JP2006152886A - Cross-flow fan, and indoor unit of air conditioner - Google Patents

Cross-flow fan, and indoor unit of air conditioner Download PDF

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JP2006152886A
JP2006152886A JP2004343027A JP2004343027A JP2006152886A JP 2006152886 A JP2006152886 A JP 2006152886A JP 2004343027 A JP2004343027 A JP 2004343027A JP 2004343027 A JP2004343027 A JP 2004343027A JP 2006152886 A JP2006152886 A JP 2006152886A
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cross
angle
flow fan
blade
fan
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Satoru Okada
覚 岡田
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Toshiba Carrier Corp
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Toshiba Carrier Corp
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Priority to JP2004343027A priority Critical patent/JP2006152886A/en
Priority to KR1020050112741A priority patent/KR100709819B1/en
Priority to CN2005101287226A priority patent/CN1782440B/en
Publication of JP2006152886A publication Critical patent/JP2006152886A/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
    • F24F1/0007—Indoor units, e.g. fan coil units
    • F24F1/0018—Indoor units, e.g. fan coil units characterised by fans
    • F24F1/0025—Cross-flow or tangential fans
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
    • F24F1/0007—Indoor units, e.g. fan coil units
    • F24F1/0043—Indoor units, e.g. fan coil units characterised by mounting arrangements
    • F24F1/0047—Indoor units, e.g. fan coil units characterised by mounting arrangements mounted in the ceiling or at the ceiling

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Air-Conditioning Room Units, And Self-Contained Units In General (AREA)

Abstract

<P>PROBLEM TO BE SOLVED: To provide a cross-flow fan capable of reducing noise while acquiring the same air flow as heretofore. <P>SOLUTION: In this cross-flow fan, the cross section of a blade vertically cut with respect to the longitudinal direction of a fan is formed in a curved state at both pressure face side and negative pressure face side, and the ratio α/β of the incident angle α and outgoing angle β of the cross section is set to be 0.20 to 0.32. Further, the setting angle formed by the straight line connecting the center of the cross-flow fan with the outer peripheral edge of the blade and that connecting the outer peripheral edge with the inner peripheral edge is set to be 20° to 30°. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

本発明は横流ファン及びこの横流ファンを備えた空気調和機の室内機に係り、特に翼の形状及びその取付け角度を改良した横流ファン及びこの横流ファンを備えた空気調和機の室内機に関する。   The present invention relates to a crossflow fan and an air conditioner indoor unit including the crossflow fan, and more particularly to a crossflow fan having an improved blade shape and mounting angle and an air conditioner indoor unit including the crossflow fan.

一般に、この種の横流ファンは空気調和機の室内機の室内ファンとして適し、横流ファンが組込まれる室内機は、本体ケーシングの前面に、吸込グリルと吹出グリルとを上下に配設し、これら吸込グリルと吹出グリルとをファンケーシング内の通風路により連通している。そして、この通風路には、室内側熱交換器の下流側に横流ファンを配設し、吸込グリルから本体ケーシング内へ吸込んだ室内空気を室内側熱交換器で熱交換して、冷風又は暖風を横流ファンにより吹出グリルから室外へ再び送風して冷房又は暖房を行なうようになっている。   In general, this type of cross-flow fan is suitable as an indoor fan for an air conditioner indoor unit, and an indoor unit in which a cross-flow fan is incorporated has a suction grill and a blow-off grill arranged on the front side of the main body casing. The grill and the blow-out grill are communicated with each other through an air passage in the fan casing. In this ventilation path, a cross-flow fan is disposed downstream of the indoor heat exchanger, and the indoor air sucked into the main body casing from the suction grille is heat-exchanged by the indoor heat exchanger, so that cold air or warm air is exchanged. The air is blown again from the blow grill to the outside by a cross-flow fan for cooling or heating.

ところで、上述した空気調和機では、送風時の送風音を低減することが高性能化を図るうえで特に望まれている。   By the way, in the air conditioner mentioned above, reducing the blowing sound at the time of ventilation is especially desired in order to improve performance.

