JP2013120046A

JP2013120046A - Outdoor unit

Info

Publication number: JP2013120046A
Application number: JP2011269688A
Authority: JP
Inventors: Takumi Kida; 琢己木田; Koichi Sakai; 浩一酒井; Makoto Tachimori; 誠朔晦
Original assignee: Panasonic Corp
Current assignee: Panasonic Corp
Priority date: 2011-12-09
Filing date: 2011-12-09
Publication date: 2013-06-17

Abstract

PROBLEM TO BE SOLVED: To provide an outdoor unit in which: the contact of a partitioned plate or the inner surface of a heat exchanger with a wingtip vortex in a blade outer periphery end, which is not surrounded by a casing in an outdoor blowing circuit, is suppressed to stabilize the wingtip vortex; the leak flow passing between the blade outer peripheral end and the casing is suppressed and controlled to stabilize the formation of the wingtip vortex; and thereby an increase in flow loss and in turbulence noise is suppressed.SOLUTION: A wingtip vortex, generated in a negative pressure surface side 13d2 of an outer peripheral end 13d of a suction side 13a of a blade 13 not surrounded by an orifice 14, is stabilized, the flow on the blade outer peripheral side is not disturbed and an increase in a flow loss and in the turbulence noise is suppressed, because an outer peripheral end 13d of the suction side 13a of the blade 13 not surrounded by the orifice 14 and the partition plate 10 in the wind path 9 of the outdoor unit 1 are separated from each other to the vicinity of the orifice 14.

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の室外ユニットに関している。 The present invention relates to an outdoor unit of a refrigeration apparatus such as an air conditioner or a heat pump type hot water heater.

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を求められており、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。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。また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。 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 required, and high efficiency and high performance of indoor and outdoor blowers are indispensable together with improvement in performance of heat exchangers. 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. Moreover, there exists what was described in patent document 1 as a prior art of the air blower for an air conditioning.

図１３から図１７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. 13 to 17 show an outdoor unit for an air conditioner described in Patent Document 1 and an air-conditioning fan impeller mounted thereon.

まず、図１３において、本室外機ユニット１１１はユニット本体１１２内に、平面Ｌ形状の室外熱交換器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、コンプレッサ１１６と、四方弁、インバータ等（図示せず）を収容している。室外送風回路１１５とコンプレッサ１１６との間を仕切板１１７により仕切っている。 First, in FIG. 13, the outdoor unit 111 includes an outdoor fan circuit 115 including a planar L 2 -shaped outdoor heat exchanger 113, a fan motor 150, an air-conditioning fan impeller 151, and a casing 159. And a compressor 116, a four-way valve, an inverter and the like (not shown). The outdoor blower circuit 115 and the compressor 116 are partitioned by a partition plate 117.

また、図１４、図１５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を中心にして薄断面の翼１５２を放射状に３枚設けている。そして、図１４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。 Further, as shown in FIGS. 14 and 15, the air-conditioning fan impeller 151 has a thin cross section centered on a hub 153 having a substantially truncated cone shape with the shaft of the motor 150 fixed to the center of the rotation axis. Three wings 152 are provided radially. Then, as shown in FIG. 14, the discharge side of the blade 152 is surrounded by an appropriate casing 159 that follows the rotation locus of the outer peripheral edge of the blade 152.

ここで、図１６（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６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。 Here, as shown in FIGS. 16 (a), (b) and (c), the radial cross-sectional shape of the wing 152 is concave with respect to the windward side on the outer peripheral end 6 side from the vicinity of 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.

また、中点線Ｅ−Ｅ付近より外周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たものである。 Further, the radius of curvature of the curve that is concave with respect to the windward side on the outer peripheral side from the vicinity of the middle dotted line EE is a radial cross section on the leading edge 154 side of the wing 152 and the radius near the center of the chord length of the wing 152. The value is increased in the order of the directional cross section and the radial cross section near the trailing edge 155 of the wing 152.

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たものである。 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に記載空気調和機用室外ユニットの動作を説明する。 Next, operation | movement of the outdoor unit for air conditioners described in patent document 1 is demonstrated 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が回転駆動して、室外熱交換器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、室外熱交換器１１３を通過する際に、コンプレッサ１１６の作動により室外熱交換器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 via the rotating shaft, and guides outdoor air into the air-conditioning fan impeller 151 via the outdoor heat exchanger 113. At that time, dynamic pressure and static pressure are applied by the blades 152 and the casing 159 provided around the blades 152 to perform a blowing action. Further, when passing through the outdoor heat exchanger 113, the compressor 116 operates to exchange heat with the refrigerant flowing in the pipe of the outdoor 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１７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 vortex, the blade tip vortex is not stable, and the flow on the blade 152 outer periphery is disturbed, increasing the flow loss and increasing 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、崩壊する。 In addition, the unstable blade tip vortex is sucked into the casing 159 along with the flow from the suction side to the discharge side of the blade 152, and contacts and collapses on the inner wall of the casing 159.

そのため、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て、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阻害し、ケーシング１５９に囲われた吐出側においても翼外周端部１５６から翼１５２の外周側にかけ流れ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。 Therefore, a leakage flow passing between the blade outer peripheral end 156 and the casing 159 is generated, thereby inhibiting 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 and being surrounded by the casing 159. Also on the discharge side, the instability of the flow is promoted from the outer peripheral edge 156 of the blade to the outer periphery of the blade 152, and large turbulent energy is released, resulting in an increase in flow loss and an increase in turbulent noise. It was.

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. Provided is an outdoor unit that stabilizes the vortex, further suppresses and controls the leakage flow passing 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. Is.

