JPS62118094A - Transverse flow blower device - Google Patents

Transverse flow blower device

Info

Publication number
JPS62118094A
JPS62118094A JP60258004A JP25800485A JPS62118094A JP S62118094 A JPS62118094 A JP S62118094A JP 60258004 A JP60258004 A JP 60258004A JP 25800485 A JP25800485 A JP 25800485A JP S62118094 A JPS62118094 A JP S62118094A
Authority
JP
Japan
Prior art keywords
impeller
stabilizer
tongue
cross
parts
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.)
Pending
Application number
JP60258004A
Other languages
Japanese (ja)
Inventor
Hisao Kusuhara
尚夫 楠原
Shotaro Ito
正太郎 伊東
Takashi Sugio
孝 杉尾
Toshiyuki Imasaka
俊之 今坂
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Panasonic Holdings Corp
Original Assignee
Matsushita Electric Industrial Co Ltd
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Matsushita Electric Industrial Co Ltd filed Critical Matsushita Electric Industrial Co Ltd
Priority to JP60258004A priority Critical patent/JPS62118094A/en
Publication of JPS62118094A publication Critical patent/JPS62118094A/en
Pending legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/44—Fluid-guiding means, e.g. diffusers
    • F04D29/441—Fluid-guiding means, e.g. diffusers especially adapted for elastic fluid pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D17/02—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps having non-centrifugal stages, e.g. centripetal
    • F04D17/04—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps having non-centrifugal stages, e.g. centripetal of transverse-flow type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
    • F04D29/661—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps
    • F04D29/663—Sound attenuation
    • F04D29/665—Sound attenuation by means of resonance chambers or interference

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Abstract

PURPOSE:To lower noise by positioning the ends of the tongue parts of a stabilizer, on the same circumference centering around the axis of an impeller, shifting adjacent tongue parts mutually by a certain angle, and shifting the parts of a rear guider opposite to said tongue parts by a specified angle. CONSTITUTION:One tongue part 2a of a stabilizer 2 is placed in a position S1 which is circumscribed about a circle centering around the axis of an impeller 1, and another tongue part 2b is placed in a position S2 which is circumscribed about the same circle at a point P2, while being shifted in the axial direction of the impeller 1. Further, the parts of a rear guider 3 which are opposite to the tongue parts 2a, 2b, are equally placed in positions t1, t2, being rotated in the same directions as the tongue parts 2a, 2b centering around the shaft center O of the impeller 1, respectively. Each of the tongue parts 2a, 2b, 2c, 2d of the stabilizer 2 and the parts 3a, 3b, 3c, 3d of the rear guider 3 are placed being opposite one to one to each run of the impeller 1. Thereby, the timing of generating a blade-pitch sound can be dispersed, reducing noise while minimizing the lowering area of wind velocity.

Description

【発明の詳細な説明】 産業上の利用分野 この発明は、空気調和機等に広く用いられている横断流
送風装置に関するものである。DETAILED DESCRIPTION OF THE INVENTION Field of Industrial Application This invention relates to a cross-flow blower device widely used in air conditioners and the like.

従来の技術 従来、この種の横断流送風装置は、例えば実開昭５９−
４１６９６号公報に示されているように、第８図および
第９図のような構成になっていた。BACKGROUND OF THE INVENTION Conventionally, this type of cross-flow blower has been developed, for example, by
As shown in Japanese Patent No. 41696, the configuration was as shown in FIGS. 8 and 9.

すなわち、複数のブレード５と、この各ブレード５を支
持する支持板５ａからなるクロスフローファン羽根車１
を中心として、その前後にスタビライザ２およびリアガ
イダ３を配設し、スタビライザ２とリアガイダ３とで、
空気の吹出口４を形成し、横断流送風機を構成していた
。That is, the cross flow fan impeller 1 is composed of a plurality of blades 5 and a support plate 5a that supports each blade 5.
A stabilizer 2 and a rear guider 3 are arranged in front and behind the center, and the stabilizer 2 and rear guider 3
An air outlet 4 was formed to constitute a cross-flow blower.

第８図の矢印で示すように、横断流送風機はその構造上
、空気の流入方向と流出方向が逆方向であること、ある
いは送風機を軸方向に延ばすと、ほぼその長さの割合に
比例して風１が増加するなど、他の送風機に見られない
特徴を有するため、近年空気調和機等に広く用いられる
ようになった。As shown by the arrows in Figure 8, due to the structure of the cross-flow blower, the inflow and outflow directions of the air are opposite, or when the blower is extended in the axial direction, it is approximately proportional to its length. It has become widely used in air conditioners and the like in recent years because it has features not found in other blowers, such as increasing the amount of air flow.