これに対応して、送風効率向上及び騒音低減を目的とする種々の提案がなされている。   In response to this, various proposals have been made for the purpose of improving the air blowing efficiency and reducing noise.

例えば、特許文献１には、外周羽角度、内周羽角度、節弦比との関係を特定することにより、風量及び静圧を向上するようにした横流ファンが記載されている。また、特許文献２には、空気調和機の室内機に組込まれる横流ファンの翼出口角を２３°以下にすることにより、低周波数帯の特異音の低減したものが記載されている。   For example, Patent Document 1 describes a cross-flow fan that improves the air volume and static pressure by specifying the relationship between the outer wing angle, the inner wing angle, and the chord ratio. Further, Patent Document 2 describes one in which the singular noise in the low frequency band is reduced by setting the blade outlet angle of the cross flow fan incorporated in the indoor unit of the air conditioner to 23 ° or less.

しかしながら、特許文献１、２に記載の横流ファンは翼の取付け角度などに改良の余地があり、横流ファンの送風効率及び騒音の低減は、未だ満足できるレベルではない。
特開平６−３２３２９４号公報 特開平１１−８３０６２号公報 However, the crossflow fans described in Patent Documents 1 and 2 have room for improvement in the blade mounting angle and the like, and the airflow efficiency and noise reduction of the crossflow fan are not yet satisfactory.
JP-A-6-323294 Japanese Patent Laid-Open No. 11-83062

本発明は上述した事情を考慮してなされたもので、従来と同一風量を得ながら騒音の低減が可能な横流ファン、空気調和機の室内機を提供することを目的とする。   The present invention has been made in view of the above-described circumstances, and an object of the present invention is to provide a cross-flow fan and an air conditioner indoor unit that can reduce noise while obtaining the same air volume as before.

本発明者等は、上記目的実現のために、鋭意研究した結果、横流ファンの翼断面の入射角と出射角の比と、横流ファン中心と翼の外周側端縁とを結ぶ直線とその外周側端縁と内周側端縁とを結ぶ直線とのなす角度である取付角の組合せが騒音に大きく影響していることを突き止め、これらを最適な組合せとすることにより、騒音低減を実現させ、本発明に想到した。   As a result of diligent research to achieve the above object, the present inventors have found that the ratio of the incident angle and the exit angle of the cross section of the cross flow fan blade, the straight line connecting the cross flow fan center and the outer peripheral edge of the blade, and the outer periphery thereof. Ascertaining that the combination of mounting angles, which is the angle between the side edge and the straight line connecting the inner peripheral edge, has a significant effect on noise, and making these optimal combinations achieves noise reduction. The present invention has been conceived.

すなわち、本発明に係る横流ファンは、複数の支持板間に複数枚の翼を環状に配列して形成された横流ファンにおいて、ファン長手方向に対し垂直に切断した翼断面形状が圧力面側、負圧面側ともに曲線状に形成されるとともに、翼断面の入射角αと出射角βの比α／βを０．２０〜０．３２とし、かつ、横流ファン中心と翼の外周側端縁とを結ぶ直線と、その外周側端縁と内周側端縁とを結ぶ直線とのなす角度である取付角を２０°〜３０°としたことを特徴とする。   That is, the cross-flow fan according to the present invention is a cross-flow fan formed by annularly arranging a plurality of blades between a plurality of support plates, the blade cross-sectional shape cut perpendicularly to the fan longitudinal direction is the pressure surface side, The suction surface side is formed in a curved shape, the ratio α / β of the incident angle α and the outgoing angle β of the blade cross section is 0.20 to 0.32, and the cross flow fan center and the outer peripheral edge of the blade are And a mounting angle that is an angle formed by a straight line connecting the outer peripheral side edge and the inner peripheral side edge is set to 20 ° to 30 °.

