JP2013213420A - Fan and outside unit using the same - Google Patents

Fan and outside unit using the same Download PDF

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JP2013213420A
JP2013213420A JP2012083584A JP2012083584A JP2013213420A JP 2013213420 A JP2013213420 A JP 2013213420A JP 2012083584 A JP2012083584 A JP 2012083584A JP 2012083584 A JP2012083584 A JP 2012083584A JP 2013213420 A JP2013213420 A JP 2013213420A
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blade
outer peripheral
blades
orifice
impeller
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JP6035508B2 (en
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Takumi Kida
琢己 木田
Takashi Sugio
孝 杉尾
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Panasonic Corp
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Abstract

PROBLEM TO BE SOLVED: To provide a fan that stabilizes the generation of vane end swirl and suppresses an increase in a flow loss and disturbance noise, and to provide an outside unit using the fan.SOLUTION: A first chamfer 15 is provided in a pressure surface side 13d1 of an outer circumferential end part 13d of an impeller, airflow is reduced and is smoothly engulfed from the pressure surface side 13d1 to a negative pressure side 13d2 by the first chamfer, wing-tip vortex, which is generated in the negative pressure side 13d2 of the outer circumferential end part 13d of an impeller suction side 13a that is enclosed by an orifice 14, is reduced and stabilized, and moreover leakage flow can be engulfed along a smooth curved shape from a second chamber 16 to a protrusion 17 of an impeller negative pressure surface side 13e2 arranged in a pressure surface side 13e1 of an impeller outer circumferential end part 13e even at the outer circumferential end part 13e of an impeller discharge side 13b enclosed by the orifice 14. Accordingly, the wing-tip vortex due to the leakage flow is reduced and stabilized, so that an increase in a flow loss and disturbance noise can be suppressed.

Description

本発明は、空気調和機やヒートポンプ式給湯機などの冷凍装置に好適な送風機とそれを用いた室外ユニットに関するものである。   The present invention relates to a blower suitable for a refrigeration apparatus such as an air conditioner or a heat pump type hot water heater, and an outdoor unit using the blower.

近年、空気調和機では、地球温暖化などの対応として省エネが急激に進んでおり、機器の低入力化が促進されている。一方、暖房快適性の向上など室内機、室外機の熱交換性能の向上も求められており、熱交換器の高性能化とともに、室内、室外の送風機の高効率高性能も必須となっている。   In recent years, in air conditioners, energy conservation has been rapidly progressing as a countermeasure against global warming and the like, and lower input of devices has been promoted. On the other hand, improvement of heat exchange performance of indoor units and outdoor units such as improvement of heating comfort is also required, and high efficiency and high performance of indoor and outdoor blowers are indispensable in addition to high performance of heat exchangers. .

従来、室外機の送風機には、大風量でかつ低騒音の観点から軸流式、あるいは斜流式の送風機が用いられてきた。しかし、空気調和機のさらなる省エネの促進のため、室外機の送風機にも低入力化が必要であり、室外機として所定の風量を維持しつつ、送風機の送風効率をさらに向上することが求められている。   Conventionally, axial blowers or mixed flow blowers have been used as blowers for outdoor units from the viewpoint of large air volume and low noise. However, in order to promote further energy saving of the air conditioner, it is necessary to reduce the input of the blower of the outdoor unit, and it is required to further improve the blowing efficiency of the blower while maintaining a predetermined air volume as the outdoor unit. ing.

この様な背景をもとに空調用送風機の従来技術として、特許文献１に記載されたものがある。   As a prior art of an air-conditioning blower based on such a background, there is one described in Patent Document 1.

図７から図１１は、特許文献１に記載の空気調和機用室外ユニット及び搭載された空調用送風機羽根車を示すものである。   FIGS. 7 to 11 show an outdoor unit for an air conditioner described in Patent Document 1 and an air blower impeller mounted for air conditioning.

まず、図７において、室外機ユニット１１１は、ユニット本体１１２内に、平面Ｌ形状の熱交換器１１３と、ファンモータ１５０と、空調用送風機羽根車１５１と、ケーシング１５９からなる室外送風回路１１５と、圧縮機１１６と、四方弁、インバータ等（図示せず）を収容している。そして、室外送風回路１１５と圧縮機１１６との間を仕切板１１７により仕切っている。   First, in FIG. 7, the outdoor unit 111 includes a planar L-shaped heat exchanger 113, a fan motor 150, an air-conditioning blower impeller 151, and an outdoor blower circuit 115 including a casing 159 in a unit main body 112. The compressor 116, a four-way valve, an inverter, etc. (not shown) are accommodated. The outdoor blower circuit 115 and the compressor 116 are partitioned by a partition plate 117.

また、図８、図９に示すように、空調用送風機羽根車１５１は、回転軸中心にモ−タ１５０のシャフトを固定して断面が略円錐台状のハブ１５３を中心に薄断面の翼１５２を放射状に３枚設けて構成してある。そして、図８のように、翼１５２外周端の回転軌跡に沿うような適切なケ−シング１５９にて翼１５２の吐出側を囲うようにしている。   As shown in FIGS. 8 and 9, the air-conditioning fan impeller 151 is a blade having a thin cross section centered on a hub 153 having a substantially frustoconical cross section with the shaft of the motor 150 fixed to the center of the rotation axis. Three of 152 are provided radially. As shown in FIG. 8, the discharge side of the blade 152 is surrounded by an appropriate casing 159 that follows the rotation locus of the outer peripheral end of the blade 152.

ここで、図１０（ａ）、（ｂ）および（ｃ）に示すように、翼１５２の半径方向の断面形状を、中点線Ｅ−Ｅ付近より外周端１５６側では風上側に対して凹形状の曲線で、中点線Ｅ−Ｅ付近よりハブ１５３側は風上側に対して凸形状の曲線にて構成している。かつ、中点線Ｅ−Ｅ付近より外周端１５６側では風上側に対して凹形状である曲線の曲率半径が、翼１５２の前縁１５４側の半径方向断面部、翼１５２の弦長の中央付近の半径方向断面部、翼１５２の後縁１５５付近の半径方向断面部の順に、その値が大きくなるようにして構成してある。すなわち、翼１５２の前縁１５４側の半径方向断面部の曲率半径をｒ１、翼１５２の弦長の中央付近の半径方向断面部の曲率半径をｒ２、翼１５２の後縁１５５付近の半径方向断面部の曲率半径をｒ３としたとき、曲率半径の大きさの関係がｒ１＜ｒ２＜ｒ３となるように構成している。   Here, as shown in FIGS. 10A, 10 </ b> B, and 10 </ b> C, the radial cross-sectional shape of the wing 152 is concave with respect to the windward side on the outer peripheral end 156 side near the middle dotted line EE. From the vicinity of the middle dotted line EE, the hub 153 side is configured by a convex curve with respect to the windward side. Further, the radius of curvature of the curve which is concave with respect to the windward side on the outer peripheral end 156 side from the vicinity of the middle dotted line EE is a radial section on the leading edge 154 side of the wing 152, near the center of the chord length of the wing 152. In the order of the radial cross section of the wing 152 and the radial cross section near the trailing edge 155 of the wing 152. That is, the radius of curvature of the radial cross section on the leading edge 154 side of the blade 152 is r1, the radius of curvature of the radial cross section near the center of the chord length of the blade 152 is r2, and the radial cross section near the trailing edge 155 of the blade 152. When the radius of curvature of the portion is r3, the relationship of the magnitude of the radius of curvature is r1 <r2 <r3.

次に、まず、特許文献１に記載の空気調和機用室外ユニットの作用を説明する。   Next, the operation of the outdoor unit for an air conditioner described in Patent Document 1 will be described first.

