JPH11337126A - Outdoor machine for air conditioner - Google Patents

Outdoor machine for air conditioner

Info

Publication number
JPH11337126A
JPH11337126A JP14900198A JP14900198A JPH11337126A JP H11337126 A JPH11337126 A JP H11337126A JP 14900198 A JP14900198 A JP 14900198A JP 14900198 A JP14900198 A JP 14900198A JP H11337126 A JPH11337126 A JP H11337126A
Authority
JP
Japan
Prior art keywords
wall
impeller
blow
blower
airflow
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
Application number
JP14900198A
Other languages
Japanese (ja)
Inventor
Takumi Kida
琢己 木田
Souzo Suzuki
創三 鈴木
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Panasonic Holdings Corp
Original Assignee
Matsushita Refrigeration Co
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Matsushita Refrigeration Co filed Critical Matsushita Refrigeration Co
Priority to JP14900198A priority Critical patent/JPH11337126A/en
Publication of JPH11337126A publication Critical patent/JPH11337126A/en
Pending legal-status Critical Current

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  • Other Air-Conditioning Systems (AREA)

Abstract

PROBLEM TO BE SOLVED: To restrain both of increases of the turbulent flow noise of a fan and hydraulic noise generated from a fan guard by restraining the turbulence as well as the speed increase of discharging air flow by the outer periphery of impellers. SOLUTION: In the parts wherein distances between an impeller 6a and the side wall 11 of a fan room are small, the axial components of outer peripheral air flow of vanes 6b are strong and the outer peripheral air flows flow near the wall surfaces of orifices whereby the increase of flow speed is restrained by the outer periphery of the discharging sides of the vanes 6b, the disturbance of discharging air flow is reduced and the inflow of reverse flow inbetween the vanes is restrained by first and second arced walls 14, 15 thereby reducing disturbance due to mixing of the reverse flow into the discharging air flow. In this case, the bias flow of the discharging air flow is restrained and the increase of flow speed is prevented by substantially bell- mouth type air outlet parts 16 at the parts whereat a distance between the side wall 12 of the fan room is big while the speed of the discharging air flow, in which the disturbance is generated upon mixing of the reverse flow into the high-speed discharging air flow, is reduced whereby the disturbance due to the discharging air flow and the reverse flow will not be generated in the whole periphery of the fan 6 but will be generated locally.

Description

【発明の詳細な説明】DETAILED DESCRIPTION OF THE INVENTION

【０００１】[0001]

【発明の属する技術分野】本発明は、家庭用から業務用
まで幅広い分野で使用されているセパレート型などの空
気調和機の室外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 outdoor unit such as a separate type air conditioner used in a wide range of fields from home use to business use.

【０００２】[0002]

【従来の技術】近年、セパレート型など空気調和機の室
外機は、機器の設置条件の多様化に伴い、より小型化，
低騒音化が望まれる傾向にある。2. Description of the Related Art In recent years, outdoor units such as separate type air conditioners have been reduced in size due to diversification of equipment installation conditions.
There is a tendency to reduce noise.

【０００３】従来の空気調和機の室外機は、特開平９−
２６４３００号公報に示されているものが知られてい
る。A conventional outdoor unit of an air conditioner is disclosed in
The one disclosed in H.264300 is known.

【０００４】以下、図面を参照しながら、上述した従来
の空気調和機の室外機について説明する。Hereinafter, an outdoor unit of the above-described conventional air conditioner will be described with reference to the drawings.

【０００５】図１０〜図１５は従来の空気調和機の室外
機の構造を示すものである。図において、１は空気調和
機の室外機の本体であり、２は箱体であり、３は箱体２
内に設けられた熱交換器であり、４は箱体２内外を仕切
る略長方形の吹出側パネル５を設けた送風機室であり、
６は吹出側パネル５の略中央部に配設した軸流式の送風
機であり、羽根車６ａの後縁部の外周を囲み吹出側先端
部を開放端とした略円筒形の第１のオリフィスリング７
と、第１のオリフィスリング７の外側に設けた略同心円
状でかつ第１のオリフィスリング７より吹出側先端の開
放端を吹出側に設けた第２のオリフィスリング８を設
け、第１のオリフィスリング７と第２のオリフィスリン
グ８の吸込側を吹出側パネル５に固定している。また、
９は、吹出側パネル５の吹出後方に設けたファンガード
である。FIGS. 10 to 15 show the structure of an outdoor unit of a conventional air conditioner. In the figure, 1 is a main body of an outdoor unit of an air conditioner, 2 is a box, and 3 is a box 2
4 is a blower room provided with a substantially rectangular blow-out side panel 5 that partitions the inside and outside of the box body 2;
Reference numeral 6 denotes an axial-flow type blower disposed substantially at the center of the blow-out side panel 5, and has a substantially cylindrical first orifice surrounding the outer periphery of the trailing edge of the impeller 6a and having an open end at the blow-out end. Ring 7
And a second orifice ring 8 provided substantially concentrically on the outside of the first orifice ring 7 and provided with an open end at a blow-side end of the first orifice ring 7 on the blow-out side. The suction side of the ring 7 and the second orifice ring 8 is fixed to the outlet side panel 5. Also,
Reference numeral 9 denotes a fan guard provided behind the outlet of the outlet side panel 5.

【０００６】以上のように構成された空気調和機の室外
機について以下その動作を説明する。The operation of the outdoor unit of the air conditioner configured as described above will be described below.

【０００７】まず、熱交換器３側から吸い込まれた空気
は、熱交換器３を通過する際に熱交換器３内を通過する
冷媒と熱交換し、温度変化する。温度変化した空気は羽
根車６ａが所定の回転方向に回転することによって、羽
根車６ａ内に吸い込まれ、オリフィスリング７，８を介
して、ファンガード９を通過して箱体２外に吹き出され
る。First, the air sucked in from the heat exchanger 3 exchanges heat with the refrigerant passing through the heat exchanger 3 when passing through the heat exchanger 3 and changes in temperature. The air whose temperature has changed is sucked into the impeller 6a by the rotation of the impeller 6a in a predetermined rotation direction, passes through the fan guard 9 via the orifice rings 7, 8, and is blown out of the box body 2. You.

【０００８】ここで、図１２で示すように、羽根車６ａ
の翼間において回転による遠心力により、翼間の気流は
羽根６ｂの外周に片寄り、羽根６ｂの後縁部外周を囲む
オリフィス７の壁面近傍では高速で乱れも大きな気流Ａ
となり斜め方向に吹き出し、さらに、羽根６ａの外周端
に発生する翼端渦Ｂを含んでいる。[0008] Here, as shown in FIG.
Due to the centrifugal force caused by the rotation between the blades, the airflow between the blades is deviated to the outer periphery of the blade 6b, and the airflow A with high speed and large turbulence near the wall of the orifice 7 surrounding the outer periphery of the trailing edge of the blade 6b
And further includes a tip vortex B generated at the outer peripheral end of the blade 6a.

【０００９】この気流Ａは羽根６ｂの外周後縁部から流
出した後、第１のオリフィスリング７の内壁に一旦短く
接触した後、第１のオリフィスリング７の先端から流出
するときに一旦剥離するが、第１のオリフィスリング７
と第２のオリフィスリング８との間の壁面のない空間１
０を流動した後、第２のオリフィスリング８に再付着
し、さらに箱体２外に吐出される。After the airflow A flows out of the outer peripheral trailing edge of the blade 6b, the airflow A once makes short contact with the inner wall of the first orifice ring 7, and then temporarily separates when flowing out of the tip of the first orifice ring 7. Is the first orifice ring 7
Space 1 without wall between the and the second orifice ring 8
After flowing through the second orifice ring 8, it is re-attached to the second orifice ring 8 and further discharged out of the box 2.

【００１０】このとき、第２のオリフィスリング８の内
径は第１のオリフィスリング７の内径より大きいため、
第２のオリフィスリング８の壁面での気流の偏流を抑
え、壁面近傍の流速の増大を防止すると共に、壁面のな
い空間１０を流動するので空間１０内で乱れが緩和さ
れ、第２のオリフィスリング８に再付着することで気流
の乱れはいっそう低減され、乱流騒音が大きく発生を抑
制する。At this time, since the inner diameter of the second orifice ring 8 is larger than the inner diameter of the first orifice ring 7,
The drift of the air flow on the wall surface of the second orifice ring 8 is suppressed, the flow velocity near the wall surface is prevented from increasing, and the turbulence in the space 10 is reduced because the air flows in the space 10 without the wall surface. 8, the turbulence of the airflow is further reduced, and the turbulence noise is largely suppressed.

【００１１】さらに、第１のオリフィスリング７と第２
のオリフィスリング８と吹出側パネル５とで囲まれた空
間は空気層として作用し、乱れた気流Ａが持つ圧力脈動
を緩衝し、乱流騒音を減衰させる効果がある。Further, the first orifice ring 7 and the second orifice ring 7
The space surrounded by the orifice ring 8 and the blow-out side panel 5 acts as an air layer, has the effect of buffering the pressure pulsation of the turbulent air flow A and attenuating the turbulent noise.

【００１２】また、気流Ａに含まれる翼端渦Ｂの作用に
より、翼間の一部分で吐出側より羽根６ｂの外周端と第
１のオリフィスリング７の隙間部から羽根車６ａ内への
逆流Ｃを、第１のオリフィスリング７と第２のオリフィ
スリング８との間の壁面のない空間１０内に誘導し、第
１にオリフィスリング７から、第２のオリフィスリング
８へ向かう高速の気流に伴流させることで再度吐出さ
せ、羽根６ｂの外周側での翼間における逆流と高速な吐
出流の混濁による乱れを低減し、乱流騒音の増加を抑え
ると共に、逆流が羽根内に流入することによる空力性能
の劣化を抑える。Also, due to the action of the blade tip vortex B included in the airflow A, a backflow C from a gap between the outer peripheral end of the blade 6b and the first orifice ring 7 into the impeller 6a from the discharge side at a part between the blades. Into the space 10 without walls between the first orifice ring 7 and the second orifice ring 8, and with the high-speed airflow from the first orifice ring 7 to the second orifice ring 8. The turbulence due to the backflow between the blades on the outer peripheral side of the blade 6b and the turbidity of the high-speed discharge flow is reduced, the increase in turbulent noise is suppressed, and the backflow flows into the blade. Reduce aerodynamic performance degradation.

【００１３】[0013]

【発明が解決しようとする課題】しかし、上記のような
構成では、羽根６ｂの外周端の翼端渦Ｂの作用により、
翼間の一部分で発生する吐出側より羽根６ｂの外周端と
第１のオリフィスリング７の隙間部から羽根車６内への
逆流Ｃを抑制することで、羽根６ｂの吐出側外周には、
流れがより集中しやすくなる。However, in the above configuration, the action of the tip vortex B on the outer peripheral end of the blade 6b causes
By suppressing the backflow C from the gap between the outer peripheral end of the blade 6b and the first orifice ring 7 into the impeller 6 from the discharge side generated at a part between the blades, the outer periphery of the discharge side of the blade 6b is
The flow becomes easier to concentrate.

【００１４】特に、図１３，１５で示すように、略長方
形の吹出側パネル５を有する送風機室４で羽根車６ａと
送風機室４の側壁４ａの距離が大きい部分では、羽根車
６ａの吸込側の外周から羽根６ｂの翼間に吸い込まれる
気流Ｄは求心的成分が強く、第１のオリフィスリング７
の吸込側の壁面に沿わず、羽根６ｂの内周側まで流入し
たあと、気流に働く遠心力により外周側に片寄る。In particular, as shown in FIGS. 13 and 15, in the blower room 4 having the substantially rectangular blow-out side panel 5, in the portion where the distance between the impeller 6a and the side wall 4a of the blower room 4 is large, the suction side of the impeller 6a is used. The airflow D sucked between the blades of the blade 6b from the outer periphery of the first orifice ring 7 has a strong centripetal component.
After flowing along the inner peripheral side of the blade 6b without following the wall surface on the suction side of the above, it is deviated to the outer peripheral side due to centrifugal force acting on the airflow.

【００１５】そのため、第１のオリフィスリング７の吸
込側へ、羽根６ｂの作用により動圧が付加され増速した
羽根６ｂの負圧面側を流れる気流Ｅがより片寄ってくる
ため、羽根６ｂの吐出側の外周では、羽根車６ａ内に逆
流する流れを抑制することで、吐出気流を妨げるものが
無くなりさらに増速させ、非常に高速な吐出気流とな
り、送風機６より吹き出し、ファンガード９の線材９ａ
に衝突し、線材の９ａの後方に大きな気流乱れを発生さ
せ、大きな流体騒音を生じる。Therefore, the airflow E flowing on the suction side of the blade 6b, to which the dynamic pressure has been increased by the action of the blade 6b, is further deviated toward the suction side of the first orifice ring 7, so that the discharge of the blade 6b is performed. In the outer periphery on the side, by suppressing the flow flowing backward into the impeller 6a, there is no obstacle to the discharge air flow, and the speed is further increased, resulting in a very high-speed discharge air flow, which is blown out from the blower 6 and the wire 9a of the fan guard 9
And a large air turbulence is generated behind the wire 9a to generate a large fluid noise.

