JP3491313B2 - Multi-blade fan and hair dryer using it - Google Patents
Multi-blade fan and hair dryer using itInfo
- Publication number
- JP3491313B2 JP3491313B2 JP00986094A JP986094A JP3491313B2 JP 3491313 B2 JP3491313 B2 JP 3491313B2 JP 00986094 A JP00986094 A JP 00986094A JP 986094 A JP986094 A JP 986094A JP 3491313 B2 JP3491313 B2 JP 3491313B2
- Authority
- JP
- Japan
- Prior art keywords
- impeller
- discharge port
- baffle plate
- blade
- blade fan
- 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
Landscapes
- Cleaning And Drying Hair (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Description
【０００１】[0001]
【産業上の利用分野】本発明は送風用に用いられる多翼
ファンとこれを用いたヘアドライヤーに関するものであ
る。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a multi-blade fan used for blowing air and a hair dryer using the same.
【０００２】[0002]
【従来の技術】ヘアドライヤーや空気清浄器等の家電機
器に用いられるファンとして、あるいはダクト内送風に
用いられるファンとして多翼ファンがある。シロッコフ
ァンとも称されているこの多翼ファンは、図８に示すよ
うに、外周部に多くのブレード１０が設けられている羽
根車１を、渦型室２０を形成しているケーシング２内に
配置し、羽根車１を回転させることによって、この羽根
車１の軸方向であるケーシング２側面に設けられた吸い
込み口２１から吸い込んだ空気を、渦型室２０内におい
て圧縮して圧力を高め、ケーシング２における羽根車１
の軸方向と直交する方向に設けられた吐出口２２に空気
を送り出すものとして構成されている。2. Description of the Related Art There is a multi-blade fan as a fan used in home electric appliances such as a hair dryer and an air purifier, or a fan used for blowing air in a duct. The multi-blade fan, which is also referred to as a sirocco fan, as shown in FIG. 8, the impeller 1 that many blades 10 on the outer peripheral portion is provided, in a casing 2 forming the vortex chamber 20 By arranging and rotating the impeller 1, the air sucked from the suction port 21 provided on the side surface of the casing 2 in the axial direction of the impeller 1 is compressed in the swirl chamber 20 to increase the pressure, Impeller 1 in casing 2
The air is sent to the discharge port 22 provided in the direction orthogonal to the axial direction of the.
【０００３】[0003]
【発明が解決しようとする課題】ところで、ファンは風
量が多く且つ騒音が少ないことが望ましく、この時、多
翼ファンにおいて風量を多くするために、ケーシング２
の渦型室２０内周壁における吐出口２２に連続する部分
であり且つ羽根車１外周との間隔が最も狭い部分である
舌部２３と羽根車１外周との間隔Ｌが小さくされている
のであるが、従来においては、この舌部２３が図８(b)
に示すように、羽根車１の軸１５と平行な縁を有するも
のとして形成されていた。By the way, it is desirable that the fan has a large air volume and a low noise level. At this time, in order to increase the air volume in the multi-blade fan, the casing 2 is used.
The interval L between the tongue portion 23 and the outer circumference of the impeller 1 which is a part of the inner peripheral wall of the whirlpool chamber 20 which is continuous with the discharge port 22 and has the narrowest distance from the outer circumference of the impeller 1 is reduced. However, in the past, this tongue portion 23 is shown in FIG.
As shown in FIG. 5, the blade was formed as having an edge parallel to the shaft 15 of the impeller 1.
【０００４】ここにおいて、羽根車１のブレード１０が
舌部２３付近を通過する時、圧力変動が生じるわけであ
るが、上記従来のものでは、この圧力変動が大きく、
ｆ＝（ＢＮ／６０）×ｎ
（Ｂ＝ブレード枚数、Ｎ＝回転数（ｒｐｍ）、ｎ＝整
数）
で定まる周波数ｆの離散周波数騒音（図９中のイ）が発
生し、これが騒音を大きくしている。Here, when the blade 10 of the impeller 1 passes near the tongue portion 23, pressure fluctuation occurs, but in the above-mentioned conventional one, this pressure fluctuation is large and f = (BN / 60). Discrete frequency noise (a in FIG. 9 ) having a frequency f determined by × n (B = the number of blades, N = the number of revolutions (rpm), n = an integer) is generated, and this increases the noise.
