JP2560793B2 - Blower - Google Patents
BlowerInfo
- Publication number
- JP2560793B2 JP2560793B2 JP63221086A JP22108688A JP2560793B2 JP 2560793 B2 JP2560793 B2 JP 2560793B2 JP 63221086 A JP63221086 A JP 63221086A JP 22108688 A JP22108688 A JP 22108688A JP 2560793 B2 JP2560793 B2 JP 2560793B2
- Authority
- JP
- Japan
- Prior art keywords
- axial fan
- air
- blade
- blower
- fan
- 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.)
- Expired - Lifetime
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
- F04D19/00—Axial-flow pumps
- F04D19/002—Axial flow fans
-
- 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
- F04D29/26—Rotors specially for elastic fluids
- F04D29/32—Rotors specially for elastic fluids for axial flow pumps
- F04D29/38—Blades
- F04D29/384—Blades characterised by form
-
- 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
- F04D29/666—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps by means of rotor construction or layout, e.g. unequal distribution of blades or vanes
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Description
【発明の詳細な説明】 [産業上の利用分野] この発明は車両用エンジンの冷却系、家庭用空調装置
の室外機等に使用される送風機に関するものである。Description: TECHNICAL FIELD The present invention relates to a blower used for a cooling system of a vehicle engine, an outdoor unit of a home air conditioner, and the like.
[従来の技術] 近年、例えば自動車のエンジンルームは、FF(フロン
トエンジン・フロントドライブ)方式化に伴うエンジン
の横置化や、自動車の高級化に伴う補器類の装着等によ
り非常に混雑している。従って、このような条件下での
エンジン冷却系の送風機は、高圧損下での使用が強いら
れることになり、特に最大高圧損時であるアイドリング
時に発生する騒音が問題となっている。[Prior Art] In recent years, for example, the engine room of an automobile has become extremely crowded due to the horizontal installation of the engine due to the FF (front engine / front drive) system and the mounting of auxiliary equipment due to the upsizing of the automobile. ing. Therefore, the blower of the engine cooling system under such a condition is forced to be used under a high pressure loss, and noise particularly during idling which is the maximum high pressure loss becomes a problem.
そこで、最近では送風機の主要部をなす軸流ファンの
構成を工夫して低騒音化を図ることが考えられている。Therefore, recently, it has been considered to reduce the noise by devising the structure of the axial fan that forms the main part of the blower.
例えば、実開昭62−185889号公報に開示された低速軸
流ファンでは、各ブレードの吸込側表面に前縁部側より
後縁部側にかけて次第に密度の高い凹凸状の粗面状態を
構成し、ファン騒音の低減を図っている(第1従来
例)。For example, in the low speed axial flow fan disclosed in Japanese Utility Model Laid-Open No. 62-185889, the suction side surface of each blade has a rough surface state of unevenness with a gradually increasing density from the leading edge side to the trailing edge side. The fan noise is reduced (first conventional example).
又、第6図に示すように、ブレード11aの形状を回転
方向Xへ所定角度(前進角)θ1だけ前進させるように
傾けて設けると共に、回転軸線Lの方向へ所定角度(前
傾角)θ2だけ前傾させて低騒音化を図るという前進・
前傾タイプの軸流ファン11も提案されている(第2従来
例)。ここで、ブレード11aの形状を前進・前傾の両者
を組み合わせて構成することにより、その騒音低減の効
果が向上し、前進・前傾の一方の形状のみで構成するこ
とにより、騒音低減の効果が低下するということが既に
知られている。Further, as shown in FIG. 6, the blade 11a is provided so as to be inclined so as to be advanced by a predetermined angle (advance angle) θ1 in the rotation direction X, and is also inclined by a predetermined angle (forward tilt angle) θ2 in the direction of the rotation axis L. Advance to lean forward to reduce noise
A forward tilt type axial fan 11 has also been proposed (second conventional example). Here, the effect of noise reduction is improved by configuring the shape of the blade 11a by combining both forward and forward leaning, and the noise reducing effect is achieved by configuring only one shape of forward and forward leaning. Is already known to decrease.