【００１６】よって、送風機６で発生する乱流騒音を低
減しても、ファンガード９で発生する流体騒音を大幅に
増加させ、室外機１の送風騒音は逆に増加する。Therefore, even if the turbulent noise generated by the blower 6 is reduced, the fluid noise generated by the fan guard 9 is greatly increased, and the blow noise of the outdoor unit 1 is increased on the contrary.

【００１７】従って、羽根６ｂの外周での吐出気流の乱
れを抑え送風機６の乱流騒音の増加を抑えると共に、フ
ァンガード９から発生する流体騒音の増加も抑えること
が要求される。Accordingly, it is required that the turbulence of the discharge airflow on the outer periphery of the blade 6b be suppressed to suppress the increase of the turbulent noise of the blower 6 and the increase of the fluid noise generated from the fan guard 9.

【００１８】本発明は、空気調和機の室外機において、
羽根の外周での吐出気流の乱れを抑えると共に、吐出気
流の増速を抑え、送風機の乱流騒音の増加とファンガー
ドから発生する流体騒音の増加の両方を抑えることを目
的とする。The present invention relates to an outdoor unit of an air conditioner,
It is an object of the present invention to suppress the turbulence of the discharge airflow on the outer periphery of the blade, suppress the increase in the discharge airflow, and suppress both the increase in the turbulent noise of the blower and the increase in the fluid noise generated from the fan guard.

【００１９】[0019]

【課題を解決するための手段】この課題を解決するため
に、本発明は、略長方形の吹出側パネルを設けた送風機
室と、前記吹出側パネルの略中央部に配設した羽根車
と、前記羽根車の後縁部外周を囲み前記吹出側パネルに
吸込側を固定したオリフィスと、前記吹出側パネルの吹
出後方に設けたファンガードで構成し、前記オリフィス
の吹出部が、前記略長方形の吹出側パネルを設けた前記
送風機室内の側壁と前記羽根車の距離が小さい側では、
吹出側先端を開放端とした第１の円弧壁と、前記第１の
円弧壁の外側に設けた略同心円状でかつ第１の円弧壁よ
り吹出側先端の開放端を吹出側に設けた第２の円弧壁で
構成され、前記略長方形の吹出側パネルを設けた前記箱
体内の側壁と前記羽根車の距離が大きい側では、吹出側
に向かうほど次第に拡がる内壁面を有することにより、
略長方形の吹出側パネルを有する送風機室で羽根車と送
風機室の側壁の距離が小さい部分では、この羽根の外周
から吐出する気流は、第１の円弧壁の内壁に一旦短く付
着し、その間の壁面のない空間を流動した後、第２の円
弧壁に再付着することで、気流の偏流を抑え、壁面近傍
の流速の増大を防止すると共に、壁面のない空間で乱れ
が緩和され、第２の円弧壁に再付着することで気流の乱
れはいっそう低減され、乱流騒音の発生を大きく抑制す
る。In order to solve this problem, the present invention provides a blower room provided with a substantially rectangular blow-out side panel, and an impeller arranged substantially at the center of the blow-out side panel. An orifice surrounding the outer periphery of the trailing edge of the impeller and having a suction side fixed to the outlet side panel, and a fan guard provided behind the outlet side of the outlet side panel, wherein the outlet of the orifice is substantially rectangular On the side where the distance between the side wall and the impeller in the blower room provided with the blow-out side panel is small,
A first arc-shaped wall having an open end at the outlet side, and a substantially concentric circular outer wall provided outside the first arc-shaped wall and having an open end at the outlet end on the outlet side of the first arc-shaped wall. 2, the side wall in the box body provided with the substantially rectangular outlet-side panel and the side where the distance between the impeller is larger has an inner wall surface that gradually expands toward the outlet side.
In a blower room having a substantially rectangular blow-out side panel, in a portion where the distance between the impeller and the side wall of the blower room is small, the airflow discharged from the outer periphery of the blade temporarily adheres to the inner wall of the first arc wall for a short time. After flowing in the space without the wall surface, it re-adheres to the second arc wall, thereby suppressing the drift of the airflow, preventing an increase in the flow velocity near the wall surface, and reducing the turbulence in the space without the wall surface. The turbulence of the airflow is further reduced by re-adhering to the circular arc wall of, and the generation of turbulent noise is largely suppressed.

【００２０】さらに、第１の円弧壁と第２の円弧壁と吹
出側パネルとで囲まれた空間は空気層として作用し、乱
れた気流が持つ圧力脈動を緩衝し、乱流騒音を減衰させ
る効果がある。Further, a space surrounded by the first arc wall, the second arc wall, and the blow-out side panel acts as an air layer, buffers the pressure pulsation of the turbulent air flow, and attenuates turbulent noise. effective.

【００２１】また、外周側の吐出気流に含まれる翼端渦
の作用により、翼間の一部分で吐出側羽根車への逆流
を、第１の円弧壁と第２の円弧壁との間の壁面のない空
間内に誘導し、第１に円弧壁から第２の円弧壁へ向かう
高速の気流に伴流させることで再度吐出させ、羽根外周
側の翼間における逆流と高速な吐出流の混濁による乱れ
を低減し、乱流騒音の増加を抑えると共に、逆流が羽根
内に流入することによる空力性能の劣化を抑える。Also, by the action of the tip vortex contained in the discharge airflow on the outer peripheral side, the backflow to the discharge side impeller at a part between the blades is reduced by the wall surface between the first arc wall and the second arc wall. In the air-free space, and firstly, the jet is discharged again by causing it to flow along the high-speed airflow from the arc-shaped wall toward the second arc-shaped wall. It reduces turbulence, suppresses an increase in turbulent noise, and suppresses aerodynamic performance degradation due to backflow flowing into the blade.

【００２２】ここで、羽根車の吸込側の外周から翼間に
吸い込まれる気流は、軸方向成分が強く、オリフィスの
壁面近傍を流れ、この際、翼間を流れる距離が短くなる
ため、羽根の作用による増速も小さく抑えられる。Here, the airflow sucked between the blades from the outer periphery on the suction side of the impeller has a strong axial component and flows near the wall surface of the orifice. At this time, the distance flowing between the blades becomes shorter. The speed increase due to the action can also be kept small.

【００２３】そして、このため、オリフィスの吸込側
へ、羽根の作用により動圧が付加され増速した羽根負圧
面側を流れる気流の片寄りも抑えられるので、羽根外周
側の吐出部の外周で逆流の抑制によって吐出気流を妨げ
るものが無くなり流速が増加するが、増加量は少ない。As a result, the dynamic pressure is applied to the suction side of the orifice by the action of the blade, and the bias of the airflow flowing on the blade negative pressure surface side, which is increased in speed, is also suppressed. Although there is nothing obstructing the discharge airflow by suppressing the backflow, the flow velocity increases, but the increase amount is small.

【００２４】よって、非常に高速な吐出気流が送風機よ
り吹き出さず、ファンガードの線材の後方での大きな気
流乱れを抑制し、大きな流体騒音の発生を抑制する。Therefore, a very high-speed discharge airflow is not blown out from the blower, and a large turbulence behind the wire rod of the fan guard is suppressed, and generation of a large fluid noise is suppressed.

【００２５】また、羽根車と送風機室の側壁の距離が大
きい部分では、吹出側に向かうほど次第に拡がる内壁面
とすることで、気流の偏流を抑え壁面近傍の流速の増大
を防止するので、送風機の乱流騒音の大幅な増加は抑え
られる。Further, in a portion where the distance between the impeller and the side wall of the blower chamber is large, the inner wall surface gradually expands toward the blow-out side to suppress the drift of the air flow and prevent the flow velocity near the wall surface from increasing. A large increase in turbulent noise of the vehicle can be suppressed.

【００２６】そして、羽根車の吸込側の外周から翼間に
吸い込まれる気流の求心的成分が強く、オリフィスの吸
込側の壁面に沿わずに羽根の内周側まで流入したあと、
気流に働く遠心力により外周側に片寄るため、オリフィ
スの吸込側へ羽根の作用により動圧が付加され増速した
羽根負圧面側を流れる気流がより外周側に片寄って流れ
ることで吐出気流は増速が、吐出気流に含まれる翼端渦
の作用による翼間の一部分で発生する逆流と混濁する
際、乱れが発生するが吐出気流は減速させる。Then, the centripetal component of the airflow sucked between the blades from the outer periphery on the suction side of the impeller is strong, and after flowing into the inner peripheral side of the blade without following the suction-side wall surface of the orifice,
Since the centrifugal force acting on the airflow causes the airflow to be deviated to the outer peripheral side, the dynamic pressure is added by the action of the blade to the suction side of the orifice, and the increased airflow flowing on the blade negative pressure side flows more deviated to the outer peripheral side to increase the discharge airflow. When the speed becomes turbid with the backflow generated in a part between the blades due to the action of the tip vortex contained in the discharge airflow, turbulence occurs but the discharge airflow is decelerated.

【００２７】ここで、吐出気流と逆流による乱れの発生
は、送風機全周では無く部分的となるため、送風機の乱
流騒音の増加は小さくなる。Here, since the turbulence due to the discharge airflow and the backflow is generated not in the entire circumference of the blower but in a part thereof, an increase in the turbulence noise of the blower is reduced.

【００２８】従って、羽根の外周での吐出気流の乱れを
抑えると共に、吐出気流の増速を抑え、送風機の乱流騒
音の増加とファンガードから発生する流体騒音の増加の
両方を抑える。Therefore, the turbulence of the discharge airflow on the outer periphery of the blade is suppressed, and the speed of the discharge airflow is suppressed, so that both the turbulent noise of the blower and the fluid noise generated from the fan guard are suppressed.

【００２９】[0029]

【発明の実施の形態】本発明の請求項１記載の発明は、
本体と、前記箱体内に設けた熱交換器と、略長方形の吹
出側パネルを設けた送風機室と、前記吹出側パネルの略
中央部に配設した羽根車と、前記羽根車の後縁部外周を
囲み前記吹出側パネルに吸込側を固定したオリフィス
と、前記吹出側パネルの吹出後方に設けたファンガード
で構成し、前記オリフィスの吹出側が、前記略長方形の
吹出側パネルを設けた前記送風機室内の側壁と前記羽根
車の距離が小さい側では、吹出側先端を開放端とした第
１の円弧壁と、前記第１の円弧壁の外側に設けた略同心
円状でかつ第１の円弧壁より吹出側先端の開放端を吐出
側に設けた第２の円弧壁で構成され、前記略長方形の吹
出側パネルを設けた前記箱体内の側壁と前記羽根車の距
離が大きい側では、吹出側に向かうほど次第に拡がる内
壁面を有する吹出部である空気調和機の室外機であり、
略長方形の吹出側パネルを有する送風機室で羽根車と送
風機室の側壁の距離が小さい部分では、この羽根の外周
から吐出する気流は、第１の円弧壁の内壁に一旦短く付
着し、その間の壁面のない空間を流動した後、第２の円
弧壁に再付着することで、気流の偏流を抑え、壁面近傍
の流速の増大を防止すると共に、壁面のない空間で乱れ
が緩和され、第２の円弧壁に再付着することで気流の乱
れはいっそう低減され、乱流騒音の発生を大きく抑制す
る。さらに、第１の円弧壁と第２の円弧壁と吹出側パネ
ルとで囲まれた空間は空気層として作用し、乱れた気流
が持つ圧力脈動を緩衝し、乱流騒音を減衰させる効果が
ある。BEST MODE FOR CARRYING OUT THE INVENTION
A main body, a heat exchanger provided in the box body, a blower room provided with a substantially rectangular blow-out panel, an impeller provided substantially in the center of the blow-side panel, and a rear edge of the impeller. The blower comprising an orifice surrounding the outer periphery and having a suction side fixed to the blow-out side panel, and a fan guard provided behind the blow-out side panel at the blow-out side, wherein the blow-out side of the orifice is provided with the substantially rectangular blow-out side panel. On the side where the distance between the side wall in the room and the impeller is small, a first arc wall having a blowing-side tip as an open end, and a substantially concentric first arc wall provided outside the first arc wall. A second arc wall provided with an open end at a discharge side tip on the discharge side, and a side on which the distance between the side wall in the box provided with the substantially rectangular blow-out side panel and the impeller is large is a blow side. Outlet with an inner wall surface that gradually widens toward A outdoor unit of a certain air conditioner,
In a blower room having a substantially rectangular blow-out side panel, in a portion where the distance between the impeller and the side wall of the blower room is small, the airflow discharged from the outer periphery of the blade temporarily adheres to the inner wall of the first arc wall for a short time. After flowing in the space without the wall surface, it re-adheres to the second arc wall, thereby suppressing the drift of the airflow, preventing an increase in the flow velocity near the wall surface, and reducing the turbulence in the space without the wall surface. The turbulence of the airflow is further reduced by re-adhering to the circular arc wall of, and the generation of turbulent noise is largely suppressed. Further, a space surrounded by the first arc wall, the second arc wall, and the blow-out side panel acts as an air layer, has an effect of buffering pressure pulsation of the turbulent air flow, and attenuating turbulent noise. .