発明か解決しようとする問題点 しかし、上記のような構成の横断流送風機は、他の種の
送風機に比べて騒音が高く、効率が低い等の問題点を有
しており、特に、スタビライザ２の近傍で発生する特異
音の発生を抑えることが最大の課題とされている。この
特異音は、その周波数がクロスフローファン羽根車１の
ブレード５の　Ｘ　　ｚ 枚数２と、毎分回転数ｎｒｐｍの積　。。Ｈｚ　とその
倍音で現われ、通常羽根ピッチ音と呼ばれる。Problems to be Solved by the Invention However, the cross-flow blower configured as described above has problems such as high noise and low efficiency compared to other types of blowers. The biggest challenge is to suppress the generation of peculiar sounds that occur in the vicinity of. The frequency of this singular sound is the product of the number of Xz blades 5 of the cross flow fan impeller 1, 2, and the number of rotations per minute, nrpm. . It appears in Hz and its harmonics, and is usually called blade pitch sound.

一般にブレード５の枚数が多い程、横断流送風機では、
羽根ピッチ音の周波数が高く、聴感的に笛を吹くような
音色として非常にうるさく感じられる。In general, the larger the number of blades 5, the more
The frequency of the blade pitch sound is high, and the sound is perceived to be very noisy, resembling a whistling sound.

また、羽根ピツチ音の強弱は、クロスフローファン羽根
車１、スタビライザ２、リアガイダ３の各形状や、相対
位置、あるいは負荷等によって変化するが、羽根ピッチ
音を押える設計と、送風機効率を上昇させる設計とはし
ばしば相反する。In addition, the strength of the blade pitch noise changes depending on the shape, relative position, load, etc. of the cross flow fan impeller 1, stabilizer 2, and rear guider 3, but the design suppresses the blade pitch noise and increases the blower efficiency. Often contradicts design.

例えば、第９図において、Ｓ寸法を小さくとれば、送風
機効率は向上するが、羽根ピツチ音は高くなる。このよ
うに、横断流送風機では、羽根ピッチ音を低く押えるた
めに効率を極限まで上げられないという問題がある。For example, in FIG. 9, if the S dimension is made smaller, the blower efficiency will improve, but the blade pitch noise will become higher. As described above, cross-flow blowers have a problem in that efficiency cannot be maximized in order to keep the blade pitch noise low.

これに対して、この羽根ピッチ音を弱めるため、いろい
ろな試みが従来から行なわれており、その代表的な例と
して、実開昭５９−１６７９９０号公報に示されている
ような一対策案例がある。第１０図（＆）は従来のクロ
スフローファン羽根車１のブレード５の相対位置を示し
ており、ファン軸中心に対する各ブレード間のピッチ角
ψは等しく、その周波数特性は、第１１図（＆）に示さ
れるようにとして一２ＸｎＸｚ−Ｈｚにピークが現われ
る。In response to this, various attempts have been made in the past to weaken this blade pitch sound, and a typical example of such a countermeasure is the one shown in Japanese Utility Model Application No. 59-167990. be. Fig. 10 (&) shows the relative position of the blades 5 of the conventional cross-flow fan impeller 1, the pitch angle ψ between each blade with respect to the fan axis center is equal, and the frequency characteristics are shown in Fig. 11 (&). ), a peak appears at -2XnXz-Hz.

これに対して、対策構造を示す第１０図（ｂｌでは、ブ
レード５間のピッチ角ψが乱数的に配列されており、図
示の対策例では、Ａ部で９°、Ｂ部で１１゜となってお
り、この部分から発生する羽根ピッチ音の周波数は□Ｈ
ｚおよび一３６０Ｘｎ６０Ｘｎ ９Ｘ６０　　　　　　　　　　　１　１　Ｘ６０Ｈｚと
なる。従って、このようにクロスフローファン羽根車に
おいて、乱数的ζこピツチ角を配列すれば、第１１図（
ｂ）に示したような特性となり、通ｎ　Ｘ　ｚ　　　　
　　　２Ｘ　ｎ　Ｘ　ｚ常　。。Ｈｚｌａ　ｏ　　　Ｈ
ｚ　　で現われる羽根ピッチ音及びその１音音のピーク
が互いに干渉し合って分散して表われる。これにより、
羽根ピッチ音は聴感的には他の周波数の音と混ざって殆
んど聞こえなくなる。On the other hand, in FIG. 10 (bl) showing a countermeasure structure, the pitch angle ψ between the blades 5 is randomly arranged. The frequency of the blade pitch sound generated from this part is □H
z and -360Xn60Xn 9X60 1 1 X60Hz. Therefore, if the random number ζ pitch angles are arranged in the cross-flow fan impeller in this way, as shown in Fig. 11 (
The characteristics are as shown in b), and the result is
2X n X z usual. . Hzla o H
The blade pitch sound appearing at z and the peak of its single sound interfere with each other and appear dispersed. This results in
The blade pitch sound is audibly mixed with sounds of other frequencies and becomes almost inaudible.

