JPH07117077B2 - Axial blower - Google Patents
Axial blowerInfo
- Publication number
- JPH07117077B2 JPH07117077B2 JP2026536A JP2653690A JPH07117077B2 JP H07117077 B2 JPH07117077 B2 JP H07117077B2 JP 2026536 A JP2026536 A JP 2026536A JP 2653690 A JP2653690 A JP 2653690A JP H07117077 B2 JPH07117077 B2 JP H07117077B2
- Authority
- JP
- Japan
- Prior art keywords
- orifice
- blower
- impeller
- side panel
- axial
- 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
- Structures Of Non-Positive Displacement Pumps (AREA)
Description
【発明の詳細な説明】 産業上の利用分野 本発明は、主にセパレート型空気調和機の室外機などに
用いられる軸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 an axial blower mainly used for an outdoor unit of a separate type air conditioner and the like.
従来の技術 近年、軸流送風機は、セパレート型空気調和機の室外機
などの送風機として、業務用から家庭用まで幅広く使用
されており、より低騒音化が望まれる傾向にある。2. Description of the Related Art In recent years, axial blowers have been widely used as blowers such as outdoor units of separate air conditioners from commercial use to household use, and there is a tendency for noise reduction to be desired.
以下、図面を参照しながら、実開昭62−1054320号公報
などで提案されている従来の軸流送風機について説明す
る。The conventional axial-flow blower proposed in Japanese Utility Model Laid-Open No. 62-1054320 will be described below with reference to the drawings.
第５図、第６図は従来の軸流送風機を搭載したセパレー
ト型空気調和機の室外機の構造を示したものであり、第
７図、第８図は従来の軸流送風機のオリフィスの断面形
状を示したものである。１はセパレート型空気調和機の
室外機本体であり、２は送風機室、３はコンプレッサー
室であり、送風機室２は略正方形の吹出側パネル４と側
板５および吹出側パネル４と反対の面に設置された熱交
換器６で形成されている。また、７は略正方形の吹出側
パネル４の略中央部に配設した羽根車であり、８は羽根
車７の周囲に設けられた吸込側先端8aがベルマウス状の
オリフィスである。以上のように構成された軸流送風機
について以下その動作を説明する。5 and 6 show the structure of an outdoor unit of a separate type air conditioner equipped with a conventional axial-flow blower, and FIGS. 7 and 8 show a cross section of an orifice of the conventional axial-flow blower. The shape is shown. 1 is an outdoor unit body of a separate type air conditioner, 2 is a blower room, 3 is a compressor room, and the blower room 2 is a substantially square blower side panel 4 and a side plate 5 and a side opposite to the blower side panel 4. It is formed of the installed heat exchanger 6. Further, 7 is an impeller arranged in a substantially central portion of the substantially square blow-out side panel 4, and 8 is a suction side tip 8a provided around the impeller 7 which is a bellmouth-shaped orifice. The operation of the axial blower configured as above will be described below.
羽根車７が所定の回転方向に回転すると、熱交換器６を
介して空気が送風機室２内に流入し、この際空気と熱交
換器６との間で熱交換が行なわれる。送風機室２内に流
入した空気は羽根車７の送風作用で静圧と動圧が付加さ
れオリフィス８を介して送風機室２外に吐出される。When the impeller 7 rotates in a predetermined rotation direction, air flows into the blower chamber 2 via the heat exchanger 6, and at this time, heat exchange is performed between the air and the heat exchanger 6. The air flowing into the blower chamber 2 is added with static pressure and dynamic pressure by the blowing action of the impeller 7, and is discharged to the outside of the blower chamber 2 through the orifice 8.
発明が解決しようとする課題 しかしながら、上記のような構成では、吹出側パネル４
が略正方形のため、吹出側パネル４の対角線部の断面
（ａ−ａ）では第７図で示すように羽根車７と側壁5a、
側壁5bとの距離が大きく、羽根車７に対して求心方向の
流入気流Ｅが発生する。一方、吹出側パネル４の短辺側
中央部の断面（ｂ−ｂ）では第８図で示すように羽根車
７と側壁5aとの距離が小さく、羽根車７に対して軸流方
向の流入気流Ｆが発生する。このように、羽根車７のオ
リフィス８付近の流入気流の方向はオリフィス８の各部
位によって異なるのに対して、オリフィス８の断面形状
は各部同一であるため、流入気流とオリフィス形状が適
合していない部分があった。例えば、第７図で示すよう
に吹出側パネル４の対角線部の断面では、求心方向成分
が多い流入気流Ｅに対し、オリフィス８の吸込側先端部
8aの曲げ曲率半径R1が小さ過ぎ流れの剥離が生じやす
く、この気流の剥離により流れが乱れ、乱流音が増加
し、送風騒音が増すという問題点があった。このため、
オリフィス８近傍のでの流れの剥離を抑えなければなら
ないという課題を有していた。DISCLOSURE OF THE INVENTION Problems to be Solved by the Invention However, in the configuration as described above, the blow-out side panel 4
Is substantially square, the cross section (a-a) of the diagonal portion of the blow-out side panel 4 has an impeller 7 and a side wall 5a, as shown in FIG.