【０００５】離散周波数騒音を少なくするために、舌部
２３と羽根車１との距離Ｌを大きくすると、風が吐出口
２２に流れずに羽根車１に再び巻き込まれてしまうため
に、風量が低下してしまう。本発明はこのような点に鑑
み為されたものであり、その目的とするところは風量の
低下を招くことなく騒音の低減を図った多翼ファンとこ
れを用いたヘアドライヤーを提供するにある。If the distance L between the tongue portion 23 and the impeller 1 is increased in order to reduce the discrete frequency noise, the wind does not flow to the discharge port 22 and is re-engaged in the impeller 1. Will fall. The present invention has been made in view of the above points, and an object of the present invention is to provide a multi-blade fan and a hair dryer using the same, in which noise is reduced without reducing the air flow. .
【０００６】[0006]
【課題を解決するための手段】しかして本発明は、外周
部に多数のブレードが設けられた羽根車と、この羽根車
が配設される渦型室を備えるとともに羽根車の軸方向に
吸い込み口を、羽根車の軸方向と直交する方向に吐出口
を備えているケーシングとからなる多翼ファンにおい
て、ケーシングの渦型室内周壁における吐出口に連続す
る部分であり且つ羽根車外周との間隔が最も狭い部分で
ある舌部から吐出口側に向けて先端縁が羽根車の軸と非
平行な傾斜縁となっている邪魔板を突出させるととも
に、この邪魔板は吐出口側から見て先端縁がＶ字形をな
すとともに両側傾斜縁が非対称となっていることに特徴
を有している。DISCLOSURE OF THE INVENTION The present invention, however, includes an impeller having a large number of blades on its outer peripheral portion and a vortex chamber in which the impeller is arranged, and sucks in the axial direction of the impeller. In a multi-blade fan comprising a casing having a discharge port in a direction orthogonal to the axial direction of the impeller, a portion that is continuous with the discharge port on the vortex type inner peripheral wall of the casing and is spaced apart from the outer periphery of the impeller. From the tongue, which is the narrowest part, toward the discharge port, the tip edge is not aligned with the shaft of the impeller.
The baffle plate, which is a parallel slanted edge, is projected, and the tip edge of this baffle plate has a V shape when viewed from the discharge port side.
In addition, it is characterized by the asymmetrical edges on both sides .
【０００７】[0007]
【作用】本発明によれば、邪魔板の先端縁が羽根車の軸
と非平行な傾斜縁となっているために、ケーシングの舌
部及び邪魔板付近を羽根車のブレードが通過する際の圧
力変動が、ブレードの幅方向において同時に発生しない
ために、特定の離散周波数において騒音が大きくなって
しまうということがないものであり、特に邪魔板が吐出
口側から見て先端縁がＶ字形をなすものとなっているた
めに、最も仕事量が多いブレードの中央部の流路を広く
とることができて、邪魔板の存在で風量低下を招いてし
まうことをなくすことができ、しかも邪魔板の両側傾斜
縁が非対称となっているために、吐出口側から見た時、
邪魔板が２カ所でブレードと交差するものの、そのタイ
ミングがずれるために、離散周波数騒音の低減に有効で
ある。 According to the present invention, since the leading edge of the baffle plate is an inclined edge that is not parallel to the axis of the impeller, when the blade of the impeller passes near the tongue portion of the casing and the baffle plate. for pressure fluctuation does not occur simultaneously in the width direction of the blade, is intended is not that noise becomes large at certain discrete frequencies, particularly baffles discharge
The tip edge was V-shaped when viewed from the mouth side.
To increase the flow path in the center of the blade
Because the presence of the baffle causes a decrease in air flow.
It is possible to eliminate spoiling, and both sides of the baffle are tilted
Since the edge is asymmetric, when viewed from the discharge port side,
Although the baffle intersects the blade at two places, its tie
This is effective in reducing discrete frequency noise because
is there.