しかし、この対策案では第１２図に示すように音圧変動
がクロスフローファン羽根車の一回転ごとに同一波形の
繰返しとして現われるため、羽根ピツチ音の低減とは別
にクロスフローファン羽根庁の回転周波数に起因し、周
波数特性としては顕著に現われないが聴感的にゴロゴロ
とした不快な回転音が、新たに発生し問題となる。However, with this countermeasure, as shown in Figure 12, sound pressure fluctuations appear as a repetition of the same waveform for each rotation of the cross-flow fan impeller, so apart from reducing the blade pitch noise, the rotation of the cross-flow fan blade Due to the frequency, an unpleasant rotating sound that is audibly rumbling, although not noticeable in terms of frequency characteristics, is newly generated and becomes a problem.

本発明は、上記従来の問題点を解消し、騒音のきわめて
少ない道断流送風装置を提供するものである。The present invention solves the above-mentioned conventional problems and provides a road-disruption blower device that generates extremely little noise.

問題点を解決するための手段 そこで、上記従来例の問題点である羽根ピツチ音の発生
と対策案により新たに生じた回転音の発生を解消する本
発明の技術的な手段は、スタビライザを、同一断面形状
あるいは断面形状の異なる複数のスタビライザより構成
し、羽根車の軸方向に連続するとともに、前記複数のス
タビライザの舌部の先端を、羽根車軸を中心とする同一
円周上に位置させかつ隣接する相互の舌部が所定の角度
ずれるをもって配置するとともに、リアガイダの前記舌
部に対向する各部分を、羽根車軸を中心に、舌部と同方
向に同角度だけずらせて配置する構成とし、さらに各舌
部およびリアガイダの各部分を羽根車の各連ごとに一対
一で対向させて配設したものである。Means for Solving the Problems Therefore, the technical means of the present invention to solve the problem of the above-mentioned conventional example, which is the generation of blade pitch noise, and the generation of rotational noise newly generated by the proposed countermeasure, is to Consisting of a plurality of stabilizers having the same cross-sectional shape or different cross-sectional shapes, continuous in the axial direction of the impeller, and with the tips of the tongues of the plurality of stabilizers located on the same circumference centered on the impeller axis, and Adjacent tongues are arranged with a predetermined angular shift, and each portion of the rear guider facing the tongue is arranged with a shift in the same direction as the tongues by the same angle around the impeller axis, Further, each tongue portion and each portion of the rear guider are arranged to face each other one-on-one for each row of the impeller.

作　　　用 この技術的手段による作用は次のようになる。For production The effect of this technical means is as follows.

すなわち、スタビライザ近傍で発生する羽根ピッチ音は
、各ブレードとスタビライザとの接近による空気圧の変
動により生じると考えられる。徹って、この接近するタ
イミングを、スタビライザの舌部およびリアガイダの位
置を少なくとも一部変えて、’−Ｅ”’−Ｈｚ　に生じ
ている羽根ピツチ音の発生を時間的にずらせることによ
り、羽根ピッチ音の発生するタイミングを分散させるこ
とが出来る。これによりタイミングのずれた各羽根ピツ
チ音は互いに干渉し合い、聴感的には他の雑音と混ざり
合って、殆んど聞えなくなる。That is, the blade pitch noise generated near the stabilizer is thought to be caused by fluctuations in air pressure due to the proximity of each blade to the stabilizer. By changing the timing of this approach by at least partially changing the position of the tongue of the stabilizer and the rear guider, and by temporally shifting the generation of the blade pitch sound occurring at '-E'''-Hz, It is possible to disperse the timing at which the blade pitch sounds are generated.As a result, the blade pitch sounds with different timings interfere with each other, and audibly mix with other noises, making them almost inaudible.

