JPH05202893A - Air blower - Google Patents
Air blowerInfo
- Publication number
- JPH05202893A JPH05202893A JP1463992A JP1463992A JPH05202893A JP H05202893 A JPH05202893 A JP H05202893A JP 1463992 A JP1463992 A JP 1463992A JP 1463992 A JP1463992 A JP 1463992A JP H05202893 A JPH05202893 A JP H05202893A
- Authority
- JP
- Japan
- Prior art keywords
- blade
- orifice
- downstream
- hub
- impeller
- 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
Landscapes
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
Description
【０００１】[0001]
【産業上の利用分野】本発明は、家庭用空調機器や冷却
ファンなどに用いられる小型の軸流、あるいは、斜流送
風機に関するものである。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a small axial flow or mixed flow blower used for household air conditioners and cooling fans.
【０００２】[0002]
【従来の技術】従来のこの種の送風装置は図３に示すよ
うに、略円筒形のハブ１の周囲に複数枚の羽根２を設け
た羽根車３のハブ中心部にボスを形成し、モータ４の回
転軸を接続するとともに、羽根車３の周囲をほぼ円筒状
のオリフィス５で囲った構成になっている。この羽根２
を回転軸周りに回転させたときの子午断面形状は、種々
のものが考案されており、図３以外にも図４に示すよう
な形も多い。しかし、一般に前縁２ａ，１２ａ，後縁２
ｂ，１２ｂはともにほぼ直線で構成されているのが普通
である。羽根の子午断面形状は送風性能と密接な関係が
あり、図３のように、気流の上流側に傾斜させることに
よって、つまり、図中の角度αをある程度大きく取るこ
とによって、主として低騒音化が図られる。これは、羽
根面上の流れが遠心力によってチップ側に流され、チッ
プ側で境界層が発達して剥離し、騒音の原因になる現象
を、羽根を傾斜させてチップ側へ流れにくくすることに
よって抑えているためである。2. Description of the Related Art As shown in FIG. 3, a conventional blower of this type has a boss formed at the center of a hub of an impeller 3 provided with a plurality of blades 2 around a substantially cylindrical hub 1. The rotary shaft of the motor 4 is connected and the impeller 3 is surrounded by a substantially cylindrical orifice 5. This feather 2
Various meridional cross-sectional shapes have been devised when rotated around the rotation axis, and in addition to FIG. 3, there are many shapes as shown in FIG. However, in general, the leading edges 2a, 12a, the trailing edge 2
It is usual that both b and 12b are substantially linear. The meridional cross-sectional shape of the blade has a close relationship with the blowing performance, and as shown in FIG. 3, it is possible to reduce the noise mainly by inclining it toward the upstream side of the air flow, that is, by making the angle α in the figure large to some extent. Planned. This is because the flow on the blade surface is caused to flow to the tip side by centrifugal force, the boundary layer develops and separates on the tip side, and causes the noise to make it difficult to flow to the tip side by tilting the blade. It is because it is suppressed by.
【０００３】また、オリフィス５の形状も性能に大きな
影響がある。流入部の曲面形状や軸方向の長さ、羽根車
との相対位置などが風量、風圧、騒音性能に対する重要
なパラメータである。一般に、オリフィス５の軸方向長
さを大きくすると、圧力特性は向上するが、風量や騒音
特性は低下する。The shape of the orifice 5 also has a great influence on the performance. The curved surface shape of the inflow portion, the axial length, the relative position to the impeller, etc. are important parameters for the air volume, wind pressure, and noise performance. Generally, when the axial length of the orifice 5 is increased, the pressure characteristic is improved, but the air volume and the noise characteristic are deteriorated.
【０００４】[0004]
【発明が解決しようとする課題】しかしながら上記従来
の構成では、羽根の傾斜角αを大きくし、羽根を上流側
に傾斜させることによって、羽根車の軸方向の寸法が大
きくなるので、薄型の羽根車が必要な場合には、羽根の
傾斜角αを小さくしなければならず、十分な低騒音効果
が得られなかった。さらに、一般に、薄型化すると静圧
特性が低下するという課題があった。However, in the above-mentioned conventional configuration, by increasing the inclination angle α of the blade and inclining the blade toward the upstream side, the axial dimension of the impeller becomes large, so that the blade is thin. When a car is required, the blade inclination angle α must be reduced, and a sufficient noise reduction effect cannot be obtained. Further, in general, there is a problem that the static pressure characteristic is deteriorated when the thickness is reduced.