【００３０】また、外周側の吐出気流に含まれる翼端渦
の作用により、翼間の一部分で吐出側羽根車への逆流
を、第１の円弧壁と第２の円弧壁との間の壁面のない空
間内に誘導し、第１に円弧壁から第２の円弧壁へ向かう
高速の気流に伴流させることで再度吐出させ、羽根外周
側の翼間における逆流と高速な吐出流の混濁による乱れ
を低減し、乱流騒音の増加を抑えると共に、逆流が羽根
内に流入することによる空力性能の劣化を抑える。Further, by the action of the tip vortex contained in the discharge airflow on the outer peripheral side, the backflow to the discharge side impeller at a part between the blades is reduced by the wall surface between the first arc wall and the second arc wall. In the air-free space, and firstly, the jet is discharged again by causing it to flow along the high-speed airflow from the arc-shaped wall toward the second arc-shaped wall. It reduces turbulence, suppresses an increase in turbulent noise, and suppresses aerodynamic performance degradation due to backflow flowing into the blade.

【００３１】ここで、羽根車の吸込側の外周から翼間に
吸い込まれる気流は、軸方向成分が強く、オリフィスの
壁面近傍を流れ、この際、翼間を流れる距離が短くなる
ため、羽根の作用による増速も小さく抑えられる。Here, the airflow sucked between the blades from the outer periphery on the suction side of the impeller has a strong axial component and flows near the wall surface of the orifice. The speed increase due to the action can also be kept small.

【００３２】そして、このため、オリフィスの吸込側
へ、羽根の作用により動圧が付加され増速した羽根負圧
面側を流れる気流の片寄りも抑えられるので、羽根外周
側の吐出部の外周で逆流の抑制によって吐出気流を妨げ
るものが無くなり流速が増加するが、増加量は少ない。[0032] For this reason, the bias of the airflow flowing on the blade negative pressure surface side where the dynamic pressure is added by the action of the blade to the suction side of the orifice and the speed is increased is also suppressed. Although there is nothing obstructing the discharge airflow by suppressing the backflow, the flow velocity increases, but the increase amount is small.

【００３３】よって、非常に高速な吐出気流が送風機よ
り吹き出さず、ファンガードの線材の後方での大きな気
流乱れを抑制し、大きな流体騒音の発生を抑制する。Therefore, a very high-speed discharge airflow is not blown out from the blower, so that a large turbulence behind the fan guard wire is suppressed, and the generation of a large fluid noise is suppressed.

【００３４】また、羽根車と送風機室の側壁の距離が大
きい部分では、吹出側に向かうほど次第に拡がる内壁面
とすることで、気流の偏流を抑え壁面近傍の流速の増大
を防止するので、送風機の乱流騒音の大幅な増加は抑え
られる。Further, in a portion where the distance between the impeller and the side wall of the blower chamber is large, the inner wall surface gradually expands toward the blow-out side to suppress the drift of the air flow and prevent an increase in the flow velocity near the wall surface. A large increase in turbulent noise of the vehicle can be suppressed.

【００３５】そして、羽根車の吸込側の外周から翼間に
吸い込まれる気流の求心的成分が強く、オリフィスの吸
込側の壁面に沿わずに羽根の内周側まで流入したあと、
気流に働く遠心力により外周側に片寄るため、オリフィ
スの吸込側へ羽根の作用により動圧が付加され増速した
羽根負圧面側を流れる気流がより外周側に片寄って流れ
ることで吐出気流は増速するが、吐出気流に含まれる翼
端渦の作用により翼間の一部分で発生する逆流と混濁す
る際、乱れが発生するが吐出気流は減速させる。The centripetal component of the airflow sucked between the blades from the outer periphery on the suction side of the impeller is strong, and after flowing into the inner peripheral side of the blade without following the wall surface on the suction side of the orifice,
Since the centrifugal force acting on the airflow causes the airflow to be deviated to the outer peripheral side, the dynamic pressure is added by the action of the blade to the suction side of the orifice, and the increased airflow flowing on the blade negative pressure side flows more deviated to the outer peripheral side to increase the discharge airflow. However, when turbidity occurs with the backflow generated in a part between the blades due to the action of the tip vortex contained in the discharge airflow, turbulence occurs but the discharge airflow is decelerated.

【００３６】ここで、吐出気流と逆流による乱れの発生
は、送風機全周では無く部分的となるため、送風機の乱
流騒音の増加は小さくなる。Here, since the turbulence due to the discharge airflow and the backflow is generated not in the entire circumference of the blower but in a part thereof, an increase in turbulence noise of the blower is reduced.

【００３７】従って、羽根の外周での吐出気流の乱れを
抑えると共に、吐出気流の増速を抑え、送風機の乱流騒
音の増加とファンガードから発生する流体騒音の増加の
両方を抑えるという作用を有する。Accordingly, the effect of suppressing the turbulence of the discharge airflow on the outer periphery of the blade, suppressing the increase of the discharge airflow, and suppressing both the increase of the turbulent noise of the blower and the increase of the fluid noise generated from the fan guard. Have.

【００３８】請求項２記載の発明は、略長方形の吹出側
パネルを設けた送風機室内の側壁と前記羽根車の距離が
小さい側の第１，第２の円弧壁と、送風機室内の側壁と
前記羽根車の距離が大きい側の吹出側に向かうほど次第
に拡がる内壁面を有する吹出部の連結部が、略長方形の
吹出側パネルの対角線上近辺に配設された請求項１記載
の空気調和機の室外機であり、略長方形の吹出側パネル
を有する送風機室の、羽根車と送風機室の側壁の小さい
側の距離が非常に小さく、略長方形の短辺と長辺の差が
大きい場合、略長方形の吹出側パネルの対角線付近で、
送風機室の羽根車と側壁の距離が急激に大きくなるの
で、羽根車と送風機室の側壁の距離が非常に小さい部分
では、羽根車の吸込側の外周から翼間に吸い込まれる気
流は、軸方向成分が強く、側壁からオリフィスの壁面近
傍を流れ、この際、翼間を流れる距離が短くなるため、
羽根の作用による増速も小さく抑えられる。According to a second aspect of the present invention, the first and second arc walls on the side where the distance between the impeller and the side wall in the blower room provided with the substantially rectangular blow-out side panel is small, the side wall in the blower room and 2. The air conditioner according to claim 1, wherein a connecting portion of the blowout portion having an inner wall surface that gradually widens as the distance of the impeller increases toward the blowout side is arranged near a diagonal line of the substantially rectangular blowout side panel. When the distance between the impeller and the small side of the side wall of the blower room is very small, and the difference between the short side and the long side of the substantially rectangular shape is substantially rectangular, Near the diagonal of the outlet side panel of
Since the distance between the impeller and the side wall of the blower room is rapidly increased, in a portion where the distance between the impeller and the side wall of the blower room is extremely small, the airflow sucked between the blades from the outer periphery on the suction side of the impeller is in the axial direction. Since the component is strong, it flows from the side wall near the wall of the orifice, and at this time, the distance flowing between the wings becomes shorter,
The speed increase due to the action of the blade can be suppressed to a small value.

【００３９】さらに、羽根外周側への羽根の作用により
動圧が付加され増速した羽根負圧面側を流れる気流の片
寄りも抑えられるので、羽根の吐出側の外周で流速の増
加を抑え、羽根の外周から吐出する気流が、第１の円弧
壁の内壁に一旦短く付着しその間の壁面のない空間を流
動した後、第２の円弧壁に再付着することで、気流の偏
流を抑え、外周からの吐出気流の乱れとそれに伴う乱流
騒音の発生を大きく低減すると共に、外周側の吐出気流
に含まれる翼端渦の作用による逆流の翼間への流入を抑
制し、羽根外周側の翼間における逆流と高速な吐出流の
混濁による乱れを低減し、乱流騒音の増加と空力性能の
劣化を抑える。Further, the bias of the airflow flowing on the blade negative pressure surface side where the dynamic pressure is added by the action of the blade on the blade outer peripheral side and the speed is increased can be suppressed, so that the increase in the flow velocity on the outer circumference on the discharge side of the blade is suppressed. The airflow discharged from the outer periphery of the blade once adheres briefly to the inner wall of the first arc wall and flows through the space without the wall therebetween, and then re-adheres to the second arc wall, thereby suppressing the drift of the airflow, In addition to greatly reducing the turbulence of the discharge airflow from the outer periphery and the generation of turbulent noise accompanying it, the flow of backflow due to the action of the wing tip vortex included in the discharge airflow on the outer peripheral side is suppressed between the blades, The turbulence caused by the turbidity of the backflow between the blades and the high-speed discharge flow is reduced, and increase in turbulent noise and deterioration of aerodynamic performance are suppressed.

【００４０】そして、略長方形の吹出側パネルの対角線
付近から吹出側パネルの長辺側にかけた羽根車と送風機
室の側壁の距離が大きい部分では、吹出側に向かうほど
次第に拡がる略ベルマウス状、あるいは略円錐状の内壁
面にて吐出気流の偏流を抑え壁面近傍の流速の増大を防
止するので、送風機の乱流騒音の大幅な増加は抑えられ
る。In the portion where the distance between the impeller and the side wall of the blower room extending from the vicinity of the diagonal line of the substantially rectangular outlet side panel to the long side of the outlet side panel is large, the bell mouth shape gradually expands toward the outlet side. Alternatively, since the uneven flow of the discharge airflow is suppressed by the substantially conical inner wall surface, and the flow velocity near the wall surface is prevented from increasing, the turbulent noise of the blower can be prevented from increasing significantly.

【００４１】また、羽根車の吸込側の外周から翼間に吸
い込まれる気流の求心的成分が強いので、オリフィスの
吸込側の壁面に沿わずに羽根の内周側まで流入したあ
と、気流に働く遠心力により外周側に片寄るため、羽根
の作用により動圧が付加され増速した羽根負圧面側を流
れる気流が羽根外周側により片寄って流れることで吐出
気流は増速するが、吐出気流に含まれる翼端渦の作用に
よる翼間の一部分で発生する逆流と混濁する際、乱れが
発生するが吐出気流は減速させる。Further, since the centripetal component of the airflow sucked between the blades from the outer periphery of the impeller on the suction side is strong, the airflow flows to the inner peripheral side of the blade without flowing along the suction-side wall surface of the orifice and acts on the airflow. Because the centrifugal force is offset toward the outer peripheral side, the airflow flowing on the blade negative pressure surface side where the dynamic pressure is added due to the action of the blade and increased in speed flows toward the outer peripheral side of the blade and the discharge airflow is accelerated, but is included in the discharge airflow. When turbidity occurs with the backflow generated in a part between the blades due to the action of the blade tip vortex, turbulence occurs, but the discharge airflow is decelerated.

【００４２】ここで、吐出気流と逆流による乱れの発生
は、送風機全周では無く部分的となるため、送風機の乱
流騒音の増加は小さくなる。Here, since the turbulence due to the discharge airflow and the backflow is generated not in the entire circumference of the blower but in a part thereof, an increase in turbulence noise of the blower is reduced.

【００４３】従って、略長方形の吹出側パネルを有する
送風機室の、羽根車と送風機室の側壁の小さい側の距離
が非常に小さく、略長方形の短辺と長辺の差が大きい場
合、羽根の外周での吐出気流の乱れを抑えると共に、吐
出気流の増速を抑え、送風機の乱流騒音の増加とファン
ガードから発生する流体騒音の増加の両方を抑える効果
が送風機全周で有効に働くという作用を有する。Therefore, when the distance between the impeller and the small side of the side wall of the blower chamber of the blower room having the substantially rectangular blow-out side panel is very small, and the difference between the short side and the long side of the substantially rectangular shape is large, The effect of suppressing the turbulence of the discharge airflow at the outer periphery, suppressing the increase in the discharge airflow, and suppressing both the increase in the turbulent noise of the blower and the increase in the fluid noise generated from the fan guard work effectively all around the blower. Has an action.