まず、ファンモータ１５０により回転軸を介して空調用送風機羽根車１５１が回転駆動し、熱交換器１１３を介して室外空気を、空調用送風機羽根車１５１内に導く。その際、
翼１５２と、翼１５２の周囲に設けられたケーシング１５９により、動圧と静圧が付加され送風作用を成す。また、熱交換器１１３を通過する際に、圧縮機１１６の作動により熱交換器１１３の管内を流動する冷媒と熱交換する。 First, the fan motor 150 rotates and drives the air-conditioning fan impeller 151 through the rotating shaft, and guides outdoor air into the air-conditioning fan impeller 151 through the heat exchanger 113. that time,
The blades 152 and the casing 159 provided around the blades 152 add dynamic pressure and static pressure to produce a blowing action. Further, when passing through the heat exchanger 113, the compressor 116 operates to exchange heat with the refrigerant flowing in the pipe of the heat exchanger 113.

そして、上記の構成によって、風下側である翼１５２の圧力面１５８から風上側である負圧面１５７に向かい、翼外周端１５６とケーシング１５９間を通過する洩れ流れが生じる。これにより翼１５２の翼外周端１５６の負圧面１５７側に発生する翼端渦の生成を翼１５２自体の上記の凹状の曲線部で促進させて低騒音化が図れる。   With the above-described configuration, a leakage flow is generated from the pressure surface 158 of the blade 152 on the leeward side toward the negative pressure surface 157 on the windward side and passing between the blade outer peripheral end 156 and the casing 159. As a result, the generation of the blade tip vortex generated on the suction surface 157 side of the blade outer peripheral end 156 of the blade 152 is promoted by the concave curved portion of the blade 152 itself, thereby reducing noise.

また、翼端渦は、翼外周端１５６の負圧面１５７に発生し、翼１５２の弦長の中心付近より後縁１５５よりの位置で、翼１５２の負圧面１５７から剥離する傾向にある。しかし、凹形状である曲線の曲率半径が、翼１５２の前縁１５４側の半径方向断面部、翼１５２の弦長の中心付近の半径方向断面部、翼１５２の後縁１５５付近の半径方向断面部の順に、その値が大きくなるようにして、翼１５２の後縁１５５付近の半径方向断面部側の曲率半径ｒ３を充分に大きくしているので、後縁付近の凹部は、この翼端渦の剥離現象が阻害されることはない。したがって、渦剥離による損失が減少して更なる効率の向上が図れる。   Further, the blade tip vortex is generated on the suction surface 157 of the blade outer peripheral end 156 and tends to be separated from the suction surface 157 of the blade 152 at a position near the trailing edge 155 from near the center of the chord length of the blade 152. However, the curved radius of curvature of the concave shape is such that the radial cross section on the leading edge 154 side of the wing 152, the radial cross section near the center of the chord length of the wing 152, and the radial cross section near the trailing edge 155 of the wing 152. Since the radius of curvature r3 on the radial cross-section side near the trailing edge 155 of the blade 152 is made sufficiently large so that the value becomes larger in the order of the portion, the recess near the trailing edge has the tip vortex. The peeling phenomenon is not hindered. Therefore, the loss due to vortex separation is reduced and the efficiency can be further improved.

特開２００３−１４８３９５号公報JP 2003-148395 A

しかしながら、上記の特許文献１に記載の従来の構成では、図１１で示すように、ケーシング１５９に囲われていない翼１５２の外周端１５６の負圧面側に翼端渦が発生する際、翼外周端１５６が仕切板１１７や、室外送風回路１１５の熱交換器１１３の内面側に近接するため、翼端渦が仕切版１１７に接触し、渦の形が崩れ、室外送風回路１１５内のケーシング１５９に囲われていない翼外周端１５６付近では、翼端渦が安定せず、翼１５２外周端側の流れが乱れ、流動損失の増加と、乱流騒音を高める要因となっている。   However, in the conventional configuration described in Patent Document 1 described above, when a blade tip vortex is generated on the suction surface side of the outer peripheral end 156 of the blade 152 not surrounded by the casing 159 as shown in FIG. Since the end 156 is close to the partition plate 117 and the inner surface side of the heat exchanger 113 of the outdoor fan circuit 115, the blade tip vortex contacts the partition plate 117, and the shape of the vortex breaks down, and the casing 159 in the outdoor fan circuit 115 In the vicinity of the blade outer periphery 156 not surrounded by the blade wing, the blade tip vortex is not stable, the flow on the blade 152 outer periphery end side is disturbed, which increases the flow loss and increases the turbulent noise.

また、安定しない翼端渦は、翼１５２の吸込側から吐出側に向かう流れとともにケーシング１５９に吸い込まれ、このケーシング１５９の内壁に接触して、不安定な翼端渦となる。   Further, the unstable blade tip vortex is sucked into the casing 159 together with the flow from the suction side to the discharge side of the blade 152, and comes into contact with the inner wall of the casing 159 to become an unstable blade tip vortex.

また、翼外周端１５６とケーシング１５９間を通過する洩れ流れにより、翼１５２の翼外周端部１５６の負圧面１５７側の翼端渦は生成を続けながら翼１５２の吐出側まで進行するが、翼１５２の外周側の凹形状の負圧面側に向けての湾曲により漏れ流れが大きくなり、ケーシング１５９に囲われた吐出側において翼外周端部１５６から翼１５２の外周端部側にかけて翼端渦の不安定さを助長し、大きな乱れエネルギが放出され、流動損失の増加と、乱流騒音が高まるという問題点を有していた。   Further, the leakage flow passing between the blade outer peripheral end 156 and the casing 159 causes the blade tip vortex on the suction surface 157 side of the blade outer peripheral end 156 of the blade 152 to proceed to the discharge side of the blade 152 while continuing to generate. The leakage flow increases due to the curve toward the negative suction surface side of the concave shape on the outer peripheral side of 152, and the vortex tip vortex from the blade outer peripheral end 156 to the outer peripheral end side of the blade 152 on the discharge side surrounded by the casing 159. Instability was promoted, and large turbulent energy was released, resulting in increased flow loss and increased turbulent noise.

本発明は、上記従来の課題を解決するもので、室外送風回路内において、ケーシングに囲われていない翼外周端部での翼端渦の仕切版、熱交換器の内面の接触を抑え翼端渦を安定化させ、さらに、翼外周端とケーシング間を通過する洩れ流れを抑制かつ制御し、翼端渦の生成を安定化させ、流動損失と乱流騒音の増加を抑える送風機とそれを用いた室外ユニットを提供するものである。   The present invention solves the above-mentioned conventional problems, and suppresses contact of the blade vortex partition plate at the outer peripheral edge of the blade not surrounded by the casing and the inner surface of the heat exchanger in the outdoor fan circuit. Use a blower that stabilizes the vortex, suppresses and controls the leakage flow that passes between the blade outer periphery and the casing, stabilizes the generation of the blade tip vortex, and suppresses increase in flow loss and turbulent noise. The outdoor unit was provided.

上記従来の課題を解決するために、本発明の送風機は、モータに連結されるハブの周囲
に配設された複数の羽根を有していて、回転によって空気流を形成する羽根車と、前記羽根車によって形成される空気流の下流側に配設され、前記複数の羽根の空気流下流側の一部を囲むオリフィスとで構成され、前記複数の羽根の外周端部は前記羽根車の負圧面側に向けて湾曲するように形成され、かつ、前記オリフィスに囲まれていない前記複数の羽根の外周端部の圧力面側には肉厚が外周に向けて薄くなるように形成される第１面取りを設けるとともに、前記オリフィスに囲まれた前記複数の羽根の外周端部の一部には肉厚部を設け、前記肉厚部は、前記オリフィスに囲まれていない前記複数の羽根の外周端部の肉厚よりも厚くなるように形成されている。 In order to solve the above-described conventional problems, a blower of the present invention has a plurality of blades disposed around a hub connected to a motor and forms an air flow by rotation, An orifice disposed downstream of the airflow formed by the impeller and surrounding a portion of the airflow downstream of the plurality of blades, and an outer peripheral end portion of the plurality of blades is a negative of the impeller A first wall is formed so as to bend toward the pressure surface side, and is formed on the pressure surface side of the outer peripheral end portions of the plurality of blades not surrounded by the orifice so that the thickness decreases toward the outer periphery. A chamfer is provided, and a thick portion is provided at a part of an outer peripheral end portion of the plurality of blades surrounded by the orifice, and the thick portion is an outer periphery of the plurality of blades not surrounded by the orifice. It is formed to be thicker than the wall thickness at the end. There.

