回転した時の状態である。また図２
に示す実施例では、隙間Ｓが上記寸法になるようにファ
ン１の羽根２の外周部２ｂを傾斜させている。つまり、
ケーシング３の内壁をストレート状にし、羽根２の外周
部２ｂが後側から前側に向けて径が小さくなるようにし
てある。図２（ａ）はファン１が静止時の状態であり、
図２（ｂ）はファン１が回転した時の状態である。In consideration of these matters, in the embodiment shown in FIG. 1, the clearance S on the rear edge 2c side of the outer peripheral portion 2b of the blade 2 of the fan 1 is 0.6 mm, and the front edge portion of the outer peripheral portion 2b of the blade 2 is set. The inner wall of the casing 3 is inclined so that the gap S on the 2a side is 1.0 mm. That is, the inner wall of the casing 3 has a tapered cylindrical shape whose diameter increases from the rear side toward the front side. FIG. 1A shows a state in which the fan 1 is stationary.
(B) is a state when the fan 1 is rotated. FIG. 2
In the embodiment shown in (1), the outer peripheral portion 2b of the blade 2 of the fan 1 is inclined so that the gap S has the above dimension. That is,
The inner wall of the casing 3 has a straight shape, and the outer peripheral portion 2b of the blade 2 has a diameter that decreases from the rear side to the front side. FIG. 2A shows a state where the fan 1 is stationary,
FIG. 2B shows a state when the fan 1 rotates.
【００１３】しかして、上記構成の軸流ファンは、モー
タ６を駆動し、ファン１が回転した場合、ファン１の羽
根２の外周部２ｂの前縁部２ａ側が広がり、ファン１と
ケーシング３との間の隙間Ｓを、ファン１の羽根２とケ
ーシング３との接触が発生しない限りにおいて最も小さ
くでき、騒音の低減が図れる。本実施例の場合、隙間Ｓ
を静止時において１．０ｍｍの一定間隔とした従来例の
場合と比較して図４に示すように各風量において、約２
〜３ｄＢの騒音レベルが低減できる。図４は風量と騒音
値の関係を示すものであり、線Ｃは本発明の実施例のも
のを示し、線Ｂは従来例のものを示す。なお、縦軸の騒
音の１目盛は１ｄＢを示す。Thus, in the axial fan having the above structure, when the motor 6 is driven and the fan 1 is rotated, the outer peripheral portion 2b of the blade 2 of the fan 1 is widened on the front edge 2a side, and the fan 1 and the casing 3 are separated. The gap S between them can be minimized as long as the blades 2 of the fan 1 and the casing 3 do not come into contact with each other, and noise can be reduced. In the case of this embodiment, the gap S
As shown in FIG. 4, in comparison with the case of the conventional example in which is set to a fixed interval of 1.0 mm at rest, as shown in FIG.
A noise level of up to 3 dB can be reduced. FIG. 4 shows the relationship between the air volume and the noise value. Line C shows the example of the present invention, and line B shows the conventional example. In addition, one scale of noise on the vertical axis represents 1 dB.
【００１４】なお、上記実施例では、隙間Ｓを前縁部２
ａ側で１．０ｍｍとし、後縁部２ｂ側で０．６ｍｍとす
るものについて述べたが、この数値に限定されるもので
ない。Incidentally, in the above embodiment, the gap S is formed in the front edge portion 2
Although the thickness is set to 1.0 mm on the a side and 0.6 mm on the trailing edge 2b side, it is not limited to this value.
【００１５】[0015]
【発明の効果】本発明は叙述のようにファンが回転して
ファンの羽根の外周部の前縁部側の径が大きくなるよう
に広がった状態で、ファンとファンの周りのケーシング
の内壁との間の隙間を一定にするために、ケーシングの
内壁を風上側の径が大きくなるように傾斜させるか、ま
たはファンの外周を風上側の径が小さくなるように傾斜
させているので、ファンが回転しンファンの羽根の外周
部の前縁部側が広がった場合にも、ファンの羽根とケー
シングの内壁との当たりを避けつつ、ファンとケーシン
グ内壁との隙間を前縁部から後縁部まで小さくでき、フ
ァンの外周部から発生する騒音を最大限低減できるもの
であり、しかもケーシングやファンの径を変更するだけ
の簡単な構造で騒音の低減が実現できるものである。As described above, according to the present invention, the fan rotates and the inner wall of the casing around the fan expands so that the diameter of the outer peripheral portion of the fan blade increases on the front edge side. In order to keep the gap between them constant, the inner wall of the casing is inclined to increase the diameter on the windward side, or the outer periphery of the fan is inclined to reduce the diameter on the windward side. Even if the fan blades rotate and the front edge of the outer peripheral part of the fan blades expands, the gap between the fan and the inner wall of the casing is reduced from the front edge to the rear edge while avoiding contact between the fan blades and the inner wall of the casing. Therefore, the noise generated from the outer peripheral portion of the fan can be reduced to the maximum extent, and the noise can be reduced with a simple structure in which the diameter of the casing or the fan is changed.