【００４４】請求項３記載の発明は、略長方形の吹出側
パネルを設けた送風機室内の側壁と前記羽根車の距離が
小さい側の第１，第２の円弧壁と、送風機室内の側壁と
前記羽根車の距離が大きい側の吹出側に向かうほど次第
に拡がる内壁面を有する吹出部の連結部が、前記略長方
形の吹出側パネルの対角線から送風機室内の側壁と前記
羽根車の距離が小さい側寄りに配設された請求項１記載
の空気調和機の室外機であり、略長方形の吹出側パネル
の短辺と長辺の差が非常に大きくない場合、略長方形の
吹出側パネルの対角線より短辺寄りで、送風機室の羽根
車と側壁の距離が急激に大きくなるので、羽根車と送風
機室の側壁の距離が小さい部分では、羽根車の吸込側の
外周から翼間に吸い込まれる気流は、軸方向成分が強
く、側壁からオリフィスの壁面近傍を流れ、この際、翼
間を流れる距離が短くなるため、羽根の作用による増速
も小さく抑えられる。According to a third aspect of the present invention, there is provided the blower chamber provided with a substantially rectangular blow-out side panel, the first and second arc walls on the side where the distance between the impeller and the impeller is shorter, the side wall in the blower chamber, The connecting portion of the outlet having an inner wall surface that gradually expands toward the outlet side on the side where the distance of the impeller is larger is closer to the side where the distance between the side wall in the blower chamber and the impeller is smaller than the diagonal line of the substantially rectangular outlet side panel. The outdoor unit of the air conditioner according to claim 1, wherein the difference between the short side and the long side of the substantially rectangular outlet side panel is not very large, and is shorter than the diagonal line of the substantially rectangular outlet side panel. Near the side, the distance between the impeller of the blower room and the side wall increases rapidly, so in the portion where the distance between the impeller and the side wall of the blower room is small, the airflow sucked between the blades from the outer periphery on the suction side of the impeller, Strong axial component, orifice from side wall Flows near the wall surface of the scan, this time, the distance flowing between blades is shortened, the speed increasing by the action of the blade can be suppressed small.

【００４５】さらに、羽根の作用により動圧が付加され
増速した羽根負圧面側を流れる気流の片寄りも抑えられ
るので、羽根の吐出側の外周で流速の増加を抑え、羽根
の外周から吐出する気流が、第１の円弧壁の内壁に一旦
短く付着しその間の壁面のない空間を流動した後、第２
の円弧壁に再付着することで、気流の偏流を抑えるの
で、外周からの吐出気流の乱れとそれに伴う乱流騒音の
発生を大きく低減すると共に、外周側の吐出気流に含ま
れる翼端渦の作用による逆流の翼間への流入を抑制し、
羽根外周側の翼間における逆流と高速な吐出流の混濁に
よる乱れを低減し、乱流騒音の増加と空力性能の劣化を
抑える。Furthermore, the bias of the airflow flowing on the blade negative pressure surface side, which has been increased by the action of the blade due to the action of the dynamic pressure, is also suppressed, so that the increase in the flow velocity is suppressed on the outer periphery on the discharge side of the blade, and the discharge from the outer periphery of the blade is suppressed. After a short period of time, the flowing air temporarily adheres to the inner wall of the first arc wall and flows through a space having no wall therebetween,
Re-adhering to the arc wall of the air flow suppresses the drift of the air flow, so that the turbulence of the discharge air flow from the outer circumference and the occurrence of turbulent noise accompanying it are greatly reduced, and the wing tip vortex included in the discharge air flow The backflow due to the action is suppressed between the blades,
Turbulence due to turbidity of backflow and high-speed discharge flow between the blades on the outer peripheral side of the blade is reduced, and increase in turbulent noise and deterioration of aerodynamic performance are suppressed.

【００４６】そして、略長方形の吹出側パネルの対角線
より短辺寄りから吹出側パネルの長辺側の羽根車と送風
機室の側壁の距離が大きい部分では、吹出側に向かうほ
ど次第に拡がる内壁面にて吐出気流の偏流を抑え壁面近
傍の流速の増大を防止するので、送風機の乱流騒音の大
幅な増加は抑えられる。In the portion where the distance between the impeller on the long side of the blow-out panel and the side wall of the blower chamber from the short side of the diagonal line of the substantially rectangular blow-out panel to the side wall of the blower chamber is large, the inner wall surface gradually widens toward the blow-out side. As a result, the drift of the discharge airflow is suppressed and the flow velocity near the wall surface is prevented from increasing, so that the turbulent noise of the blower can be prevented from increasing significantly.

【００４７】また、羽根車の吸込側の外周から翼間に吸
い込まれる気流の求心的成分が強いので、オリフィスの
吸込側の壁面に沿わずに羽根の内周側まで流入したあ
と、気流に働く遠心力により外周側に片寄るため、オリ
フィスの吸込側へ羽根の作用により動圧が付加され増速
した羽根負圧面側を流れる気流が羽根外周側により片寄
って流れることで吐出気流は増速するが、吐出気流に含
まれる翼端渦の作用による翼間の一部分で発生する逆流
と混濁する際、乱れが発生するが吐出気流は減速させ
る。Further, since the centripetal component of the airflow sucked between the blades from the outer periphery on the suction side of the impeller is strong, the airflow does not follow the suction-side wall surface of the orifice but flows into the inner peripheral side of the blade and acts on the airflow. Since the centrifugal force causes the airflow to flow to the suction side of the orifice due to the action of the blade due to the action of the blade, the airflow flowing on the blade negative pressure surface side, which has increased in speed, flows toward the blade outer circumference side and the discharge airflow increases. When turbidity occurs with the backflow generated in a part between the blades due to the action of the blade tip vortex contained in the discharge airflow, turbulence occurs but the discharge airflow is decelerated.

【００４８】ここで、吐出気流と逆流による乱れの発生
は、送風機全周では無く部分的となるため、送風機の乱
流騒音の増加は小さくなる。Here, since the turbulence due to the discharge airflow and the backflow is generated not in the entire circumference of the blower but in a part thereof, an increase in turbulence noise of the blower is reduced.

【００４９】従って、略長方形の吹出側パネルの短辺と
長辺の差が非常に大きくない場合、羽根の外周での吐出
気流の乱れを抑えると共に、吐出気流の増速を抑え、送
風機の乱流騒音の増加とファンガードから発生する流体
騒音の増加の両方を抑える効果が送風機全周で有効に働
くという作用を有する。Therefore, when the difference between the short side and the long side of the substantially rectangular blow-out side panel is not very large, the turbulence of the discharge airflow on the outer periphery of the blade is suppressed, the increase in the discharge airflow is suppressed, and the turbulence of the blower is suppressed. The effect of suppressing both the increase in the flow noise and the increase in the fluid noise generated from the fan guard has an effect that it works effectively all around the blower.

【００５０】請求項４記載の発明は、第１の円弧壁と、
吹出側に向かうほど次第に拡がる略ベルマウス状、ある
いは略円錐状の内壁面を有する吹出部の連結部が、第２
の円弧壁と、吹出側に向かうほど次第に拡がる内壁面を
有する吹出部の連結部より回転方向に前傾した請求項１
または２または３記載の空気調和機の室外機であり、羽
根車外周、あるいは吸込側から流入した気流は、羽根車
が回転することにより、吐出側では回転方向に進んだ状
態で吐出され、さらに羽根外周からの吐出気流の大半
が、遠心力による半径方向成分と共に羽根の作用による
回転方向への周方向成分を有するので、第１の円弧壁が
第２の円弧壁より回転方向に前傾して吹出側に向かうほ
ど次第に拡がる内壁面を有する吹き出し形状と連結する
ことで、羽根車と送風機室の側壁の距離が大きく変化す
る部分では、羽根外周からの吐出気流の上流側での吸込
状態の流れの連続的で緩やかな移行に伴う吐出気流の変
化に合わせたオリフィス吐出形状とすることができ、羽
根の外周での吐出気流の乱れを抑えると共に、吐出気流
の増速を抑え、送風機の乱流騒音の増加とファンガード
から発生する流体騒音の増加の両方を抑える効果が送風
機全周で有効に働くと共に、連結部の急激な吐出形状の
変化による吐出気流の乱れを防ぎ、連結部での乱れによ
る乱流騒音の増加を抑える。According to a fourth aspect of the present invention, the first circular arc wall comprises:
The connecting portion of the blowing portion having a substantially bell-mouth shape or a substantially conical inner wall surface that gradually expands toward the blowing side is a second portion.
And a connecting portion between the arc wall and the blowing portion having an inner wall surface gradually expanding toward the blowing side.
Or the outdoor unit of the air conditioner according to 2 or 3, wherein the airflow flowing from the outer periphery of the impeller or the suction side is discharged in a state where the impeller rotates in the rotation direction on the discharge side, and Most of the discharge airflow from the outer periphery of the blade has a radial component due to the centrifugal force and a circumferential component in the rotation direction due to the action of the blade, so that the first arc wall is inclined forward in the rotation direction from the second arc wall. In the part where the distance between the impeller and the side wall of the blower chamber changes greatly by connecting with the blowing shape having an inner wall surface that gradually widens toward the blowing side, the suction state on the upstream side of the discharge airflow from the blade outer periphery The orifice discharge shape can be changed according to the change of the discharge airflow due to the continuous and gentle transition of the flow, and the turbulence of the discharge airflow on the outer periphery of the blade is suppressed, and the increase of the discharge airflow is suppressed, The effect of suppressing both the increase in turbulent noise of the fan and the increase in fluid noise generated from the fan guard works effectively on the entire circumference of the blower, and also prevents the turbulence of the discharge air flow due to the sudden change in the discharge shape of the connection part, The increase in turbulent noise due to turbulence in the vehicle.

【００５１】[0051]

【実施例】以下、本発明の実施例について図１〜図１０
を用いて説明する。DESCRIPTION OF THE PREFERRED EMBODIMENTS Embodiments of the present invention will be described below with reference to FIGS.
This will be described with reference to FIG.

【００５２】尚、従来例と同一構成の部分については重
複をさけるため、同一符号を付けて説明を省略する。The same components as in the conventional example are denoted by the same reference numerals to avoid duplication, and description thereof is omitted.

【００５３】（実施例１）図１〜図５は本発明の実施例
１の空気調和機の室外機を示す。図において、１１は略
長方形の吹出側パネル５を設けた送風機室４の羽根車６
ａと距離が小さい側の側壁であり、１２は羽根車６ａと
距離が大きい側の側壁である。(Embodiment 1) FIGS. 1 to 5 show an outdoor unit of an air conditioner according to Embodiment 1 of the present invention. In the figure, reference numeral 11 denotes an impeller 6 of a blower room 4 provided with a substantially rectangular blow-out side panel 5.
a is a side wall on the side closer to the impeller 6a, and 12 is a side wall on the side closer to the impeller 6a.

【００５４】１３は、羽根車６ａの後縁部外周を囲み、
吸込側を吹出側パネル５に固定したオリフィスであり、
１４は側壁１１側のオリフィス１３の吐出側に設けた吹
出側先端１４ａを開放端とした第１の円弧壁であり、１
５は第１の円弧壁１４の外側に設けた略同心円状でかつ
第１の円弧壁１４より吹出側先端１５ａの開放端を吹出
側に設けた第２の円弧壁である。13 surrounds the outer periphery of the trailing edge of the impeller 6a,
An orifice whose suction side is fixed to the outlet side panel 5,
Reference numeral 14 denotes a first arc-shaped wall having an open end 14b on the discharge side of the orifice 13 on the side wall 11 side.
Reference numeral 5 denotes a second arc wall provided substantially outside of the first arc wall 14 and provided with an open end of the blow-side tip 15a on the blow side from the first arc wall 14.

【００５５】また、１６は側壁１２側のオリフィス１３
の吹出側に設けた吹出側に向かうほど次第に拡がる略ベ
ルマウス状内壁面を有する吹出部である。Reference numeral 16 denotes an orifice 13 on the side wall 12 side.
The blowout portion has a substantially bell-mouth-like inner wall surface which gradually expands toward the blowout side provided on the blowout side of the airbag.