また、本発明に係る空気調和機の室内機は、請求項１または２に記載の横流ファンを備え、吸込角θ１を１４５°〜１６０°、巻き始め角θ２を４５°〜５０°、巻き始め長さＬ１と横流ファン径φの比Ｌ１／φを０．１８〜０．２２、巻き始め隙間ｔと横流ファン径φの比ｔ／φを０．０４〜０．０６としたことを特徴とする。   Moreover, the indoor unit of the air conditioner according to the present invention includes the cross-flow fan according to claim 1, wherein the suction angle θ1 is 145 ° to 160 °, the winding start angle θ2 is 45 ° to 50 °, and the winding starts. The ratio L1 / φ between the length L1 and the crossflow fan diameter φ is 0.18 to 0.22, and the ratio t / φ between the winding start gap t and the crossflow fan diameter φ is 0.04 to 0.06. To do.

本発明に係る横流ファン、空気調和機の室内機によれば、従来と同一風量を得ながら騒音の低減が可能な横流ファン、空気調和機の室内機を提供することができる。   According to the cross-flow fan and air conditioner indoor unit of the present invention, it is possible to provide a cross-flow fan and air conditioner indoor unit capable of reducing noise while obtaining the same air volume as before.

以下、本発明に係る横流ファンの一実施形態について添付図面を参照して説明する。   Hereinafter, an embodiment of a cross-flow fan according to the present invention will be described with reference to the accompanying drawings.

図１は本発明の一実施形態に係る横流ファンの斜視図であり、図２はその分解斜視図、図３はその多翼羽車の斜視図である。   FIG. 1 is a perspective view of a cross-flow fan according to an embodiment of the present invention, FIG. 2 is an exploded perspective view thereof, and FIG. 3 is a perspective view of a multi-blade impeller.

図１に示すように、本実施形態に係る横流ファン１は、空気調和機の室内機の室内ファンとして組み込んで用いるのに好適であり、支持板を構成する左右一対の円板状の端板１０、１１及び複数の環状の仕切板１２間に、複数の翼１３を同心状に配するとともに、この翼１３を中心軸ｏに対し所定角度傾斜させて横架固着しており、中心軸線ｏ周りに回転することにより送風するようになっている。   As shown in FIG. 1, the cross-flow fan 1 according to the present embodiment is suitable for being incorporated and used as an indoor fan of an indoor unit of an air conditioner, and includes a pair of left and right disc-shaped end plates that constitute a support plate. A plurality of wings 13 are concentrically arranged between 10, 11 and the plurality of annular partition plates 12, and the wings 13 are horizontally fixed while being inclined at a predetermined angle with respect to the center axis o. It is designed to blow air by rotating around.

図２に示すように、この横流ファン１は一体成形の複数駒の多翼羽車１４を軸方向に順次同心状に固着してなり、図中右端の多翼羽根車１４の端板１０には、図示しないモータ等の回転軸を止めねじ等により着脱自在に結合させるボス部１０ａを同心状に一体、または一体的に形成している。   As shown in FIG. 2, the cross-flow fan 1 is formed by integrally fixing a plurality of integrally formed multi-blade impellers 14 concentrically in the axial direction, and is attached to the end plate 10 of the multi-blade impeller 14 at the right end in the figure. A boss portion 10a for detachably coupling a rotation shaft of a motor or the like (not shown) with a set screw or the like is integrally or integrally formed concentrically.

一方、図中、左端の端板１１は、その図中右隣の多翼羽根車１４の各翼１３の先端部を各嵌合溝１１ａ内に嵌入固着させるものであり、その外面中央部には同心状に軸１１ｂを一体、または一体的に突設している。   On the other hand, the end plate 11 at the left end in the figure is for fitting and fixing the tip end of each blade 13 of the multi-blade impeller 14 on the right side in the figure into each fitting groove 11a. The shaft 11b is formed concentrically or integrally.

図２及び図３に示すように、各多翼羽根車１４は、環状の仕切板１２の一面に、隣り合う多翼羽根車１４の各翼１３の先端部をそれぞれ嵌入させて固着する嵌合凹部１２ａを形成する一方、仕切板１２の他面には、複数の翼１３を周方向に取付ピッチを不等間隔にするとともに、中心軸線ｏに対し所定角度傾斜させて射出成型等により一体に立設している。   As shown in FIGS. 2 and 3, each multiblade impeller 14 is fitted into one surface of an annular partition plate 12 so that the tip of each blade 13 of the adjacent multiblade impeller 14 is fitted and fixed. While the recess 12a is formed, the other surface of the partition plate 12 is integrally formed by injection molding or the like with a plurality of blades 13 provided at uneven intervals in the circumferential direction and inclined at a predetermined angle with respect to the central axis o. Standing up.