The distance from the side wall 5b is large, and the inflow airflow E in the centripetal direction is generated with respect to the impeller 7. On the other hand, as shown in FIG. 8, the distance between the impeller 7 and the side wall 5a is small in the cross section (bb) of the blower side panel 4 on the shorter side, and the inflow of the impeller 7 in the axial direction is small. Airflow F is generated. As described above, the direction of the inflow airflow in the vicinity of the orifice 8 of the impeller 7 differs depending on each part of the orifice 8, but the cross-sectional shape of the orifice 8 is the same for each part, so the inflow airflow and the orifice shape are compatible. There was no part. For example, as shown in FIG. 7, in the cross section of the diagonal portion of the blow-out side panel 4, the suction-side tip portion of the orifice 8 with respect to the inflow airflow E with many centripetal direction components.
The bending radius of curvature R1 of 8a was too small, and flow separation was likely to occur, and the flow separation disturbed the flow, increasing the turbulent sound and increasing the blast noise. For this reason,
There is a problem in that the separation of the flow near the orifice 8 must be suppressed.
本発明は上記課題に鑑み、吹出側パネルを略正方形に保
持したままで、羽根車のオリフィス付近の異なった流入
気流の方向に対応し、オリフィス近傍のでの流れの剥離
を抑えた低騒音の軸流送風機を提供するものである。In view of the above problems, the present invention corresponds to different inflow airflow directions near the orifice of the impeller while keeping the outlet side panel in a substantially square shape, and a low noise shaft that suppresses flow separation near the orifice. It is intended to provide a blower.
課題を解決するための手段 上記課題を解決するために本発明の軸流送風機は、送風
機室と、前記送風機室内の略正方形の吹出側パネルの略
中央部に設けた羽根車と、前記羽根車の周囲に設けたオ
リフィスとで構成し、前記オリフィスの吸込側先端部の
曲げの曲率半径を、前記略正方形の吹出側パネルの各辺
の中央部で最小とし、対角線部を最大とするものであ
る。Means for Solving the Problems In order to solve the above problems, an axial blower of the present invention is a blower chamber, an impeller provided in a substantially central portion of a substantially square blow-out side panel in the blower chamber, and the impeller. And the radius of curvature of the bending of the suction side tip of the orifice is minimized at the center of each side of the substantially square blow-out side panel, and the diagonal line is maximized. is there.
作用 この構成によって、軸流送風機の羽根車に対して求心方
向の流入気流が発生する部分ではオリフィスの吸込側先
端部の曲げの曲率半径が大きく、流入気流が無理なくオ
リフィスに沿って流れ、オリフィス付近での気流の急激
な曲折による気流の剥離を抑え、乱流音の増加を防止す
る。Effect With this configuration, the radius of curvature of the bending of the suction side tip of the orifice is large at the portion where the inflow air flow in the centripetal direction with respect to the impeller of the axial blower is large, and the inflow air flow smoothly along the orifice It suppresses the separation of the air flow due to the rapid bending of the air flow in the vicinity, and prevents the increase of turbulent sound.
実施例 以下本発明の一実施例の軸流送風機について図面を参照
しながら説明する。尚、従来例と同一部分に関しては同
一番号を付し、説明を省略する。第１図、第２図は本発
明の一実施例における軸流送風機を搭載したセパレート
型空気調和機の室外機の構造を示したものであり、第３
図、第４図は本実施例の軸流送風機のオリフィスの断面
形状を示したものである。９は略正方形の吹出側パネル
４の略中央部に配設した羽根車７の周囲に設けられたオ
リフィスであり、吹出側パネル４の対角線部の断面（ｃ
−ｃ）が第３図、短辺側中央部の断面（ｄ−ｄ）が第４
図である。すなわち、オリフィス７の吸込側先端部9aの
曲げの曲率半径を、前記略正方形の吹出側パネルの上下
左右の短辺側中央部で最小R1とし、対角線部で最大R2
（R2＞R1）としてある。Embodiment An axial fan according to an embodiment of the present invention will be described below with reference to the drawings. The same parts as those of the conventional example are designated by the same reference numerals and the description thereof will be omitted. 1 and 2 show the structure of an outdoor unit of a separate type air conditioner equipped with an axial blower according to an embodiment of the present invention.