[発明が解決しようとする課題] ところが、前記第1従来例の低速軸流ファンでは、各
位ブレードの吸込側表面に前縁部側より後縁部側にかけ
て次第に密度の高い凹凸状の粗面状態を構成しなければ
ならず、そのための表面加工が容易でなかった。[Problem to be Solved by the Invention] However, in the low-speed axial flow fan of the first conventional example, the suction side surface of each blade has a rough surface state of unevenness with a gradually increasing density from the leading edge side to the trailing edge side. Had to be configured, and surface processing for that was not easy.
又、前記第2従来例では、その取付スペースの点で問
題があった。例えば、第8図に示すように自動車のラジ
エタ12に送風機を組付けた場合、ラジエタ12の広い範囲
から空気を吸い込んで冷却効果を向上させるために、ラ
ジエタ12の後側面全体を覆うようにしてシュラウド13を
設け、そのシュラウド13の後側に設けた管状の空気導通
部13aに前記前進・前傾タイプの軸流ファン11を設ける
ことになる。Further, the second conventional example has a problem in terms of its mounting space. For example, as shown in FIG. 8, when a blower is attached to a radiator 12 of an automobile, in order to improve the cooling effect by sucking air from a wide range of the radiator 12, the entire rear surface of the radiator 12 is covered. A shroud 13 is provided, and the tubular air-conducting portion 13a provided on the rear side of the shroud 13 is provided with the forward / forward tilt type axial fan 11.
従って、この軸流ファン11の各ブレード11aの前傾形
状により軸流ファン11の回転軸線Lの方向の幅aが大き
くなり、これに合わせて空気導通部13aの前後幅bを必
然的に大きくしなければならず、送風機全体の前後方向
の体格Wが大きくなることになった。このため、限られ
たスペースのエンジンルームにおいて、送風機の取付け
が困難になるという問題があった。Therefore, the width a of the axial fan 11 in the direction of the rotation axis L is increased due to the forward tilted shape of each blade 11a of the axial fan 11, and accordingly the front-back width b of the air conducting portion 13a is necessarily increased. Therefore, the physique W in the front-rear direction of the entire blower becomes large. Therefore, there is a problem that it is difficult to install the blower in the engine room with a limited space.
この発明は前述した事情に鑑みてなされたものであっ
て、その目的は、各ブレード表面に特殊な加工を施す必
要がなく、小さなスペースで取付けて騒音低下を実現し
得る送風機を提供することにある。The present invention has been made in view of the above circumstances, and an object thereof is to provide a blower that can be mounted in a small space to realize noise reduction without requiring special processing on each blade surface. is there.
[課題を解決するための手段] 上記の目的を達成するためにこの発明においては、駆
動源により回転される軸流ファンを備え、その軸流ファ
ンの後方に所定量のスペースを確保しつつ当該軸流ファ
ンを内包する管状の空気導通部と、同軸流ファン前方の
広範囲の空気を空気導通部へ導くために空気導通部に連
続して軸流ファンの前方へ開放される開放部とからなる
シュラウドを備えた送風機において、シュラウドの開放
部を空気導通部へ収束させるように斜状に形成し、前記
軸流ファンの各ブレードを、その回転方向へ前進させる
ように傾けて設ける一方、軸流ファンの回転軸線に対し
ては当該軸線方向において各ブレードの前縁部が略垂直
となるようにし、その軸流ファンの回転軸方向の前端側
を前記空気導通部と開放部との境目から前記開放部へ所
定量だけ前進させて配置している。[Means for Solving the Problems] In order to achieve the above object, in the present invention, an axial fan that is rotated by a drive source is provided, and a predetermined amount of space is secured behind the axial fan. It is composed of a tubular air-conducting part that encloses the axial fan, and an open part that is open to the front of the axial fan continuously with the air-conducting part in order to guide a wide range of air in front of the coaxial fan to the air-conducting part. In a blower equipped with a shroud, an open part of the shroud is formed in a slanted shape so as to converge to an air-conducting part, and each blade of the axial fan is provided so as to be inclined so as to advance in its rotation direction, while an axial flow is provided. The front edge of each blade is substantially perpendicular to the rotation axis of the fan in the axial direction, and the front end side of the axial fan in the rotation axis direction is defined from the boundary between the air conducting portion and the open portion. It is arranged by advancing a predetermined amount toward the open part.
