JP3661579B2 - Air conditioner indoor unit - Google Patents
Air conditioner indoor unit Download PDFInfo
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- JP3661579B2 JP3661579B2 JP2000266829A JP2000266829A JP3661579B2 JP 3661579 B2 JP3661579 B2 JP 3661579B2 JP 2000266829 A JP2000266829 A JP 2000266829A JP 2000266829 A JP2000266829 A JP 2000266829A JP 3661579 B2 JP3661579 B2 JP 3661579B2
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- JP
- Japan
- Prior art keywords
- blade
- air conditioner
- indoor unit
- flow
- cross
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- 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.)
- Expired - Lifetime
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- Air-Conditioning Room Units, And Self-Contained Units In General (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Description
【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。
【0002】
【従来の技術】
従来の空気調和機は特開平9−100795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。
【0003】
従来の空気調和機は特開平10−77988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。
【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。
【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。
【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。
【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複数のブレードを周方向に環状に配した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を、最大肉厚位置が前記ブレードの弦長の内側(内径側)から4%の箇所に設けられると共に、前記最大肉厚位置から前記ブレードの両端に向って前記ブレードの肉厚を順次薄くしたことを特徴とするものである。
【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。
【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。
【0011】
最大肉厚位置を、弦長の内側から2%〜60%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%〜35%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。
【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。
【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。
【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。
【図面の簡単な説明】
【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
【図2】P−Q特性図
【図3】静圧の高低と肉厚分布位置の関係を示す図
【図4】騒音あたりの風量性能を示す図
【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
【図6】従来の貫流ファンの正面図
【図7】従来の貫流ファンの正面図
【図8】従来のブレード吹き出し部の流速ベクトル図
【符号の説明】
1 貫流ファン
2 円板
3 羽根[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a cross-flow fan used in an indoor unit of an air conditioner that performs indoor cooling or heating.
[0002]
[Prior art]
A conventional air conditioner has a shape as shown in FIG. 6 as described in JP-A-9-1000079. The cross-flow fan 1 is divided into a plurality of blocks partitioned by a
[0003]
A conventional air conditioner has a shape as shown in FIG. 7 as described in JP-A-10-77788. A plurality of
[0004]
And the thickness distribution of these blade shapes is classified into the following two types. First, the wall thickness is constant from the leading edge to the trailing edge. Second, the maximum thickness position is in the middle between the leading edge and the trailing edge.
[0005]
[Problems to be solved by the invention]
However, in the fan blade of the first conventional example, the length of the blade is different when a load is applied (for example, when dust adheres to the air cleaning filter), the two-dimensional flow is likely to be disrupted. Therefore, especially in the vicinity of the side wall portion, the two-dimensional flow is likely to be disrupted, and an intermittent abnormal sound of “bazabasa” is generated, which is extremely uncomfortable. Furthermore, when the load is applied, the air blowing performance is significantly deteriorated, so that the cooling capacity or the heating capacity is lowered.
[0006]
The blade of the fan of the second conventional example has the same problem. In addition, as is apparent from the flow velocity vector of the blowing portion having the conventional blade shape shown in FIG. 8, it can be seen that the flow is separated at the leading edge portion and turbulence is generated. The present invention solves such a conventional problem, and as a method of giving the blade-shaped thickness distribution of the cross-flow fan, by placing the maximum thickness position inside from the center, even when a load is applied, A stable flow field can be formed.
[0007]
[Means for Solving the Problems]
In order to solve the above-described problems, the present invention provides an air conditioner including a cross-flow fan in which a plurality of blades are arranged annularly in a circumferential direction as a blower fan of an indoor unit, wherein the blade shape of the cross-flow fan is set to a maximum thickness position. Is provided at a
[0009]
【Example】
Embodiments of the present invention will be described below with reference to the drawings.
[0010]
FIG. 1 is a cross-sectional view of a crossflow fan mounted on an indoor unit of an air conditioner and an enlarged view of one blade of the crossflow fan in the first embodiment of the present invention. The chord length of the blade is represented by line segment IO. The blade shape is characterized in that the maximum thickness position is disposed inside the center of the line segment.