次に、翼１３の断面形状について説明する。図４は図１のＡ―Ａ断面、すなわち、横流ファン１の長手方向（中心軸線ｏ）に対し垂直に切断した断面（翼は２枚のみ示す）であり、図５はその要部拡大図である。   Next, the cross-sectional shape of the wing 13 will be described. 4 is a cross-sectional view taken along the line AA in FIG. 1, that is, a cross-section (only two blades are shown) cut perpendicular to the longitudinal direction (center axis o) of the cross-flow fan 1, and FIG. It is.

翼１３の翼断面形状は圧力面１３ａ、負圧面１３ｂともに曲線状に形成されている。また翼１３の入射角度αと出射角度βとの関係がα／β＝０．２０〜０．３２で、翼の取付角度θを２０°〜３０°となるようにしてある。ここで、入射角度αとは、翼１３の外周側端縁ａにおける翼曲線（肉厚中心）の接線ｂと、中心（軸線）ｏと外周側端縁ａとを結ぶ直線ｃの外周側端縁ａにおける垂線ｄとのなす角度である。   The blade cross-sectional shape of the blade 13 is formed in a curved shape on both the pressure surface 13a and the suction surface 13b. Further, the relation between the incident angle α and the outgoing angle β of the blade 13 is α / β = 0.20 to 0.32, and the blade mounting angle θ is set to 20 ° to 30 °. Here, the incident angle α is the outer peripheral end of a straight line c connecting the tangent line b of the blade curve (thickness center) at the outer peripheral edge a of the blade 13 and the center (axis) o and the outer peripheral edge a. This is the angle formed by the perpendicular d at the edge a.

また、出射角度βとは、翼１３の内周側端縁ｅにおける翼曲線の接線ｆと、中心軸線ｏと内周側端縁ｅとを結ぶ直線ｇの内周側端縁ｅにおける垂線ｈとのなす角度である。   The emission angle β is a perpendicular h at the inner peripheral edge e of a straight line g connecting the tangent line f of the blade curve at the inner peripheral edge e of the blade 13 and the central axis o and the inner peripheral edge e. The angle between

さらに、取付角度θとは、翼外周側端縁ａと翼内周側端縁ｅとを結ぶ直線ｉと、中心（軸線）ｏと翼外周側端縁ａを結ぶ直線ｃとのなす角度である。   Further, the attachment angle θ is an angle formed by a straight line i connecting the blade outer peripheral edge a and the blade inner peripheral edge e and a straight line c connecting the center (axis) o and the blade outer peripheral edge a. is there.

また、図６に示すように、翼１３の断面形状において、負圧面１３ｂ側の外周側に直線部（平面部）１３ｃを形成し、その直線部１３ｃの長さの割合を翼１３の弦長をＬ、直線部の長さをｌとした場合、ｌ／Ｌ＝０．０５〜０．２０の範囲とするのが好ましい。これにより、全て曲線からなり直線部を設けないものに比較して、吸込み時の剥離低減効果がより大きくなり、騒音は上記実施例に対してさらに低減効果が得られる。また、直線部を翼外周側へ設けることにより、埃付着を軽減でき、サージング特性が向上する。   Further, as shown in FIG. 6, in the cross-sectional shape of the blade 13, a straight portion (plane portion) 13 c is formed on the outer peripheral side on the suction surface 13 b side, and the ratio of the length of the straight portion 13 c is the chord length of the blade 13. Is L and the length of the straight line portion is l, it is preferable that l / L = 0.05 to 0.20. As a result, the effect of reducing the peeling at the time of suction is greater and the noise can be further reduced as compared with the above-described embodiment, as compared with the case where all of the curves are formed and the straight portion is not provided. Further, by providing the straight portion on the blade outer peripheral side, dust adhesion can be reduced, and surging characteristics are improved.