さらに、第１４図（ａｌおよび第１４図（ｂｉに示すよ
うに、クロスフローファン羽根車１の端板５ａおよび支
技板５ｂ近傍では、風速が著しく低下し、また、上記の
スタビライザの舌部およびリアガイダの位置および形状
の変化する近傍に於いても同様に風速の低下が生じるの
で、第５図に示すように各舌部を前記羽根車の各連ごと
に一対一で対向させることにより、風速の低下域を最小
限にすることが出来る。Furthermore, as shown in FIG. 14 (al) and FIG. 14 (bi), the wind speed decreases significantly near the end plate 5a and support plate 5b of the cross-flow fan impeller 1, and the tongue portion of the stabilizer Also, the wind speed similarly decreases in the vicinity where the position and shape of the rear guider changes. Therefore, as shown in FIG. The area where the wind speed decreases can be minimized.

さらに、本発明のスタビライザおよびリアガイダを各ブ
レード間のピッチ角が等しいクロスフローファンに用い
た場合、音圧変動は第３図（ｂｌに示したように、羽根
車軸中心に対してスタビライザおよびリアガイダの相対
位置の異なる分だけ時間的にずれ、その音圧波形は同じ
であるため、第１２図に示されているようなファンの回
転周波数に起因する特異な波形の繰返しは生じなくなり
、聴感的に不快なゴロゴロとした回転音も生じない。Furthermore, when the stabilizer and rear guider of the present invention are used in a cross-flow fan in which the pitch angle between each blade is equal, the sound pressure fluctuation is The sound pressure waveform is the same even though there is a time difference due to the difference in relative position, so the repetition of the peculiar waveform caused by the rotational frequency of the fan as shown in Figure 12 does not occur, and the audible There is no unpleasant rumbling noise.

また、本発明のスタビラ・イザを第１０図［ｂｌに示さ
れるクロスフローファンに用いた場合も、同様の効果が
得られることが実験結果より解析されたが、これについ
ては後で述べる。Furthermore, it has been analyzed from experimental results that similar effects can be obtained when the stabilizer/Iza of the present invention is used in the cross-flow fan shown in FIG. 10 [bl], but this will be discussed later.

実施例 以下、本発明の実施例を添付図面に基づいて説明する。Example Embodiments of the present invention will be described below with reference to the accompanying drawings.

なお、従来例と同じものについては同じ符号を付して説
明を省略する。Components that are the same as those in the conventional example are designated by the same reference numerals, and description thereof will be omitted.

第１図および第２図は、本発明の原理を示している。1 and 2 illustrate the principle of the invention.

同図において、羽根車中心に対して各ブレード間のピッ
チ角が等しいクロスフローファン羽根車１の外径から寸
法Ｓだけ離れた点Ｐ１を通り、クロスフローファン羽根
車１の軸中心０を中心とする円に外接した位置Ｓ１に、
スタビライザ２の一つの舌部２ａが配されており、また
、羽根車１の軸方向にずれてスタビライザ２の別の舌部
２ｂが同じ円と点Ｐ２で外接する位置Ｓ２に配設されて
いる。In the same figure, the pitch angle between each blade is equal to the center of the impeller, passing through a point P1 that is distanced by a dimension S from the outer diameter of the cross-flow fan impeller 1, and centered on the axial center 0 of the cross-flow fan impeller 1. At the position S1 circumscribed to the circle,
One tongue portion 2a of the stabilizer 2 is disposed, and another tongue portion 2b of the stabilizer 2, shifted in the axial direction of the impeller 1, is disposed at a position S2 that circumscribes the same circle at a point P2. .

さらに、リアガイダ３の、スタビライザの各舌部２ａ、
２ｂに対向した部分も、同様にクロスフローファン羽根
車１の軸中心Ｏを中心として、舌部２ａ、２ｂと同方向
に回転させて位置ｔ１　　。Furthermore, each tongue portion 2a of the stabilizer of the rear guider 3,
The portion facing 2b is similarly rotated about the axial center O of the cross-flow fan impeller 1 in the same direction as the tongues 2a and 2b to position t1.

ｔ２に配設されている。尚、本実施例においては、リア
ガイダ３には突起７が付設されており、前記舌部２　ａ
　、　２　ｂには、突起７ａ、７ｂが対向しており、こ
れらの突起７ａ、７ｂの位置については、前記リアガイ
ダ３ａ、３ｂのずれに従萬し、羽根車１の軸○を中心に
同心円上にθだけずれた位置に配置している。It is arranged at t2. In this embodiment, the rear guider 3 is provided with a protrusion 7, and the tongue portion 2 a
, 2b have protrusions 7a, 7b facing each other, and the positions of these protrusions 7a, 7b follow the deviation of the rear guiders 3a, 3b, and are arranged concentrically around the axis ○ of the impeller 1. It is placed at a position shifted by θ.