【００５６】略長方形の吹出側パネル５を有する送風機
室４で羽根車６ａとの距離が小さい側壁１１側では、羽
根６ｂの外周から吐出する気流Ａは、第１の円弧壁１４
の内壁に一旦短く付着し、その間の壁面のない空間１７
を流動した後、第２の円弧壁１５に再付着することで、
気流の偏流を抑え、第１の円弧壁１４の壁面近傍の流速
の増大を防止すると共に、壁面のない空間１７で乱れが
緩和され、第２の円弧壁１５に再付着することで気流の
乱れはいっそう低減され、乱流騒音の発生を大きく抑制
する。On the side of the side wall 11 where the distance from the impeller 6 a is short in the blower room 4 having the substantially rectangular blow-out side panel 5, the airflow A discharged from the outer periphery of the blade 6 b is applied to the first arc wall 14.
Space that once adheres to the inner wall of the
After flowing through the second arc wall 15,
The drift of the air current is suppressed, the flow velocity near the wall surface of the first arc wall 14 is prevented from increasing, and the turbulence is reduced in the space 17 without the wall surface, and the turbulence of the air flow is reattached to the second arc wall 15. Is further reduced, and the generation of turbulent noise is greatly suppressed.

【００５７】さらに、第１の円弧壁１４と第２の円弧壁
１５と吹出側パネル５とで囲まれた空間１７は空気層と
して作用し、乱れた気流が持つ圧力脈動を緩衝し、乱流
騒音を減衰させる効果がある。Further, the space 17 surrounded by the first arc wall 14, the second arc wall 15, and the blow-out side panel 5 acts as an air layer, buffers the pressure pulsation of the turbulent air flow, and It has the effect of attenuating noise.

【００５８】また、外周側の吐出気流Ａに含まれる翼端
渦Ｂの作用により、翼間の一部分で吐出側の羽根車６ａ
内への逆流Ｃを、第１の円弧壁１４と第２の円弧壁１５
との間の壁面のない空間内１７に誘導し、第１に円弧壁
１４から第２の円弧壁１５へ向かう高速の気流に伴流さ
せることで再度吐出させ、羽根６ｂの外周側の翼間にお
ける逆流Ｃと高速な吐出流Ａの混濁による乱れを低減
し、乱流騒音の増加を抑えると共に、逆流Ｃが翼間内に
流入することによる空力性能の劣化を抑える。Further, due to the action of the blade tip vortex B contained in the discharge air flow A on the outer peripheral side, a part of the blades 6a on the discharge side is formed between the blades.
The backflow C into the first arc wall 14 and the second arc wall 15
Between the blades 6b on the outer peripheral side of the blade 6b. The turbulence caused by the turbidity of the backflow C and the high-speed discharge flow A at the time is reduced, the increase in turbulence noise is suppressed, and the deterioration of aerodynamic performance due to the backflow C flowing into the space between the blades is suppressed.

【００５９】ここで、羽根車６ａの吸込側の外周から翼
間に吸い込まれる気流Ｆは、軸方向成分が強く、オリフ
ィス１３の壁面近傍を流れ、この際、翼間を流れる距離
が短くなるため、羽根６ｂの作用による増速も小さく抑
えられる。Here, the air flow F sucked between the blades from the outer periphery on the suction side of the impeller 6a has a strong axial component and flows near the wall surface of the orifice 13, and at this time, the distance flowing between the blades becomes shorter. The speed increase due to the action of the blade 6b can be suppressed to a small value.

【００６０】そして、このため、オリフィス１３の吸込
側へ、羽根６ａの作用により動圧が付加され増速した羽
根６ｂの負圧面側を流れる気流Ｅの片寄りも抑えられる
ので、羽根６ｂ外周の吐出側で逆流を抑制することで吐
出気流Ａを妨げるものが無くなり流速は増加するが増加
量は小さい。よって、非常に高速な吐出気流が送風機６
より吹き出さず、ファンガード９の線材９ａの後方での
大きな気流乱れを抑制し、大きな流体騒音の発生を抑制
する。As a result, the dynamic pressure is applied to the suction side of the orifice 13 by the action of the blade 6a, and the bias of the airflow E flowing on the negative pressure side of the blade 6b, which is increased in speed, is also suppressed. By suppressing the backflow on the discharge side, there is no obstacle to the discharge airflow A, and the flow velocity increases, but the increase amount is small. Therefore, a very high-speed discharge airflow is generated by the blower 6.
Without blowing out more, large air turbulence behind the wire 9a of the fan guard 9 is suppressed, and generation of large fluid noise is suppressed.

【００６１】また、羽根車６ａと送風機室４で羽根車６
ａとの距離が大きい側壁１２側では、吹出側に向かうほ
ど次第に拡がる略ベルマウス状の内壁面を有する吹出部
１６を設けることで、吐出気流Ａの偏流を抑え、吹出部
１６の壁面近傍の流速の増大を防止するので、送風機６
の乱流騒音の大幅な増加は抑えられる。The impeller 6a and the blower room 4
On the side of the side wall 12 where the distance to the side a is large, the blowout portion 16 having a substantially bell-mouth-like inner wall surface that gradually expands toward the blowout side is provided, thereby suppressing the drift of the discharge airflow A and the vicinity of the wall surface of the blowout portion 16. To prevent the flow velocity from increasing, the blower 6
A large increase in turbulent noise of the vehicle can be suppressed.

【００６２】そして、羽根車６ａの吸込側の外周から翼
間に吸い込まれる気流Ｄの求心的成分が強く、オリフィ
ス１３の吸込側の壁面に沿わずに羽根６ｂの内周側まで
流入したあと、気流に働く遠心力により外周側に片寄る
ため、オリフィス１３の吸込側へ羽根６ｂの作用により
動圧が付加され増速した羽根負圧面側を流れる気流Ｅが
より外周側に片寄って流れることで吐出気流Ａは増速す
るが、吐出気流Ａに含まれる翼端渦Ｂの作用により翼間
の一部分で発生する逆流Ｃと混濁の際、乱れが発生する
が吐出気流Ａは減速させる。Then, the centripetal component of the airflow D sucked between the blades from the outer periphery of the suction side of the impeller 6a is strong, and after flowing into the inner peripheral side of the blade 6b without following the wall surface of the orifice 13 on the suction side, Since the centrifugal force acting on the air current causes the blade to deviate toward the outer peripheral side, dynamic pressure is applied to the suction side of the orifice 13 by the action of the blade 6b, and the increased airflow E flowing on the blade negative pressure surface side flows further toward the outer peripheral side to discharge. Although the airflow A increases in speed, the turbulence occurs in the backflow C generated in a part between the blades due to the action of the blade tip vortex B included in the discharge airflow A, and turbulence occurs, but the discharge airflow A is decelerated.

【００６３】ここで、吐出気流Ａと逆流Ｃによる乱れの
発生は、送風機６全周では無く部分的となるため、送風
機６の乱流騒音の増加は小さくなる。従って、羽根６ｂ
の外周での吐出気流Ａの乱れを抑えると共に、吐出気流
Ａの増速を抑え、送風機６の乱流騒音の増加とファンガ
ード９から発生する流体騒音の増加の両方を抑える。Here, since the turbulence due to the discharge airflow A and the backflow C is not generated on the entire circumference of the blower 6 but is partially generated, the increase of the turbulent noise of the blower 6 is reduced. Therefore, the blade 6b
In addition to suppressing the turbulence of the discharge airflow A on the outer periphery of the fan, the acceleration of the discharge airflow A is suppressed, and both the increase in the turbulent noise of the blower 6 and the increase in the fluid noise generated from the fan guard 9 are suppressed.

【００６４】（実施例２）図６〜図８は本発明の実施例
２の空気調和機の室外機を示す。尚、実施例１と同一構
成の部分については重複をさけるため同一符号を付け説
明を省略する。(Embodiment 2) FIGS. 6 to 8 show an outdoor unit of an air conditioner according to Embodiment 2 of the present invention. The same components as those in the first embodiment are denoted by the same reference numerals to avoid duplication, and description thereof is omitted.

【００６５】図において略長方形の吹出側パネル５を設
けた送風機室４内の羽根車６ａとの距離が小さい側壁１
１側の第１，第２の円弧壁１４，１５と、羽根車６ａと
の距離が大きい側壁１２側の略ベルマウス状吹出１６の
連結部１８が、略長方形の吹出側パネル５の対角線上近
辺に配設されている。In the drawing, the side wall 1 having a short distance from the impeller 6a in the blower room 4 provided with the substantially rectangular outlet side panel 5 is provided.
The connecting portions 18 of the substantially bell-mouth-shaped blowouts 16 on the side wall 12 side where the distance between the first and second arc walls 14 and 15 on the first side and the impeller 6a are large are on the diagonal line of the substantially rectangular blowout side panel 5. It is located near.

【００６６】略長方形の吹出側パネル５を有する送風機
室４の、羽根車６ａと送風機室４の側壁１１の距離が非
常に小さく、略長方形の吹出側パネル５の短辺と長辺の
差が大きい場合、略長方形の吹出側パネル５の対角線付
近で、送風機室４の羽根車６ａと側壁の距離が急激に大
きくなるので、羽根車６ａと送風機室４の側壁１１の距
離が非常に小さい部分では、羽根車６ａの吸込側の外周
から翼間に吸い込まれる気流Ｆは、軸方向成分が強く、
側壁１１からオリフィス１３の壁面近傍を流れ、この
際、翼間を流れる距離が短くなるため、羽根６ｂの作用
による増速も小さく抑えられる。The distance between the impeller 6a and the side wall 11 of the blower room 4 of the blower room 4 having the substantially rectangular blow-out side panel 5 is very small, and the difference between the short side and the long side of the substantially rectangular blow-out side panel 5 is small. When the distance is large, the distance between the impeller 6a of the blower room 4 and the side wall is sharply increased near the diagonal line of the substantially rectangular blow-out side panel 5, so that the distance between the impeller 6a and the side wall 11 of the blower room 4 is very small. Then, the airflow F sucked between the blades from the outer periphery on the suction side of the impeller 6a has a strong axial component,
Since the air flows from the side wall 11 to the vicinity of the wall surface of the orifice 13 and the distance flowing between the blades is reduced, the speed increase due to the action of the blade 6b is also suppressed.

【００６７】さらに、羽根６ｂの外周側への羽根６ｂの
作用により動圧が付加され増速した羽根６ｂの負圧面側
を流れる気流Ｅの片寄りも抑えられるので、羽根６ｂの
吐出側の外周で流速の増加を抑え、羽根６ｂの外周から
吐出する気流Ａが、第１の円弧壁１４の内壁に一旦短く
付着しその間の壁面のない空間を流動した後、第２の円
弧壁１５に再付着することで、気流の偏流を抑えるの
で、羽根６ｂの外周側からの吐出気流の乱れとそれに伴
う乱流騒音の発生を大きく低減すると共に、羽根６ｂの
外周側の吐出気流に含まれる翼端渦Ｂの作用による逆流
Ｃの翼間への流入を抑制し、羽根６ｂの外周側の翼間に
おける逆流Ｃと高速な吐出流Ａの混濁による乱れを低減
し、乱流騒音の増加と空力性能の劣化を抑える。Further, since the dynamic pressure is applied by the action of the blade 6b on the outer peripheral side of the blade 6b, the bias of the airflow E flowing on the negative pressure surface side of the accelerated blade 6b can be suppressed, and the outer peripheral side of the discharge side of the blade 6b can be suppressed. The airflow A discharged from the outer periphery of the blade 6b once adheres to the inner wall of the first arc wall 14 for a short time and flows through the space without the wall, and then re-applies to the second arc wall 15. By adhering, the drift of the airflow is suppressed, so that the turbulence of the discharge airflow from the outer peripheral side of the blade 6b and the generation of the turbulent noise associated therewith are greatly reduced, and the blade tip included in the discharge airflow on the outer peripheral side of the blade 6b. The flow of the backflow C into the space between the blades due to the action of the vortex B is suppressed, the turbulence due to the turbidity of the backflow C and the high-speed discharge flow A between the blades on the outer peripheral side of the blade 6b is reduced, and the turbulence noise is increased and the aerodynamic performance is increased. Deterioration of deterioration.

【００６８】また、略長方形の吹出側パネル５の対角線
付近から吹出側パネル５の長辺側にかけた羽根車６ａと
送風機室４の側壁１２の距離が大きい部分では、略ベル
マウス状の吹出部１６により、吐出気流Ａの偏流を抑え
壁面近傍の流速の増大を防止するので、送風機６の乱流
騒音の大幅な増加は抑えられる。In a portion where the distance between the impeller 6a and the side wall 12 of the blower chamber 4 extending from near the diagonal line of the substantially rectangular blow-out side panel 5 to the long side of the blow-out side panel 5 is large, a substantially bell-mouth-shaped blow-out portion is provided. By 16, the drift of the discharge airflow A is suppressed and the flow velocity near the wall surface is prevented from increasing, so that the turbulent noise of the blower 6 can be prevented from greatly increasing.