本発明者等が入射角度αと出射角度βの比α／β、及び取付角度θを変化させて騒音測定試験を行った結果を示した表１から明らかなように、入射角度αと出射角度βの比α／βを０．２０〜０．３２とし、かつ、取付角度を２０°〜３０°とした場合には、同一風量時の騒音低減効果が得られることがわかる。これに対して、α／βまたは取付角度のいずれか一方のみを本発明の条件（数値）範囲にしても、十分な騒音低減効果が得られないことがわかる。   As is apparent from Table 1 showing the results of the noise measurement test performed by the inventors changing the ratio α / β of the incident angle α and the outgoing angle β and the mounting angle θ, the incident angle α and the outgoing angle. It can be seen that when the β ratio α / β is 0.20 to 0.32 and the mounting angle is 20 ° to 30 °, a noise reduction effect at the same air volume can be obtained. On the other hand, it can be seen that a sufficient noise reduction effect cannot be obtained even when only one of α / β and the mounting angle is within the condition (numerical value) range of the present invention.

また、上記試験結果を示す図７は、上記数値条件内の実施例と数値条件範囲外の比較例の静圧−風量、ファン効率−風量の関係を示すものであり、実施例は比較例に対して、静圧が向上して空気の流れがよくなり、騒音を低減させることができ、また、ファン効率が向上していることがわかる。当該試験に用いた実施例の翼は、α／βが０．２６、取付角度が２５°のものであり、比較例の翼はα／βが０．３４、取付角度が３０°のものである。   Moreover, FIG. 7 which shows the said test result shows the relationship of the static pressure-air volume and fan efficiency-air volume of the Example within the said numerical conditions, and the comparative example outside a numerical condition range, and an Example is a comparative example. On the other hand, it can be seen that the static pressure is improved, the air flow is improved, noise can be reduced, and the fan efficiency is improved. The blade of the example used in the test has an α / β of 0.26 and an attachment angle of 25 °, and the blade of the comparative example has an α / β of 0.34 and an attachment angle of 30 °. is there.

なお、翼断面形状における圧力面１３ａ、負圧面１３ｂの曲線形状は、１つ又は複数の円弧で形成してもよいし、スパイラル曲線等で形成してもよい。特に複数の円弧またはスパイラル曲線で形成すると、上記数値範囲の翼を形成するのが容易である。さらに、スパイラル曲線にした場合には、圧力面１３ａ、負圧面１３ｂの内周側から外周側の全体に渡ってより滑らかな曲線に形成することができ、複数の円弧で形成したものに比べて、剥離を防止して騒音低減効果を増大することができる。   The curved shapes of the pressure surface 13a and the negative pressure surface 13b in the blade cross-sectional shape may be formed by one or a plurality of arcs, spiral curves, or the like. In particular, when a plurality of circular arcs or spiral curves are formed, it is easy to form wings in the above numerical range. Furthermore, in the case of a spiral curve, it can be formed into a smoother curve from the inner peripheral side to the outer peripheral side of the pressure surface 13a and the negative pressure surface 13b, as compared with those formed by a plurality of arcs. , Peeling can be prevented and the noise reduction effect can be increased.