FIG. 4 and FIG. 4 show the sectional shape of the orifice of the axial blower of this embodiment. Reference numeral 9 denotes an orifice provided around the impeller 7 arranged in the substantially central portion of the blowing-side panel 4 having a substantially square shape, and a cross-section (c of the diagonal line portion of the blowing-side panel 4).
-C) is FIG. 3, and the cross section (dd) of the central portion on the short side is the fourth.
It is a figure. That is, the radius of curvature of bending of the suction-side tip portion 9a of the orifice 7 is set to a minimum R1 at the center of the short side on the upper, lower, left, and right sides of the substantially square-shaped outlet side panel, and a maximum R2 at the diagonal portion.
(R2> R1).
羽根車７が所定の回転方向に回転すると、熱交換器６を
介して空気が送風機室２内に流入し、この際空気と熱交
換器６との間で熱交換が行なわれる。送風機室２内に流
入した空気は羽根車７の送風作用で静圧と動圧が付加さ
れオリフィス９を介して送風機室２外に吐出される。こ
こで、吹出側パネル４は略正方形のため、対角線部の断
面（ｃ−ｃ）では第３図で示すように羽根車７と側壁5
a、側壁5bとの距離が大きく、羽根車７に対して求心方
向の流入気流Ｇが発生する。しかし、断面（ｃ−ｃ）お
けるオリフィス９の吸込側先端部9aの曲げの曲率半径R2
は他の部分に比べ最大となるように設定してあるから、
流入気流Ｇがオリフィス９に沿って無理なく湾曲して流
れ、気流の急激な曲折による気流の剥離を起こさず、従
って、乱流の発生を抑え、乱流音の増加を防止すること
ができる。しかも、吹出側パネル４の短辺側中央部の断
面（ｄ−ｄ）では第４図で示すように羽根車７と側壁5a
の距離が小さく、羽根車７に対して流入気流Ｈは軸流方
向からの流れとなるため、オリフィス９の吸込側先端部
9aの曲げの曲率半径R1を他の部分に比べ最小に設定する
ことにより吹出側パネル４の上下左右のうち短辺側の寸
法を小さくすることができ、製品寸法を小さくすること
ができる。When the impeller 7 rotates in a predetermined rotation direction, air flows into the blower chamber 2 via the heat exchanger 6, and at this time, heat exchange is performed between the air and the heat exchanger 6. The air flowing into the blower chamber 2 is added with static pressure and dynamic pressure by the blowing action of the impeller 7, and is discharged to the outside of the blower chamber 2 through the orifice 9. Here, since the blow-out side panel 4 is substantially square, in the cross section (cc) of the diagonal line portion, as shown in FIG.
Since the distance between a and the side wall 5b is large, an inflow air flow G in the centripetal direction is generated with respect to the impeller 7. However, the curvature radius R2 of the bending of the suction side tip portion 9a of the orifice 9 in the cross section (cc) is
Is set to be the maximum compared to other parts,
The inflowing airflow G flows smoothly along the orifice 9 without causing separation of the airflow due to abrupt bending of the airflow. Therefore, it is possible to suppress the occurrence of turbulence and prevent an increase in turbulent sound. Moreover, as shown in FIG. 4, in the cross section (d-d) of the central portion on the short side of the blow-out side panel 4, as shown in FIG.
Is small and the inflow airflow H flows from the impeller 7 in the axial direction, so that the suction side tip of the orifice 9 is
By setting the radius of curvature R1 of the bending of 9a to the minimum as compared with the other portions, it is possible to reduce the dimension of the short side of the blow-out side panel 4 in the upper, lower, left, and right sides, thus reducing the product dimension.
