JP2001193956A - Indoor unit of air-conditioner - Google Patents
Indoor unit of air-conditionerInfo
- Publication number
- JP2001193956A JP2001193956A JP2000266829A JP2000266829A JP2001193956A JP 2001193956 A JP2001193956 A JP 2001193956A JP 2000266829 A JP2000266829 A JP 2000266829A JP 2000266829 A JP2000266829 A JP 2000266829A JP 2001193956 A JP2001193956 A JP 2001193956A
- Authority
- JP
- Japan
- Prior art keywords
- fan
- blade
- air
- indoor unit
- maximum thickness
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
Abstract
Description
【0001】[0001]
【発明の属する技術分野】本発明は、室内の冷房あるい
は暖房を行う空気調和機の室内ユニットに用いられてい
る貫流ファンに関するものである。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a cross-flow fan used in an indoor unit of an air conditioner for cooling or heating a room.
【0002】[0002]
【従来の技術】従来の空気調和機は特開平9−1007
95号公報に記載されているように、図6のような形状
となっている。前記貫流ファン1を円板2で仕切られる
複数のブロックに分割し、少なくとも一つのブロックの
羽根3の外径をそのブロックの円板間において変化する
部分を有し、前記少なくとも一つのブロックと隣接する
ブロックの隣接部での羽根外径が異なる構造とする。2. Description of the Related Art A conventional air conditioner is disclosed in JP-A-9-1007.
As described in Japanese Patent Publication No. 95, the shape is as shown in FIG. The cross-flow fan 1 is divided into a plurality of blocks partitioned by a disk 2 and has a portion where the outer diameter of the blade 3 of at least one block changes between the disks of the block, and is adjacent to the at least one block. The structure is such that the outer diameters of the blades are different at the adjacent portions of the blocks.
【0003】従来の空気調和機は特開平10−7798
8号公報に記載されているように、図7のような形状と
なっている。円板状または環状の一対の端板2−1、2
―2間に複数の羽根3を周方向に所定の取付ピッチで環
状に配して横架固着し、羽根3の軸方向中間部に端板2
を配設する。羽根3の軸方向両端部を翼弦長の長い拡幅
部Lb、Lcに形成する一方、軸方向中間部Laを翼弦長
の短い弦幅部Laに一体に連成する。A conventional air conditioner is disclosed in Japanese Patent Application Laid-Open No. 10-7798.
As described in Japanese Unexamined Patent Publication No. 8 (KOKAI) No. 8, the shape is as shown in FIG. A pair of disk-shaped or annular end plates 2-1 and 2
, A plurality of blades 3 are arranged in a ring at a predetermined mounting pitch in the circumferential direction and fixed laterally between them, and an end plate 2 is provided at an intermediate portion of the blades 3 in the axial direction.
Is arranged. Both ends in the axial direction of the blade 3 are formed into widened portions Lb and Lc having a long chord length, while the intermediate portion La in the axial direction is integrally connected to a chord width portion La having a short chord length.
【0004】そして、これらのブレード形状の肉厚分布
は、以下の2種に分類される。第1は、前縁から後縁に
かけて肉厚が一定であるものである。第2は、最大肉厚
位置が、前縁と後縁の中間にあるものである。The thickness distribution of these blade shapes is classified into the following two types. First, the thickness is constant from the leading edge to the trailing edge. Second, the maximum thickness position is located between the leading edge and the trailing edge.
【0005】[0005]
【発明が解決しようとする課題】しかしながら、上記第
1の従来例のファンのブレードでは、負荷がかかった時
(空気清浄用フィルタにゴミが付着した時等)にブレー
ドの長さが異なるため、2次元流れが崩れ易い。そのた
め、側壁部近傍では特に2次元流れが崩れ易く、「バサ
バサ」という断続的な異常音が発生するため極めて不快
感を呈する。さらに、負荷がかかった時、著しく送風性
能が劣化するため、冷房能力または暖房能力が低下す
る。However, in the fan blade of the first conventional example, the length of the blade differs when a load is applied (for example, when dust adheres to the air cleaning filter). Two-dimensional flow easily collapses. Therefore, especially in the vicinity of the side wall, the two-dimensional flow is easily broken, and an intermittent abnormal sound called “unsteady sound” is generated. Further, when a load is applied, the air blowing performance is significantly deteriorated, so that the cooling capacity or the heating capacity is reduced.