本第１実施形態の横流ファンによれば、上記複数の翼を中心軸ｏに対し所定角度傾斜させているので、横流ファンを組込んだ装置のノーズとファンケーシングの間隙で発生する圧力を連続的に変動させることができて、横流ファンの回転音を低減することができ、また周方向の取付ピッチを不等間隔に設定しているので、複数翼の傾斜形状により低減せしめた回転音のピーク周波数を分散させることができ、耳障り感を低減して聴感を改善することができるとともに、さらに、翼断面形状が圧力面側、負圧面側ともに曲線状に形成されるとともに、翼断面の入射角度αと出射角度βの比α／βを０．２０〜０．３２とし、かつ、横流ファン中心と翼の外周側端縁とを結ぶ直線と、その外周側端縁と内周側端縁とを結ぶ直線とのなす角度である取付角度が２０°〜３０°であるので、同一風量時の騒音低減が可能となる。すなわち、翼の所定角度傾斜させた取付け、取付けピッチの不等間隔化の作用に加えて、入射角度と出射角度の比及び取付け角度の同時規制による作用の相乗効果により、同一風量時の騒音低減が実現される。   According to the cross flow fan of the first embodiment, since the plurality of blades are inclined at a predetermined angle with respect to the central axis o, the pressure generated at the gap between the nose of the apparatus incorporating the cross flow fan and the fan casing is continuously applied. The rotational sound of the cross flow fan can be reduced, and the circumferential mounting pitch is set at unequal intervals. The peak frequency can be dispersed, the harshness can be reduced and the hearing can be improved. In addition, the blade cross-sectional shape is curved on both the pressure side and suction side, and the incidence of the blade cross-section is incident. The ratio α / β of the angle α and the emission angle β is 0.20 to 0.32, the straight line connecting the center of the cross flow fan and the outer peripheral edge of the blade, the outer peripheral edge and the inner peripheral edge The angle formed by the straight line connecting The angle is at 20 ° to 30 °, it is possible to reduce noise at the same air volume. In other words, in addition to the effect of mounting the blades at a predetermined angle and making the mounting pitch non-uniformly spaced, the synergistic effect of the effect of simultaneous control of the ratio of the incident angle and the outgoing angle and the mounting angle reduces noise at the same air volume. Is realized.

次に本発明の横流ファンを組み込んだ空気調和機の室内機の一実施形態について説明する。   Next, an embodiment of an indoor unit of an air conditioner incorporating the cross-flow fan of the present invention will be described.

図８は本実施形態に係る空気調和機の室内機の縦断面図である。   FIG. 8 is a longitudinal sectional view of the indoor unit of the air conditioner according to the present embodiment.

図８に示すように、本実施形態に係る空気調和機の室内機１００は、本体ケーシング１０１の前面１０１ａに、吸込グリル１０２と吹出グリル１０３とを図中上下に配設し、これら吸込グリル１０２と吹出グリル１０３とをファンケーシング１０４内の通風路１０５により連通している。   As shown in FIG. 8, the indoor unit 100 of the air conditioner according to the present embodiment has a suction grill 102 and a blow grill 103 arranged on the front surface 101 a of the main body casing 101 in the vertical direction in the figure. And the blowout grill 103 are communicated with each other through a ventilation path 105 in the fan casing 104.

この通風路１０５には、室内側熱交換器１０６の下流側に室内ファンとして本発明に係る横流ファン１を配設し、吸込グリル１０２から本体ケーシング１０１内へ吸込んだ室内空気を室内側熱交換器１０６で熱交換して、冷風又は暖風を横流ファン１により吹出グリル１０３から室外へ再び送風して冷房又は暖房を行なうようになっている。   In this ventilation path 105, the cross-flow fan 1 according to the present invention is disposed as an indoor fan downstream of the indoor heat exchanger 106, and indoor air sucked into the main body casing 101 from the suction grill 102 is exchanged indoors. Heat is exchanged in the cooler 106, and cool air or warm air is again blown from the blow grill 103 to the outside by the cross-flow fan 1 to perform cooling or heating.

図９に示すように、吸込角θ１、すなわちノーズ１０７と横流ファン１との最小隙間ｔ１となる点と横流ファン中心ｏとを結んだ線ｊと、ファンケーシング１０４の最上部１０４ａと横流ファン中心ｏとを結んだ線ｋとの角度を１４５°〜１６０°、ファンケーシング１０４の巻始め角θ２、すなわちファンケーシング１０４の最上部１０４ａの延長線ｌと最上部１０４ａを通る水平線ｍとの角度を４５°〜５０°、ファンケーシング１０４の巻始め長さＬ１すなわち最上部１０４ａとファンケーシング１０４と横流ファンと最小隙間ｔ２となる点１０４ｂとの距離を横流ファン径φに対して、Ｌ１／φ＝０．１８〜０．２２、巻始め隙間ｔ２をｔ２／φ＝０．０４〜０．０６とする。   As shown in FIG. 9, the line j connecting the suction angle θ 1, that is, the point where the nose 107 and the cross-flow fan 1 become the minimum gap t 1 and the cross-flow fan center o, the uppermost portion 104 a of the fan casing 104, and the cross-flow fan center. The angle with the line k connecting o is 145 ° to 160 °, the winding start angle θ2 of the fan casing 104, that is, the angle between the extension line 1 of the uppermost part 104a of the fan casing 104 and the horizontal line m passing through the uppermost part 104a. 45 ° to 50 °, the winding start length L1 of the fan casing 104, that is, the distance between the uppermost portion 104a, the fan casing 104, the cross-flow fan, and the point 104b where the minimum gap t2 is given, is L1 / φ = 0.18 to 0.22, and the winding start gap t2 is set to t2 / φ = 0.04 to 0.06.