【００６９】そして、羽根車６ａの吸込側の外周から翼
間に吸い込まれる気流Ｄの求心的成分が強く、オリフィ
ス１３の吸込側の壁面に沿わずに羽根６ｂの内周側まで
流入したあと、気流に働く遠心力により外周側に片寄る
ため、オリフィス１３の吸込側へ羽根６ｂの作用により
動圧が付加され増速した羽根負圧面側を流れる気流Ｅが
より外周側に片寄って流れることで吐出気流Ａは増速す
るが、吐出気流Ａに含まれる翼端渦Ｂの作用により翼間
の一部分で発生する逆流Ｃと混濁の際、乱れが発生する
が吐出気流Ａは減速させる。Then, the centripetal component of the airflow D sucked between the blades from the outer periphery of the impeller 6a on the suction side is strong, and flows into the inner peripheral side of the blade 6b without following the suction-side wall surface of the orifice 13. Since the centrifugal force acting on the air current causes the blade to deviate toward the outer peripheral side, dynamic pressure is applied to the suction side of the orifice 13 by the action of the blade 6b, and the increased airflow E flowing on the blade negative pressure surface side flows further toward the outer peripheral side to discharge. Although the airflow A increases in speed, the turbulence occurs in the backflow C generated in a part between the blades due to the action of the blade tip vortex B included in the discharge airflow A, and turbulence occurs, but the discharge airflow A is decelerated.

【００７０】ここで、吐出気流Ａと逆流Ｃによる乱れの
発生は、送風機６全周では無く部分的となるため、送風
機６の乱流騒音の増加は小さくなる。Here, the turbulence caused by the discharge airflow A and the backflow C is generated not in the entire circumference of the blower 6 but in a part thereof, so that the increase of the turbulent noise of the blower 6 is reduced.

【００７１】従って、略長方形の吹出側パネル５を有す
る送風機室４の、羽根車６ａと送風機室４の側壁１１の
距離が非常に小さく、略長方形の吹出側パネル５の短辺
と長辺の差が大きい場合、羽根６ｂの外周での吐出気流
の乱れを抑えると共に、吐出気流の増速を抑え、送風機
６の乱流騒音の増加とファンガード９から発生する流体
騒音の増加の両方を抑える効果が送風機６全周で有効に
働く。Accordingly, the distance between the impeller 6a and the side wall 11 of the blower room 4 of the blower room 4 having the substantially rectangular blow-out side panel 5 is very small, and the short side and the long side of the substantially rectangular blow-out side panel 5 are small. When the difference is large, the turbulence of the discharge airflow on the outer periphery of the blade 6b is suppressed, the acceleration of the discharge airflow is suppressed, and both the increase of the turbulent noise of the blower 6 and the increase of the fluid noise generated from the fan guard 9 are suppressed. The effect works effectively all around the blower 6.

【００７２】（実施例３）図９は本発明の実施例３の空
気調和機の室外機を示す。尚、実施例１，２と同一構成
の部分については重複をさけるため同一符号を付け説明
を省略する。Embodiment 3 FIG. 9 shows an outdoor unit of an air conditioner according to Embodiment 3 of the present invention. The same components as those in the first and second embodiments are denoted by the same reference numerals to avoid duplication, and description thereof is omitted.

【００７３】図において略長方形の吹出側パネル５を設
けた送風機室４内の羽根車６ａとの距離が小さい側壁１
１側の第１，第２の円弧壁１４，１５と、羽根車６ａと
の距離が大きい側壁１２側の略ベルマウス状吹出部１６
の連結部１９が、略長方形の吹出側パネル５の対角線か
ら送風機室内４の羽根車６ａと側壁１１の距離が小さい
側寄りに配設されている。In the drawing, the side wall 1 having a short distance from the impeller 6a in the blower room 4 provided with the substantially rectangular blow-out side panel 5
A substantially bell-mouth-shaped outlet 16 on the side wall 12 where the distance between the first and second arc walls 14 and 15 on the first side and the impeller 6a is large.
Is disposed closer to the side where the distance between the impeller 6a and the side wall 11 of the blower room 4 is small from the diagonal line of the substantially rectangular outlet side panel 5.

【００７４】略長方形の吹出側パネル５の短辺と長辺の
差が非常に大きくない場合、略長方形の吹出側パネル５
の対角線より短辺寄りで、送風機室４の羽根車６ａと側
壁１１の距離が急激に大きくなるので、羽根車６ａと送
風機室４の側壁１１の距離が小さい部分では、羽根車６
ａの吸込側の外周から翼間に吸い込まれる気流Ｆは、軸
方向成分が強く、オリフィス１３の壁面近傍を流れ、羽
根６ｂの吐出側の外周で流速の増加を抑え、第１，第２
の円弧壁１４，１５により、羽根６ｂの外周側からの吐
出気流の乱れとそれに伴う乱流騒音の発生を大きく低減
すると共に、羽根６ｂの外周側の吐出気流に含まれる翼
端渦Ｂの作用による逆流Ｃの翼間への流入を抑制し、羽
根６ｂの外周側の翼間における逆流Ｃと高速な吐出流Ａ
の混濁による乱れを低減し、乱流騒音の増加と空力性能
の劣化を抑える。When the difference between the short side and the long side of the substantially rectangular outlet side panel 5 is not very large, the substantially rectangular outlet side panel 5
The distance between the impeller 6a of the blower room 4 and the side wall 11 is sharply increased near the diagonal line of the impeller 6, and the impeller 6a is small in the portion where the distance between the impeller 6a and the side wall 11 of the blower room 4 is small.
The airflow F sucked between the blades from the outer periphery on the suction side of a has a strong axial component, flows near the wall surface of the orifice 13, and suppresses an increase in the flow velocity on the outer periphery on the discharge side of the blade 6b.
The arc walls 14 and 15 greatly reduce the turbulence of the discharge airflow from the outer peripheral side of the blade 6b and the generation of turbulent noise associated therewith, and the action of the blade tip vortex B included in the discharge airflow on the outer peripheral side of the blade 6b. To prevent the backflow C from flowing into the space between the blades, and the backflow C and the high-speed discharge flow A between the blades on the outer peripheral side of the blade 6b.
To reduce turbulence due to cloudiness, and to suppress increase in turbulent noise and deterioration of aerodynamic performance.

【００７５】そして、略長方形の吹出側パネル５の対角
線付近より短辺寄りから吹出側パネル５の長辺側の羽根
車６ａと送風機室４の側壁１２の距離が大きい部分で
は、吐出気流Ａの偏流を抑え、流速の増大を防止するの
で、送風機６の乱流騒音の大幅な増加は抑えると共に、
高速な吐出気流Ａと翼端渦Ｂの作用により翼間の一部分
で羽根車６ａ内への逆流Ｃの混濁の際、乱れが発生する
が吐出気流Ａは減速させる。ここで、吐出気流と逆流に
よる乱れの発生は、送風機６全周では無く部分的となる
ため、送風機６の乱流騒音の増加は小さくなる。Then, in a portion where the distance between the impeller 6a on the long side of the blow-out side panel 5 and the side wall 12 of the blower chamber 4 from the short side near the diagonal line of the substantially rectangular blow-out side panel 5 is large. Since the drift is suppressed and the flow velocity is prevented from increasing, the turbulent noise of the blower 6 is suppressed from being greatly increased.
When the backflow C into the impeller 6a becomes turbid at a part between the blades due to the action of the high-speed discharge airflow A and the blade tip vortex B, turbulence occurs, but the discharge airflow A is decelerated. Here, since the turbulence due to the discharge airflow and the backflow is generated not in the entire circumference of the blower 6 but in a part thereof, an increase in the turbulent noise of the blower 6 is reduced.

【００７６】従って、略長方形の吹出側パネル５の短辺
と長辺の差が非常に大きくない場合羽根６ｂの外周での
吐出気流の乱れを抑えると共に、吐出気流の増速を抑
え、送風機６の乱流騒音の増加とファンガード９から発
生する流体騒音の増加の両方を抑える効果が送風機６全
周で有効に働く。Therefore, when the difference between the short side and the long side of the substantially rectangular blow-out side panel 5 is not very large, the turbulence of the discharge airflow on the outer periphery of the blade 6b is suppressed, and the increase of the discharge airflow is suppressed, so that the blower 6 The effect of suppressing both the increase in the turbulent noise of the fan and the increase in the fluid noise generated from the fan guard 9 works effectively on the entire circumference of the blower 6.

【００７７】（実施例４）図１０は本発明の実施例４の
空気調和機の室外機を示す。尚、実施例１，２，３と同
一構成の部分については重複をさけるため同一符号を付
け説明を省略する。Embodiment 4 FIG. 10 shows an outdoor unit of an air conditioner according to Embodiment 4 of the present invention. The same components as those of the first, second, and third embodiments are denoted by the same reference numerals to avoid duplication, and description thereof is omitted.

【００７８】図において第１の円弧壁１４と、吹出側に
向かうほど次第に拡がる略ベルマウス状の内壁面を有す
る吹出部１６の連結部２０が、第２の円弧壁１５と吹出
部１６の連結部２１より回転方向に前傾している。In the figure, a connecting portion 20 of a first arc wall 14 and a blowing portion 16 having a substantially bell-mouth-like inner wall surface gradually expanding toward the blowing side is connected to a connecting portion of the second arc wall 15 and the blowing portion 16. It is inclined forward in the rotation direction from the part 21.

【００７９】羽根車６ａの外周、あるいは吸込側から流
入した気流は、羽根車６ａが回転することにより、吐出
側では回転方向に進んだ状態で吐出され、さらに羽根６
ｂ外周からの吐出気流の大半が、遠心力による半径方向
成分と共に羽根６ｂの作用による回転方向への周方向成
分を有するが、第１の円弧壁１４が第２の円弧壁１５よ
り回転方向に前傾して、吹出側に向かうほど次第に拡が
る略ベルマウス状の内壁面を有する吹出部１６と連結す
ることで、羽根車６ａと送風機室４の側壁の距離が大き
く変化する部分では、羽根６ｂの外周からの吐出気流の
上流側での吸込状態の流れの連続的で緩やかな移行に伴
う吐出気流の変化に合わせたオリフィス１３の吐出形状
とすることができ、羽根６ｂの外周での吐出気流の乱れ
を抑えると共に、吐出気流の増速を抑え、送風機６の乱
流騒音の増加とファンガード９から発生する流体騒音の
増加の両方を抑える効果が送風機６全周で有効に働くと
共に、連結部２０，２１付近の急激な吐出形状の変化に
よる吐出気流の乱れを防ぎ、連結部２０，２１での乱れ
による乱流騒音の増加を抑える。The airflow that has flowed in from the outer periphery of the impeller 6a or from the suction side is discharged in a state where the impeller 6a rotates in the rotation direction on the discharge side, and is further discharged.
b Most of the discharge airflow from the outer periphery has a radial component due to the centrifugal force and a circumferential component in the rotational direction due to the action of the blade 6b, but the first arc wall 14 is more rotationally moved than the second arc wall 15 in the rotational direction. By connecting to the outlet 16 having a bell mouth-like inner wall surface which is inclined forward and gradually expands toward the outlet side, the blade 6b is provided at a portion where the distance between the impeller 6a and the side wall of the blower chamber 4 greatly changes. The shape of the orifice 13 can be adjusted in accordance with the change of the discharge airflow accompanying the continuous and gentle transition of the suction flow on the upstream side of the discharge airflow from the outer periphery of the blade 6b. The effect of suppressing the turbulence of the blower, suppressing the increase of the discharge airflow, suppressing both the increase of the turbulent noise of the blower 6 and the increase of the fluid noise generated from the fan guard 9 works effectively on the entire circumference of the blower 6, and Part 20 Prevent disturbance of discharge airflow by a rapid change in the discharge shape around 21, suppressing an increase in turbulence noise due to turbulence at the connecting portion 20, 21.

【００８０】尚、以上の説明では、軸流式の送風機を例
に説明したが、斜流式の低圧型の送風機でも同様に実施
可能である。In the above description, the axial flow type blower has been described as an example. However, a diagonal flow type low pressure type blower can be similarly implemented.