【図１】本発明の一実施例の要部を示す断面図であり、
（ａ）はファンの静止時の状態を示し、（ｂ）はファン
の回転時の状態を示す。FIG. 1 is a cross-sectional view showing a main part of an embodiment of the present invention,
(A) shows the state when the fan is stationary, and (b) shows the state when the fan is rotating.
【図２】同上の他の実施例の要部を示す断面図であり、
（ａ）はファンの静止時の状態を示し、（ｂ）はファン
の回転時の状態を示す。FIG. 2 is a sectional view showing a main part of another embodiment of the above,
(A) shows the state when the fan is stationary, and (b) shows the state when the fan is rotating.
【図３】同上の軸流ファン全体を示す断面図である。FIG. 3 is a cross-sectional view showing the entire axial fan of the above.
【図４】軸流ファンの騒音値を説明する説明図である。FIG. 4 is an explanatory diagram illustrating a noise value of an axial fan.
【図５】ファンの外観を示す斜視図である。FIG. 5 is a perspective view showing an appearance of a fan.
【図６】ファンの正面図である。FIG. 6 is a front view of a fan.
【図７】従来例の要部を示す断面図であり、（ａ）はフ
ァンの静止時の状態を示し、（ｂ）はファンの回転時の
状態を示す。7A and 7B are cross-sectional views showing a main part of a conventional example, in which FIG. 7A shows a state when the fan stands still, and FIG. 7B shows a state when the fan rotates.
１ ファン ２ 羽根 ２ａ 羽根の前縁部 ２ｂ 羽根の外周部 ２ｃ 羽根の後縁部 ３ ケーシング ４ 吸い込み口 ５ 吐風口 ６ モータ ７ 整流翼 Ｓ 隙間 DESCRIPTION OF SYMBOLS 1 Fan 2 Blade 2a Blade front edge 2b Blade outer periphery 2c Blade trailing edge 3 Casing 4 Suction port 5 Air outlet 6 Motor 7 Rectifier blade S Gap
Claims (2)
に吐風口を有する筒状のケーシング内に、ファンと、フ
ァンを駆動するモータと、モータの保持と風の整流を目
的とした整流翼とをモータや整流翼がファンより吐風口
側である後側に位置するように配設した軸流ファンにお
いて、ファンが回転してファンの羽根の外周部の前縁部
側の径が大きくなるように広がった状態で、ファンとフ
ァンの周りのケーシングの内壁との間の隙間を一定にす
るために、ケーシングの内壁を風上側の径が大きくなる
ように傾斜させて成ることを特徴とする軸流ファン。1. A fan, a motor for driving the fan, a motor for driving the fan, and a motor for holding and rectifying wind in a cylindrical casing having a suction port at one end on the front side and an air outlet at the other end on the rear side. In the axial flow fan in which the motor and the flow straightening vanes are located rearward of the fan, that is, on the outlet side, the fan rotates and the diameter of the outer peripheral edge of the fan blade on the front edge side. In order to keep the gap between the fan and the inner wall of the casing around the fan constant, the inner wall of the casing should be inclined so that the diameter on the windward side increases. A characteristic axial fan.
に吐風口を有する筒状のケーシング内に、ファンと、フ
ァンを駆動するモータと、モータの保持と風の整流を目
的とした整流翼とをモータや整流翼がファンより吐風口
側である後側に位置するように配設した軸流ファンにお
いて、ファンが回転してファンの羽根の外周部の前縁部
側の径が大きくなるように広がった状態で、ファンとフ
ァンの周りのケーシングの内壁との間の隙間を一定にす
るために、ファンの外周を風上側の径が小さくなるよう
に傾斜させて成ることを特徴とする軸流ファン。2. A fan, a motor for driving the fan, a motor for driving the fan, a motor for holding the motor, and rectifying the wind in a cylindrical casing having a suction port at one end on the front side and an air outlet at the other end on the rear side. In the axial flow fan in which the motor and the flow straightening vanes are located rearward of the fan, that is, on the outlet side, the fan rotates and the diameter of the outer peripheral edge of the fan blade on the front edge side. In order to keep the gap between the fan and the inner wall of the casing around the fan constant, the outer circumference of the fan is inclined so that the diameter on the windward side becomes smaller. A characteristic axial fan.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP13340394A JP3577739B2 (en) | 1994-06-15 | 1994-06-15 | Axial fan |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP13340394A JP3577739B2 (en) | 1994-06-15 | 1994-06-15 | Axial fan |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH084698A true JPH084698A (en) | 1996-01-09 |
| JP3577739B2 JP3577739B2 (en) | 2004-10-13 |
Family
ID=15103941
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP13340394A Expired - Fee Related JP3577739B2 (en) | 1994-06-15 | 1994-06-15 | Axial fan |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP3577739B2 (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPWO2012098652A1 (en) * | 2011-01-19 | 2014-06-09 | 日立アプライアンス株式会社 | Blower and air conditioner outdoor unit equipped with the same |
| US9803495B2 (en) | 2014-06-10 | 2017-10-31 | Rolls-Royce Plc | Assembly |
| JP2019060320A (en) * | 2017-09-28 | 2019-04-18 | 日本電産株式会社 | Axial flow fan |
-
1994
- 1994-06-15 JP JP13340394A patent/JP3577739B2/en not_active Expired - Fee Related
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPWO2012098652A1 (en) * | 2011-01-19 | 2014-06-09 | 日立アプライアンス株式会社 | Blower and air conditioner outdoor unit equipped with the same |