【０００８】そして、邪魔板が吐出口の軸方向と直交す
る面よりも羽根車側に傾いているものとなっておれば、
邪魔板を設けたことで羽根車に再度巻き込まれてしまう
風の量が多くなってしまうことをなくすことができ、ま
た、吐出口側から見た邪魔板の先端縁と羽根車の側縁と
の交点が羽根車の外周縁よりも羽根車の軸側に位置して
おれば、邪魔板を設けたことによる騒音低下に関して最
も良好な結果を得ることができる。If the baffle plate is inclined toward the impeller side with respect to the plane orthogonal to the axial direction of the discharge port,
That it is possible to eliminate the amount of wind that get caught again to the impeller by providing the baffle plate becomes many, or
Also, if the intersection of the tip edge of the baffle plate and the side edge of the impeller as viewed from the discharge port side is located closer to the shaft side of the impeller than the outer peripheral edge of the impeller, noise due to the baffle plate is provided. The best results can be obtained regarding the reduction.
【０００９】また、このような多翼ファンを用いたヘア
ドライヤーは、風量が多いにもかかわらず、騒音が少な
いものとなる。Further, a hair dryer using such a multi-blade fan produces a small amount of noise despite the large amount of air.
【００１０】[0010]
【実施例】以下本発明を図示の実施例に基づいて詳述す
ると、図１及び図２において、図中１は羽根車、２はケ
ーシングであり、軸１５を中心に回転駆動される羽根車
１は、その外周部に多数のブレード１０を有している。
ケーシング２は上記羽根車１をその渦型室２０内に配し
ているもので、羽根車１の軸方向である側面に吸い込み
口２１を、羽根車１の軸方向と直交する方向に吐出口２
２を備えたものとして形成されている。DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS The present invention will be described in detail below with reference to the illustrated embodiments. In FIGS. 1 and 2, 1 is an impeller, 2 is a casing, and an impeller is driven to rotate about a shaft 15. 1 has a large number of blades 10 on its outer peripheral portion.
The casing 2 has the impeller 1 arranged in the swirl chamber 20, and has a suction port 21 on a side surface which is the axial direction of the impeller 1 and a discharge port in a direction orthogonal to the axial direction of the impeller 1. Two
2 is formed.
【００１１】また、ケーシング１における渦型室２０
は、その内周壁と羽根車１との間の間隔が、周方向にお
いて漸次変化するようにされているわけであるが、渦型
室２０内周壁における吐出口２２に連続する部分であり
且つ羽根車１外周との間隔が最も狭い部分である舌部２
３から吐出口２２側に向けて邪魔板３を突出させてい
る。この邪魔板３は、図１(a)から明らかなように、吐
出口２２の軸方向と直交する面よりも羽根車１側に傾い
ているとともに、両側縁がケーシング１における羽根車
１の軸方向である両側面につながっているもので、図１
(b)に示すように、吐出口２２側から見た時、羽根車１
の軸１５に対して非平行となっている先端縁がＶ字形を
なすものとなっている。また、吐出口２２側から見た邪
魔板３の先端縁と羽根車１の側縁との交点Ｐは、羽根車
１の外周縁よりも羽根車１の軸１５側に位置している。Further, the vortex chamber 20 in the casing 1
The interval between the inner peripheral wall and the impeller 1 gradually changes in the circumferential direction, but is a part of the inner peripheral wall of the vortex chamber 20 that is continuous with the discharge port 22 and the blade. Tongue 2 which is the narrowest distance from the outer circumference of the car 1
The baffle plate 3 is projected from the discharge port 3 toward the discharge port 22 side. As is apparent from FIG. 1 (a), the baffle plate 3 is inclined toward the impeller 1 side with respect to a plane orthogonal to the axial direction of the discharge port 22 and has both side edges of the shaft of the impeller 1 in the casing 1. It is connected to both sides which is the direction.
As shown in (b), when viewed from the discharge port 22 side, the impeller 1
The tip edge, which is non-parallel to the axis 15 of, is V-shaped. Further, the intersection point P of the tip edge of the baffle plate 3 and the side edge of the impeller 1 as viewed from the discharge port 22 side is located closer to the shaft 15 side of the impeller 1 than the outer peripheral edge of the impeller 1.