【０００５】本発明は上記課題を解決するもので、上流
側への羽根の傾斜を十分にとり、低騒音を実現するとと
もに、薄型化を図り、かつ、圧力特性を高めることを目
的としたものである。The present invention has been made to solve the above-mentioned problems, and has an object to achieve sufficient noise by achieving a sufficient inclination of the blades toward the upstream side, to achieve a low profile, and to enhance pressure characteristics. is there.
【０００６】[0006]
【課題を解決するための手段】本送風装置は上記目的を
達成するため、中心にボス部を有する略円筒形のハブの
周囲に複数枚の羽根を設けた羽根車と、前記羽根車を囲
うオリフィスと、前記羽根車の上流に位置して、回転軸
が前記羽根車に接続されたモータを備え、前記羽根車は
回転軸周りに回転させたときの子午断面形状が、前縁、
後縁ともに下流側に凸形の頂点を持つ曲線で構成され、
前縁とチップの接合点Ａが前縁とハブの接合点Ｂよりも
上流側に位置するとともに、後縁とチップの接合点Ｃが
後縁とハブの接合点Ｄよりも上流側に位置し、さらに、
前記オリフィスは羽根と対抗する部分の軸方向長さがチ
ップの軸方向長さの約１／２以下であり、かつ、その下
流端が前記接合点Ｃとほぼ同じ位置に設けた構成として
ある。In order to achieve the above-mentioned object, the present air blower encloses an impeller having a plurality of blades around a substantially cylindrical hub having a boss portion at the center, and the impeller. An orifice and a motor that is located upstream of the impeller and has a rotation shaft connected to the impeller, wherein the impeller has a meridional cross-sectional shape when rotated around the rotation shaft, a leading edge,
Both trailing edges are composed of curved lines with convex vertices on the downstream side,
The joining point A between the leading edge and the tip is located upstream of the joining point B between the leading edge and the hub, and the joining point C between the trailing edge and the tip is located upstream of the joining point D between the trailing edge and the hub. ,further,
The orifice has a structure in which the axial length of a portion facing the blade is about ½ or less of the axial length of the tip, and the downstream end thereof is provided at substantially the same position as the joint point C.
【０００７】[0007]
【作用】本発明は上記構成によって、羽根車を回転軸周
りに回転させたときの羽根の子午断面形状が、ハブ付近
では下流側に傾斜しており、チップ側では上流側に傾斜
しているので、同じ軸方向長さの羽根車において、羽根
のチップ側については大きな傾斜を与えることができ
る。つまり、流量が多く、遠心力も大きなチップ側で羽
根の傾斜が大きくなるので、境界層の発達を抑える効果
が大きくなる。さらに、羽根後縁を下流側に凸部を持っ
た曲線で構成しているので、オリフィスの下流端をチッ
プの下流端に一致させた場合でも、ハブ下流端とオリフ
ィス下流端を結ぶ線よりも下流側に羽根後縁が突出する
ことになり、高負荷時の特性も向上する。According to the present invention, the meridional cross-sectional shape of the blade when the impeller is rotated about the rotation axis is inclined to the downstream side near the hub and is inclined to the upstream side on the tip side. Therefore, in the impeller having the same axial length, a large inclination can be given to the tip side of the blade. That is, since the blade has a large inclination on the side of the tip having a large flow rate and a large centrifugal force, the effect of suppressing the development of the boundary layer becomes large. Furthermore, since the trailing edge of the blade is composed of a curved line with a convex portion on the downstream side, even when the downstream end of the orifice is aligned with the downstream end of the tip, it is more than the line connecting the hub downstream end and the orifice downstream end. The blade trailing edge projects to the downstream side, and the characteristics under high load are also improved.
【０００８】[0008]
【実施例】以下本発明の実施例を図を参照して説明す
る。Embodiments of the present invention will be described below with reference to the drawings.