上記従来の課題を解決するために、本発明の室外ユニットは、筐体内に、圧縮機と、前記圧縮機と接続される熱交換器と、前記熱交換器を強制通風する送風機と、を収納する機械室で、前記送風機の吸込み側に前記熱交換器を有し、前記送風機と前記圧縮機は仕切板によって左右に仕切って配置される室外ユニットにおいて、前記送風機の羽根の外周径は
、吸込み側となる前記羽根の前縁部が最も小さくなるように変形させ、吐出側となる前記羽根の後縁部が最も大きくなるように変形させ、前記前縁部は記送風機のオリフィスの外側に位置し、前記後縁部は前記送風機のオリフィスの内側に位置したものである。 In order to solve the above-described conventional problems, an outdoor unit of the present invention houses a compressor, a heat exchanger connected to the compressor, and a blower for forcibly ventilating the heat exchanger in a housing. In an outdoor unit in which the heat exchanger is provided on the suction side of the blower and the blower and the compressor are divided into left and right by a partition plate, the outer peripheral diameter of the blades of the blower is the suction The blade is deformed so that the leading edge of the blade on the side becomes the smallest, and the trailing edge of the blade on the discharge side is deformed so as to become the largest, and the leading edge is located outside the orifice of the blower. The trailing edge portion is located inside the orifice of the blower.

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と、室外機の風路内の仕切板や熱交換器の内面側との距離がオリフィス近傍まで離れているため、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, the distance between the outer peripheral end on the suction side of the blade not surrounded by the orifice and the inner side of the partition plate in the air passage of the outdoor unit and the heat exchanger is far to the vicinity of the orifice. The blade tip vortex generated on the suction side of the outer peripheral end of the blade that is not surrounded by the orifice is stabilized, the flow on the outer periphery of the blade is not disturbed, and the increase in flow loss and turbulent noise is suppressed. .

また、安定しない翼端渦は、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、羽根外周端部とオリフィス間を通過する洩れ流れより羽根外周端の負圧面側に発生する翼端渦の生成を阻害せず、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の安定し、大きな乱れエネルギが放出されず、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。 Unstable blade tip vortices are 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 blade outer vortex is negatively affected by the leakage flow passing between the blade outer periphery and the orifice. The generation of the tip vortex generated on the pressure surface side is not obstructed, and even on the discharge side surrounded by the orifice, the flow is stabilized from the outer peripheral edge of the blade to the outer periphery of the blade, and no large turbulent energy is released. The large flow loss and the increase of turbulent noise are minimized.

本発明の室外ユニットは、風路内において、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、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 outdoor unit of the present invention stabilizes the blade tip vortex by suppressing the contact of the blade vortex partition plate and the inner surface of the heat exchanger at the suction blade outer peripheral end not surrounded by the orifice in the air passage. In addition, the leakage flow that passes between the orifice peripheral edge on the discharge side surrounded by the orifice and the orifice is suppressed and controlled, the generation of the tip vortex is stabilized, and the increase in flow loss and turbulent noise is minimized. Can do.

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 図３のＯ−Ａ断面における羽根外周要部拡大図Enlarged view of the main part of the outer periphery of the blade in the OA cross section of FIG. 実施の形態２における送風機の断面図Sectional drawing of the air blower in Embodiment 2. 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 図６のＯ−Ｂ断面における羽根外周要部拡大図Enlarged view of the main part of the blade outer periphery in the OB cross section of FIG. 図６のＯ−Ｃ断面における羽根外周要部拡大図Enlarged view of the main part of the outer periphery of the blade in the OC section of FIG. 実施の形態３における送風機の断面図Sectional drawing of the air blower in Embodiment 3. 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 図１０のＯ−Ｄ断面における羽根外周要部拡大図Enlarged view of the main part of the blade outer periphery in the OD cross section of FIG. 図１０のＯ−Ｅ断面における羽根外周要部拡大図Enlarged view of the main part of the blade outer periphery in the OE cross section of FIG. 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 従来の一部回転軌跡のある送風機の子午断面図A meridional section of a conventional blower with a partial rotation trajectory 従来の送風機の正面図Front view of conventional blower （ａ）図１５のＡ−Ｏ断面（同羽根車の前縁側半径方向断面図）（ｂ）図１５のＢ−Ｏ断面（同羽根車の翼の弦長の中央付近の半径方向断面図（ｃ）図１５のＣ−Ｏ断面（同羽根車の後縁側半径方向断面図）(A) AO cross section of FIG. 15 (radial sectional view of the leading edge side of the impeller) (b) BO cross section of FIG. 15 (radial cross section near the center of the chord length of the blade of the impeller ( c) C-O cross section of FIG. 15 (rear edge side radial cross-sectional view 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

請求項１に記載の発明の室外ユニットは、筐体内に、圧縮機と、前記圧縮機と接続される熱交換器と、前記熱交換器を強制通風する送風機と、を収納する機械室で、前記送風機の吸込み側に前記熱交換器を有し、前記送風機と前記圧縮機は仕切板によって左右に仕切って配置される室外ユニットにおいて、前記送風機の羽根の外周径は、吸込み側となる前記羽根の前縁部が最も小さくなるように変形させ、吐出側となる前記羽根の後縁部が最も大きくなるように変形させ、前記前縁部は記送風機のオリフィスの外側に位置し、前記後
縁部は前記送風機のオリフィスの内側に位置したものである。 The outdoor unit of the invention described in claim 1 is a machine room that houses a compressor, a heat exchanger connected to the compressor, and a blower that forcibly ventilates the heat exchanger in a housing. In the outdoor unit which has the heat exchanger on the suction side of the blower, and the blower and the compressor are divided by a partition plate on the left and right, the outer diameter of the blade of the blower is the suction side The leading edge of the blade is deformed to become the smallest, the trailing edge of the blade on the discharge side is deformed to be the largest, the leading edge is located outside the orifice of the blower, and the trailing edge The part is located inside the orifice of the blower.

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と、室外機の風路内の仕切板や熱交換器の内面側との距離がオリフィス近傍まで離れているため、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ことができる。 By adopting such a configuration, the distance between the outer peripheral end on the suction side of the blade not surrounded by the orifice and the inner side of the partition plate in the air passage of the outdoor unit and the heat exchanger is far to the vicinity of the orifice. The blade tip vortex generated on the suction side of the outer peripheral end of the blade that is not surrounded by the orifice is stabilized, the flow on the outer periphery of the blade is not disturbed, and the increase in flow loss and turbulent noise is suppressed. be able to.