【００１２】しかして、この多翼ファンにおいて、羽根
車１を回転させれば、吸い込み口２１から渦型室２０内
に吸い込まれた空気は、渦型室２０内において羽根車１
の回転で圧縮されて圧力を高め、吐出口２２へ送り出さ
れるものであり、この時、羽根車１のブレード１０は、
邪魔板３及び舌部２３の部分を通過する時、圧力変動を
生じさせるものの、邪魔板３の先端縁が羽根車１の軸１
５と非平行な傾斜縁となっているために、ブレード１０
の幅方向において圧力変動が同時に発生せず、特定の離
散周波数の騒音だけが大きくなってしまうということが
ないものである。In this multi-blade fan, however, when the impeller 1 is rotated, the air sucked into the swirl chamber 20 through the suction port 21 is moved in the swirl chamber 20.
The pressure is increased by the rotation of, and the pressure is increased to be sent out to the discharge port 22. At this time, the blade 10 of the impeller 1 is
Although the pressure fluctuation is generated when passing through the baffle plate 3 and the tongue portion 23, the tip edge of the baffle plate 3 is the shaft 1 of the impeller 1.
Blade 10 because of the beveled edge that is not parallel to 5
The pressure fluctuation does not occur at the same time in the width direction, and only the noise of a specific discrete frequency does not increase.
【００１３】特に、図示例のものにおいては、邪魔板３
の両側傾斜縁が非対称となっていることから、吐出口２
２側から見た時、邪魔板３が２カ所でブレード１０と交
差するものの、回転するブレード１０が両側傾斜縁を横
切るタイミングが異なるために、離散周波数騒音の低減
が更に有効に働くものであり、また吐出口２２側から見
た邪魔板３の先端縁と羽根車１の側縁との交点Ｐが羽根
車１の外周縁よりも羽根車１の軸１５側に位置してい
て、羽根車１のブレード１０はその全幅において邪魔板
３の傾斜縁を横切ることから、邪魔板３を設けたことに
よる騒音低減効果をブレード１０の全幅において得られ
るものである。In particular, in the illustrated example, the baffle plate 3
Since the inclined edges on both sides are asymmetrical, the discharge port 2
When viewed from the 2 side, the baffle plate 3 intersects with the blade 10 at two places, but since the rotating blade 10 crosses the inclined edges on both sides at different timings, the reduction of discrete frequency noise works more effectively. The intersection point P of the tip edge of the baffle plate 3 and the side edge of the impeller 1 when viewed from the discharge port 22 side is located closer to the shaft 15 side of the impeller 1 than the outer peripheral edge of the impeller 1, Since the blade 10 of No. 1 crosses the inclined edge of the baffle plate 3 in its entire width, the noise reduction effect due to the provision of the baffle plate 3 can be obtained in the entire width of the blade 10.
【００１４】しかも、このように舌部２３から吐出口２
２側に突出する邪魔板３を設けているとはいえ、邪魔板
１が吐出口２２の軸方向と直交する面よりも羽根車１側
に傾いていることから、邪魔板３が羽根車１に再度巻き
込まれてしまう風の量を多くしてしまうということがな
く、邪魔板３が吐出口２２側から見て先端縁がＶ字形を
なすものとなっていて、最も仕事量の多いブレード１０
の中央部の流路が広くとられていることもあって、邪魔
板３の存在で風量低下を招いてしまうことがないもので
ある。Moreover, in this way, the tongue portion 23 extends from the discharge port 2
Although the baffle plate 3 protruding to the 2 side is provided, since the baffle plate 1 is tilted toward the impeller 1 side with respect to the plane orthogonal to the axial direction of the discharge port 22, the baffle plate 3 is formed. The baffle plate 3 has a V-shaped tip edge when viewed from the discharge port 22 side without increasing the amount of wind that is re-engaged with the blade 10.
Since the flow path in the central part of the is large, the presence of the baffle plate 3 does not cause a decrease in air flow.