【0006】上記第2の従来例のファンのブレードにお
いても、同様の課題を有している。また、図8に示す、
従来のブレード形状による吹き出し部の流速ベクトルか
ら明らかなように、前縁部での流れの剥離がおき、乱流
がおきていることがわかる。本発明はこのような従来の
課題を解決するものであり、貫流ファンのブレード形状
の肉厚分布の与え方として、最大肉厚位置を中央より内
側にすることにより、負荷がかかった時にも、安定した
流れ場を形成することができる。The above-mentioned second conventional fan blade also has the same problem. Also, as shown in FIG.
As is apparent from the flow velocity vector of the blow-out portion due to the conventional blade shape, it can be seen that the flow is separated at the leading edge and turbulent flow occurs. The present invention is to solve such a conventional problem, as a way of giving the thickness distribution of the blade shape of the once-through fan, even when a load is applied by setting the maximum thickness position inside the center, A stable flow field can be formed.
【0007】[0007]
【課題を解決するための手段】上記課題を解決するため
に本発明は、室内機の送風ファンとして貫流ファンを備
えた空気調和機において、前記貫流ファンのブレード形
状の肉厚分布の与え方として、最大肉厚位置を内側にし
たことを特徴とすることである。SUMMARY OF THE INVENTION In order to solve the above-mentioned problems, the present invention relates to an air conditioner provided with a once-through fan as a blower fan for an indoor unit, and a method of giving a blade-shaped thickness distribution of the once-through fan. , Characterized in that the maximum thickness position is on the inside.
【0008】さらに、顕著に効果を呈するために、前記
貫流ファンのブレード形状の最大肉厚位置が、弦長の内
側から2%〜35%の位置にすることを特徴とすること
である。Further, in order to exhibit a remarkable effect, the maximum thickness position of the blade shape of the once-through fan is set at a position of 2% to 35% from the inside of the chord length.
【0009】[0009]
【実施例】以下本発明の実施例について図面を参照して
説明する。Embodiments of the present invention will be described below with reference to the drawings.
【0010】図1は本発明の第1の実施例における、空
気調和機の室内機に搭載されているクロスフローファン
の断面図と、そのクロスフローファンの1個のブレード
の拡大図である。そのブレードの弦長は、線分IOで表
わされる。その線分の中央より内側に最大肉厚位置を配
設することを特徴とするブレード形状である。FIG. 1 is a cross-sectional view of a cross-flow fan mounted on an indoor unit of an air conditioner and an enlarged view of one blade of the cross-flow fan in the first embodiment of the present invention. The chord length of the blade is represented by a line segment IO. The blade shape is characterized in that the maximum thickness position is disposed inside the center of the line segment.
【0011】最大肉厚位置を、弦長の内側から2%〜6
0%の位置に変化させて、そのP−Q特性を分析した結
果を図2に示す。開放点での傾斜が、静圧の高低を表わ
す。その傾斜と肉厚分布位置の関係を図3に示す。これ
より、静圧の上昇しているピークが、4%付近と20%
付近にあり、また、最大肉厚位置が内周側に移動するほ
ど、静圧の上昇する傾向にある。従って、最大肉厚位置
が、2%〜35%の位置で安定して高静圧が得られるこ
とがわかる。さらに、騒音あたりの風量性能を図4に示
す。これより、最大肉厚位置が弦長の内側から2%〜3
5%の領域では、ほぼ安定している。ここでも、中央よ
り内側に2%〜35%の位置に最大肉厚位置があると騒
音あたりの風量性能が安定していることがわかる。The maximum thickness position is 2% to 6% from the inside of the chord length.