なお、他の舌部２ｃ１２ｄおよびリアガイダ３ｃ、３ｄ
１さらには突起７ｃ　、７ｄについても位置Ｓ１．３２
およびｔｌ、ｔ２と同様の関係にある位置３３．３４お
よびｔ３　、ｔ４に配設されている。つまり、位置Ｓ３
はＳｌと、Ｓ４はＳ２とｔ３はｔｌと、ｔ４はｔ２と軸
方向において重合している。In addition, other tongue parts 2c12d and rear guiders 3c, 3d
1 Furthermore, the protrusions 7c and 7d are also located at the position S1.32.
and positions 33, 34, t3, and t4 in the same relationship as tl and t2. That is, position S3
is superposed in the axial direction with Sl, S4 with S2, t3 with tl, and t4 with t2.

さらには羽根車の各連に対してスタビライザ２の各舌部
２ａ、２ｂ、２ｃ、２ｄ、およびリアガイダ３ａ、３ｂ
、３ｃ、３ｄが一対一で対向して配設されている。Furthermore, each tongue part 2a, 2b, 2c, 2d of the stabilizer 2 and the rear guider 3a, 3b are attached to each impeller row.
, 3c, and 3d are arranged facing each other one-on-one.

以下の説明は、位置Ｓ３　、Ｓ４およびｔ３゜ｔ４の関
係が位１１ｓ１．Ｓ２およびｔｌ、ｔ２と同じであるた
め、又説明の便宜上位置ｓ１．ｓ２およびｔｌ、ｔ２の
みについて説明する。そして、位置Ｓ１とＳ２およびｔ
ｌとｔ２とは、それぞれクロスフローファン羽根車１の
軸中心に対して角度０のずれを持っており、このスタビ
ライザ２の両舌部で発生する羽根ピッチ音の時間的なず
れは、この関係を第３図［ａｌ　、　（ｂｌて示す。In the following explanation, the relationship between positions S3, S4 and t3°t4 is 11s1. S2 and tl, t2 are the same, and for convenience of explanation, the position s1. Only s2, tl, and t2 will be explained. and positions S1 and S2 and t
l and t2 each have an angle of 0 deviation with respect to the axial center of the cross-flow fan impeller 1, and the time deviation of the blade pitch sound generated at both tongues of the stabilizer 2 is based on this relationship. Figure 3 [al, (shown as bl).

第３図ｆａｌは、従来の均一な側壁を持つスタビライザ
およびリアガイダを用いた場合の、時間キ音圧の関係を
示すものであり、第３図（ｂｌは、本発明によるスタビ
ライザおよびリアガイダを用いた場合の、同種の関係を
示している。Figure 3 (fal) shows the relationship between time and sound pressure when using the conventional stabilizer and rear guider with uniform side walls, and Figure 3 (bl) shows the relationship between the time and the sound pressure when using the stabilizer and rear guider according to the present invention. It shows a homogeneous relationship in cases.

また、これに関する実験の周波数特性を、それぞれ第４
図（ａｌ　、　（ｂｌに示す。第４図（ａｌは第３図（
ａｌに、また第４図（ｂ）は第３図（ｂｌに対応してい
る。In addition, the frequency characteristics of experiments related to this are
Figures (al, (bl) are shown in Figure 4 (al is shown in Figure 3 (
al, and FIG. 4(b) corresponds to FIG. 3(bl).

このように、本実施例によれば、２つの波形が互いに干
渉し合って、打消す効果が生じる。これにより、スタビ
ライザ近傍での音圧変化は、互いに打消し合って減少し
、羽根ピッチ音は減少する。In this way, according to this embodiment, the two waveforms interfere with each other, producing a canceling effect. As a result, changes in sound pressure near the stabilizer are reduced by canceling each other out, and blade pitch noise is reduced.

さらに、等ピッチのクロスフローファンを用いているの
で、音圧変動の波形は変わらず、第１２図に示したよう
に、ファンの回転周波数に起因する特異な波形の繰返し
がなくなり、聴感的に不快なゴロゴロとした回転音も生
じない。Furthermore, since a cross-flow fan with an equal pitch is used, the waveform of the sound pressure fluctuation does not change, and as shown in Figure 12, there is no repetition of the peculiar waveform caused by the rotational frequency of the fan, which improves the auditory sense. There is no unpleasant rumbling noise.