【００１５】図７に上記実施例に係る多翼ファンの騒音
特性を示す。図９で示した従来例の場合に比して、離散
周波数騒音が消えていることがわかる。また図６は羽根
車外径が７５ｍｍ、吐出口２２高さが６０ｍｍ、舌部２
３と羽根車１との間隔が約４ｍｍ、邪魔板３と羽根車１
との最小間隔が約３ｍｍである時、吐出口２２側から見
た舌部２３からの羽根車１の高さＨと前記交点Ｐの高さ
ｈとの比ｈ／Ｈと風量との関係を示すもので、風量は
１．３５ｍ3を１とした時の比で示している。ｈ／Ｈの
値は０．５〜１程度であることが望ましいことがわか
る。尚、上記実施例では、図１(b)において左側の交点
Ｐのｈ／Ｈの値を０．８、右側の交点Ｐのｈ／Ｈの値を
０．５としている。FIG. 7 shows the noise characteristics of the multi-blade fan according to the above embodiment. It can be seen that the discrete frequency noise disappears as compared with the case of the conventional example shown in FIG . Further, in FIG. 6, the outer diameter of the impeller is 75 mm, the height of the discharge port 22 is 60 mm, the tongue 2
The distance between the impeller 3 and the impeller 1 is about 4 mm, and the baffle plate 3 and the impeller 1
When the minimum distance between H and H is about 3 mm, the relationship between the air volume and the ratio h / H between the height H of the impeller 1 from the tongue 23 viewed from the discharge port 22 side and the height h of the intersection P is shown. The air flow rate is shown as a ratio when 1.35 m 3 is 1. It can be seen that the value of h / H is preferably about 0.5 to 1. In the above embodiment, the value of h / H at the intersection P on the left side in FIG. 1B is 0.8, and the value of h / H at the intersection P on the right side is 0.5.
【００１６】図３〜図５は上記実施例にかかる多翼ファ
ンを送風用として用いているヘアドライヤーを示してお
り、図中４は上記ケーシング２を兼ねるとともにグリッ
プ５が連結されたハウジング、４０はメインスイッチ、
４１はＷ数切換スイッチ、４２，４３は夫々吸い込み口
２１と吐出口２２とに配された異物混入防止用フィルタ
ー、図４中の６はヒータブロックである。羽根車１の駆
動用のモータ７は羽根車１の内部に配設されている。ま
た邪魔板３は、図５に示すように、２つ割りで形成され
た合成樹脂製のハウジング４（ケーシング２）に一体に
設けられている。このヘアドライヤーは風量が多く、し
かも騒音が少ないものとなっている。3 to 5 show a hair dryer using the multi-blade fan according to the above-mentioned embodiment for blowing air. In FIG. 3, 4 is a housing which doubles as the casing 2 and to which a grip 5 is connected, 40 Is the main switch,
Reference numeral 41 is a W number changeover switch, 42 and 43 are foreign matter mixing prevention filters arranged at the suction port 21 and the discharge port 22, respectively, and 6 in FIG. 4 is a heater block. A motor 7 for driving the impeller 1 is arranged inside the impeller 1. Further, as shown in FIG. 5, the baffle plate 3 is provided integrally with a housing 4 (casing 2) made of a synthetic resin and formed in two. This hair dryer has a large air volume and is low in noise.
【００１７】[0017]
【００１８】[0018]
【発明の効果】以上のように本発明においては、邪魔板
の先端縁が羽根車の軸と非平行な傾斜縁となっているた
めに、風量を多くするために舌部と羽根車との間隔を小
さくしても、ケーシングの舌部及び邪魔板付近を羽根車
のブレードが通過する際の圧力変動が、ブレードの幅方
向において同時に発生せず、従って特定の離散周波数の
騒音だけが大きくなってしまうということがなくて、騒
音レベルが低いものであり、特に邪魔板が吐出口側から
見て先端縁がＶ字形をなすために、最も仕事量が多いブ
レードの中央部の流路を広くとることができるために、
邪魔板が風量低下を招く存在となってしまうことを防ぐ
ことができ、この時、邪魔板の両側傾斜縁が非対称であ
るために、吐出口側から見た時、邪魔板が２カ所でブレ
ードと交差するものの、そのタイミングがずれるため
に、離散周波数騒音の低減に有効なものである。As described above, in the present invention, since the leading edge of the baffle plate is an inclined edge that is not parallel to the axis of the impeller, the tongue portion and the impeller are formed to increase the air volume. Even if the interval is reduced, pressure fluctuations when the blade of the impeller passes near the tongue and the baffle of the casing do not occur in the width direction of the blade at the same time, so only noise of a specific discrete frequency increases. The noise level is low and the baffle plate is especially
The tip has a V-shape when viewed, so it has the most work.