FIG. 2 shows the result of analyzing the PQ characteristics by changing the position to 0%. The slope at the open point indicates the level of static pressure. FIG. 3 shows the relationship between the inclination and the thickness distribution position. From this, the peak where the static pressure rises is around 4% and 20%
And the static pressure tends to increase as the maximum thickness position moves toward the inner peripheral side. Therefore, it is understood that a high static pressure can be stably obtained at the position where the maximum thickness position is 2% to 35%. FIG. 4 shows the air volume performance per noise. Thus, the maximum thickness position is 2% to 3% from the inside of the chord length.
In the region of 5%, it is almost stable. Here also, it can be seen that the air volume performance per noise is stable when the maximum thickness position is at a position of 2% to 35% inside the center.
【0012】これにより、図5に示す、本実施例ブレー
ド形状による吹き出し部の流速ベクトルから明らかなよ
うに、前縁部での流れの剥離が減少して、スムーズな流
れを生み出し、風量性能を向上することができた。Thus, as is apparent from the flow velocity vector of the blow-off portion having the blade shape of the present embodiment shown in FIG. 5, the separation of the flow at the leading edge is reduced, so that a smooth flow is produced and the air volume performance is improved. Could be improved.
【0013】[0013]
【発明の効果】上記実施例から明らかなように、高静圧
化されているため、エアコン本体に負荷がかかろうとも
バサバサという異常音が発生しにくい。また、冷暖房時
に吹き出し部に着目して流れの状況を分析すると、前縁
部での流れの剥離が減少して風量性能が向上する。ま
た、翼間の最短距離から吹き出し部にかけて徐々に拡大
していくため、後縁剥離が減少して風量性能が向上す
る。As is apparent from the above embodiment, since the static pressure is increased, an abnormal noise is less likely to occur even if a load is applied to the air conditioner body. In addition, when the flow condition is analyzed by paying attention to the blowout portion during cooling and heating, the separation of the flow at the leading edge is reduced, and the air volume performance is improved. In addition, since the width gradually increases from the shortest distance between the blades to the blowout portion, trailing edge separation is reduced and the air volume performance is improved.
【0014】以上の現状から、乱流成分が減少して騒音
も低減されることになり、同一騒音当たりの風量性能が
向上する。さらに、開放点付近での圧力が上昇すること
になり、エアコンなどに応用されるとき、冷房時の熱交
換器の露付き、フィルタにゴミが付着した時などに発生
する(バサバサ音)などを抑制することができる。From the above situation, the turbulence component is reduced and the noise is reduced, and the air volume performance per the same noise is improved. Furthermore, the pressure near the open point will increase, and when it is applied to air conditioners, etc., the heat exchanger will be exposed to dew during cooling, and the dust generated on the filter (buzzing noise) will be generated. Can be suppressed.
【0015】さらに、負荷がかかった時に、著しく送風
性能が劣化するため、冷房能力または暖房能力が低下す
る。Further, when a load is applied, the air blowing performance is significantly deteriorated, so that the cooling capacity or the heating capacity is reduced.
【図1】本発明の一実施例を示す断面図と1個のブレー
ドの拡大図FIG. 1 is a sectional view showing one embodiment of the present invention and an enlarged view of one blade.
【図2】P−Q特性図FIG. 2 is a graph showing PQ characteristics.
【図3】静圧の高低と肉厚分布位置の関係を示す図FIG. 3 is a diagram showing the relationship between the level of static pressure and the thickness distribution position.
【図4】騒音あたりの風量性能を示す図FIG. 4 is a diagram showing air volume performance per noise;
【図5】本発明一実施例のブレード吹き出し部の流速ベ
クトル図FIG. 5 is a flow velocity vector diagram of a blade blowing portion according to one embodiment of the present invention.
【図6】従来の貫流ファンの正面図FIG. 6 is a front view of a conventional once-through fan.
【図7】従来の貫流ファンの正面図FIG. 7 is a front view of a conventional once-through fan.
【図8】従来のブレード吹き出し部の流速ベクトル図FIG. 8 is a flow velocity vector diagram of a conventional blade blowing section.