【００８１】[0081]

【発明の効果】以上のように本発明によれば、略長方形
の吹出側パネルを設けた送風機室の略中央部に設けた送
風機のオリフィスの吐出側を、前記略長方形の吹出側パ
ネルを設けた前記送風機室内の側壁と前記羽根車の距離
が小さい側では、吹出側先端を開放端とした第１の円弧
壁と、前記第１の円弧壁の外側に設けた略同心円状でか
つ第１の円弧壁より吹出側先端の開放端を吹出側に設け
た第２の円弧壁で構成し、箱体内の側壁と前記羽根車の
距離が大きい側では、吹出側に向かうほど次第に拡がる
内壁面を有する吹出部とすることにより、羽根車と送風
機室の側壁の距離が小さい部分では、気流の偏流を抑
え、壁面近傍の流速の増大を防止すると共に、気流の乱
れはいっそう低減され、乱流騒音の発生を大きく低減す
る抑制する。As described above, according to the present invention, the discharge side of the blower orifice provided substantially at the center of the blower room provided with the substantially rectangular blow-out side panel is provided with the substantially rectangular blow-out side panel. On the side where the distance between the side wall in the blower chamber and the impeller is small, a first arc-shaped wall having an open end at the blow-out end, and a substantially concentric and first concentric circle provided outside the first arc-shaped wall. The arcuate wall has an open end at the blow-out end on the blow-out side, and on the side where the distance between the side wall in the box and the impeller is large, the inner wall surface that gradually widens toward the blow-out side. By having the blowout section, in a portion where the distance between the impeller and the side wall of the blower room is small, the drift of the airflow is suppressed, the flow velocity near the wall surface is prevented from increasing, and the turbulence of the airflow is further reduced. The occurrence of occurrence is greatly reduced.

【００８２】また、羽根外周側の翼間における逆流と高
速な吐出流の混濁による乱れを低減し、乱流騒音の増加
を抑えると共に、逆流が羽根内に流入することによる空
力性能の劣化を抑える。Further, the turbulence due to the turbidity of the backflow and the high-speed discharge flow between the blades on the outer peripheral side of the blades is reduced, the increase in turbulence noise is suppressed, and the deterioration of aerodynamic performance due to the backflow flowing into the blades is suppressed. .

【００８３】そして、非常に高速な吐出気流が送風機よ
り吹き出さず、ファンガードの線材の後方での大きな気
流乱れを抑制し、大きな流体騒音の発生を抑制する。Then, a very high-speed discharge airflow does not blow out from the blower, so that large turbulence behind the fan guard wire is suppressed, and generation of large fluid noise is suppressed.

【００８４】さらに、羽根車と送風機室の側壁の距離が
大きい部分では、気流の偏流を抑え吐出部の壁面近傍の
流速の増大を防止するので、送風機の乱流騒音の大幅な
増加は抑えられると共に、高速な吐出気流と逆流の混濁
の際、乱れが発生するが吐出気流は減速させる。Further, in a portion where the distance between the impeller and the side wall of the blower chamber is large, the drift of the air flow is suppressed and the flow velocity near the wall surface of the discharge section is prevented from increasing, so that the turbulent noise of the blower can be prevented from greatly increasing. At the same time, when the high-speed discharge airflow and the reverse flow are turbid, turbulence occurs, but the discharge airflow is decelerated.

【００８５】ここで、吐出気流と逆流による乱れの発生
は、送風機全周では無く、部分的となるため、大幅な送
風機の乱流騒音の増加は抑えられる。Here, since the turbulence due to the discharge airflow and the backflow is generated not in the entire circumference of the blower but in a part thereof, a large increase in turbulence noise of the blower can be suppressed.

【００８６】従って、羽根の外周での吐出気流の乱れを
抑えると共に、吐出気流の増速を抑え、送風機の乱流騒
音の増加とファンガードから発生する流体騒音の増加の
両方を抑えるという有利な効果が得られる。Therefore, the turbulence of the discharge airflow on the outer periphery of the blade is suppressed, the acceleration of the discharge airflow is suppressed, and both the increase in the turbulent noise of the blower and the increase in the fluid noise generated from the fan guard are suppressed. The effect is obtained.

【００８７】また、略長方形の吹出側パネルを設けた送
風機室内の側壁と羽根車の距離が小さい側の第１，第２
の円弧壁と、送風機室内の側壁と羽根車の距離が大きい
側の吹出側に向かうほど次第に拡がる内壁面を有する吹
出部の連結部が、略長方形の吹出側パネルの対角線上近
辺に配設してあることにより、略長方形の吹出側パネル
を有する送風機室の、羽根車と送風機室の側壁の小さい
側の距離が非常に小さく、略長方形の短辺と長辺の差が
非常に大きい場合、羽根車と送風機室の側壁の距離が非
常に小さい部分では、気流の偏流を抑え、壁面近傍の流
速の増大を防止すると共に、気流の乱れはいっそう低減
され、乱流騒音の発生を大きく低減する抑制する。Further, the first and second sides of the side where the distance between the impeller and the side wall in the blower room provided with the substantially rectangular outlet side panel are small.
And a connecting portion of a blowout portion having an inner wall surface that gradually expands toward the blowout side on the side where the distance between the side wall and the impeller in the blower chamber is large is disposed near a diagonal line of the substantially rectangular blowout side panel. By the fact that the distance between the impeller and the small side of the side wall of the blower room of the blower room having the substantially rectangular blow-out side panel is very small, and the difference between the short side and the long side of the substantially rectangular shape is very large, In the part where the distance between the impeller and the side wall of the fan room is very small, the drift of the air flow is suppressed, the flow velocity near the wall is prevented from increasing, and the turbulence of the air flow is further reduced, and the generation of turbulent noise is greatly reduced. Suppress.

【００８８】また、羽根外周側の翼間における逆流と高
速な吐出流の混濁による乱れを低減し、乱流騒音の増加
を抑えると共に、逆流が羽根内に流入することによる空
力性能の劣化を抑える。Further, turbulence due to the turbidity of the backflow and the high-speed discharge flow between the blades on the outer peripheral side of the blades is reduced, the increase in turbulent noise is suppressed, and the deterioration of aerodynamic performance due to the backflow flowing into the blades is suppressed. .

【００８９】そして、非常に高速な吐出気流が送風機よ
り吹き出さず、ファンガードの線材の後方での大きな気
流乱れを抑制し、大きな流体騒音の発生を抑制する。Then, a very high-speed discharge airflow does not blow out from the blower, so that a large turbulence behind the fan guard wire is suppressed, and the generation of a large fluid noise is suppressed.

【００９０】そして、略長方形の吹出側パネルの対角線
付近から吹出側パネルの長辺側の羽根車と送風機室の側
壁の距離が大きい部分では、羽根車と送風機室の側壁の
距離が大きい部分では、気流の偏流を抑え吹出部の壁面
近傍の流速の増大を防止するので、送風機の乱流騒音の
大幅な増加は抑えられると共に、高速な吐出気流と逆流
の混濁の際、乱れが発生するが吐出気流は減速させる。In the portion where the distance between the impeller and the side wall of the blower room on the long side of the blow-out panel from the vicinity of the diagonal line of the substantially rectangular blow-out panel is large, in the portion where the distance between the impeller and the side wall of the blower room is large. This suppresses the drift of the air flow and prevents an increase in the flow velocity near the wall surface of the blow-out part, so that the turbulent noise of the blower can be prevented from significantly increasing, and turbulence occurs when the high-speed discharge air flow and the reverse flow are turbid. The discharge airflow is decelerated.

【００９１】ここで、吐出気流と逆流による乱れの発生
は、送風機全周では無く、部分的となるため、大幅な送
風機の乱流騒音の増加は抑えられる。Here, since the turbulence due to the discharge airflow and the backflow is generated not in the entire circumference of the blower but in a part thereof, a significant increase in turbulence noise of the blower is suppressed.

【００９２】従って、羽根の外周での吐出気流の乱れを
抑えると共に、吐出気流の増速を抑え、送風機の乱流騒
音の増加とファンガードから発生する流体騒音の増加の
両方を抑える効果が送風機全周で有効に働くという有利
な効果が得られる。Accordingly, the effect of suppressing the turbulence of the discharge airflow on the outer periphery of the blade, suppressing the increase of the discharge airflow, and suppressing both the increase of the turbulent noise of the blower and the increase of the fluid noise generated from the fan guard are improved. The advantageous effect of working effectively all around is obtained.

【００９３】また、略長方形の吹出側パネルを設けた送
風機室内の側壁と前記羽根車の距離が小さい側の第１，
第２の円弧壁と、送風機室内の側壁と前記羽根車の距離
が大きい側の吹出側に向かうほど次第に拡がる内壁面を
有する吹出部の連結部が、前記略長方形の吹出側パネル
の対角線から送風機室内の側壁と前記羽根車の距離が小
さい側寄りに配設されていることにより、略長方形の吹
出側パネルの短辺と長辺の差が非常に大きくない場合、
略長方形の吹出側パネルの対角線より短辺寄りで、送風
機室の羽根車と側壁の距離が急激に大きくなるので、羽
根車と送風機室の側壁の距離が小さい部分では、気流の
偏流を抑え、壁面近傍の流速の増大を防止すると共に、
気流の乱れはいっそう低減され、乱流騒音の発生を大き
く低減する抑制する。[0093] The first and second impellers on the side where the distance between the impeller and the side wall in the blower room provided with a substantially rectangular outlet side panel is small.
A connecting portion of a second arc wall and a blowout portion having an inner wall surface gradually expanding toward a blowout side on a side where a distance between the side wall in the blower chamber and the impeller is large is formed by a blower from a diagonal line of the substantially rectangular blowout side panel. When the distance between the side wall in the room and the impeller is disposed closer to the smaller side, when the difference between the short side and the long side of the substantially rectangular outlet side panel is not very large,
Since the distance between the impeller and the side wall of the blower room is sharply increased near the diagonal line of the substantially rectangular outlet side panel, the drift of the air flow is suppressed in a portion where the distance between the impeller and the side wall of the blower room is small, While preventing an increase in flow velocity near the wall,
The turbulence of the airflow is further reduced, and the generation of turbulent noise is greatly reduced.

【００９４】また、羽根外周側の翼間における逆流と高
速な吐出流の混濁による乱れを低減し、乱流騒音の増加
を抑えると共に、逆流が羽根内に流入することによる空
力性能の劣化を抑える。In addition, turbulence due to the turbidity of the backflow and the high-speed discharge flow between the blades on the outer peripheral side of the blades is reduced, the increase in turbulent noise is suppressed, and the deterioration of aerodynamic performance due to the backflow flowing into the blades is suppressed. .

【００９５】そして、非常に高速な吐出気流が送風機よ
り吹き出さず、ファンガードの線材の後方での大きな気
流乱れを抑制し、大きな流体騒音の発生を抑制する。Then, a very high-speed discharge airflow does not blow out from the blower, so that a large turbulence behind the wire rod of the fan guard is suppressed, and the generation of a large fluid noise is suppressed.

【００９６】そして、略長方形の吹出側パネルの対角線
より短辺寄りから吹出側パネルの長辺側の羽根車と送風
機室の側壁の距離が大きい部分では、羽根車と送風機室
の側壁の距離が大きい部分では、気流の偏流を抑え吹出
部の壁面近傍の流速の増大を防止するので、送風機の乱
流騒音の大幅な増加は抑えられると共に、高速な吐出気
流と逆流の混濁の際、乱れが発生するが吐出気流は減速
させる。ここで、吐出気流と逆流による乱れの発生は、
送風機全周では無く、部分的となるため、大幅な送風機
の乱流騒音の増加は抑えられる。In a portion where the distance between the impeller on the long side of the blow-out panel and the side wall of the blower chamber is large from the short side of the diagonal line of the substantially rectangular blow-out side panel, the distance between the impeller and the side wall of the blower room is large. In the large part, the drift of the airflow is suppressed and the increase of the flow velocity near the wall of the blowout part is prevented, so that the turbulent noise of the blower can be prevented from increasing significantly. Although it occurs, the discharge airflow is decelerated. Here, the turbulence caused by the discharge airflow and the backflow is
Since the blower is not the entire circumference but a partial blower, a large increase in turbulent noise of the blower can be suppressed.

【００９７】従って、羽根の外周での吐出気流の乱れを
抑えると共に、吐出気流の増速を抑え、送風機の乱流騒
音の増加とファンガードから発生する流体騒音の増加の
両方を抑える効果が送風機全周で有効に働くという有利
な効果が得られる。Accordingly, the effect of suppressing the turbulence of the discharge airflow on the outer periphery of the blade, suppressing the increase of the discharge airflow, and suppressing both the increase in the turbulent noise of the blower and the increase in the fluid noise generated from the fan guard are obtained. The advantageous effect of working effectively all around is obtained.