また、この翼端渦は、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、羽根外周端部とオリフィス間を通過する洩れ流れより羽根外周端の負圧面側に発生する翼端渦の生成を阻害せず、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の安定し、大きな乱れエネルギが放出されず、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ことができる。 In addition, the blade tip vortex is sucked into the orifice along with the flow from the blade suction side to the discharge side, but since it is stabilized, the suction surface of the blade outer periphery is less than the leakage flow passing between the blade outer periphery and the orifice. Generation of the tip vortex generated on the nozzle side is not obstructed, and even on the discharge side surrounded by the orifice, the flow is stabilized from the outer peripheral edge of the blade to the outer periphery of the blade, and no large turbulent energy is released. Large flow loss and increase in turbulent noise can be reduced.

請求項２に記載の発明は、前記羽根のオリフィスに囲まれていない部分の羽根外周端部を羽根の負圧面側に湾曲させたものである。 In the invention according to claim 2, the blade outer peripheral end portion of the blade not surrounded by the orifice of the blade is curved toward the suction surface side of the blade.

かかる構成とすることにより、請求項１に記載の発明に加え、オリフィスに囲まれていない吸込側の羽根外周端部の圧力面側から負圧面側へ回り込む気流は緩やかに方向転換して回り込み、かつ負圧面側から吹き出す気流も湾曲した負圧面に沿って前記回り込み気流とほぼ同方向に吐出されるため、気流の境界で生じる乱れは小さく、羽根外周端部の負圧面側で発生する翼端渦が小さくなり羽根外周部における気流の乱れを抑制する。 By adopting such a configuration, in addition to the invention of claim 1, the airflow that circulates from the pressure surface side to the suction surface side of the suction-side blade outer peripheral portion not surrounded by the orifice gradually turns around and wraps around, In addition, since the airflow blown out from the suction surface side is discharged along the curved suction surface in substantially the same direction as the wraparound airflow, the turbulence generated at the boundary of the airflow is small, and the blade tip generated on the suction surface side of the outer peripheral edge of the blade The vortex becomes smaller and the turbulence of the air current in the outer periphery of the blade is suppressed.

その結果、この部分での流動損失の増加と乱流騒音の発生を抑制することができる。 As a result, it is possible to suppress an increase in flow loss and generation of turbulent noise in this portion.

請求項３に記載の発明は、前記羽根の外周端部は吸込み側から吐出側にかけて羽根の負圧面側に湾曲し、オリフィスに囲まれた吐出側の湾曲部が、オリフィスに囲まれていない吸込み側の湾曲部に比べ小さいことを特徴としたものである。 According to a third aspect of the present invention, the outer peripheral end of the blade is curved toward the suction surface side of the blade from the suction side to the discharge side, and the discharge side curved portion surrounded by the orifice is not surrounded by the orifice. It is characterized by being smaller than the curved portion on the side.

さらに、羽根のオリフィスに囲まれた部分の羽根外周端部を羽根負圧面側に小さく湾曲させているため、羽根外周端部とオリフィス間を通過する洩れ流れが少なくなり、発生する翼端渦は小さく抑えられる。また、オリフィスに囲まれた羽根外周端部では負圧面の吐出流れは湾曲した羽根の負圧面近傍に沿って流れるため、翼端渦を外周に押しやる作用を弱め、反対に翼端渦を羽根外周端部から内側に移動させ、翼端渦とオリフィスとの接触を抑制しオリフィス内での翼端渦の崩壊を防止し、オリフィスに囲われた吐出側において羽根外周端部で翼端渦が安定して羽根車から吐出する。 Furthermore, since the blade outer peripheral edge of the portion surrounded by the blade orifice is curved slightly toward the blade suction surface side, the leakage flow passing between the blade outer edge and the orifice is reduced, and the generated blade tip vortex is Can be kept small. In addition, the discharge flow of the suction surface flows along the vicinity of the negative pressure surface of the curved blade at the blade outer peripheral edge surrounded by the orifice, so that the action of pushing the blade tip vortex to the outer periphery is weakened. The tip vortex is moved inward to suppress contact between the tip vortex and the orifice, preventing the tip vortex from collapsing inside the orifice, and the tip vortex is stabilized at the outer periphery of the blade on the discharge side surrounded by the orifice. And discharge from the impeller.

請求項４に記載の発明は、前記羽根の外周端部の圧力面側に面取りを設けたものである。 According to a fourth aspect of the present invention, chamfering is provided on the pressure surface side of the outer peripheral end of the blade.

かかる構成とすることにより、請求項１から３に記載の発明に加え、吸込側の羽根外周端部の圧力面側から負圧面側へ回り込む際に羽根外端の圧力面側のエッジでの気流の剥離、及びそれに伴う乱れの発生を小さく抑え、翼端渦の生成の際の不安定化を小さく抑制す
る。 By adopting such a configuration, in addition to the invention according to claims 1 to 3, the air flow at the pressure surface side edge of the outer end of the blade when the blade outer periphery end portion wraps around from the pressure surface side to the suction surface side. , And the occurrence of turbulence associated therewith are kept small, and instability during the generation of blade tip vortices is kept small.

請求項５に記載の発明は、前記羽根の外周端部の圧力面に面取りを設け、オリフィスに囲まれた吐出側の面取りの曲率半径が、オリフィスに囲まれていない吸込み側の面取りの曲率半径に対し小さくしたものである。 The invention according to claim 5 provides a chamfer on the pressure surface of the outer peripheral end of the blade, and the radius of curvature of the chamfer on the discharge side surrounded by the orifice is the radius of curvature of the chamfer on the suction side not surrounded by the orifice. It is a small one.

かかる構成とすることにより、請求項４に記載の発明に加え、羽根外周端部とオリフィス間を通過する洩れ流れが圧力面側のエッジ近傍を通過する際の乱れが抑えられ、漏れ損失が小さくなる。 By adopting such a configuration, in addition to the invention described in claim 4, turbulence when the leak flow passing between the blade outer peripheral end and the orifice passes near the edge on the pressure surface side is suppressed, and leakage loss is reduced. Become.