1 貫流ファン 2 円板 3 羽根 1 once-through fan 2 disk 3 blade
フロントページの続き (72)発明者 成相 茂 大阪府門真市大字門真1006番地 松下電器 産業株式会社内 (72)発明者 今坂 俊之 大阪府門真市大字門真1006番地 松下電器 産業株式会社内 Fターム(参考) 3H031 AA03 BA02 3H033 AA02 AA18 BB02 BB09 DD03 EE06 EE08 3H035 CC01 CC06 3L049 BB07 BD02 Continued on the front page (72) Inventor Shigeru Nari 1006 Kadoma Kadoma, Osaka Prefecture Inside Matsushita Electric Industrial Co., Ltd. Reference) 3H031 AA03 BA02 3H033 AA02 AA18 BB02 BB09 DD03 EE06 EE08 3H035 CC01 CC06 3L049 BB07 BD02
Claims (2)
備えた空気調和機において、前記貫流ファンのブレード
形状を、最大肉厚位置を中央より内側(内径側)にした
ことを特徴とする空気調和機の室内ユニット。1. An air conditioner having a cross-flow fan as a blower fan for an indoor unit, wherein the blade shape of the cross-flow fan is such that a maximum thickness position is located inside (inner diameter side) from a center. Indoor unit of the machine.
厚位置が、弦長の内側から2%〜35%の位置にあるこ
とを特徴とする空気調和機の室内ユニット用貫流ファ
ン。2. The cross-flow fan for an indoor unit of an air conditioner, wherein the maximum thickness position of the blade shape of the cross-flow fan is 2% to 35% from the inside of the chord length.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2000266829A JP3661579B2 (en) | 1999-10-22 | 2000-09-04 | Air conditioner indoor unit |
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP30096599 | 1999-10-22 | ||
JP11-300965 | 1999-10-22 | ||
JP2000266829A JP3661579B2 (en) | 1999-10-22 | 2000-09-04 | Air conditioner indoor unit |
Publications (2)
Publication Number | Publication Date |
---|---|
JP2001193956A true JP2001193956A (en) | 2001-07-17 |
JP3661579B2 JP3661579B2 (en) | 2005-06-15 |
Family
ID=26562519
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP2000266829A Expired - Lifetime JP3661579B2 (en) | 1999-10-22 | 2000-09-04 | Air conditioner indoor unit |
Country Status (1)
Country | Link |
---|---|
JP (1) | JP3661579B2 (en) |
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2008241188A (en) * | 2007-03-28 | 2008-10-09 | Mitsubishi Electric Corp | Cross flow air blower and air conditioner |
WO2015098689A1 (en) * | 2013-12-27 | 2015-07-02 | ダイキン工業株式会社 | Cross-flow fan blade |
JP2016223352A (en) * | 2015-05-29 | 2016-12-28 | ダイキン工業株式会社 | Cross flow fan and air conditioner using the same |
WO2018002987A1 (en) * | 2016-06-27 | 2018-01-04 | 三菱電機株式会社 | Multi-blade fan and air conditioner |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP5143317B1 (en) | 2012-04-06 | 2013-02-13 | 三菱電機株式会社 | Air conditioner indoor unit |
-
2000
- 2000-09-04 JP JP2000266829A patent/JP3661579B2/en not_active Expired - Lifetime
Cited By (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2008241188A (en) * | 2007-03-28 | 2008-10-09 | Mitsubishi Electric Corp | Cross flow air blower and air conditioner |
JP4687675B2 (en) * | 2007-03-28 | 2011-05-25 | 三菱電機株式会社 | Cross-flow blower and air conditioner |
WO2015098689A1 (en) * | 2013-12-27 | 2015-07-02 | ダイキン工業株式会社 | Cross-flow fan blade |
JP2016223352A (en) * | 2015-05-29 | 2016-12-28 | ダイキン工業株式会社 | Cross flow fan and air conditioner using the same |
WO2018002987A1 (en) * | 2016-06-27 | 2018-01-04 | 三菱電機株式会社 | Multi-blade fan and air conditioner |
Also Published As
Publication number | Publication date |
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