さらに、第５図および第１４図（ａｌ　、　（ｂｌで示
したように羽根車の各連とスタビライザの各舌部および
リアガイダの各部分が、一対一で対向して配設されてい
るので、風速の低下域を最小限におさえることが出来る
。Furthermore, as shown in FIGS. 5 and 14 (al, (bl), each series of impellers, each tongue part of the stabilizer, and each part of the rear guider are arranged one-on-one to face each other. It is possible to minimize the area where the wind speed decreases.

さらに、本発明のスタビライザを、不等ピッチのクロス
フローファンに用いた場合も等ピッチのクロスフローフ
ァンを用いた場合と同様に羽根ピッチ音および回転音が
低減する。これは、第１３図に示したように、第１２図
に示す特異な音圧波形が、その特異性を保ったままで、
時間的に果として、音圧波形が互いに干渉し合うためと
考えられる。従って、本発明のスタビライザは、等ピツ
チのクロスフローファンのみならず、不等ピッチのクロ
スフローファンにも適用出来るといえる。Furthermore, when the stabilizer of the present invention is used in a cross-flow fan with unequal pitches, blade pitch noise and rotational noise are reduced in the same way as in the case where a cross-flow fan with equal pitches is used. This is because, as shown in Fig. 13, the unique sound pressure waveform shown in Fig. 12 maintains its specificity.
This is thought to be due to the sound pressure waveforms interfering with each other as a result of time. Therefore, it can be said that the stabilizer of the present invention can be applied not only to equal-pitch cross-flow fans but also to unequal-pitch cross-flow fans.

第５図および第６図は、本発明の原理にもとづき、実際
の空気調和機として用いた実施例の構造図と、要部断面
図を示す。図中、６はファンモータを示す。また第７図
は本発明の別の実施例の要部断面図である。これらはス
タビライザ２の舌部およびリアガイダ３が異なる位置Ｓ
１と８２およ第３図（ａｔ　、　（ｂｌに示したように
、音圧波形のピーク位置がずれることになり、互いの波
形が干渉し合って、騒音が減少する。FIGS. 5 and 6 show a structural diagram and a sectional view of essential parts of an embodiment used as an actual air conditioner based on the principle of the present invention. In the figure, 6 indicates a fan motor. Further, FIG. 7 is a sectional view of a main part of another embodiment of the present invention. These are the positions S where the tongue part of the stabilizer 2 and the rear guider 3 are different.
As shown in Figures 1 and 82 and Figures 3 (at and bl), the peak positions of the sound pressure waveforms shift, and the waveforms interfere with each other, reducing noise.

なお、スタビライザ２およびリアガイダ３の具体的な製
作については、樹脂の金型成形等で容易に実現できる。Note that the stabilizer 2 and the rear guider 3 can be easily manufactured by resin molding or the like.

またスタビライザ２の舌部の形状は鋭角、あるいは鋭角
状の円弧さらには単なる円弧状であってもよい。Further, the shape of the tongue portion of the stabilizer 2 may be an acute angle, an acute-angled circular arc, or even a simple circular arc shape.

発明の効果 以上のように、本発明のスタビライザとリアガイダを用
いれば、聴感的に不快な羽根ピッチ音や回転音のない静
寂な送風機を提供でき、さらには、風速分布域が小さい
所（各連の接続部）で各舌部およびリアガイダの各部分
の段差部が位置しているため、かかる箇所で生じるうす
の影響を受けることもきわめて少なく、今次騒音により
制限されていた送風機効率を、著しく改善することが可
能となる。Effects of the Invention As described above, by using the stabilizer and rear guider of the present invention, it is possible to provide a quiet blower with no audibly unpleasant blade pitch noise or rotation noise, and furthermore, it is possible to provide a quiet blower that does not produce audibly unpleasant blade pitch noise or rotation noise. Since the steps of each tongue and each part of the rear guider are located at the joints (connections of the It becomes possible to improve.