かかる構成とすることにより、オリフィスに囲われていない羽根の吸込み側の外周端部側では、羽根の外周端部で圧力面側から負圧面側に小さくかつ滑らかに気流が回り込み、オリフィスに囲われていない羽根の吸込み側の外周端部の負圧面側で生成される翼端渦が小さくかつ安定化し、羽根外周側の流れが乱れず、流動損失と乱流騒音の増加を抑制する。   By adopting such a configuration, on the outer peripheral end portion on the suction side of the blade that is not surrounded by the orifice, the airflow smoothly flows from the pressure surface side to the suction surface side at the outer peripheral end portion of the blade, and is surrounded by the orifice. The blade tip vortex generated on the suction surface side of the outer peripheral end of the non-blade suction side is small and stabilized, the flow on the blade outer peripheral side is not disturbed, and the increase in flow loss and turbulent noise is suppressed.

さらに、安定した翼端渦は、羽根の吸込側から吐出側に向かう流れとともにオリフィスに吸い込まれるが、安定化しているので、オリフィスに囲われた吐出側においても羽根外周端部から羽根の外周側にかけ流れを安定させ、大きな乱れエネルギが放出されず、吐出側での流動損失と乱流騒音の高まりを小さく抑える。   Further, the stable blade tip vortex is sucked into the orifice along with the flow from the suction side to the discharge side of the blade, but since it is stabilized, the outer peripheral side of the blade from the outer peripheral edge of the blade is also stabilized on the discharge side surrounded by the orifice. The flow is stabilized and large turbulent energy is not released, and the flow loss and turbulent noise increase on the discharge side are kept small.

また、オリフィスに囲まれた羽根の吐出側の外周端部側では、オリフィスに囲まれていない前記複数の羽根の外周端部の肉厚よりも厚くなる肉厚部により、外周端とオリフィスの間を通過する洩れ流れにより、羽根の外周端の負圧面側の翼端渦は生成を続けながら羽根の吐出側まで進行するが、漏れ流れが抑制され、オリフィスに囲われた吐出側において羽根外周端部から羽根の外周側にかけて翼端渦を安定させ、吐出側での大きな流動損失と乱流騒音の高まりを小さく抑える。   In addition, on the outer peripheral end side of the discharge side of the blade surrounded by the orifice, a thicker portion that is thicker than the outer peripheral end portion of the plurality of blades not surrounded by the orifice causes a gap between the outer peripheral end and the orifice. The blade tip vortex on the suction surface side of the outer peripheral edge of the blade advances to the discharge side of the blade while continuing to generate due to the leakage flow that passes through the blade, but the leakage flow is suppressed, and the blade outer edge on the discharge side surrounded by the orifice The blade tip vortex is stabilized from the part to the outer peripheral side of the blade, and large flow loss and increase in turbulent noise on the discharge side are suppressed.

本発明の送風機は、オリフィスに囲われていない吸込側の羽根外周端部での翼端渦を安定化させ、さらに、オリフィスに囲われた吐出側の羽根外周端とオリフィス間を通過する洩れ流れを抑制かつ制御し、翼端渦の生成を安定化させ、流動損失と乱流騒音の増加を小さく抑えることができる。   The blower of the present invention stabilizes the blade tip vortex at the suction blade outer peripheral end not surrounded by the orifice, and further leaks between the discharge peripheral blade outer periphery surrounded by the orifice and the orifice. Can be suppressed and controlled, the generation of the tip vortex can be stabilized, and the increase in flow loss and turbulent noise can be suppressed to a small level.

本発明の実施の形態１における空気調和機の室外ユニットの断面図Sectional drawing of the outdoor unit of the air conditioner in Embodiment 1 of this invention 同実施の形態における送風機の断面図Sectional drawing of the air blower in the same embodiment 同実施の形態における送風機の平面図Top view of the blower in the same embodiment （ａ）図３のＯ−Ａ断面における羽根外周要部拡大図（ｂ）図３のＯ−Ｂ断面における羽根外周要部拡大図(A) Enlarged view of essential part of blade outer periphery in section OA in FIG. 3 (b) Enlarged view of essential part of blade periphery in section OB in FIG. （ａ）実施の形態２における図３のＯ−Ａ断面における羽根外周要部拡大図（ｂ）同実施の形態における図３のＯ−Ｂ断面における羽根外周要部拡大図(A) Enlarged view of essential part of blade outer periphery in section OA in FIG. 3 in Embodiment 2 (b) Enlarged view of essential part of blade periphery in section OB in FIG. 3 in the embodiment （ａ）実施の形態３における図３のＯ−Ａ断面における羽根外周要部拡大図（ｂ）同実施の形態における図３のＯ−Ｂ断面における羽根外周要部拡大図(A) Enlarged view of essential part of blade outer periphery in section OA in FIG. 3 in Embodiment 3 (b) Enlarged view of essential part of blade periphery in section OB in FIG. 3 in the embodiment 従来の空気調和機の室外ユニットの断面図Sectional view of an outdoor unit of a conventional air conditioner 従来の送風機の子午断面図A meridional section of a conventional blower 従来の送風機の正面図Front view of conventional blower （ａ）図９のＡ−Ｏ断面図（同羽根車の前縁側半径方向断面図）（ｂ）図９のＢ−Ｏ断面図（同羽根車の翼の弦長の中央付近の半径方向断面図）（ｃ）図９のＣ−Ｏ断面図（同羽根車の後縁側半径方向断面図）(A) AO sectional view of FIG. 9 (radial sectional view in front edge side of the impeller) (b) BO sectional view of FIG. 9 (radial section in the vicinity of the center of the chord length of the blade of the impeller) (C) CO sectional view of FIG. 9 (radial sectional view of the rear edge side of the impeller) 従来の羽根外周要部拡大図Enlarged view of the main part of a conventional blade outer periphery

第１の発明の送風機は、モータに連結されるハブの周囲に配設された複数の羽根を有していて、回転によって空気流を形成する羽根車と、前記羽根車によって形成される空気流の下流側に配設され、前記複数の羽根の空気流下流側の一部を囲むオリフィスとで構成され、前記複数の羽根の外周端部は前記羽根車の負圧面側に向けて湾曲するように形成され、かつ、前記オリフィスに囲まれていない前記複数の羽根の外周端部の圧力面側には肉厚が外周に向けて薄くなるように形成される第１面取りを設けるとともに、前記オリフィスに囲まれた前記複数の羽根の外周端部の一部には肉厚部を設け、前記肉厚部は、前記オリフィスに囲まれていない前記複数の羽根の外周端部の肉厚よりも厚くなるように形成された構成としてある。   An air blower according to a first aspect of the present invention has a plurality of blades disposed around a hub connected to a motor, and forms an air flow by rotation, and an air flow formed by the impeller And an orifice that surrounds a portion of the plurality of blades on the downstream side of the air flow, and an outer peripheral end portion of the plurality of blades is curved toward the suction surface side of the impeller. And a first chamfer formed on the pressure surface side of the outer peripheral ends of the plurality of blades that are not surrounded by the orifice so that the thickness decreases toward the outer periphery, and the orifice A thick portion is provided in a part of the outer peripheral end portions of the plurality of blades surrounded by the wall, and the thick portion is thicker than the thickness of the outer peripheral end portions of the plurality of blades not surrounded by the orifice. It is as the structure formed so that it might become.