【０００９】図１において、６は羽根車であり、略円筒
形のハブ７の周りに複数枚の羽根８を配設した構造であ
る。ハブ７の中央部にはボス部が設けられ、羽根車６の
上流側に置かれたモータ４の回転軸に接続されている。
羽根８はその回転軸周りの子午断面形状において、前縁
８ａ，後縁８ｂともに下流側に凸形の頂点を持つ曲線で
構成され、前縁８ａとチップの接合点Ａは前縁８ａとハ
ブの接合点Ｂよりも上流側に位置するとともに、後縁８
ｂとチップの接合点Ｃは後縁８ｂとハブの接合点Ｄより
も上流側に位置している。さらに、羽根車６の周囲を取
り巻くオリフィス９は羽根と対向する部分の長さ（Ｌ
ｏ）を羽根のチップの長さ（Ｌｔ）の約３０％以下にす
るとともに、その下流端を前記接合点Ｃとほぼ一致させ
てある。In FIG. 1, reference numeral 6 denotes an impeller, which has a structure in which a plurality of blades 8 are arranged around a substantially cylindrical hub 7. A boss is provided at the center of the hub 7 and is connected to the rotary shaft of the motor 4 placed upstream of the impeller 6.
In the meridional cross-sectional shape of the blade 8 around its axis of rotation, both the leading edge 8a and the trailing edge 8b are composed of curves having convex vertices on the downstream side, and the joining point A between the leading edge 8a and the tip is the leading edge 8a and the hub. Of the trailing edge 8
The junction point C between b and the tip is located upstream of the junction point D between the trailing edge 8b and the hub. Further, the orifice 9 surrounding the impeller 6 has a length (L
o) is set to about 30% or less of the length (Lt) of the tip of the blade, and the downstream end thereof is made to substantially coincide with the joint point C.
【００１０】上記構成における羽根の傾斜角と軸方向寸
法の関係を従来例と比較して図２に示す。（ａ）に示す
従来例は羽根の前縁と後縁がともに直線で構成されてお
り、羽根の傾斜角はほぼ一定値である。一方、（ｂ）に
示す本発明の羽根車は前縁８ａと後縁８ｂが下流側に凸
の曲線で構成されているため、ハブ付近の羽根傾斜角β
１は負の角度になる。したがって、同じ軸方向寸法の羽
根でも、前、後縁の凸部より外周側では大きな傾斜角β
２が得られる。FIG. 2 shows the relationship between the inclination angle of the blade and the axial dimension in the above structure in comparison with the conventional example. In the conventional example shown in (a), both the leading edge and the trailing edge of the blade are formed by straight lines, and the inclination angle of the blade is substantially constant. On the other hand, in the impeller of the present invention shown in (b), since the leading edge 8a and the trailing edge 8b are constituted by a curved curve convex toward the downstream side, the blade inclination angle β near the hub
1 is a negative angle. Therefore, even with blades having the same axial dimension, a larger inclination angle β is provided on the outer peripheral side than the convex portions on the front and rear edges.
2 is obtained.
【００１１】このような傾斜角を持った羽根車で送風を
行なった場合、羽根のチップ側では大きな傾斜角の効果
によって、羽根面上の流れが遠心力によって外周側へ流
れる現象が抑えられるので、境界層剥離による騒音が制
御され、低騒音化が図れるという効果がある。一方、ハ
ブ側では羽根の傾斜角が逆向きになっているので遠心力
の効果を抑えることが出来ないが、ハブ側はもともと羽
根の周速度が小さく、遠心力が弱い上に、途中からは傾
斜角が大きくなっているので、それ以上外周側へ流れて
行くことはない。また、流量自体もハブ側よりもチップ
側が相当多く流れており、全体としてみたときのハブ側
の影響は少ない。When air is blown by an impeller having such an inclination angle, the effect of the large inclination angle on the tip side of the blade suppresses the phenomenon that the flow on the blade surface flows to the outer peripheral side due to centrifugal force. The effect of controlling the noise due to the separation of the boundary layer can be reduced. On the other hand, on the hub side, the inclination angle of the blades is opposite, so the effect of centrifugal force cannot be suppressed, but on the hub side, the peripheral speed of the blades is originally small, the centrifugal force is weak, and from the middle Since the inclination angle is large, it will not flow further to the outer peripheral side. Moreover, the flow rate itself is considerably larger on the tip side than on the hub side, and the influence on the hub side as a whole is small.