請求項６に記載の発明は、前記羽根の外周端部のオリフィスに囲まれていない吸込み側では圧力面に面取りを設け、羽根の外周端部のオリフィスに囲まれた吐出側では負圧面に面取りを設けたものである。 According to a sixth aspect of the present invention, a chamfer is provided on the pressure surface on the suction side not surrounded by the orifice at the outer peripheral end portion of the blade, and a negative pressure surface is chamfered on the discharge side surrounded by the orifice at the outer peripheral end portion of the blade. Is provided.

かかる構成とすることにより、請求項１から３に記載の発明に加え、吸込側の羽根外周端部の圧力面側から負圧面側へ回り込む際に羽根外端の圧力面側のエッジでの気流の剥離、及びそれに伴う乱れの発生を小さく抑え、吸込側の羽根外周端部、翼端渦の生成の際の不安定化を小さく抑制する。 By adopting such a configuration, in addition to the invention according to claims 1 to 3, the air flow at the pressure surface side edge of the outer end of the blade when the blade outer periphery end portion wraps around from the pressure surface side to the suction surface side. , And the occurrence of turbulence associated therewith, are suppressed to a small extent, and the instability at the time of generation of the blade outer peripheral end and blade tip vortex on the suction side is suppressed to a small extent.

さらに、羽根のオリフィスに囲まれた部分で、オリフィスと羽根外周端部の間のシール力を高め、漏れ流れを防止し、オリフィスに囲われた吐出側の外周端部負圧面側での漏れ流れによる翼端渦の発生を防止し、羽根外周側の空力特性を向上する。 Furthermore, at the part surrounded by the orifice of the blade, the sealing force between the orifice and the outer peripheral edge of the blade is increased to prevent leakage flow, and the leakage flow at the discharge side outer peripheral edge suction surface surrounded by the orifice This prevents the generation of blade tip vortices and improves the aerodynamic characteristics of the blade outer periphery.

請求項７に記載の発明は、前記羽根の外周端部のオリフィスに囲まれた吐出側では負圧面に設けた面取りの曲率半径が、前記羽根の外周端部のオリフィスに囲まれていない吸込み側の圧力面に設けた面取りの曲率半径より小さいものである。 According to a seventh aspect of the present invention, on the discharge side surrounded by the orifice at the outer peripheral end of the blade, the chamfered curvature radius provided on the suction surface is not surrounded by the orifice at the outer peripheral end of the blade. This is smaller than the radius of curvature of the chamfer provided on the pressure surface.

かかる構成とすることにより、請求項６に記載の発明に加え、羽根のオリフィスに囲まれた部分で、オリフィスと羽根外周端部の間をわずかに流れる漏れ流れが湾曲した羽根外周端部の負圧面に沿って内部に流れるため、羽根外周端部の負圧面側近傍でオリフィスの内壁と干渉して乱れることを防止する。 By adopting such a configuration, in addition to the invention described in claim 6, in the portion surrounded by the orifice of the blade, the negative flow at the outer peripheral end of the blade where the leakage flow slightly flowing between the orifice and the outer peripheral end of the blade is curved. Since it flows inward along the pressure surface, it is prevented from being disturbed by interference with the inner wall of the orifice in the vicinity of the suction surface side of the blade outer peripheral end.

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である。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は図３のＯ−Ａ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 according to Embodiment 1 of the present invention. 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, and FIG. 4 is an enlarged view of the main part of the blade outer periphery in the OA cross section of FIG.

図１において、本室外ユニット１は筐体２内に、平面がＬ形状の室外熱交換器３と、モータ４と、羽根車５と、オリフィス１４からなる送風機７と、コンプレッサ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、室外熱熱交器３と、送風機７からなる風路９とコンプレッサ８との間を仕切板１０により仕切っている。 In FIG. 1, a main outdoor unit 1 is provided in a housing 2, an outdoor heat exchanger 3 having a flat L shape, a motor 4, an impeller 5, a blower 7 including an orifice 14, a compressor 8, and a four-way valve. Inverters and the like (not shown) are accommodated. A partition plate 10 partitions the outdoor heat exchanger 3, 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、回転軸中心にモ− タ４のシャフト１１を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 has a thin wing-shaped blade 13 radially about a substantially cylindrical hub 12 having a shaft 11 of the motor 4 fixed to the center of the rotation axis. Two are provided. 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、オリフィス１４に囲われていない羽根１３の吸込み側１３ａの外周径が羽根１３の前縁１５からオリフィス１４近傍にかけて漸次大きくなりオリフィス１４に囲われた吐出側１３ｂで、外周径となる羽根１３の後縁１６はオリフィス１４の最小内径と一定の隙間を確保する最大径となるものである。 Here, the outer peripheral diameter of the suction side 13 a of the blade 13 not surrounded by the orifice 14 gradually increases from the front edge 15 of the blade 13 to the vicinity of the orifice 14, and the blade having the outer diameter on the discharge side 13 b surrounded by the orifice 14. The trailing edge 16 of 13 has a minimum inner diameter of the orifice 14 and a maximum diameter that ensures a certain gap.

さらに、羽根１３のオリフィス１４に囲まれていない吸込側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に面取りＲ１を設けたものである。 Further, the outer peripheral end 13d of the suction side 13a not surrounded by the orifice 14 of the blade 13 is curved to the negative pressure surface side 13d2, and the chamfer R1 is provided on the pressure surface side 13d1 of the outer peripheral end portion 13d of the blade 13. It is.

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

まず、モータ４により回転軸４ａを介して羽根車５が回転駆動して、室外熱交換器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、室外熱交換器３を通過する際に、コンプレッサ８の作動により室外熱交換器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 rotating shaft 4 a, and outdoor air is guided into the impeller 5 via the outdoor 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 outdoor heat exchanger 3, heat exchange is performed with the refrigerant flowing in the pipe of the outdoor 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と、室外ユニット１の風路９内の仕切板１１や室外熱交換器３の内面側との距離がオリフィス１４近傍まで離れているため、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ことができる。 The distance between the outer peripheral end 13d of the suction side 13a of the blade 13 not surrounded by the orifice 14 and the inner surface side of the partition plate 11 or the outdoor heat exchanger 3 in the air passage 9 of the outdoor unit 1 is near the orifice 14. The blade tip vortex generated on the suction side 13d2 of the outer peripheral end 13d of the suction side 13a of the blade 13 not surrounded by the orifice 14 is stabilized, the flow on the outer peripheral side of the blade is not disturbed, and the flow Loss and increase in turbulent noise can be suppressed.