Because the flow path in the center of the raid can be wide,
Prevent the baffle from becoming an air conditioner
At this time, both side slanted edges of the baffle are asymmetric.
Therefore, when viewed from the discharge port side, the baffle is blurred in two places.
Although it intersects with the card, the timing is off
In addition, it is effective for reducing discrete frequency noise .
【００１９】また、邪魔板が吐出口の軸方向と直交する
面よりも羽根車側に傾いているものでは、邪魔板を設け
たことで羽根車に再度巻き込まれてしまう風の量が多く
なってしまうことをなくすことができて、風量低下を招
くことがないものであり、さらに、吐出口側から見た邪
魔板の先端縁と羽根車の側縁との交点を羽根車の外周縁
よりも羽根車の軸側に位置させておけば、邪魔板を設け
たことによる騒音低下に関して最も良好な結果を得るこ
とができるものである。Further, in the case where the baffle plate is inclined toward the impeller side with respect to the plane orthogonal to the axial direction of the discharge port, the baffle plate is provided to increase the amount of wind that is re-engaged in the impeller. and it can be eliminated thereby, it is those that not caused the air volume reduction, further, the outer periphery of the impeller and the intersection of the side edges of the baffles leading edge and the impeller as viewed from the discharge port side If it is also located on the shaft side of the impeller, the best result can be obtained with respect to noise reduction due to the provision of the baffle plate.
【００２０】そして、このような多翼ファンを用いたヘ
アドライヤーは、風量が多いにもかかわらず、騒音が少
なくて、きわめて好ましい性能を得ることができる。A hair dryer using such a multi-blade fan produces little noise, despite the large amount of air flow, and can obtain extremely favorable performance.
【図１】一実施例を示すもので、(a)は縦断面図、(b)は
破断正面図である。1A and 1B show an embodiment, wherein FIG. 1A is a vertical sectional view and FIG. 1B is a cutaway front view.
【図２】同上の側面図である。FIG. 2 is a side view of the above.
【図３】同上の多翼ファンを用いたヘアドライヤーの側
面図である。FIG. 3 is a side view of a hair dryer using the above multi-blade fan.
【図４】(a)は同上のヘアドライヤーの縦断面図、(b)は
破断正面図である。FIG. 4 (a) is a vertical cross-sectional view of the above-mentioned hair dryer, and FIG. 4 (b) is a cutaway front view.
【図５】同上のヘアドライヤーの２つ割りとなっている
ハウジングの一方側の斜視図である。FIG. 5 is a perspective view of one side of the housing, which is divided into two parts of the above hair dryer.
【図６】同上の風量特性図である。FIG. 6 is an air volume characteristic diagram of the above.
【図７】同上の騒音特性図である。FIG. 7 is a noise characteristic diagram of the above.
【図８】従来例を示すもので、(a)は縦断面図、(b)は破
断正面図である。 FIG. 8 shows a conventional example, in which (a) is a longitudinal sectional view and (b) is a broken view.
FIG.
【図９】同上の騒音特性図である。 FIG. 9 is a noise characteristic diagram of the above.
１ 羽根車 ２ ケーシング ３ 邪魔板 １０ ブレード ２０ 渦型室 ２１ 吸い込み口 ２２ 吐出口 ２３ 舌部 1 impeller 2 casing 3 baffles 10 blades 20 Whirlpool chamber 21 Suction mouth 22 Discharge port 23 tongue
───────────────────────────────────────────────────── フロントページの続き (58)調査した分野(Int.Cl.7，ＤＢ名) F04D 29/44 A45D 20/10 F04D 17/04 F04D 29/66 ─────────────────────────────────────────────────── ─── Continuation of the front page (58) Fields surveyed (Int.Cl. 7 , DB name) F04D 29/44 A45D 20/10 F04D 17/04 F04D 29/66
Claims (4)
根車と、この羽根車が配設される渦型室を備えるととも
に羽根車の軸方向に吸い込み口を、羽根車の軸方向と直
交する方向に吐出口を備えているケーシングとからなる
多翼ファンにおいて、ケーシングの渦型室内周壁におけ
る吐出口に連続する部分であり且つ羽根車外周との間隔
が最も狭い部分である舌部から吐出口側に向けて先端縁
が羽根車の軸と非平行な傾斜縁となっている邪魔板を突
出させるとともに、この邪魔板は吐出口側から見て先端
縁がＶ字形をなすとともに両側傾斜縁が非対称となって
いることを特徴とする多翼ファン。1. An impeller having a large number of blades on the outer periphery thereof, and a vortex chamber in which the impeller is disposed, and has a suction port in the axial direction of the impeller, which is orthogonal to the axial direction of the impeller. In a multi-blade fan including a casing having a discharge port in the direction of discharge, the discharge is made from the tongue part which is the part that is continuous with the discharge port on the vortex type inner peripheral wall of the casing and has the narrowest distance from the outer circumference of the impeller. Edge toward the exit side
While protruding the baffle plate that has an inclined edge that is not parallel to the axis of the impeller, and this baffle plate is the tip when viewed from the discharge port side.