【図面の簡単な説明】[Brief explanation of drawings]

第１図、第２図はそれぞれ本発明の送風装置の原理を示
す要部の斜視図および断面図、第３図（ａ）。 （ｂ）はそれぞれ従来例と本発明の実施例による音圧レ
ベルの比較を示す音圧波形図、第４図（ａｔ　、　［ｂ
）はそれぞれ従来例と本発明の実施例による騒音レベル
比較を示す周波数特性図、第５図、第６図はそれぞれ本
発明の一実施例の送風装置を空気調和機に応用した例を
示す平面図と要部断面図、第７図は本発明の他の実施例
を示す第６図相当図、第８図、第９図はそれぞれ従来例
の送風装置の構造を示す斜視図および要部断面図、第１
０図（ａｔ　、　（ｂｌはそれぞれ異なる従来例を示す
羽根車の要部断面図、第１１図（ａ）　、　（ｂｌはそ
れぞれ第１０図（ａ）　、　（ｂ）による羽根車を具備
した送風装置の周波数特性図、第１２図は従来の羽根車
を具備した送風装置の音圧波形図、第１３図は本発明の
実施例による送風装置の音圧波形図、第１４図（ａｌ　
、　（ｂｌはそれぞれ同羽根車側およびスタビライザ側
による風速分右図である。 １・・・・・・羽根車、２・・・・・・スタビライザ、
２ａ。 ２ｂ　、２ｃ　、２ｄ・・・・・・舌部、３・・・・・
・リアガイダ、４・・・・・・吹出口、５・・・・・・
ブレード、５ａ・・・・・・端板、５ｂ・・・・・・支
枝板、６・・・・・・ファンモータ、７ａ。 ７ｂ、７ｃ、７ｄ・・・・・・突起。 代理人の氏名　弁理士　中　尾　敏　男　ほか１名／−
−−羽技車 ？−−−　スクヒ“フイプ゛ ６−−−７”レード ム、７本−−−突、由コ ＄　３　図 ｔ５εＣ ａｎ ＬＪに 第４図 （α） ”ｌ　Ｌ　ｅ（（Ｈｚ） ／−ｍ−クロス７ｒ）−７ｙ　７千（え車Ｚ−−−　人
りごライ１゛ 、３に一一一久衿挾 ６−−−）１ン七−り ／−−−り９人７０−７７７羽項車 ２−−−　スフこフブブ′ 、３−−−＋ｔア刀−ブタ゛ ノーーー　クロ入７０−７７７羽１」率Ｚ−−−スフこ
°ライサ′ ３−−−’ノアη゛イク′ 第７図　　　　　　　４−吹出口 ６−−−ブレード ／−ｍ−りＤスフローフ丁〉月斗膚り唱Ｚ−−−又りヒ
゛ライゾ。 第　８　図　　　　　　　　　　　　　　　　　　　　
　Ｊ〜−一・ノア力・イヂ４−−−咲出口 ５−ｍ−フし−Ｆ ノー−−クロ入７Ｏ−７ｔン羽艮車 第　９　図　　　　　　　　　　　　　　　　　　　　
　　？−−−　又りじうづブーＪ−’ノアη゛イグ ４−−−ｖ′ｆＸ、ｔ口 第１Ｏ図 第１１図 （０−］ 岡涙表　（Ｎｚ） （ｂン 周　及叙　（ＨＬ） 第１２図 ２　　　　　　況ＣFIGS. 1 and 2 are a perspective view and a cross-sectional view of essential parts showing the principle of the blower of the present invention, and FIG. 3(a), respectively. (b) is a sound pressure waveform diagram showing a comparison of the sound pressure levels according to the conventional example and the embodiment of the present invention, respectively;
) are frequency characteristic diagrams showing a comparison of noise levels between a conventional example and an embodiment of the present invention, and FIGS. 5 and 6 are plane views each showing an example in which the blower according to an embodiment of the present invention is applied to an air conditioner. Fig. 7 is a view corresponding to Fig. 6 showing another embodiment of the present invention, and Figs. 8 and 9 are a perspective view and a sectional view of main parts showing the structure of a conventional blower device, respectively. Figure, 1st
Figures 0 (at and BL are sectional views of essential parts of impellers showing different conventional examples, respectively, and Figures 11 (a) and (bl) are blowers equipped with impellers according to Figures 10 (a) and (b), respectively. A frequency characteristic diagram of the device, FIG. 12 is a sound pressure waveform diagram of a blower equipped with a conventional impeller, FIG. 13 is a sound pressure waveform diagram of a blower according to an embodiment of the present invention, and FIG. 14 (al
, (bl is the diagram on the right showing the wind speed from the impeller side and the stabilizer side, respectively. 1... Impeller, 2... Stabilizer,
2a. 2b, 2c, 2d...tongue, 3...
・Rear guider, 4... Outlet, 5...
Blade, 5a... End plate, 5b... Branch plate, 6... Fan motor, 7a. 7b, 7c, 7d...protrusions. Name of agent: Patent attorney Toshio Nakao and 1 other person/-
-- Impeller? --- Sukhi "Fip6--7" radom, 7 pieces ---Tsu, Yuko $ 3 Figure t5εC an LJ to Figure 4 (α) ``l Le ((Hz) /-m-cross 7r)-7y 7,000 (Eguruma Z----Rigorai 1゛, 3 to 111ku collar 6----) 1 n7-ri/---ri 9 people 70-777 items Car 2---Sufkofububu', 3---+t sword-pig No-- Black included 70-777 feathers 1'' rate Z---Sufko゛raisa'3----'Noahη゛Iku' Fig. 7 4-Blowout outlet 6--Blade/-m-ri D sloof knife>Tsukito Derisho Z---Also Hiraizo. Figure 8
J～-1・Noah Riki・Iji 4---Saki Exit 5-m-Fushi-F No---Black 7O-7ton waving car Figure 9
? --- Matari Jiuzu Boo J-'Noah η゛Ig 4--v'f ) Figure 12 2 Situation C