【００１２】さらに、羽根の後縁が下流側に凸の曲線で
構成されているので、オリフィスの下流端を羽根チップ
の下流端Ｃとほぼ同じ位置に設定した場合でも、図１の
網掛け部Ｘがオリフィスよりも下流側に突出した形にな
る。このため、オリフィスよりも下流側に流れを送る働
きが強くなり、軸方向の長さ（Ｌｏ）が羽根チップの長
さ（Ｌｔ）の１／２以下という薄いオリフィスを用い
て、低負荷時の風量と低騒音を重視した場合でも、高負
荷時の性能を確保することが出来るという効果がある。Further, since the trailing edge of the blade is formed by a curved line which is convex toward the downstream side, even when the downstream end of the orifice is set at substantially the same position as the downstream end C of the blade tip, the shaded portion in FIG. The shape of X projects to the downstream side of the orifice. For this reason, the action of sending the flow to the downstream side of the orifice becomes stronger, and a thin orifice whose axial length (Lo) is 1/2 or less of the blade tip length (Lt) is used to reduce the load. Even when the air volume and the low noise are emphasized, there is an effect that the performance under high load can be secured.
【００１３】[0013]
【発明の効果】以上説明したように本発明の送風装置
は、羽根の前縁、後縁を下流側に凸の曲線で構成したこ
とにより、羽根の軸方向寸法を増すことなく、羽根の傾
斜角を大きくすることが可能になり、低騒音化を図るこ
とが出来る。また、後縁の凸形状は高負荷時の性能向上
に効果があり、薄型のオリフィスと組み合わせて、低負
荷時の大風量、低騒音を満足しつつ、高負荷時の性能も
維持するという効果がある。As described above, in the air blower of the present invention, the leading edge and the trailing edge of the blade are constituted by the curved lines convex toward the downstream side, so that the inclination of the blade can be increased without increasing the axial dimension of the blade. It is possible to increase the angle and reduce noise. In addition, the convex shape of the trailing edge is effective in improving the performance at high load, and in combination with a thin orifice, it is effective in satisfying large air volume and low noise at low load while maintaining performance at high load. There is.
【図１】本発明の一実施例における送風装置の断面図FIG. 1 is a sectional view of an air blower according to an embodiment of the present invention.
【図２】同送風装置の羽根車と従来の羽根車を比較した
断面図FIG. 2 is a cross-sectional view comparing an impeller of the blower with a conventional impeller.
【図３】従来の送風装置の断面図FIG. 3 is a sectional view of a conventional blower.
【図４】従来の他の送風装置の断面図FIG. 4 is a sectional view of another conventional blower.
４ モータ ６ 羽根車 ７ ハブ ８ 羽根 ８ａ 前縁 ８ｂ 後縁 ９ オリフィス 4 Motor 6 Impeller 7 Hub 8 Blade 8a Leading Edge 8b Trailing Edge 9 Orifice
Claims (1)
囲に複数枚の羽根を設けた羽根車と、前記羽根車を囲う
オリフィスと、前記羽根車の上流に位置して、回転軸が
前記羽根車に接続されたモータを備え、前記羽根車は回
転軸周りに回転させたときの子午断面形状が、前縁、後
縁ともに下流側に凸形の頂点を持つ曲線で構成され、前
縁とチップの接合点Ａが前縁とハブの接合点Ｂよりも上
流側に位置するとともに、後縁とチップの接合点Ｃが後
縁とハブの接合点Ｄよりも上流側に位置し、さらに、前
記オリフィスは羽根と対向する部分の軸方向長さがチッ
プの軸方向長さの１／２以下であり、かつ、その下流端
が前記接合点Ｃとほぼ同じ位置にある送風装置。1. An impeller in which a plurality of blades are provided around a substantially cylindrical hub having a boss portion in the center, an orifice surrounding the impeller, and an rotary shaft located upstream of the impeller. Includes a motor connected to the impeller, the impeller has a meridional cross-sectional shape when rotated about a rotation axis, the leading edge, the trailing edge is configured with a curve having a convex vertex on the downstream side, The joining point A between the leading edge and the tip is located upstream of the joining point B between the leading edge and the hub, and the joining point C between the trailing edge and the tip is located upstream of the joining point D between the trailing edge and the hub. Furthermore, the blower is such that the axial length of the portion of the orifice facing the blade is less than or equal to 1/2 of the axial length of the tip, and the downstream end of the orifice is at substantially the same position as the junction point C.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1463992A JPH05202893A (en) | 1992-01-30 | 1992-01-30 | Air blower |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1463992A JPH05202893A (en) | 1992-01-30 | 1992-01-30 | Air blower |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH05202893A true JPH05202893A (en) | 1993-08-10 |