[作用] 即ち、各ブレードには軸流ファンの回転軸線方向に前
傾角が設けられず、軸流ファンの回転軸線方向の前端側
をシュラウドの空気導通部から開放部へ所定量だけ前進
させて配置しているので、軸流ファンの後方に所定量の
スペースを確保しながら空気導通部の前後幅を小さくし
て、送風機全体の前後方向の体格を小さくすることがで
きる。[Operation] That is, each blade is not provided with a forward tilt angle in the rotational axis direction of the axial fan, and the front end side of the axial fan in the rotational axis direction is advanced by a predetermined amount from the air conducting portion of the shroud to the open portion. Since they are arranged, it is possible to reduce the front-rear width of the air-conducting portion while ensuring a predetermined amount of space behind the axial fan, and to reduce the overall size of the blower in the front-rear direction.
又、軸流ファンの回転軸線方向の前端側を空気導通部
から開放部へ所定量だけ前進させて配置していること
と、シュラウドの開放部を空気導通部へ収束するように
斜状に形成していることとにより、軸流ファンの各ブレ
ードにかかる空気力の圧力中心を軸流ファンの前方へ移
動させることができ、これによって各ブレードを通過す
る空気の流れが求心方向へ向けられる。即ち、斜状の開
放部との干渉により、軸流ファンを通過する空気の流れ
が求心方向へ向けられる。Further, the front end side of the axial flow fan in the rotation axis direction is arranged so as to be advanced from the air conducting portion to the opening portion by a predetermined amount, and the opening portion of the shroud is formed in an oblique shape so as to converge to the air conducting portion. By doing so, the center of pressure of the aerodynamic force exerted on each blade of the axial fan can be moved to the front of the axial fan, whereby the air flow passing through each blade is directed in the centripetal direction. That is, due to the interference with the oblique opening, the air flow passing through the axial fan is directed in the centripetal direction.
そして、軸流ファンの各ブレードをその回転方向へ前
進させるように傾けていることと、前記求心方向へ向け
られる空気流とが相俟って、送風機における騒音の発生
が低減される。Further, the fact that each blade of the axial fan is inclined so as to be advanced in the rotation direction thereof and the air flow directed in the centripetal direction are combined with each other to reduce noise generation in the blower.
[実施例] 以下、この発明を自動車のラジエタ冷却用送風機に具
体化した一実施例を図面に基いて詳細に説明する。[Embodiment] An embodiment in which the present invention is embodied in a radiator cooling fan of an automobile will be described in detail with reference to the drawings.
第1,2図に示すように、ラジエタ1の後側面側にはそ
の全体を覆うようにしてシュラウド2が設けられてい
る。このシュラウド2は管状の空気導通部2aを備え、そ
の前側には前方の広範囲の空気、即ちラジエタ1の後側
全面からの空気を導入するために開放される開放部2bが
空気導通部2aに連続して形成されている。又、シュラウ
ド2の開放部2bは空気導通部2aへ収束するように斜状に
形成され、その内側が斜面2cになっている。As shown in FIGS. 1 and 2, a shroud 2 is provided on the rear side of the radiator 1 so as to cover the whole. The shroud 2 is provided with a tubular air-conducting portion 2a, and an opening portion 2b which is opened to introduce a wide range of front air, that is, air from the entire rear side of the radiator 1 is provided in the front portion of the shroud 2a. It is formed continuously. Further, the open portion 2b of the shroud 2 is formed in a slanted shape so as to converge to the air conducting portion 2a, and the inside thereof is a slope 2c.
又、駆動源としてのモータ3により回転される軸流フ
ァン4は、空気導通部2aに内包されるように配設されて
いる。この軸流ファン4はボス部4aを備え、その外周に
は複数枚(この実施例では合計4枚)のブレード4bが設
けられている。各ブレード4bはその回転方向Xへ前進さ
せるように所定の前進角θ1をもって傾けられている。The axial fan 4 rotated by the motor 3 as a drive source is arranged so as to be included in the air conducting portion 2a. The axial fan 4 includes a boss portion 4a, and a plurality of blades 4b (a total of four blades in this embodiment) are provided on the outer periphery of the boss portion 4a. Each blade 4b is inclined at a predetermined advance angle θ1 so as to advance in the rotation direction X thereof.