【００９８】また、第１の円弧壁と、吹出側に向かうほ
ど次第に拡がる略ベルマウス状、あるいは略円錐状の内
壁面を有する吹出部の連結部が、第２の円弧壁と、吹出
側に向かうほど次第に拡がる内壁面を有する吹出部の連
結部より回転方向に前傾していることにより、羽根車と
送風機室の側壁の距離が大きく変化する部分では、羽根
外周からの吐出気流の上流側での吸込状態の流れの連続
的で緩やかな移行に伴う吐出気流の変化に合わせたオリ
フィス吐出形状とすることができ、羽根の外周での吐出
気流の乱れを抑えると共に、吐出気流の増速を抑え、送
風機の乱流騒音の増加とファンガードから発生する流体
騒音の増加の両方を抑える効果が送風機全周で有効に働
くと共に、連結部の急激な吐出形状の変化による吐出気
流の乱れを防ぎ、連結部での乱れによる乱流騒音の増加
を抑える。A connecting portion between the first arc wall and a blowing portion having a substantially bell-mouth-shaped or substantially conical inner wall surface gradually expanding toward the blowing side is formed on the second arc wall and the blowing side. In the part where the distance between the impeller and the side wall of the blower chamber changes greatly by being inclined forward in the rotation direction from the connection part of the blowout part having an inner wall surface that gradually widens toward the upstream side of the discharge airflow from the outer periphery of the blade The orifice discharge shape can be adapted to the change of the discharge airflow due to the continuous and gradual transition of the flow of the suction state at the time of suction, suppressing the turbulence of the discharge airflow on the outer periphery of the blade and increasing the discharge airflow The effect of suppressing both the increase in turbulence noise of the blower and the increase in fluid noise generated from the fan guard works effectively on the entire circumference of the blower, and also prevents turbulence in the discharge airflow due to sudden changes in the discharge shape of the connection part , Suppress an increase in turbulence noise due to turbulence in the forming section.

【図面の簡単な説明】[Brief description of the drawings]

【図１】本発明の実施例１における空気調和機の室外機
の断面図FIG. 1 is a cross-sectional view of an outdoor unit of an air conditioner according to a first embodiment of the present invention.

【図２】本発明の実施例１における空気調和機の室外機
の吐出側正面図FIG. 2 is a discharge side front view of the outdoor unit of the air conditioner according to the first embodiment of the present invention.

【図３】本発明の実施例１における軸流型の送風機のＢ
−Ｂ断面図FIG. 3 is a diagram illustrating an axial flow type blower B according to the first embodiment of the present invention.
-B sectional view

【図４】本発明の実施例１における軸流型の送風機のＡ
−Ａ断面図FIG. 4 shows A of the axial-flow type blower according to the first embodiment of the present invention.
-A sectional view

【図５】本発明の実施例１における空気調和機の室外機
に搭載された軸流型の送風機の羽根車と側壁との距離が
大きい側の羽根負圧近傍の気流の模式図FIG. 5 is a schematic diagram of an airflow near a blade negative pressure on a side where a distance between an impeller and a side wall of an axial flow type blower mounted on an outdoor unit of an air conditioner according to the first embodiment of the present invention is large.

【図６】本発明の実施例２における空気調和機の室外機
の吐出側正面図FIG. 6 is a discharge side front view of an outdoor unit of an air conditioner according to Embodiment 2 of the present invention.

【図７】本発明の実施例２における軸流型の送風機のＢ
−Ｂ断面図FIG. 7 is an axial flow type blower B according to a second embodiment of the present invention.
-B sectional view

【図８】本発明の実施例２における軸流型の送風機のＡ
−Ａ断面図FIG. 8 is a diagram illustrating an axial-flow type blower A according to a second embodiment of the present invention.
-A sectional view

【図９】本発明の実施例３における空気調和機の室外機
の吐出側正面図FIG. 9 is a discharge side front view of an outdoor unit of an air conditioner according to Embodiment 3 of the present invention.

【図１０】本発明の実施例４における空気調和機の室外
機の吐出側正面図FIG. 10 is a discharge side front view of an outdoor unit of an air conditioner according to Embodiment 4 of the present invention.

【図１１】従来の空気調和機の室外機の断面図FIG. 11 is a cross-sectional view of an outdoor unit of a conventional air conditioner.

【図１２】従来の空気調和機の室外機の吐出側正面図FIG. 12 is a front view of a discharge side of an outdoor unit of a conventional air conditioner.

【図１３】従来の空気調和機の室外機に搭載された軸流
型の送風機のＢ−Ｂ断面図FIG. 13 is a cross-sectional view of the axial-flow type blower mounted on the outdoor unit of the conventional air conditioner, taken along the line BB.

【図１４】従来の空気調和機の室外機に搭載された軸流
型の送風機のＡ−Ａ断面図FIG. 14 is an AA cross-sectional view of an axial-flow type blower mounted on an outdoor unit of a conventional air conditioner.

【図１５】従来の空気調和機の室外機に搭載された軸流
型の送風機の羽根車と側壁との距離が小さい側の羽根負
圧近傍の気流の模式図FIG. 15 is a schematic diagram of an airflow near a blade negative pressure on a side where a distance between an impeller and a side wall of an axial flow type blower mounted on an outdoor unit of a conventional air conditioner is small.

【符号の説明】[Explanation of symbols]

１ 室外機本体 ２ 箱体 ３ 熱交換器 ４ 送風機室 ５ 吹出パネル ６ 送風機 ６ａ 羽根車 ９ ファンガード １１ 羽根車との距離が小さい側壁 １２ 羽根車との距離が大きい側壁 １３ オリフィス １４ 第１の円弧壁 １５ 第２の円弧壁 １６ 吹出部 １８，１９，２０，２１ 連結部 DESCRIPTION OF SYMBOLS 1 Outdoor unit main body 2 Box 3 Heat exchanger 4 Blower room 5 Blow-out panel 6 Blower 6a Impeller 9 Fan guard 11 Side wall with small distance to impeller 12 Side wall with large distance from impeller 13 Orifice 14 First arc Wall 15 Second arc wall 16 Blow-out portion 18, 19, 20, 21 Connecting portion

Claims (4)

【特許請求の範囲】[Claims] 【請求項１】 本体と、前記箱体内に設けた熱交換器
と、前記箱体内外を仕切る略長方形の吹出側パネルを設
けた送風機室と、前記吹出側パネルの略中央部に配設し
た羽根車と、前記羽根車の後縁部外周を囲み前記吹出側
パネルに吸込側を固定したオリフィスと、前記吹出側パ
ネルの吹出後方に設けたファンガードで構成され、前記
オリフィスの吹出部が、前記略長方形の吹出側パネルを
設けた前記送風機室内の側壁と前記羽根車の距離が小さ
い側では、吹出側先端を開放端とした第１の円弧壁と、
前記第１の円弧壁の外側に設けた略同心円状でかつ第１
の円弧壁より吹出側先端の開放端を吹出側に設けた第２
の円弧壁で構成され、前記略長方形の吹出側パネルを設
けた前記箱体内の側壁と前記羽根車の距離が大きい側で
は、吹出側に向かうほど次第に拡がる内壁面を有する空
気調和機の室外機。1. A main body, a heat exchanger provided in the box body, a blower room provided with a substantially rectangular blow-out panel partitioning the inside and the outside of the box body, and a blower room provided in a substantially central portion of the blow-side panel. An impeller, an orifice surrounding the outer periphery of the trailing edge of the impeller and having a suction side fixed to the blow-out side panel, and a fan guard provided behind the blow-out side panel at the blow-out side, wherein the blow-out portion of the orifice, On the side where the distance between the side wall and the impeller provided with the substantially rectangular blow-out side panel and the impeller is small, a first arc-shaped wall having a blow-side tip as an open end;
A substantially concentric and first concentric circle provided outside the first circular arc wall
The open end of the blow-out end is provided on the blow-out side from the arc wall of the second.
An outdoor unit of an air conditioner having an arc-shaped wall and having an inner wall surface that gradually widens toward the blow-off side on the side where the distance between the side wall in the box provided with the substantially rectangular blow-out side panel and the impeller is large. . 【請求項２】 略長方形の吹出側パネルを設けた送風機
室内の側壁と前記羽根車の距離が小さい側の第１，第２
の円弧壁と、送風機室内の側壁と前記羽根車の距離が大
きい側の吹出側に向かうほど次第に拡がる内壁面を有す
る吹出部の連結部が、略長方形の吹出側パネルの対角線
上近辺に配設された請求項１記載の空気調和機の室外
機。2. The air conditioner according to claim 1, wherein the first and second impellers have a smaller distance between a side wall in the blower chamber provided with a substantially rectangular outlet-side panel and the impeller.
And a connecting portion of a blowout portion having an inner wall surface which gradually widens toward a blowout side on a side where the distance between the side wall in the blower chamber and the impeller is large is disposed near a diagonal line of a substantially rectangular blowout side panel. The outdoor unit of the air conditioner according to claim 1, wherein 【請求項３】 略長方形の吹出側パネルを設けた送風機
室内の側壁と前記羽根車の距離が小さい側の第１，第２
の円弧壁と、送風機室内の側壁と前記羽根車の距離が大
きい側の吹出側に向かうほど次第に拡がる内壁面を有す
る吹出部の連結部が、前記略長方形の吹出側パネルの対
角線から送風機室内の側壁と前記羽根車の距離が小さい
側寄りに配設された請求項１記載の空気調和機の室外
機。3. A first and second side of the impeller in which the distance between the side wall in the blower room provided with a substantially rectangular blow-out side panel and the impeller is small.
The arcuate wall and a connecting portion of a blowout portion having an inner wall surface which gradually widens toward a blowout side on a side where the distance between the side wall in the blower room and the impeller is large, a diagonal line of the substantially rectangular blowout side panel inside the blower room. The outdoor unit of an air conditioner according to claim 1, wherein the outdoor unit is disposed closer to a side where a distance between a side wall and the impeller is small. 【請求項４】 第１の円弧壁と、吹出側に向かうほど次
第に拡がる略ベルマウス状、あるいは略円錐状の内壁面
を有する吹出部の連結部が、第２の円弧壁と、吹出側に
向かうほど次第に拡がる内壁面を有する吹出部の連結部
より回転方向に前傾した請求項１または２または３記載
の空気調和機の室外機。4. A connecting portion between a first arc wall and a blow-out portion having a substantially bell-mouth-like or substantially conical inner wall surface gradually expanding toward the blow-off side is formed on the second arc-shaped wall and the blow-out side. The outdoor unit of an air conditioner according to claim 1, wherein the connecting portion of the blowing portion having an inner wall surface that gradually widens toward the front is inclined forward in the rotation direction.
JP14900198A 1998-05-29 1998-05-29 Outdoor machine for air conditioner Pending JPH11337126A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP14900198A JPH11337126A (en) 1998-05-29 1998-05-29 Outdoor machine for air conditioner

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP14900198A JPH11337126A (en) 1998-05-29 1998-05-29 Outdoor machine for air conditioner

Publications (1)

Publication Number Publication Date
JPH11337126A true JPH11337126A (en) 1999-12-10

Family

ID=15465499

Family Applications (1)

Application Number Title Priority Date Filing Date
JP14900198A Pending JPH11337126A (en) 1998-05-29 1998-05-29 Outdoor machine for air conditioner

Country Status (1)

Country Link
JP (1) JPH11337126A (en)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AU2002221045B2 (en) * 2000-12-28 2005-10-06 Daikin Industries, Ltd. Blower, and outdoor unit for air conditioner
JP2011226725A (en) * 2010-04-22 2011-11-10 Panasonic Corp Indoor unit of air conditioner
WO2017077576A1 (en) * 2015-11-02 2017-05-11 三菱電機株式会社 Air conditioner outdoor unit and refrigeration cycle device

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AU2002221045B2 (en) * 2000-12-28 2005-10-06 Daikin Industries, Ltd. Blower, and outdoor unit for air conditioner
JP2011226725A (en) * 2010-04-22 2011-11-10 Panasonic Corp Indoor unit of air conditioner
WO2017077576A1 (en) * 2015-11-02 2017-05-11 三菱電機株式会社 Air conditioner outdoor unit and refrigeration cycle device
JPWO2017077576A1 (en) * 2015-11-02 2018-06-07 三菱電機株式会社 Air conditioner outdoor unit and refrigeration cycle apparatus
GB2557130A (en) * 2015-11-02 2018-06-13 Mitsubishi Electric Corp Air conditioner outdoor unit and refrigeration cycle device
US10495328B2 (en) 2015-11-02 2019-12-03 Mitsubishi Electric Corporation Outdoor unit of air conditioner and refrigeration cycle device
GB2557130B (en) * 2015-11-02 2021-01-06 Mitsubishi Electric Corp Outdoor Unit of Air Conditioner and Refrigeration Cycle Device

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