Family
ID=11866773
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP1463992A Pending JPH05202893A (en) | 1992-01-30 | 1992-01-30 | Air blower |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH05202893A (en) |
Cited By (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP4662608B2 (en) * | 2000-06-09 | 2011-03-30 | エルジー エレクトロニクス インコーポレイティド | Fan motor with integrated axial fan and motor |
| WO2013069397A1 (en) * | 2011-11-10 | 2013-05-16 | 三菱電機株式会社 | External cooling unit of vehicular air-conditioning device |
| JP2013217315A (en) * | 2012-04-10 | 2013-10-24 | Sharp Corp | Propeller fan, fluid feed device and molding mold |
| JP2015017616A (en) * | 2014-10-03 | 2015-01-29 | シャープ株式会社 | Propeller fan, fluid feeding device and molding die |
| JP2015017617A (en) * | 2014-10-03 | 2015-01-29 | シャープ株式会社 | Propeller fan, fluid feeding device and molding die |
| JP2016205399A (en) * | 2016-07-29 | 2016-12-08 | シャープ株式会社 | Electric fan or propeller fan for circulator, electric fan or circulator, and molding die |
| JP2017031981A (en) * | 2016-10-28 | 2017-02-09 | シャープ株式会社 | Electric fan or propeller fan for circulator, electric fan or circulator, and molding die |
| US9726190B2 (en) | 2012-04-10 | 2017-08-08 | Sharp Kabushiki Kaisha | Propeller fan, fluid feeder, electric fan, and molding die |
| US9816521B2 (en) | 2012-04-10 | 2017-11-14 | Sharp Kabushiki Kaisha | Propeller fan, fluid feeder, and molding die |
| JP2019090382A (en) * | 2017-11-16 | 2019-06-13 | 日本電産株式会社 | Axial flow fan |
| CN117419071A (en) * | 2023-12-19 | 2024-01-19 | 珠海格力电器股份有限公司 | Fan blade assembly and axial flow fan with same |
-
1992
- 1992-01-30 JP JP1463992A patent/JPH05202893A/en active Pending
Cited By (16)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP4662608B2 (en) * | 2000-06-09 | 2011-03-30 | エルジー エレクトロニクス インコーポレイティド | Fan motor with integrated axial fan and motor |
| WO2013069397A1 (en) * | 2011-11-10 | 2013-05-16 | 三菱電機株式会社 | External cooling unit of vehicular air-conditioning device |
| CN103946556A (en) * | 2011-11-10 | 2014-07-23 | 三菱电机株式会社 | External cooling unit of vehicular air-conditioning device |
| US10052931B2 (en) | 2011-11-10 | 2018-08-21 | Mitsubishi Electric Corporation | Outdoor cooling unit in vehicle air-conditioning apparatus |
| JPWO2013069397A1 (en) * | 2011-11-10 | 2015-04-02 | 三菱電機株式会社 | Outdoor cooling unit for vehicle air conditioner |
| EP2778430A4 (en) * | 2011-11-10 | 2015-08-26 | Mitsubishi Electric Corp | External cooling unit of vehicular air-conditioning device |
| US9726190B2 (en) | 2012-04-10 | 2017-08-08 | Sharp Kabushiki Kaisha | Propeller fan, fluid feeder, electric fan, and molding die |
| JP2013217315A (en) * | 2012-04-10 | 2013-10-24 | Sharp Corp | Propeller fan, fluid feed device and molding mold |
| US9816521B2 (en) | 2012-04-10 | 2017-11-14 | Sharp Kabushiki Kaisha | Propeller fan, fluid feeder, and molding die |
| JP2015017616A (en) * | 2014-10-03 | 2015-01-29 | シャープ株式会社 | Propeller fan, fluid feeding device and molding die |
| JP2015017617A (en) * | 2014-10-03 | 2015-01-29 | シャープ株式会社 | Propeller fan, fluid feeding device and molding die |
| JP2016205399A (en) * | 2016-07-29 | 2016-12-08 | シャープ株式会社 | Electric fan or propeller fan for circulator, electric fan or circulator, and molding die |
| JP2017031981A (en) * | 2016-10-28 | 2017-02-09 | シャープ株式会社 | Electric fan or propeller fan for circulator, electric fan or circulator, and molding die |
| JP2019090382A (en) * | 2017-11-16 | 2019-06-13 | 日本電産株式会社 | Axial flow fan |
| US11480196B2 (en) | 2017-11-16 | 2022-10-25 | Nidec Corporation | Axial fan |
| CN117419071A (en) * | 2023-12-19 | 2024-01-19 | 珠海格力电器股份有限公司 | Fan blade assembly and axial flow fan with same |
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