かかる構成により、オリフィスに囲われていない羽根の吸込み側の外周端部側では、羽根の外周端部で圧力面側から負圧面側に小さくかつ滑らかに気流が回り込み、オリフィスに囲われていない羽根の吸込み側の外周端部の負圧面側で生成される翼端渦が小さくかつ安定化し、羽根外周側の流れが乱れず、流動損失と乱流騒音の増加を抑制する。   With this configuration, on the outer peripheral end portion on the suction side of the blade not surrounded by the orifice, a small and smooth air flow from the pressure surface side to the suction surface side at the outer peripheral end portion of the blade, and the blade not surrounded by the orifice The blade tip vortex generated on the suction surface side of the outer peripheral end of the suction side is small and stabilized, the flow on the blade outer peripheral side is not disturbed, and the increase in flow loss and turbulent noise is suppressed.

さらに、安定した翼端渦は、羽根の吸込側から吐出側に向かう流れとともにオリフィスに吸い込まれるが、安定化しているので、オリフィスに囲われた吐出側においても羽根外周端部から羽根の外周側にかけ流れを安定させ、大きな乱れエネルギーが放出されず、吐出側での流動損失と乱流騒音の高まりを小さく抑える。   Further, the stable blade tip vortex is sucked into the orifice along with the flow from the suction side to the discharge side of the blade, but since it is stabilized, the outer peripheral side of the blade from the outer peripheral edge of the blade is also stabilized on the discharge side surrounded by the orifice. The flow is stabilized and large turbulent energy is not released, and the flow loss and turbulent noise on the discharge side are kept small.

また、オリフィスに囲まれた羽根の吐出側の外周端部側では、オリフィスに囲まれていない前記複数の羽根の外周端部の肉厚よりも厚くなる肉厚部により、外周端とオリフィスの間を通過する洩れ流れにより、羽根の外周端の負圧面側の翼端渦は生成を続けながら羽根の吐出側まで進行するが、漏れ流れが抑制され、オリフィスに囲われた吐出側において羽根外周端部から羽根の外周側にかけて翼端渦を安定させ、吐出側での大きな流動損失と乱流騒音の高まりを小さく抑える。   In addition, on the outer peripheral end side of the discharge side of the blade surrounded by the orifice, a thicker portion that is thicker than the outer peripheral end portion of the plurality of blades not surrounded by the orifice causes a gap between the outer peripheral end and the orifice. The blade tip vortex on the suction surface side of the outer peripheral edge of the blade advances to the discharge side of the blade while continuing to generate due to the leakage flow that passes through the blade, but the leakage flow is suppressed, and the blade outer edge on the discharge side surrounded by the orifice The blade tip vortex is stabilized from the part to the outer peripheral side of the blade, and large flow loss and increase in turbulent noise on the discharge side are suppressed.

第２の発明は、第１の発明において、前記肉厚部が前記複数の羽根の外周端部に向けて厚くなるように形成されたものである。   According to a second invention, in the first invention, the thick portion is formed so as to become thicker toward an outer peripheral end portion of the plurality of blades.

かかる構成とすることにより、オリフィスに囲まれた羽根の吐出側の外周端部側では、外周端とオリフィスの間を通過する洩れ流れがさらに抑制されることで、オリフィスに囲われた吐出側において羽根外周端部から羽根の外周側にかけて翼端渦を小さくかつ安定させることができる。   By adopting such a configuration, the leakage flow passing between the outer peripheral end and the orifice is further suppressed at the outer peripheral end portion on the discharge side of the blade surrounded by the orifice, so that the discharge side surrounded by the orifice The blade tip vortex can be made small and stable from the blade outer periphery to the blade outer periphery.

第３の発明は、第１または第２の発明において、前記オリフィスに囲まれた前記複数の羽根の外周端部の圧力面側に肉厚が外周に向けて薄くなるように形成される第２面取りを有し、肉厚部は、前記オリフィスに囲まれた前記複数の羽根の外周端部の負圧面側に配設され、羽根車の半径方向断面の形状が前記複数の羽根の負圧面に対して凸となる凸部によって形成されたものである。   According to a third invention, in the first or second invention, the second invention is formed such that the thickness decreases toward the outer periphery on the pressure surface side of the outer peripheral end portions of the plurality of blades surrounded by the orifice. A chamfer is provided, and the thick portion is disposed on the suction surface side of the outer peripheral ends of the plurality of blades surrounded by the orifice, and the shape of the radial cross section of the impeller is formed on the suction surface of the plurality of blades. On the other hand, it is formed by convex portions that are convex.

かかる構成にすることで、オリフィスに囲まれた羽根の吐出側の外周端部側でも、羽根の外周端部の圧力面側に配設され、羽根の肉厚が外周に向けて薄くなるように形成される第２面取りにより、圧力面側から負圧面側に滑らかに乱れることなく気流が小さく回り込み、負圧面に対して凸となる凸部により、漏れ流れが抑制され、漏れ流れによる翼端渦が小さく、安定度が増すことができる。   With this configuration, even on the outer peripheral end side of the discharge side of the blade surrounded by the orifice, it is disposed on the pressure surface side of the outer peripheral end portion of the blade so that the thickness of the blade becomes thinner toward the outer periphery. Due to the second chamfering that is formed, the airflow circulates from the pressure surface side to the suction surface side smoothly without being disturbed smoothly, and the leakage flow is suppressed by the convex portion that is convex with respect to the suction surface. Is small and the stability can be increased.

第４の発明は、第３の発明において前記第２面取りの表面と前記凸部の表面とが滑らか
につながれているものである。 According to a fourth aspect, in the third aspect, the surface of the second chamfer and the surface of the convex portion are smoothly connected.

かかる構成により、オリフィスに囲まれた羽根の吐出側の外周端部で、圧力面側から負圧面側に回り込む曲率が最も小さくなる部分で滑らかな略曲線状の形状に沿って漏れ流れが回り込むことができ、漏れ流れによる翼端渦の安定度を極大とすることができる。   With such a configuration, at the outer peripheral end of the blade surrounded by the orifice, the leakage flow circulates along a smooth, substantially curved shape at the portion where the curvature that wraps around from the pressure surface side to the suction surface side becomes the smallest. And the stability of the tip vortex due to leakage flow can be maximized.

第５の発明は、第１または第２の発明において、前記肉厚部は、前記オリフィスに囲まれた前記複数の羽根の外周端部の圧力面側に配設され、前記羽根車の半径方向断面の形状が前記複数の羽根の圧力面に対して凸となる凸部によって形成されるものである。   According to a fifth invention, in the first or second invention, the thick portion is disposed on a pressure surface side of an outer peripheral end portion of the plurality of blades surrounded by the orifice, and the radial direction of the impeller The cross-sectional shape is formed by convex portions that are convex with respect to the pressure surfaces of the plurality of blades.

かかる構成により、オリフィスに囲まれた羽根の吐出側の外周端部で、外周端とオリフィスの間を通過する洩れ流れを小さく抑制されると共に、外周端部の圧力面側の漏れ流れの一部をそのまま圧力面側より羽根車の吹き出し側に吐出させることができ、送風機の空力性能を向上させることができる。   With this configuration, at the outer peripheral end of the blade surrounded by the orifice, the leakage flow passing between the outer peripheral end and the orifice is suppressed to be small, and a part of the leakage flow on the pressure surface side of the outer peripheral end. Can be discharged from the pressure surface side to the blowout side of the impeller as it is, and the aerodynamic performance of the blower can be improved.