本実施形態に係る空気調和機の室内機は、上述した本発明の横流ファンを組込み、吸込角度θ１を１４５°〜１６０°、巻始め角度θ２を４５°〜５０°、巻始め長さＬ１と横流ファン径φの比Ｌ１／φを０．１８〜０．２２、巻始め隙間ｔと横流ファン径φの比ｔ／φが０．０４〜０．０６としたので、上述した本発明の横流ファン単体の騒音低減効果との相乗作用によって、同一風量当りの騒音がより低減可能となり、またファン効率が向上して、外周側での埃付着量が低減できサージング特性が向上する。   The indoor unit of the air conditioner according to the present embodiment incorporates the above-described cross-flow fan of the present invention, the suction angle θ1 is 145 ° to 160 °, the winding start angle θ2 is 45 ° to 50 °, and the winding start length L1 is The ratio L1 / φ of the crossflow fan diameter φ is 0.18 to 0.22, and the ratio t / φ of the winding start gap t and the crossflow fan diameter φ is 0.04 to 0.06. The synergistic effect with the noise reduction effect of the fan alone makes it possible to further reduce the noise per unit air flow, improve the fan efficiency, reduce the amount of dust adhesion on the outer peripheral side, and improve the surging characteristics.

なお、上記実施形態では、横流ファンは複数の翼を中心軸線に対し所定角度傾斜するとともに、周方向に取付けピッチを不等間隔にした例で説明したが、本発明に係る横流ファンはこれに限定されるものではない。

Figure 2006152886
In the above embodiment, the cross flow fan has been described with an example in which a plurality of blades are inclined at a predetermined angle with respect to the central axis, and the mounting pitch is unevenly spaced in the circumferential direction, but the cross flow fan according to the present invention is not limited thereto. It is not limited.
Figure 2006152886

本発明に係る横流ファンの斜視図。The perspective view of the crossflow fan which concerns on this invention. 本発明に係る横流ファンの分解斜視図。The disassembled perspective view of the crossflow fan which concerns on this invention. 本発明に係る横流ファンに用いられる多翼羽根車の斜視図。The perspective view of the multiblade impeller used for the crossflow fan which concerns on this invention. 図１のＡ−Ａ線に沿う断面図。Sectional drawing in alignment with the AA of FIG. 図４の要部を拡大して示す断面図。Sectional drawing which expands and shows the principal part of FIG. 本発明に係る横流ファンの翼の他の実施例の断面図。Sectional drawing of the other Example of the blade | wing of the crossflow fan based on this invention. 本発明に係る横流ファンの特性試験の結果図。The result figure of the characteristic test of the crossflow fan based on this invention. 本発明に係る空気調和機の室内機の縦断面図。The longitudinal cross-sectional view of the indoor unit of the air conditioner which concerns on this invention. 図８の横流ファン及びケーシングの関係を示す説明図。Explanatory drawing which shows the relationship between the crossflow fan of FIG. 8, and a casing.

符号の説明Explanation of symbols

１…横流ファン、１０、１１…端板、１１ｂ…軸、１２…仕切板、１３…翼、１３ａ…圧力面、１３ｂ…負圧面、１４…多翼羽車。   DESCRIPTION OF SYMBOLS 1 ... Cross-flow fan, 10, 11 ... End plate, 11b ... Shaft, 12 ... Partition plate, 13 ... Blade | wing, 13a ... Pressure surface, 13b ... Negative pressure surface, 14 ... Multi-blade impeller.