第4図はこの前進角θ1の大きさと軸流ファンから発
生する騒音との関係を示すグラフである。この図から明
らかなように、前進角θ1が大きいほど軸流ファンの騒
音が小さくなることがわかる。そして、幾何学的には前
進角θ1を360度以上の角度に設定することができる
が、この実施例の軸流ファン4では、騒音低減の効果と
各ブレード4bの機械的強度を鑑みて前進角θ1を45度に
設定している。FIG. 4 is a graph showing the relationship between the magnitude of the advance angle θ1 and the noise generated from the axial fan. As is clear from this figure, the noise of the axial fan decreases as the advancing angle θ1 increases. Although the advancing angle θ1 can be geometrically set to an angle of 360 degrees or more, in the axial fan 4 of this embodiment, the advancing is made in consideration of the noise reduction effect and the mechanical strength of each blade 4b. The angle θ1 is set to 45 degrees.
又、第3図に示すように、軸流ファン4はその回転軸
線Lの方向の前端側4cを空気導通部2aの開放部2bとの境
目である前側位置Pから開放部2bへ所定量(以下「前進
量」という)αだけ前進させて配置されている。この前
進量αは、軸流ファンにおける各ブレードの前傾角θ2
(第7図参照)、即ち軸流ファンの回転軸線方向前方へ
の傾き角の大きさに関係があることがわかっている。
尚、本実施例では第3図に示すように、軸流ファン4の
回転軸線方向における各ブレード4b前縁部が軸流ファン
4の回転軸線Lに対し略垂直となっており、各ブレード
4bには前傾角θ2が設けられていない。Further, as shown in FIG. 3, the axial fan 4 has a front end side 4c in the direction of the rotation axis L from the front side position P, which is a boundary between the open portion 2b of the air conducting portion 2a, to the open portion 2b by a predetermined amount ( Hereinafter, it is arranged by advancing by α). This advance amount α is the forward inclination angle θ2 of each blade in the axial fan.
(See FIG. 7), that is, it is known that it is related to the magnitude of the inclination angle of the axial fan toward the front in the rotation axis direction.
In this embodiment, as shown in FIG. 3, the front edge of each blade 4b in the rotational axis direction of the axial fan 4 is substantially perpendicular to the rotational axis L of the axial fan 4, and each blade is
No forward tilt angle θ2 is provided on 4b.
第5図は前記前傾角θ2の大きさと軸流ファンの騒音
発生との関係を示すグラフである。この図から明らかな
ように、前傾角θ2が22.5度のときに騒音が最小になる
ことがわかる。そして、この実施例では、前記22.5度の
前傾角θ2の騒音低減に相当する効果を得るために、前
進量αを下記の式に基いて設定している。FIG. 5 is a graph showing the relationship between the magnitude of the forward tilt angle θ2 and the noise generation of the axial fan. As is clear from this figure, the noise is minimized when the forward tilt angle θ2 is 22.5 degrees. Further, in this embodiment, the advance amount α is set based on the following equation in order to obtain the effect corresponding to the noise reduction of the forward tilt angle θ2 of 22.5 degrees.
α=(D0−D1)÷2×sin(θ2) ここで、D0は軸流ファン4の外径であり、D1はボス部
4aの外径である(第1図参照)。α = (D0−D1) ÷ 2 × sin (θ2) where D0 is the outer diameter of the axial fan 4, and D1 is the boss.
It is the outer diameter of 4a (see FIG. 1).
この実施例では、上記の式により前進量αを40mmに設
定している。即ち、第3図に示すように、空気導通部2a
の前側位置Pを基準にして、軸流ファン4のボス部4aの
前端側4cを開放部2b側へ40mmだけ前進させて配置してい
る。In this embodiment, the advance amount α is set to 40 mm by the above formula. That is, as shown in FIG. 3, the air conducting portion 2a
The front end side 4c of the boss portion 4a of the axial fan 4 is arranged by advancing by 40 mm toward the open portion 2b side with reference to the front side position P.
又、一般にはシュラウドの空気導通部と開放部との境
目の円弧の大きさは、シュラウドの前後方向の体格の大
きさと関係があり、その体格が大きいほど円弧を大きく
するのが良いとされている。しかしながら、この実施例
のシュラウド2では、上記のような関係にかかわりな
く、第1図に示すようにシュラウド2の前後幅c、空気
導通部2aと開放部2bとの境目の円弧Rの大きさを比較的
大まかに設定することができる。即ち、前記円弧Rの大
きさは、前記シュラウド2の前後幅cにかかわりなく、
空気導通部2aの前側位置Pが明らかになるように且つピ
ン角にならない程度に設定すればよい。Generally, the size of the arc at the boundary between the air-conducting part and the open part of the shroud is related to the size of the shroud in the front-rear direction, and it is said that the larger the size, the larger the arc. There is. However, in the shroud 2 of this embodiment, the front-back width c of the shroud 2 and the size of the arc R of the boundary between the air conducting portion 2a and the open portion 2b are shown in FIG. 1 regardless of the above relationship. Can be set relatively roughly. That is, the size of the arc R is irrespective of the front-back width c of the shroud 2,
It may be set so that the front side position P of the air conducting portion 2a becomes clear and does not form a pin angle.