第６の発明は、第１または第２の発明において、前記肉厚部は、前記オリフィスに囲まれた前記複数の羽根の外周端部の負圧面側に配設され、前記羽根車の半径方向断面の形状が前記複数の羽根の負圧面に対して凸となる第一の凸部と、前記オリフィスに囲まれた前記複数の羽根の外周端部の圧力面側に配設され、前記羽根車の半径方向断面の形状が前記複数の羽根の圧力面に対して凸となる第二の凸部とによって形成され、前記第一の凸部の表面と前記第二の凸部の表面が滑らかにつながれているものである。   In a sixth aspect based on the first or second aspect, the thick portion is disposed on a suction surface side of an outer peripheral end portion of the plurality of blades surrounded by the orifice, and the radial direction of the impeller A first convex portion whose cross-sectional shape is convex with respect to the suction surfaces of the plurality of blades, and a pressure surface side of an outer peripheral end portion of the plurality of blades surrounded by the orifice; The shape of the radial cross section is formed by a second convex portion that is convex with respect to the pressure surfaces of the plurality of blades, and the surface of the first convex portion and the surface of the second convex portion are smooth It is connected.

かかる構成により、オリフィスに囲まれた羽根の吐出側の外周端部側で、負圧面側の第一の凸部と圧力面側の第二の凸部により、外周端とオリフィスの間を通過する洩れ流れが極力抑制されると共に、圧力面側の第二の凸部により外周端部の圧力面側の漏れ流れの一部をそのまま圧力面側から羽根車の吹き出し側に吐出させることができ、漏れ損失を極力小さくし、翼端渦を小さくかつ安定させかつ、送風機の空力特性を向上させることが両立できる。   With this configuration, the first convex portion on the suction surface side and the second convex portion on the pressure surface side pass between the outer peripheral end and the orifice on the outer peripheral end portion side on the discharge side of the blade surrounded by the orifice. The leakage flow is suppressed as much as possible, and a part of the leakage flow on the pressure surface side of the outer peripheral end portion can be directly discharged from the pressure surface side to the blowout side of the impeller by the second convex portion on the pressure surface side, It is possible to reduce leakage loss as much as possible, to reduce and stabilize the blade tip vortex, and to improve the aerodynamic characteristics of the blower.

第７の発明は、筐体と、前記筐体内に設けられた圧縮機と、筐体内の吸込み側開口部に設けられた熱交換器と、前記筐体の熱交換器の空気吸込側と反対の面に設けられた第１から第６の発明のいずれかに記載の送風機と、前記熱交換器と前記送風機が配置された風路と、前記風路と前記圧縮機との間を仕切る仕切板とを有する室外ユニットとしてある。   The seventh invention is a housing, a compressor provided in the housing, a heat exchanger provided in a suction side opening in the housing, and opposite to an air suction side of the heat exchanger of the housing. The air blower according to any one of the first to sixth inventions provided on the surface, an air passage in which the heat exchanger and the air blower are disposed, and a partition that partitions the air passage and the compressor As an outdoor unit having a plate.

かかる構成により、第１から第６の発明のいずれかの送風機を搭載することで、送風機のモータへの入力が少なく空力性能を高くすることができ、さらに送風機の送風騒音を抑制することができる。従って、ヒートポンプユニットとしての高い熱交換能力を発揮して、省エネルギーでかつ低騒音な室外ユニットを実現できるものである。   With such a configuration, by mounting the blower of any of the first to sixth inventions, it is possible to increase the aerodynamic performance with less input to the motor of the blower, and to further suppress the blowing noise of the blower. . Therefore, it is possible to realize an energy saving and low noise outdoor unit that exhibits high heat exchange capability as a heat pump unit.

以下、本発明の実施の形態について、図面を参照しながら説明する。なお、この実施の形態によってこの発明が限定されるものではない。   Hereinafter, embodiments of the present invention will be described with reference to the drawings. The present invention is not limited to the embodiments.

（実施の形態１）
図１は実施の形態１における空気調和機の室外ユニットの断面図であり、図２は同実施の形態における送風機の断面図であり、図３は同実施の形態における送風機の平面図であり、図４（ａ）は図３のＯ−Ａ断面における羽根外周要部拡大図であり、図４（ｂ）は図３のＯ−Ｂ断面における羽根外周要部拡大図である。 (Embodiment 1)
1 is a cross-sectional view of an outdoor unit of an air conditioner in Embodiment 1, FIG. 2 is a cross-sectional view of the blower in the same embodiment, FIG. 3 is a plan view of the blower in the same embodiment, 4A is an enlarged view of the main part of the blade outer periphery in the section OA in FIG. 3, and FIG. 4B is an enlarged view of the main part of the outer periphery of the blade in the section OB in FIG. 3.

図１において、室外ユニット１は、筐体２内に、平面がＬ形状の熱交換器３と、モータ４、羽根車５、オリフィス１４からなる送風機７と、圧縮機８と、四方弁、インバータ等
（図示せず）を収容している。そして、熱交換器３と、送風機７からなる風路９と圧縮機８との間を仕切板１０により仕切っている。 In FIG. 1, an outdoor unit 1 includes a heat exchanger 3 having an L-shaped plane, a blower 7 including a motor 4, an impeller 5, and an orifice 14, a compressor 8, a four-way valve, and an inverter. Etc. (not shown) are accommodated. A partition plate 10 partitions the heat exchanger 3 and the air path 9 including the blower 7 and the compressor 8.

また、図２、図３に示すように、羽根車５は、モータ４のシャフト１１に固定された略円筒状のハブ１２を中心にして薄肉翼状の羽根１３を放射状に２枚設けて構成している。そして、羽根１３の外周端部１３ｄの回転軌跡に沿うような適切なオリフィス１４にて羽根１３の吐出側１３ｂを囲うようにしている。   As shown in FIGS. 2 and 3, the impeller 5 is configured by providing two thin wing-like blades 13 radially around a substantially cylindrical hub 12 fixed to the shaft 11 of the motor 4. ing. And the discharge side 13b of the blade | wing 13 is enclosed by the appropriate orifice 14 which follows the rotation locus | trajectory of the outer peripheral edge part 13d of the blade | wing 13. FIG.

ここで、図４（ａ）で示すように、羽根１３のオリフィス１４に囲まれていない吸込み側１３ａの外周端部１３ｄを負圧面側１３ｄ２に湾曲させ、また、羽根１３の外周端部１３ｄの圧力面側１３ｄ１に外周に向けて薄くなる第１面取り１５を設けている。   Here, as shown in FIG. 4A, the outer peripheral end 13d of the suction side 13a not surrounded by the orifice 14 of the blade 13 is curved to the suction surface side 13d2, and the outer peripheral end 13d of the blade 13 is A first chamfer 15 that is thinner toward the outer periphery is provided on the pressure surface side 13d1.

さらに、図４（ｂ）で示すように、羽根１３のオリフィス１４に囲まれている吐出側１３ｂの羽根１３の外周端部１３ｅの圧力面側１３ｅ１に配設され、外周に向けて薄くなるように形成される第２面取り１６を有し、羽根１３の外周端部１３ｅの負圧面側１３ｅ２に配設され、羽根車５の半径方向断面の形状が羽根１３の負圧面側１３ｅ２に対して凸となる凸部１７を設けている。   Further, as shown in FIG. 4 (b), it is disposed on the pressure surface side 13e1 of the outer peripheral end portion 13e of the vane 13 on the discharge side 13b surrounded by the orifice 14 of the vane 13 so as to become thinner toward the outer periphery. And is disposed on the suction surface side 13e2 of the outer peripheral end portion 13e of the blade 13, and the shape of the radial section of the impeller 5 is convex with respect to the suction surface side 13e2 of the blade 13. Convex portion 17 is provided.

そして、さらに、第２面取り１６の表面と、凸部１７の表面とが滑らかにつながれているものである。   Further, the surface of the second chamfer 16 and the surface of the convex portion 17 are smoothly connected.