また、この翼端渦は、羽根１３の吸込側１３ａから吐出側１３ｂに向かう流れとともにオリフィス１４に吸い込まれるが、安定化しているので、羽根１３の外周端部１３ｄとオリフィス１４の間を通過する洩れ流れより外周端１３ｄの負圧面側１３ｄ２に発生する翼端渦の生成を阻害せず、オリフィス１４に囲われた吐出側１３ｂにおいても外周端部１３ｄから羽根１３の外周側にかけ流れの安定し、大きな乱れエネルギが放出されず、吐出側１３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ことができる。 Further, the blade tip vortex is sucked into the orifice 14 together with the flow from the suction side 13a to the discharge side 13b of the blade 13, but since it is stabilized, it passes between the outer peripheral end portion 13d of the blade 13 and the orifice 14. The generation of the blade tip vortex generated on the suction surface side 13d2 of the outer peripheral end 13d from the leakage flow is not hindered, and the flow is stabilized from the outer peripheral end portion 13d to the outer peripheral side of the blade 13 also on the discharge side 13b surrounded by the orifice 14. Large turbulent energy is not released, and a large flow loss and turbulent noise increase on the discharge side 13 can be reduced.

さらに、オリフィス１４に囲まれていない吸込側１３ａの外周端部１３ｄを負圧面側１３ｄ２に湾曲させているので、オリフィス１４に囲まれていない吸込側１３ａの羽根１３の外周端部１３ｄの圧力面側１３ｄ１から負圧面側１３ｄ２へ回り込む気流は緩やかに方向転換して回り込み、かつ負圧面側１３ｄ２から吹き出す気流も湾曲した羽根１３の負圧面に沿って回り込み気流とほぼ同方向に吐出されるため、気流の境界で生じる乱れは小さく、羽根１３の外周端部１３ｄの負圧面側１３ｄ２で発生する翼端渦が小さくなり羽根１３の外周部における気流の乱れを抑制する。 Further, since the outer peripheral end 13d of the suction side 13a not surrounded by the orifice 14 is curved to the negative pressure side 13d2, the pressure surface of the outer peripheral end 13d of the blade 13 of the suction side 13a not surrounded by the orifice 14 The airflow that circulates from the side 13d1 to the suction surface side 13d2 changes direction gradually, and the airflow that blows out from the suction surface side 13d2 is also discharged in the same direction as the wraparound airflow along the suction surface of the curved blade 13. The turbulence generated at the boundary of the airflow is small, and the blade tip vortex generated on the suction surface side 13d2 of the outer peripheral end portion 13d of the blade 13 is reduced to suppress the turbulence of the airflow in the outer peripheral portion of the blade 13.

さらに、また、面取りＲ１により、吸込側１３ａの羽根１３の外周端部１３ｄの圧力面側１３ｄ１から負圧面側１３ｄ２へ回り込む際に外端部１３ｄの圧力面側１３ｄ１のエッジで，気流の剥離、及びそれに伴う乱れの発生を小さく抑え、翼端渦の生成の際の不安定化を小さく抑制する。 Furthermore, due to chamfering R1, air current is separated at the edge of the pressure surface side 13d1 of the outer end portion 13d when the pressure surface side 13d1 of the outer peripheral end portion 13d of the blade 13 on the suction side 13a wraps from the pressure surface side 13d2. In addition, the occurrence of turbulence associated therewith is suppressed, and instability during generation of the tip vortex is reduced.

（実施の形態２）
図５は実施の形態２における送風機の断面図であり、図６は同実施の形態における送風機の平面図であり、図７は図６のＯ−Ｂ断面における羽根外周要部拡大図であり、図８は図６のＯ−Ｃ断面における羽根外周要部拡大図である。 (Embodiment 2)
5 is a cross-sectional view of the blower in the second embodiment, FIG. 6 is a plan view of the blower in the same embodiment, FIG. 7 is an enlarged view of the main part of the blade outer periphery in the OB cross section of FIG. FIG. 8 is an enlarged view of the main part of the outer periphery of the blade in the OC section of FIG.

尚、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から図８で示すように、羽根１３の外周端部１３ｅは吸込み側１３ｅ（ａ）から吐出側１３ｅ（ｂ）にかけて羽根１３の負圧面側に湾曲し、オリフィス１４に囲まれた吐出側の湾曲部１３ｅ（ｂ）が、オリフィス１４に囲まれていない吸込側の湾曲部１３ｅ（ａ）に比べ小さく、さらに、羽根１３の外周端部１３ｅの圧力面側１３ｅ（ａ）１、１３ｅ（ｂ）１に面取りＲ２、Ｒ３を設け、オリフィス１４に囲まれた外周端部１３ｅの圧力面側１３ｅ（ｂ）１の面取りＲ３の曲率半径が、オリフィス１４に囲まれていない圧力面側１３ｅ（ａ）１の面取りＲ２の曲率半径に対し小さくしたものである。 As shown in FIGS. 5 to 8, the outer peripheral end 13 e of the blade 13 is curved toward the suction surface side of the blade 13 from the suction side 13 e (a) to the discharge side 13 e (b) and is surrounded by the orifice 14. The curved portion 13e (b) is smaller than the curved portion 13e (a) on the suction side not surrounded by the orifice 14, and the pressure surface side 13e (a) 1, 13e ( b) Chamfering R2 and R3 are provided in 1 and the radius of curvature of the chamfering R3 on the pressure surface side 13e (b) 1 of the outer peripheral end 13e surrounded by the orifice 14 is equal to the pressure surface side 13e (not surrounded by the orifice 14). a) It is made smaller than the curvature radius of the chamfer R2 of 1.