発明の効果 以上のように、本発明の軸流送風機は、送風機室と、前
記送風機室内の略正方形の吹出側パネルの略中央部に設
けた羽根車と、前記羽根車の周囲に設けたオリフィスと
で構成し、前記オリフィスの吸込側先端部の曲げの曲率
半径を、前記略正方形の吹出側パネルの各辺の中央部で
最小とし、対角線部を最大とすることにより、羽根車に
対して求心方向の流入気流が発生する部分でも流入気流
がオリフィスに沿って無理なく湾曲して流れ、オリフィ
ス近傍での気流の剥離を抑え、乱流による送風騒音の増
加を抑えると共に、送風機室を小さくすることができ、
製品寸法を小さくすることができる。EFFECTS OF THE INVENTION As described above, the axial blower of the present invention includes a blower chamber, an impeller provided in a substantially central portion of a substantially square blow-out side panel in the blower chamber, and an orifice provided around the impeller. And the radius of curvature of bending of the suction-side tip of the orifice is minimized at the center of each side of the substantially square blow-out side panel, and the diagonal line is maximized so that the impeller is Even in the part where the inflow air flow in the centripetal direction is generated, the inflow air flow smoothly curves along the orifice, suppresses the separation of the air flow near the orifice, suppresses the increase of blast noise due to turbulence, and reduces the size of the blower room. It is possible,
The product size can be reduced.
第１図は本発明の一実施例における軸流送風機を搭載し
たセパレート型空気調和機の室外機の正面図、第２図は
第１図の中央断面図、第３図は第１図のｃ−ｃ断面図、
第４図は第１図のｄ−ｄ断面図、第５図は従来の軸流送
風機を搭載したセパレート型空気調和機の室外機の正面
図、第６図は第５図の中央断面図、第７図は第５図のａ
−ａ断面図、第８図は第５図のｂ−ｂ断面図である。 ２……送風機室、４……吹出側パネル、７……羽根車、
９……オリフィス、9a……吸込側先端部。FIG. 1 is a front view of an outdoor unit of a separate type air conditioner equipped with an axial blower according to an embodiment of the present invention, FIG. 2 is a central sectional view of FIG. 1, and FIG. 3 is c of FIG. -C sectional view,
4 is a sectional view taken along line d-d of FIG. 1, FIG. 5 is a front view of an outdoor unit of a separate type air conditioner equipped with a conventional axial blower, and FIG. 6 is a central sectional view of FIG. FIG. 7 is a of FIG.
-A sectional view and FIG. 8 are sectional views taken along the line bb of FIG. 2 ... Blower room, 4 ... Blow-off side panel, 7 ... Impeller,
9 ... Orifice, 9a ... Suction side tip.
Claims (1)
吹出側パネルの略中央部に設けた羽根車と、前記羽根車
の周囲に設けたオリフィスとで構成し、前記オリフィス
の吸込側先端部の曲げの曲率半径を、前記略正方形の吹
出側パネルの各辺の中央部で最小とし、対角線部を最大
とした軸流送風機。1. A blower chamber, an impeller provided at a substantially central portion of a substantially square blow-out side panel in the blower chamber, and an orifice provided around the impeller, and a suction side tip of the orifice. An axial blower in which the radius of curvature of the bent portion is minimized at the center of each side of the substantially square blow-out side panel and the diagonal portion is maximized.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2026536A JPH07117077B2 (en) | 1990-02-06 | 1990-02-06 | Axial blower |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2026536A JPH07117077B2 (en) | 1990-02-06 | 1990-02-06 | Axial blower |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH03233198A JPH03233198A (en) | 1991-10-17 |
| JPH07117077B2 true JPH07117077B2 (en) | 1995-12-18 |
Family
ID=12196215
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP2026536A Expired - Fee Related JPH07117077B2 (en) | 1990-02-06 | 1990-02-06 | Axial blower |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH07117077B2 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US9513021B2 (en) | 2008-11-04 | 2016-12-06 | Mitsubishi Electric Corporation | Blower and heat pump apparatus using the same |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH01134135A (en) * | 1987-11-18 | 1989-05-26 | Matsushita Electric Ind Co Ltd | Blower in separate type air conditioner |
-
1990
- 1990-02-06 JP JP2026536A patent/JPH07117077B2/en not_active Expired - Fee Related
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US9513021B2 (en) | 2008-11-04 | 2016-12-06 | Mitsubishi Electric Corporation | Blower and heat pump apparatus using the same |
Also Published As
| Publication number | Publication date |
|---|---|
| JPH03233198A (en) | 1991-10-17 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| LAPS | Cancellation because of no payment of annual fees |