Claims (3)

【特許請求の範囲】[Claims] （１）複数のブレードとこのブレードを支持する支持板
および端板からなる連を複数軸方向に連結して横断流型
の羽根車を構成し、さらにこの羽根車と、この羽根車を
駆動するファンモータと、リアガイダと、スタビライザ
によって横断流送風機を構成し、前記スタビライザに複
数の舌部を設け、この各舌部の先端を、羽根車軸を中心
とする同一円周上に位置させかつ隣接する相互の舌部が
所定の角度ずれるをもって配置するとともに、前記リア
ガイダの前記各舌部に対向する部分を、羽根車軸を中心
に、前記各舌部と同方向に同角度だけずらせて配置する
構成とし、さらに各舌部および各リアガイダを前記羽根
車の各連ごとに一対一で対向させた横断流送風装置。(1) A cross-flow type impeller is constructed by connecting a plurality of blades, a support plate supporting the blades, and an end plate in a plurality of axial directions, and further drives this impeller. A crossflow blower is configured by a fan motor, a rear guider, and a stabilizer, and the stabilizer is provided with a plurality of tongues, and the tips of the tongues are located on the same circumference centered on the impeller axis and adjacent to each other. The tongues are arranged with a predetermined angular deviation from each other, and the portion of the rear guider facing each of the tongues is arranged with the same angle in the same direction as each of the tongues about the impeller axle. Further, each tongue portion and each rear guider are opposed to each other in a one-to-one manner for each row of the impeller. （２）各舌部の断面形状を同じとした特許請求の範囲第
１項に記載の横断流送風装置。(2) The cross-flow blower device according to claim 1, wherein each tongue has the same cross-sectional shape. （３）羽根車の各連における各ブレード間のピツチ角を
、一定でないように配設した特許請求の範囲第１項また
は第２項に記載の横断流送風装置。(3) The cross-flow blower device according to claim 1 or 2, wherein the pitch angle between each blade in each series of impellers is arranged so as not to be constant.
JP60258004A 1985-11-18 1985-11-18 Transverse flow blower device Pending JPS62118094A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP60258004A JPS62118094A (en) 1985-11-18 1985-11-18 Transverse flow blower device

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP60258004A JPS62118094A (en) 1985-11-18 1985-11-18 Transverse flow blower device

Publications (1)

Publication Number Publication Date
JPS62118094A true JPS62118094A (en) 1987-05-29

Family

ID=17314197

Family Applications (1)

Application Number Title Priority Date Filing Date
JP60258004A Pending JPS62118094A (en) 1985-11-18 1985-11-18 Transverse flow blower device

Country Status (1)

Country Link
JP (1) JPS62118094A (en)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2002257091A (en) * 2001-03-05 2002-09-11 Daikin Ind Ltd Multiblade fan
WO2014050335A1 (en) 2012-09-28 2014-04-03 ダイキン工業株式会社 Air conditioner
WO2014125711A1 (en) 2013-02-12 2014-08-21 ダイキン工業株式会社 Air conditioner

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2002257091A (en) * 2001-03-05 2002-09-11 Daikin Ind Ltd Multiblade fan
WO2014050335A1 (en) 2012-09-28 2014-04-03 ダイキン工業株式会社 Air conditioner
EP3382290A1 (en) 2012-09-28 2018-10-03 Daikin Industries, Limited Air conditioner
US10156376B2 (en) 2012-09-28 2018-12-18 Daikin Industries, Ltd. Air conditioner
WO2014125711A1 (en) 2013-02-12 2014-08-21 ダイキン工業株式会社 Air conditioner

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