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.

まず、オリフィス１４に囲まれていない吸込側１３ａの羽根１３の外周端部１３ｅの湾曲部１３ｅ（ａ）の圧力面側１３ｅ（ａ）１から負圧面側１３ｅ（ａ）２へ回り込む気流は緩やかに方向転換して回り込み、かつ負圧面側１３ｅ（ａ）２から吹き出す気流も湾曲した負圧面に沿って回り込み気流とほぼ同方向に吐出されるため、気流の境界で生じる乱れは小さく、羽根１３の外周端部１３ｅの負圧面側１３ｅ（ａ）２で発生する翼端渦が小さくなり羽根１３の外周部における気流の乱れを抑制する。 First, the airflow flowing from the pressure surface side 13e (a) 1 of the curved portion 13e (a) of the outer peripheral end 13e of the blade 13 on the suction side 13a not surrounded by the orifice 14 to the negative pressure surface side 13e (a) 2 is gentle. Since the airflow that turns around and turns out from the suction surface side 13e (a) 2 is also discharged along the curved suction surface in almost the same direction as the wraparound airflow, the turbulence generated at the boundary of the airflow is small, and the blade 13 Blade tip vortex generated on the suction surface side 13e (a) 2 of the outer peripheral end portion 13e is reduced, and the turbulence of the air current in the outer peripheral portion of the blade 13 is suppressed.

さらに、羽根１３のオリフィス１４に囲まれた部分の外周端部１３ｅの湾曲部１３ｅ（ｂ）を負圧面側１３ｅ（ｂ）２に小さく湾曲させているため、湾曲部１３ｅ（ｂ）とオリフィス１４の間を通過する洩れ流れが少なくなり、発生する翼端渦は小さく抑えられる。また、オリフィス１４に囲まれた外周端部１３ｅの湾曲部１３ｅ（ｂ）では負圧面側１３ｅ（ｂ）２の吐出流れは湾曲した負圧面近傍に沿って流れるため、翼端渦を外周に押しやる作用を弱め、反対に翼端渦を外周端部１３ｅの湾曲部１３ｅ（ｂ）から内側に移動させ、翼端渦とオリフィス１４との接触を抑制しオリフィス１４内での翼端渦の崩壊を防止し、オリフィス１４に囲われた吐出側において外周端部１３ｅの湾曲部１３ｅ（ｂ）で翼端渦が安定して羽根車５から吐出する。 Further, since the curved portion 13e (b) of the outer peripheral end portion 13e of the portion surrounded by the orifice 14 of the blade 13 is slightly curved to the suction surface side 13e (b) 2, the curved portion 13e (b) and the orifice 14 are curved. Leakage flow passing between the two is reduced, and the generated tip vortex is kept small. Further, in the curved portion 13e (b) of the outer peripheral end portion 13e surrounded by the orifice 14, the discharge flow on the suction surface side 13e (b) 2 flows along the vicinity of the curved suction surface, so that the blade tip vortex is pushed to the outer periphery. On the contrary, the blade tip vortex is moved inward from the curved portion 13e (b) of the outer peripheral end portion 13e to suppress the contact between the blade tip vortex and the orifice 14, thereby causing the blade tip vortex to collapse in the orifice 14. The blade tip vortex is stably discharged from the impeller 5 at the curved portion 13e (b) of the outer peripheral end portion 13e on the discharge side surrounded by the orifice 14.

そして、面取りＲ２により、羽根１３の吸込側の外周端部１３ｅの湾曲部１３ｅ（ａ）の圧力面側１３ｅ（ａ）１から負圧面側１３ｅ（ａ）２へ回り込む際に外端部１３ｅの湾曲部１３ｅ（ａ）の圧力面側１３ｅ（ａ）１のエッジで、気流の剥離、及びそれに伴う乱れの発生を小さく抑え、翼端渦の生成の際の不安定化を小さく抑制する。 And by chamfering R2, when it goes around from the pressure surface side 13e (a) 1 of the curved portion 13e (a) of the outer peripheral end portion 13e on the suction side of the blade 13 to the negative pressure surface side 13e (a) 2, the outer end portion 13e At the edge of the pressure surface side 13e (a) 1 of the curved portion 13e (a), the separation of the air flow and the occurrence of the turbulence associated therewith are suppressed, and the instability during generation of the blade tip vortex is suppressed to a small extent.

また、さらに、面取りＲ３により、外周端部１３ｅの湾曲部１３ｅ（ｂ）とオリフィス１４の間を通過する洩れ流れが圧力面側１３ｅ（ｂ）１のエッジ近傍を通過する際の乱れが抑えられ、漏れ損失が小さくなる。 Further, the chamfer R3 suppresses the disturbance when the leakage flow passing between the curved portion 13e (b) of the outer peripheral end portion 13e and the orifice 14 passes near the edge of the pressure surface side 13e (b) 1. Leakage loss is reduced.

（実施の形態３）
図９は実施の形態３における送風機の断面図であり、図１０は同実施の形態における送風機の平面図であり、図１１は図１０のＯ−Ｄ断面における羽根外周要部拡大図であり、図１２は図１０のＯ−Ｅ断面における羽根外周要部拡大図である。 (Embodiment 3)
9 is a cross-sectional view of the blower in the third embodiment, FIG. 10 is a plan view of the blower in the same embodiment, FIG. 11 is an enlarged view of the main part of the blade outer periphery in the OD cross section of FIG. FIG. 12 is an enlarged view of the main part of the outer periphery of the blade in the OE cross section of FIG.

尚、実施の形態１、実施の形態２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。 The same constituent elements as those in the first embodiment and the second embodiment are denoted by the same reference numerals and description thereof is omitted.