[0011]
FIG. 2 shows the result of analyzing the PQ characteristics by changing the maximum wall thickness position from 2% to 60% from the inside of the chord length. The slope at the open point represents the level of static pressure. The relationship between the inclination and the thickness distribution position is shown in FIG. From this, the peaks where the static pressure increases are in the vicinity of 4% and 20%, and the static pressure tends to increase as the maximum thickness position moves to the inner peripheral side. Therefore, it can be seen that a high static pressure can be stably obtained when the maximum thickness position is 2% to 35%. Furthermore, the air volume performance per noise is shown in FIG. As a result, the maximum thickness position is almost stable in the region of 2% to 35% from the inside of the chord length. Here again, it can be seen that the airflow performance per noise is stable if the maximum thickness position is at a position of 2% to 35% inside the center.
[0012]
As shown in FIG. 5, the flow separation at the leading edge is reduced, as shown in the flow velocity vector of the blowing portion according to the blade shape of the present embodiment, and a smooth flow is generated and the air flow performance is improved. I was able to.
[0013]
【The invention's effect】
As is clear from the above-described embodiment, since the static pressure is increased, abnormal noise such as rustling is unlikely to occur even when a load is applied to the air conditioner body. Further, when the flow state is analyzed by focusing on the blowing portion during cooling and heating, the separation of the flow at the front edge portion is reduced and the air flow performance is improved. Moreover, since it expands gradually from the shortest distance between blades to a blowing part, trailing edge peeling reduces and air volume performance improves.
[0014]
From the above situation, the turbulence component is reduced and the noise is also reduced, and the air volume performance per the same noise is improved. In addition, the pressure near the open point will increase, and when applied to air conditioners, etc., heat exchanger dew will be generated during cooling, and dust will adhere to the filter (buzzing sound). Can be suppressed.
[Brief description of the drawings]
FIG. 1 is a sectional view showing an embodiment of the present invention and an enlarged view of one blade. FIG. 2 is a PQ characteristic diagram. FIG. 3 is a diagram showing the relationship between the level of static pressure and the thickness distribution position. FIG. 4 is a diagram showing air volume performance per noise. FIG. 5 is a flow velocity vector diagram of a blade blowing portion according to an embodiment of the present invention. FIG. 6 is a front view of a conventional cross-flow fan. FIG. 8 Flow velocity vector diagram of conventional blade blowing part
1
Claims (1)
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
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JP2000266829A JP3661579B2 (en) | 1999-10-22 | 2000-09-04 | Air conditioner indoor unit |
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP11-300965 | 1999-10-22 | ||
JP30096599 | 1999-10-22 | ||
JP2000266829A JP3661579B2 (en) | 1999-10-22 | 2000-09-04 | Air conditioner indoor unit |
Publications (2)
Publication Number | Publication Date |
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JP2001193956A JP2001193956A (en) | 2001-07-17 |
JP3661579B2 true JP3661579B2 (en) | 2005-06-15 |
Family
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Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP2000266829A Expired - Lifetime JP3661579B2 (en) | 1999-10-22 | 2000-09-04 | Air conditioner indoor unit |
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Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2013150673A1 (en) | 2012-04-06 | 2013-10-10 | 三菱電機株式会社 | Indoor unit for air conditioning device |
WO2015098689A1 (en) | 2013-12-27 | 2015-07-02 | ダイキン工業株式会社 | Cross-flow fan blade |
Families Citing this family (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP4687675B2 (en) * | 2007-03-28 | 2011-05-25 | 三菱電機株式会社 | Cross-flow blower and air conditioner |
JP6634704B2 (en) * | 2015-05-29 | 2020-01-22 | 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 |
-
2000
- 2000-09-04 JP JP2000266829A patent/JP3661579B2/en not_active Expired - Lifetime
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2013150673A1 (en) | 2012-04-06 | 2013-10-10 | 三菱電機株式会社 | Indoor unit for air conditioning device |
US10436496B2 (en) | 2012-04-06 | 2019-10-08 | Mitsubishi Electric Corporation | Indoor unit for air-conditioning apparatus |
WO2015098689A1 (en) | 2013-12-27 | 2015-07-02 | ダイキン工業株式会社 | Cross-flow fan blade |
US10690142B2 (en) | 2013-12-27 | 2020-06-23 | Daikin Industries, Ltd. | Blade of cross-flow fan |
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Publication number | Publication date |
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JP2001193956A (en) | 2001-07-17 |
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