Claims (3)

複数の支持板間に複数枚の翼を環状に配列して形成された横流ファンにおいて、ファン長手方向に対し垂直に切断した翼断面形状が圧力面側、負圧面側ともに曲線状に形成されるとともに、前記翼の外周側端縁における翼曲線の接線と、前記横流ファンの中心と前記外周側端縁とを結ぶ直線の前記外周側端縁における垂線とのなす入射角の角度をαとし、前記翼の内周側端縁における翼曲線の接線と、前記横流ファンの中心と前記内周側端縁とを結ぶ直線の前記内周側端縁における垂線とのなす出射角の角度をβとするとき、入射角度αと出射角度βとの比α／βを０．２０〜０．３２とし、かつ、横流ファン中心と翼の外周側端縁とを結ぶ直線と、その外周側端縁と内周側端縁とを結ぶ直線とのなすである取付角の角度を２０°〜３０°としたことを特徴とする横流ファン。 In a crossflow fan formed by annularly arranging a plurality of blades between a plurality of support plates, the blade cross-sectional shape cut perpendicular to the longitudinal direction of the fan is formed in a curved shape on both the pressure surface side and the suction surface side. In addition, the angle of incidence angle between the tangent line of the blade curve at the outer peripheral edge of the blade and the perpendicular line at the outer peripheral edge of the straight line connecting the center of the cross flow fan and the outer peripheral edge is α, The angle of the emission angle between the tangent line of the blade curve at the inner peripheral edge of the blade and the perpendicular line at the inner peripheral edge of the straight line connecting the center of the cross flow fan and the inner peripheral edge is β. When the ratio α / β of the incident angle α and the outgoing angle β is 0.20 to 0.32, a straight line connecting the center of the cross flow fan and the outer peripheral edge of the blade, and the outer peripheral edge The angle of the mounting angle formed by the straight line connecting the inner edge is set to 20 ° to 30 °. A cross-flow fan characterized by 請求項１に記載の横流ファンにおいて、前記翼断面形状が、負圧面側の外周側に直線部を有し、その直線部の長さｌと翼の弦長Ｌの比ｌ／Ｌを０．０５〜０．２の範囲としたことを特徴とする横流ファン。 2. The cross-flow fan according to claim 1, wherein the blade cross-sectional shape has a straight portion on the outer peripheral side on the suction surface side, and a ratio 1 / L of the length l of the straight portion to the chord length L of the blade is set to 0. A cross-flow fan characterized by having a range of 05 to 0.2. 請求項１または２に記載の横流ファンを備え、ノーズと横流ファン間が最小隙間となる点と横流ファン中心を結んだ線と、ファンケーシングの最上部と横流ファン中心を結んだ線とがなす吸込角の角度θ１を１４５°〜１６０°、前記最上部の延長線と前記最上部を通る水平線とがなす前記ファンケーシングの巻始め角の角度θ２を４５°〜５０°、前記最上部から前記ファンケーシングと前記横流ファン間に形成される最小隙間の巻始め隙間ｔ２となる点までの距離である巻始め長さＬ１と、横流ファン径φとの比Ｌ１／φを０．１８〜０．２２、前記巻始め隙間ｔ２と前記横流ファン径φとの比ｔ２／φを０．０４〜０．０６としたことを特徴とする空気調和機の室内機。 A cross flow fan according to claim 1 or 2, comprising a line connecting the cross flow fan center and a point where the nose and the cross flow fan have a minimum gap, and a line connecting the top of the fan casing and the cross flow fan center. The angle θ1 of the suction angle is 145 ° to 160 °, the angle θ2 of the winding start angle of the fan casing formed by the extension line of the uppermost part and the horizontal line passing through the uppermost part is 45 ° to 50 °, and from the uppermost part The ratio L1 / φ between the winding start length L1 which is the distance to the point where the minimum gap formed between the fan casing and the crossflow fan becomes the winding start gap t2 and the crossflow fan diameter φ is set to 0.18-0. 22. An indoor unit of an air conditioner, wherein a ratio t2 / φ between the winding start gap t2 and the cross-flow fan diameter φ is 0.04 to 0.06.
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