図９から図１２で示すように、羽根１３の外周端部１３ｅは吸込み側１３ｅ（ａ）から吐出側１３ｅ（ｂ）にかけて羽根１３の負圧面側に湾曲し、オリフィス１４に囲まれた吐出側の湾曲部１３ｅ（ｂ）が、オリフィス１４に囲まれていない吸込側の湾曲部１３ｅ（ａ）に比べ小さい。 As shown in FIGS. 9 to 12, the outer peripheral end 13 e of the blade 13 is curved toward the suction surface side of the blade 13 from the suction side 13 e (a) to the discharge side 13 e (b), and is surrounded by the orifice 14. The curved portion 13e (b) is smaller than the curved portion 13e (a) on the suction side not surrounded by the orifice 14.

そして、オリフィス１４に囲われていない羽根１３の外周端部１３ｅの湾曲部１３ｅ（ａ）の圧力面側１３ｅ（ａ）１に面取りＲ４を設け、オリフィス１４に囲われた羽根１３の外周端部１３ｅの湾曲部１３ｅ（ｂ）の負圧面側１３ｅ（ｂ）２に面取りＲ５を設けている。 A chamfer R4 is provided on the pressure surface side 13e (a) 1 of the curved portion 13e (a) of the outer peripheral end portion 13e of the blade 13 not surrounded by the orifice 14, and the outer peripheral end portion of the blade 13 surrounded by the orifice 14 is provided. A chamfer R5 is provided on the suction surface side 13e (b) 2 of the curved portion 13e (b) of 13e.

さらに、オリフィス１４に囲まれた外周端部１３ｅの湾曲部１３ｅ（ｂ）の圧力面側１３ｅ（ｂ）１の面取りＲ５の曲率半径が、オリフィス１４に囲まれていない外周端部１３ｅの湾曲部１３ｅ（ａ）圧力面側１３ｅ（ａ）１の面取りＲ４の曲率半径に対し小さくしている。 Further, the curvature radius of the chamfer R5 on the pressure surface side 13e (b) 1 of the curved portion 13e (b) of the outer peripheral end portion 13e surrounded by the orifice 14 is the curved portion of the outer peripheral end portion 13e not surrounded by the orifice 14. 13e (a) The pressure surface side 13e (a) 1 is made smaller than the radius of curvature of the chamfer R4.

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.

まず、オリフィス１４に囲まれていない吸込側の外周端部１３ｅの湾曲部１３ｅ（ａ）では、面取りＲ４により、羽根１３の吸込側の外周端部１３ｅの湾曲部１３ｅ（ａ）の圧力面側１３ｅ（ａ）１から負圧面側１３ｅ（ａ）２へ回り込む際に湾曲部１３ｅ（ａ）の圧力面側１３ｅ（ａ）１のエッジで，気流の剥離、及びそれに伴う乱れの発生を小さく抑え、翼端渦の生成の際の不安定化を小さく抑制する。 First, in the curved portion 13e (a) of the outer peripheral end portion 13e on the suction side not surrounded by the orifice 14, the pressure surface side of the curved portion 13e (a) of the outer peripheral end portion 13e on the suction side of the blade 13 is chamfered R4. At the edge of the pressure surface side 13e (a) 1 of the curved portion 13e (a), the separation of the air flow and the occurrence of the turbulence associated therewith are suppressed to a small extent when going from the pressure surface side 13e (a) 2 to the pressure surface side 13e (a) 2. Instability during generation of blade tip vortex is minimized.

さらに、オリフィス１４に囲われた羽根１３の吐出側１３ｂでは、外周端部１３ｅの湾曲部１３ｅ（ｂ）の負圧面側１３ｅ（ｂ）２に面取りＲ５を設けることにより、オリフィス１４に囲まれた外周端部１３ｅの湾曲部１３ｅ（ｂ）では、オリフィス１４と羽根１３の外周端部１３ｅの間のシール力を高め、漏れ流れを防止し、オリフィス１４に囲われた外周端部１３ｅの湾曲部１３ｅ（ｂ）の負圧面側１３ｅ（ｂ）２での漏れ流れによる翼端渦の発生を防止し、羽根１３の外周側の空力特性を向上する。 Further, the discharge side 13b of the blade 13 surrounded by the orifice 14 is surrounded by the orifice 14 by providing a chamfer R5 on the negative pressure surface side 13e (b) 2 of the curved portion 13e (b) of the outer peripheral end portion 13e. In the curved portion 13e (b) of the outer peripheral end portion 13e, the sealing force between the orifice 14 and the outer peripheral end portion 13e of the blade 13 is increased to prevent leakage flow, and the curved portion of the outer peripheral end portion 13e surrounded by the orifice 14 The generation of blade tip vortex due to leakage flow on the suction surface side 13e (b) 2 of 13e (b) is prevented, and the aerodynamic characteristics on the outer peripheral side of the blade 13 are improved.

また、さらに、オリフィス１４に囲まれた外周端部１３ｅの湾曲部１３ｅ（ｂ）の圧力面側１３ｅ（ｂ）１の面取りＲ５の曲率半径が小さいので、オリフィス１４に囲われた羽根１３の吐出側１３ｂでは、オリフィス１４と羽根１３の外周端部１３ｅ（ｂ）の間をわずかに流れる漏れ流れが外周端部１３ｅ（ｂ）の負圧面１３ｅ（ｂ）２の面取りＲ５に沿って羽根３の内周側に流れるため、羽根１３の外周端部１３ｅの湾曲部１３ｅ（ｂ）の負圧面側１３ｅ（ｂ）２近傍でオリフィス１４の内壁と干渉して乱れることを防止する。 Further, since the radius of curvature of the chamfer R5 on the pressure surface side 13e (b) 1 of the curved portion 13e (b) of the outer peripheral end portion 13e surrounded by the orifice 14 is small, the discharge of the blade 13 surrounded by the orifice 14 is performed. On the side 13b, the leakage flow that slightly flows between the orifice 14 and the outer peripheral end portion 13e (b) of the blade 13 flows along the chamfer R5 of the negative pressure surface 13e (b) 2 of the outer peripheral end portion 13e (b). Since it flows to the inner peripheral side, it interferes with the inner wall of the orifice 14 in the vicinity of the negative pressure surface side 13e (b) 2 of the curved portion 13e (b) of the outer peripheral end 13e of the blade 13 and is prevented from being disturbed.