以上のように構成された室外ユニット及び送風機について、以下その動作、作用を説明する。   About the outdoor unit and air blower comprised as mentioned above, the operation | movement and an effect | action are demonstrated below.

まず、モータ４によりシャフト１１を介して羽根車５が回転駆動して、熱交換器３を介して室外空気を、羽根車５内に導く。その際、複数の羽根１３と、羽根１３の周囲に設けられたオリフィス１４により、動圧と静圧が付加され送風作用を成す。また、熱交換器３を通過する際に、圧縮機８の作動により熱交換器３の管内を流動する冷媒と熱交換する。   First, the impeller 5 is rotationally driven by the motor 4 via the shaft 11, and the outdoor air is guided into the impeller 5 via the heat exchanger 3. At that time, dynamic pressure and static pressure are applied by the plurality of blades 13 and the orifices 14 provided around the blades 13 to perform a blowing action. Further, when passing through the heat exchanger 3, heat exchange is performed with the refrigerant flowing in the pipe of the heat exchanger 3 by the operation of the compressor 8.

そして、オリフィス１４に囲われていない羽根１３の吸込み側１３ａの外周端部１３ｄ側では、羽根１３の外周端部１３ｄは羽根１３の負圧面側１３ｄ２に向けて湾曲し、羽根１３の外周端部１３ｄの圧力面側１３ｄ１の羽根１３の肉厚が外周に向けて薄くなるように形成されている第１面取り１５により、羽根１３の外周端部１３ｄで圧力面側１３ｄ１から負圧面側１３ｄ２に小さくかつ滑らかに気流が回り込み、オリフィス１４に囲われていない羽根１３の吸込み側１３ａの外周端部１３ｄの負圧面側１３ｄ２で生成される翼端渦が小さくかつ安定化し、羽根１３の外周端部１３ｄの流れが乱れず、流動損失と乱流騒音の増加を抑制する。   And on the outer peripheral end 13 d side of the suction side 13 a of the blade 13 not surrounded by the orifice 14, the outer peripheral end portion 13 d of the blade 13 curves toward the negative pressure surface side 13 d 2 of the blade 13, and the outer peripheral end portion of the blade 13. By the first chamfer 15 formed so that the thickness of the blade 13 on the pressure surface side 13d1 of the 13d decreases toward the outer periphery, the outer peripheral end portion 13d of the blade 13 decreases from the pressure surface side 13d1 to the negative pressure surface side 13d2. In addition, the airflow smoothly flows and the blade tip vortex generated on the suction surface side 13d2 of the outer peripheral end 13d of the suction side 13a of the blade 13 not surrounded by the orifice 14 is small and stabilized, and the outer peripheral end 13d of the blade 13 is stabilized. The flow of air is not disturbed, and the increase of flow loss and turbulent noise is suppressed.

さらに、安定した翼端渦は、羽根１３の吸込み側１３ａから吐出側１３ｂに向かう流れとともにオリフィス１４内に吸い込まれるが、安定化しているので、オリフィス１４に囲われた羽根１３の吐出側１３ｂにおいても羽根１３の外周端部１３ｄから羽根１３の外周端部１３ｄにかけ流れを安定させ、大きな乱れエネルギーが放出されず、羽根１３の吐出側１３ｂでの流動損失と乱流騒音の高まりを小さく抑える。   Further, the stable blade tip vortex is sucked into the orifice 14 together with the flow from the suction side 13a of the blade 13 toward the discharge side 13b. However, since it is stabilized, on the discharge side 13b of the blade 13 surrounded by the orifice 14 Also, the flow is stabilized from the outer peripheral end portion 13d of the blade 13 to the outer peripheral end portion 13d of the blade 13, large turbulent energy is not released, and the flow loss and the increase in turbulent noise on the discharge side 13b of the blade 13 are suppressed to a small level.

また、オリフィス１４に囲まれた羽根１３の吐出側１３ｂの外周端部１３ｅでも、羽根１３の外周端部１３ｅの圧力面側１３ｅ１に配設され、羽根１３の肉厚が外周に向けて薄くなるように形成される第２面取り１６から羽根１３の負圧面側１３ｅ２の凸部１７にかけ、圧力面側１３ｅ１から負圧面側１３ｅ２に気流が回り込む曲率が最も小さくなる部分で滑らかな略曲線状の形状に沿って漏れ流れが回り込むことができ、外周端部１３ｅの圧力面側１３ｅ１から負圧面側１３ｅ２に滑らかに乱れることなく気流が小さく回り込み、
負圧面側１３ｅ２に対して凸となる凸部１７により、漏れ流れが抑制され、漏れ流れによる翼端渦が小さく、安定度を極大とすることができる。 Also, the outer peripheral end 13e of the discharge side 13b of the blade 13 surrounded by the orifice 14 is disposed on the pressure surface side 13e1 of the outer peripheral end 13e of the blade 13, and the thickness of the blade 13 becomes thinner toward the outer periphery. From the second chamfer 16 formed as described above to the convex portion 17 on the suction surface side 13e2 of the blade 13, a smooth substantially curved shape is formed at a portion where the curvature of the airflow from the pressure surface side 13e1 to the suction surface side 13e2 is minimized. , And the airflow wraps around smoothly without being disturbed smoothly from the pressure surface side 13e1 of the outer peripheral end portion 13e to the suction surface side 13e2.
By the convex portion 17 that is convex with respect to the suction surface side 13e2, the leakage flow is suppressed, the tip vortex due to the leakage flow is small, and the stability can be maximized.

従ってこの送風機７は、モータ４への入力が少なく空力性能を高くすることができ、さらに送風機７の送風騒音を抑制することができ、例えばヒートポンプの室外機に組み込むことにより、ヒートポンプユニットとして高い熱交換能力を発揮して、省エネルギーでかつ低騒音な室外ユニット１を実現できるものである。   Therefore, this blower 7 has less input to the motor 4 and can improve the aerodynamic performance. Further, the blower 7 can suppress the blowing noise of the blower 7. For example, by incorporating it in the outdoor unit of the heat pump, the heat blower 7 has high heat. It is possible to realize the outdoor unit 1 which exhibits the exchange capability and is energy saving and low noise.

（実施の形態２）
図５（ａ）は実施の形態２における図３のＯ−Ａ断面の羽根外周要部拡大図であり、図５（ｂ）は同実施の形態における図３のＯ−Ｂ断面における羽根外周要部拡大図である。 (Embodiment 2)
FIG. 5A is an enlarged view of the main part of the blade outer periphery of the OA cross section of FIG. 3 in the second embodiment, and FIG. 5B is the main part of the blade outer periphery of the OB cross section of FIG. FIG.

なお、実施の形態１と同じ構成要件については同一の符号を付して説明を省略する。   Note that the same constituent elements as those of the first embodiment are denoted by the same reference numerals and description thereof is omitted.

図５（ｂ）で示すように，オリフィス１４に囲まれた羽根１３の外周端部１３ｆの圧力面側１３ｆ１に、羽根車５の半径方向断面の形状が外周端部１３ｆの圧力面側１３ｆ１に対して凸となる凸部１８を配設している。   As shown in FIG. 5B, the shape of the radial cross section of the impeller 5 on the pressure surface side 13f1 of the outer peripheral end portion 13f is the pressure surface side 13f1 of the outer peripheral end portion 13f of the blade 13 surrounded by the orifice 14. On the other hand, convex portions 18 that are convex are disposed.

以上のように構成された実施の形態２の室外ユニット１の特に送風機７の動作、作用を説明する。   The operation and action of the blower 7 in the outdoor unit 1 of the second embodiment configured as described above will be described.