The edges are V-shaped and the inclined edges on both sides are asymmetric.
Multi-blade fan, characterized in that there.
りも羽根車側に傾いていることを特徴とする請求項１記
載の多翼ファン。2. The multi-blade fan according to claim 1, wherein the baffle plate is inclined toward the impeller side with respect to a plane orthogonal to the axial direction of the discharge port.
車の側縁との交点が羽根車の外周縁よりも羽根車の軸側
に位置していることを特徴とする請求項１記載の多翼フ
ァン。3. The front edge of the baffle plate and the blade as viewed from the discharge port side
The intersection with the side edge of the wheel is closer to the axis of the wheel than the outer edge of the wheel.
The multi-blade fan according to claim 1, wherein the multi-blade fan is located at .
でのいずれかの項に記載の多翼ファンを備えていること
を特徴とするヘアドライヤー。 4. A blower fan according to any one of claims 1 to 3.
Equipped with a multi-blade fan as described in any of
A hair dryer.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP00986094A JP3491313B2 (en) | 1994-01-31 | 1994-01-31 | Multi-blade fan and hair dryer using it |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP00986094A JP3491313B2 (en) | 1994-01-31 | 1994-01-31 | Multi-blade fan and hair dryer using it |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH07217598A JPH07217598A (en) | 1995-08-15 |
| JP3491313B2 true JP3491313B2 (en) | 2004-01-26 |
Family
ID=11731896
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP00986094A Expired - Fee Related JP3491313B2 (en) | 1994-01-31 | 1994-01-31 | Multi-blade fan and hair dryer using it |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP3491313B2 (en) |
Families Citing this family (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP5476773B2 (en) | 2009-04-07 | 2014-04-23 | パナソニック株式会社 | Blower |
| KR101901303B1 (en) * | 2012-01-31 | 2018-09-21 | 엘지전자 주식회사 | Air conditioner |
| CN104033982B (en) * | 2013-03-06 | 2019-07-23 | 珠海格力电器股份有限公司 | Through-flow ventilation device, control method and air conditioner using same |
| JP2015128466A (en) * | 2014-01-06 | 2015-07-16 | 日本電産株式会社 | dryer |
| JP2015217259A (en) * | 2014-05-21 | 2015-12-07 | 三發電器製造廠有限公司 | Hair dryer |
| FR3056287B1 (en) * | 2016-09-19 | 2019-05-10 | Valeo Systemes Thermiques | AIR INTAKE HOUSING AND HEATING, VENTILATION AND / OR AIR CONDITIONING INSTALLATION FOR A CORRESPONDING MOTOR VEHICLE |
| KR102518665B1 (en) * | 2018-05-02 | 2023-04-06 | 현대자동차주식회사 | Flow Rate Performance Optimized type Bidirectional Blower |
| KR102134484B1 (en) * | 2019-01-22 | 2020-07-16 | 유태승 | Low noise type hair dryer |
| WO2023135783A1 (en) * | 2022-01-17 | 2023-07-20 | 三菱電機株式会社 | Centrifugal blower and air conditioning device |
-
1994
- 1994-01-31 JP JP00986094A patent/JP3491313B2/en not_active Expired - Fee Related
Also Published As
| Publication number | Publication date |
|---|---|
| JPH07217598A (en) | 1995-08-15 |
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