以上のように、本発明にかかる構成の室外ユニットは、風路内において、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、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 outdoor unit having the configuration according to the present invention provides contact between the blade vortex partition plate and the inner surface of the heat exchanger at the outer peripheral end of the suction blade not surrounded by the orifice in the air passage. It stabilizes the blade tip vortex and suppresses and controls the leakage flow that passes between the discharge-side blade outer periphery surrounded by the orifice and the orifice, stabilizes the blade tip vortex generation, and reduces flow loss and turbulence. An increase in the flow noise can be suppressed to a small level.

従って、かかる羽根車、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 an impeller and blower and the high heat exchanging ability as a heat pump unit, and further noise reduction. It can be applied not only to refrigeration and refrigeration equipment such as household refrigerator-freezers 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室内ユニット
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吸込側
１３ｂ吐出側
１３ｄ、１３ｅ、１３ｅ（ａ）、１３ｅ（ｂ）外周端部（湾曲部）
１３ｄ１、１３ｅ（ａ）１、１３ｅ（ｂ）１圧力面側
１３ｄ２、１３ｅ（ａ）２、１３ｅ（ｂ）１２負圧面側
１４オリフィス
１５前縁
１６後縁
Ｒ１、Ｒ２、Ｒ３，Ｒ４圧力面側の面取り
Ｒ５負圧面側の面取り DESCRIPTION OF SYMBOLS 1 Indoor unit 2 Housing | casing 3 Heat exchanger 4 Motor 5 Impeller 7 Blower 8 Compressor 9 Air path 10 Partition plate 12 Hub 13 Blade 13a Suction side 13b Discharge side 13d, 13e, 13e (a), 13e (b) Outer periphery End (curved part)
13d1, 13e (a) 1, 13e (b) 1 Pressure side 13d2, 13e (a) 2, 13e (b) 12 Negative pressure side 14 Orifice 15 Front edge 16 Rear edge R1, R2, R3, R4 Pressure side Chamfer R5 Chamfer on suction side

Claims

筐体内に、圧縮機と、前記圧縮機と接続される熱交換器と、前記熱交換器を強制通風する送風機と、を収納する機械室で、前記送風機の吸込み側に前記熱交換器を有し、前記送風機と前記圧縮機は仕切板によって左右に仕切って配置される室外ユニットにおいて、前記送風機の羽根の外周径は、吸込み側となる前記羽根の前縁部が最も小さくなるように変形させ、吐出側となる前記羽根の後縁部が最も大きくなるように変形させ、前記前縁部は記送風機のオリフィスの外側に位置し、前記後縁部は前記送風機のオリフィスの内側に位置したことを特徴とした室外ユニット。 A machine room that houses a compressor, a heat exchanger connected to the compressor, and a blower that forcibly ventilates the heat exchanger in a housing, and has the heat exchanger on the suction side of the blower. However, in the outdoor unit in which the blower and the compressor are arranged to be divided into left and right by a partition plate, the outer peripheral diameter of the blade of the blower is deformed so that the front edge of the blade on the suction side becomes the smallest. The rear edge of the blade on the discharge side is deformed to be the largest, the front edge is located outside the orifice of the blower, and the rear edge is located inside the orifice of the blower. An outdoor unit characterized by

前記オリフィスに囲まれていない部分の羽根外周端部を羽根の負圧面側に湾曲させた請求項１に記載の室外ユニット。 The outdoor unit according to claim 1, wherein a blade outer peripheral end portion not surrounded by the orifice is curved toward the suction surface side of the blade.

前記羽根の外周端部は吸込み側から吐出側にかけて羽根の負圧面側に湾曲し、オリフィスに囲まれた吐出側の湾曲部が、オリフィスに囲まれていない吸込み側の湾曲部に比べ小さいことを特徴とした請求項１に記載の室外ユニット。 The outer peripheral edge of the blade is curved toward the suction side of the blade from the suction side to the discharge side, and the discharge side curved portion surrounded by the orifice is smaller than the suction side curved portion not surrounded by the orifice. The outdoor unit according to claim 1, wherein the outdoor unit is characterized.

前記羽根の外周端部の圧力面側に面取りを設けた請求項１から３のいずれかに記載の室外ユニット。 The outdoor unit according to any one of claims 1 to 3, wherein a chamfer is provided on a pressure surface side of an outer peripheral end portion of the blade.

前記羽根の外周端部の圧力面に面取りを設け、オリフィスに囲まれた吐出側の面取りの曲率半径が、オリフィスに囲まれていない吸込み側の面取りの曲率半径に対し小さいことを特徴とした請求項４に記載の室外ユニット。 The pressure surface of the outer peripheral end of the blade is chamfered, and the radius of curvature of the chamfer on the discharge side surrounded by the orifice is smaller than the radius of curvature of the chamfer on the suction side not surrounded by the orifice. Item 5. The outdoor unit according to Item 4.

前記羽根の外周端部のオリフィスに囲まれていない吸込み側では圧力面に面取りを設け、羽根の外周端部のオリフィスに囲まれた吐出側では負圧面に面取りを設けたことを特徴とした請求項１から３のいずれかに記載の室外ユニット。 The pressure surface is chamfered on the suction side not surrounded by the orifice at the outer peripheral end of the blade, and the suction surface is chamfered on the discharge side surrounded by the orifice at the outer peripheral end of the blade. Item 4. The outdoor unit according to any one of Items 1 to 3.

前記羽根の外周端部のオリフィスに囲まれた吐出側では負圧面に設けた面取りの曲率半径が、前記羽根の外周端部のオリフィスに囲まれていない吸込み側の圧力面に設けた面取りの曲率半径より小さいことを特徴とした請求項６に記載の室外ユニット。 On the discharge side surrounded by the orifice at the outer peripheral edge of the blade, the radius of curvature of the chamfer provided on the suction surface is the curvature of the chamfer provided on the suction side pressure surface not surrounded by the orifice at the outer peripheral end of the blade. The outdoor unit according to claim 6, wherein the outdoor unit is smaller than the radius.