オリフィス１４に囲まれた羽根１３の吐出側１３ｂの外周端部１３ｆで，圧力面側１３ｆ１に対して凸となる凸部１８により、外周端部１３ｆとオリフィス１４の間を通過する洩れ流れを小さく抑制されると共に、外周端部１３ｆの圧力面側１３ｆ１の漏れ流れの一部をそのまま圧力面側１３ｆ１より羽根車５の吹き出し側に吐出させることができ、送風機７の空力性能を向上させることができる。   At the outer peripheral end portion 13f on the discharge side 13b of the blade 13 surrounded by the orifice 14, the convex portion 18 that is convex with respect to the pressure surface side 13f1 reduces the leakage flow passing between the outer peripheral end portion 13f and the orifice 14. In addition to being suppressed, a part of the leakage flow on the pressure surface side 13f1 of the outer peripheral end portion 13f can be discharged as it is from the pressure surface side 13f1 to the blowout side of the impeller 5, and the aerodynamic performance of the blower 7 can be improved. it can.

（実施の形態３）
図６（ａ）は実施の形態３における図３のＯ−Ａ断面の羽根外周要部拡大図であり、図６（ｂ）は同実施の形態における図３のＯ−Ｂ断面における羽根外周要部拡大図である。 (Embodiment 3)
FIG. 6A is an enlarged view of the main part of the blade outer periphery of the OA cross section of FIG. 3 in Embodiment 3, and FIG. 6B is the main part of the blade outer periphery of the OB cross section of FIG. FIG.

なお、実施の形態１と同じ構成要件については同一の符号を付して説明を省略する。   Note that the same constituent elements as those of the first embodiment are denoted by the same reference numerals and description thereof is omitted.

図６（ｂ）で示すように、オリフィス１４に囲まれた羽根１３の外周端部１３ｇの負圧面側１３ｇ２には、羽根車５の半径方向断面の形状が外周端部１３ｇの負圧面側１３ｇ２に対して凸となる第一の凸部１９が配設され、オリフィス１４に囲まれた羽根１３の外周端部１３ｇの圧力面側１３ｇ１には、羽根車５の半径方向断面の形状が羽根１３の外周端部１３ｇの圧力面側１３ｇ１に対して凸となる第二の凸部２０を配設し、第一の凸部１９の表面と第二の凸部２０の表面が滑らかにつながれている。   As shown in FIG. 6B, the suction surface side 13g2 of the outer peripheral end portion 13g of the blade 13 surrounded by the orifice 14 has a shape in the radial cross section of the impeller 5 which is the negative pressure surface side 13g2 of the outer peripheral end portion 13g. Is formed on the pressure surface side 13 g 1 of the outer peripheral end 13 g of the blade 13 surrounded by the orifice 14, the shape of the impeller 5 in the radial direction is the blade 13. The second convex portion 20 that is convex with respect to the pressure surface side 13g1 of the outer peripheral end portion 13g is disposed, and the surface of the first convex portion 19 and the surface of the second convex portion 20 are smoothly connected. .

以上のように構成された実施の形態３の室外ユニット１の特に送風機７の動作、作用を説明する。   The operation and action of the blower 7 of the outdoor unit 1 of the third embodiment configured as described above will be described.

オリフィス１４に囲まれた羽根１３の吐出側１３ｂの外周端部１３ｇで、負圧面側１３ｇ２の第一の凸部１９と圧力面側１３ｇ１の第二の凸部２０により、外周端部１３ｇとオリフィス１４の間を通過する洩れ流れが極力抑制されると共に、圧力面側１３ｇ１の第二の凸部２０により、外周端部１３ｇの圧力面側１３ｇ１の漏れ流れの一部をそのまま圧力面側１３ｇ１から羽根車５の吹き出し側に吐出させることができ、漏れ損失を極力小さくし、翼端渦を小さくかつ安定させかつ、送風機７の空力特性を向上させることが両立できる。   At the outer peripheral end 13g on the discharge side 13b of the blade 13 surrounded by the orifice 14, the outer peripheral end 13g and the orifice are formed by the first convex portion 19 on the suction side 13g2 and the second convex portion 20 on the pressure side 13g1. 14 is suppressed as much as possible, and part of the leakage flow on the pressure surface side 13g1 of the outer peripheral end 13g is directly transferred from the pressure surface side 13g1 by the second convex portion 20 on the pressure surface side 13g1. It can be discharged to the blow-out side of the impeller 5, and it is possible to reduce leakage loss as much as possible, to make the blade tip vortex small and stable, and to improve the aerodynamic characteristics of the blower 7.

以上のように、本発明にかかる構成の送風機とそれを用いた室外ユニットは、オリフィスに囲われていない吸込側の羽根外周端部での翼端渦を安定化させ、さらに、オリフィスに囲われた吐出側の羽根外周端とオリフィス間を通過する洩れ流れを抑制かつ制御し、翼端渦の生成を安定化させ、流動損失と乱流騒音の増加を小さく抑えることができる。   As described above, the blower having the configuration according to the present invention and the outdoor unit using the same stabilize the blade tip vortex at the suction blade outer peripheral end not surrounded by the orifice, and are further surrounded by the orifice. Further, the leakage flow passing between the outer peripheral edge of the discharge-side blade and the orifice can be suppressed and controlled, the generation of the blade tip vortex can be stabilized, and the increase in flow loss and turbulent noise can be suppressed to a small level.

従って、かかる送風機を用いた室外ユニットの送風効率の向上とヒートポンプユニットとしての高い熱交換能力を両立でき、さらに低騒音化が可能となるので、家庭用、業務用等エアコンの空調機器、家庭用冷凍冷蔵庫や自動販売機等の冷凍冷蔵機器、給湯機等のヒートポンプ機器、さらに熱電子部品を有する電子機器のみならず、ＡＶ機器、廃熱回収機器などの用途にも適用できる。   Therefore, it is possible to achieve both the improvement of the blowing efficiency of the outdoor unit using such a blower and the high heat exchange capability as a heat pump unit, and further noise reduction. The present invention can be applied not only to freezer / refrigeration equipment such as refrigerators and vending machines, heat pump equipment such as water heaters, and electronic equipment having thermoelectric components, but also to AV equipment and waste heat recovery equipment.

１ 室外ユニット
２ 筐体
３ 熱交換器
４ モータ
５ 羽根車
７ 送風機
８ 圧縮機
９ 風路
１０ 仕切板
１２ ハブ
１３ 羽根
１３ａ 吸込み側
１３ｂ 吐出側
１３ｄ、１３ｅ、１３ｆ、１３ｇ 外周端部（湾曲部）
１３ｄ１、１３ｅ１、１３ｆ１、１３ｇ１ 圧力面側
１３ｄ２、１３ｅ２、１３ｆ２、１３ｇ２ 負圧面側
１４ オリフィス
１５ 第１面取り（圧力面側）
１６ 第２面取り（圧力面側）
１７ 凸部（負圧面側）
１８ 凸部（圧力面側）
１９ 第一の凸部（負圧面側）
２０ 第二の凸部（圧力面側） DESCRIPTION OF SYMBOLS 1 Outdoor unit 2 Case 3 Heat exchanger 4 Motor 5 Impeller 7 Blower 8 Compressor 9 Air passage 10 Partition plate 12 Hub 13 Blade 13a Suction side 13b Discharge side 13d, 13e, 13f, 13g Outer peripheral end (curved part)
13d1, 13e1, 13f1, 13g1 Pressure side 13d2, 13e2, 13f2, 13g2 Negative pressure side 14 Orifice 15 First chamfer (pressure side)
16 Second chamfer (pressure side)
17 Convex (suction side)
18 Convex (pressure side)
19 First convex part (vacuum surface side)
20 Second convex part (pressure face side)

Claims (7)