| JP5752714B2 (en) * | 2011-01-19 | 2015-07-22 | 日立アプライアンス株式会社 | Blower and air conditioner outdoor unit equipped with the same |
| US9803495B2 (en) | 2014-06-10 | 2017-10-31 | Rolls-Royce Plc | Assembly |
| EP2955327B1 (en) * | 2014-06-10 | 2019-07-17 | Rolls-Royce plc | A blade tip sealing assembly |
| JP2019060320A (en) * | 2017-09-28 | 2019-04-18 | 日本電産株式会社 | Axial flow fan |
Also Published As
| Publication number | Publication date |
|---|---|
| JP3577739B2 (en) | 2004-10-13 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US4531890A (en) | Centrifugal fan impeller | |
| CN100508332C (en) | Cooling device of motor | |
| JP2003532026A (en) | Ventilator, especially for ventilation of electronic equipment | |
| JP2003254297A (en) | Fan and shroud assembly | |
| JPH11125196A (en) | Fan and shroud assembly employing the fan | |
| GB1171001A (en) | Axial Flow Propeller Fan. | |
| JP2006263249A (en) | Hair-drier | |
| JPH10122188A (en) | Centrifugal blower | |
| JP2001115997A (en) | Multi-blade fan | |
| JP2921384B2 (en) | Mixed flow fan | |
| JPH10148199A (en) | Axial flow fan device | |
| JPH102299A (en) | Centrifugal blower | |
| JPH084698A (en) | Axial flow fan | |
| JP3092267B2 (en) | Centrifugal fan | |
| JP2002201944A (en) | Axial fan | |
| JP2003180051A (en) | Moving blade of totally-enclosed fan-cooled rotating electric machine | |
| JP2005171987A (en) | Small-sized mixed flow fan motor | |
| KR20030016175A (en) | Vortex flow fan | |
| JP3193222B2 (en) | Multi-wing blower | |
| JP2924372B2 (en) | Axial fan motor fan | |
| JPH0544697A (en) | Thin type mixed flow fan | |
| JP2718943B2 (en) | Axial fan | |
| JP3380897B2 (en) | Compressor | |
| JPS6270698A (en) | Motor fan | |
| JP3161127B2 (en) | Blower |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| A977 | Report on retrieval |
Free format text: JAPANESE INTERMEDIATE CODE: A971007 Effective date: 20040315 |
|
| A131 | Notification of reasons for refusal |
Free format text: JAPANESE INTERMEDIATE CODE: A131 Effective date: 20040323 |
|
| A521 | Written amendment |
Free format text: JAPANESE INTERMEDIATE CODE: A523 Effective date: 20040524 |
|
| TRDD | Decision of grant or rejection written | ||
| A01 | Written decision to grant a patent or to grant a registration (utility model) |
Free format text: JAPANESE INTERMEDIATE CODE: A01 Effective date: 20040622 |
|
| A61 | First payment of annual fees (during grant procedure) |
Free format text: JAPANESE INTERMEDIATE CODE: A61 Effective date: 20040705 |
|
| FPAY | Renewal fee payment (prs date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20070723 Year of fee payment: 3 |
|
| FPAY | Renewal fee payment (prs date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20080723 Year of fee payment: 4 |
|
| FPAY | Renewal fee payment (prs date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20090723 Year of fee payment: 5 |
|
| FPAY | Renewal fee payment (prs date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20090723 Year of fee payment: 5 |
|
| S533 | Written request for registration of change of name |
Free format text: JAPANESE INTERMEDIATE CODE: R313533 |
|
| FPAY | Renewal fee payment (prs date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20090723 Year of fee payment: 5 |
|
| R350 | Written notification of registration of transfer |
Free format text: JAPANESE INTERMEDIATE CODE: R350 |
|
| FPAY | Renewal fee payment (prs date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20090723 Year of fee payment: 5 |
|
| FPAY | Renewal fee payment (prs date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20100723 Year of fee payment: 6 |
|
| FPAY | Renewal fee payment (prs date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20100723 Year of fee payment: 6 |
|
| FPAY | Renewal fee payment (prs date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20110723 Year of fee payment: 7 |
|
| FPAY | Renewal fee payment (prs date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20120723 Year of fee payment: 8 |
|
| FPAY | Renewal fee payment (prs date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20120723 Year of fee payment: 8 |
|
| FPAY | Renewal fee payment (prs date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20130723 Year of fee payment: 9 |
|
| LAPS | Cancellation because of no payment of annual fees |