モータと、モータに連結されるハブ、ハブの周囲に配設された複数の羽根を有していて、回転によって空気流を形成する羽根車と、前記羽根車によって形成される空気流の下流側に配設され、前記複数の羽根の空気流下流側の一部を囲むオリフィスとで構成され、前記複数の羽根の外周端部は前記羽根車の負圧面側に向けて湾曲するように形成され、かつ、前記オリフィスに囲まれていない前記複数の羽根の外周端部の圧力面側には肉厚が外周に向けて薄くなるように形成される第１面取りを設けるとともに、前記オリフィスに囲まれた前記複数の羽根の外周端部の一部には肉厚部を設け、前記肉厚部は、前記オリフィスに囲まれていない前記複数の羽根の外周端部の肉厚よりも厚くなるように形成されている送風機。 A motor, a hub connected to the motor, a plurality of blades disposed around the hub, and an impeller that forms an air flow by rotation, and a downstream side of the air flow formed by the impeller And an orifice surrounding a part of the plurality of blades on the downstream side of the air flow, and an outer peripheral end portion of the plurality of blades is formed to be curved toward the suction surface side of the impeller. In addition, a first chamfer is formed on the pressure surface side of the outer peripheral ends of the plurality of blades not surrounded by the orifice so as to be thinner toward the outer periphery, and is surrounded by the orifice. In addition, a thick portion is provided in a part of the outer peripheral ends of the plurality of blades, and the thick portion is thicker than the thickness of the outer peripheral ends of the plurality of blades not surrounded by the orifice. The blower being formed. 羽根の肉厚部は羽根外周端部に向けて厚くなるように形成された請求項１に記載の送風機。 The blower according to claim 1, wherein the thick part of the blade is formed so as to become thicker toward the outer peripheral end of the blade. 送風機は、さらに、オリフィスに囲まれた複数の羽根の外周端部の圧力面側に肉厚が外周に向けて薄くなるように形成される第２面取りを有し、肉厚部は、前記オリフィスに囲まれた前記複数の羽根の外周端部の負圧面側に配設され、羽根車の半径方向断面の形状が前記複数の羽根の負圧面に対して凸となる凸部によって形成される請求項１または２に記載の送風機。 The blower further has a second chamfer formed on the pressure surface side of the outer peripheral end portions of the plurality of blades surrounded by the orifice so that the thickness is reduced toward the outer periphery, and the thick portion is the orifice The blade is disposed on the suction surface side of the outer peripheral ends of the plurality of blades surrounded by the blade, and the shape of the radial cross section of the impeller is formed by a protrusion that is convex with respect to the suction surfaces of the plurality of blades. Item 3. A blower according to item 1 or 2. 羽根の第２面取りの表面と凸部の表面とが滑らかにつながれている請求項３に記載の送風機。 The blower according to claim 3, wherein the second chamfered surface of the blade and the surface of the convex portion are smoothly connected. 肉厚部は、オリフィスに囲まれた複数の羽根の外周端部の圧力面側に配設され、羽根車の半径方向断面の形状が前記複数の羽根の圧力面に対して凸となる凸部によって形成される請求項１または２に記載の送風機。 The thick wall portion is disposed on the pressure surface side of the outer peripheral end portion of the plurality of blades surrounded by the orifice, and the shape of the radial cross section of the impeller is convex with respect to the pressure surface of the plurality of blades The blower according to claim 1 or 2, formed by: 肉厚部は、オリフィスに囲まれた複数の羽根の外周端部の負圧面側に配設され、羽根車の半径方向断面の形状が前記複数の羽根の負圧面に対して凸となる第一の凸部と、前記オリフィスに囲まれた前記複数の羽根の外周端部の圧力面側に配設され、前記羽根車の半径方向断面の形状が前記複数の羽根の圧力面に対して凸となる第二の凸部とによって形成され、前記第一の凸部の表面と前記第二の凸部の表面が滑らかにつながれている請求項１または２に記載の送風機。 The thick portion is disposed on the suction surface side of the outer peripheral ends of the plurality of blades surrounded by the orifice, and the shape of the radial cross section of the impeller is convex with respect to the suction surfaces of the plurality of blades. And the shape of the radial cross section of the impeller is convex with respect to the pressure surfaces of the plurality of blades. The blower according to claim 1, wherein the blower is formed by a second convex portion, and the surface of the first convex portion and the surface of the second convex portion are smoothly connected. 筐体と、前記筐体内に設けられた圧縮機と、筐体内の吸込み側開口部に設けられた熱交換器と前記筐体の熱交換器の空気吸込側と反対の面に設けられた請求項１から６のいずれかに記載の送風機と、前記熱交換器と前記送風機が配置された風路と、前記風路と前記圧縮機との間を仕切る仕切板とを有する室外ユニット。 A casing, a compressor provided in the casing, a heat exchanger provided in a suction side opening in the casing, and a surface of the casing opposite to the air suction side of the heat exchanger. The outdoor unit which has the air blower in any one of claim | item 1 to 6, the air path in which the said heat exchanger and the said air fan are arrange | positioned, and the partition plate which partitions off between the said air path and the said compressor.
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Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2015092924A1 (en) * 2013-12-20 2015-06-25 三菱電機株式会社 Axial flow fan
EP3029336A1 (en) * 2014-12-03 2016-06-08 ebm-papst Mulfingen GmbH & Co. KG Blade of a fan wheel, fan wheel and axial fan
JP2017129018A (en) * 2016-01-18 2017-07-27 東芝キヤリア株式会社 Propeller fan and heat source unit
JP2018053762A (en) * 2016-09-28 2018-04-05 パナソニックＩｐマネジメント株式会社 Blower and outdoor unit of air conditioner
JPWO2021111582A1 (en) * 2019-12-05 2021-06-10

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5181830A (en) * 1991-11-21 1993-01-26 Chou Rudy S Blade for axial flow fan
JPH07301198A (en) * 1994-05-09 1995-11-14 Matsushita Refrig Co Ltd Blower
JP2001280293A (en) * 2000-03-30 2001-10-10 Sanyo Electric Co Ltd Wind sending device
JP2003148395A (en) * 2001-11-09 2003-05-21 Matsushita Electric Ind Co Ltd Impeller of air-conditioning fan
JP2006177205A (en) * 2004-12-21 2006-07-06 Toshiba Kyaria Kk Axial fan, outdoor unit for air conditioner

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5181830A (en) * 1991-11-21 1993-01-26 Chou Rudy S Blade for axial flow fan
JPH07301198A (en) * 1994-05-09 1995-11-14 Matsushita Refrig Co Ltd Blower
JP2001280293A (en) * 2000-03-30 2001-10-10 Sanyo Electric Co Ltd Wind sending device
JP2003148395A (en) * 2001-11-09 2003-05-21 Matsushita Electric Ind Co Ltd Impeller of air-conditioning fan
JP2006177205A (en) * 2004-12-21 2006-07-06 Toshiba Kyaria Kk Axial fan, outdoor unit for air conditioner

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2015092924A1 (en) * 2013-12-20 2015-06-25 三菱電機株式会社 Axial flow fan
JPWO2015092924A1 (en) * 2013-12-20 2017-03-16 三菱電機株式会社 Axial blower
EP3029336A1 (en) * 2014-12-03 2016-06-08 ebm-papst Mulfingen GmbH & Co. KG Blade of a fan wheel, fan wheel and axial fan
JP2017129018A (en) * 2016-01-18 2017-07-27 東芝キヤリア株式会社 Propeller fan and heat source unit
JP2018053762A (en) * 2016-09-28 2018-04-05 パナソニックＩｐマネジメント株式会社 Blower and outdoor unit of air conditioner
JPWO2021111582A1 (en) * 2019-12-05 2021-06-10
WO2021111582A1 (en) * 2019-12-05 2021-06-10 三菱電機株式会社 Axial flow fan, blowing device, and refrigeration cycle device
JP7275312B2 (en) 2019-12-05 2023-05-17 三菱電機株式会社 Axial fan, air blower, and refrigeration cycle device

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