尚、第3図に示すように、この実施例における軸流フ
ァン4とシュラウド2とのクリアランスSは、従来の送
風機と同様に3mmに設定されている。Incidentally, as shown in FIG. 3, the clearance S between the axial fan 4 and the shroud 2 in this embodiment is set to 3 mm as in the conventional blower.
次に、上記のように構成された送風機の作用について
説明する。Next, the operation of the blower configured as above will be described.
この送風機では、前記第2従来例におけるブレード11
aに前傾角θ2を設けた軸流ファン11とは異なり、軸流
ファン4の角ブレード4bに前傾角θ2を設けていないの
で、軸流ファン4の前後方向の幅が大きくなることはな
い。又、シュラウド2と軸流ファン4との位置関係にお
いて、軸流ファン4のボス部4aの前端側4cを空気導通部
2aの前側位置Pから開放部2bへ所定の前進量αだけ前進
させて配置している。このため、開放部2bの前後方向の
寸法を略従来通りの大きさにしながら、且つ軸流ファン
4の後方スペースを充分に確保しながら空気導通部2aの
前後幅bを小さくすることができ、シュラウド2の前後
幅cを小さくして送風機全体の前後方向の体格Wを小さ
くすることができる。In this blower, the blade 11 in the second conventional example is used.
Unlike the axial fan 11 in which the forward inclination angle θ2 is provided in a, since the forward inclination angle θ2 is not provided in the angular blade 4b of the axial fan 4, the axial width of the axial fan 4 does not increase in the front-rear direction. Further, in the positional relationship between the shroud 2 and the axial fan 4, the front end side 4c of the boss portion 4a of the axial fan 4 is connected to the air conducting portion.
It is arranged by advancing by a predetermined advance amount α from the front position P of 2a to the opening 2b. Therefore, the front-rear width b of the air-conducting portion 2a can be reduced while the dimension of the open portion 2b in the front-rear direction is substantially the same as that of the conventional one and the rear space of the axial fan 4 is sufficiently secured. The front-rear width c of the shroud 2 can be reduced to reduce the front-rear physique W of the blower as a whole.
この結果、混雑したエンジンルームにおいても、送風
機の基本的な送風性能を維持させながら比較的小さなス
ペースで送風機を取付けることができる。As a result, even in a congested engine room, the blower can be installed in a relatively small space while maintaining the basic blow performance of the blower.
又、軸流ファン4のボス部4aの前端側4cを空気導通部
2aから開放部2bへ前進量αだけ前進させて配置している
ことと、シュラウド2の開放部2bを空気導通部2aへ収束
するように斜状に形成していることとにより、軸流ファ
ン4の各ブレード4bにかかわる空気力の圧力中心を軸流
ファン4の前方へ移動させることができる。これによっ
て、第1,3図に矢印で示すように、各ブレード4bを通過
する空気の流れが軸流ファン4の求心方向へ向けられ
る。即ち、開放部2bへ導かれた空気の流れがその斜面2c
との干渉により求心方向へ向けられる。In addition, the front end side 4c of the boss portion 4a of the axial fan 4 is connected to the air conducting portion.
By arranging the shroud 2 so as to advance from the opening portion 2b to the opening portion 2b by an advance amount α, and by forming the opening portion 2b of the shroud 2 in an oblique shape so as to converge to the air conducting portion 2a, the axial fan It is possible to move the pressure center of the aerodynamic force related to each blade 4b of No. 4 to the front of the axial fan 4. As a result, the flow of air passing through each blade 4b is directed in the centripetal direction of the axial fan 4, as shown by the arrows in FIGS. That is, the flow of air guided to the open portion 2b is the slope 2c.
Directed toward the centripetal direction by interference with.
この結果、各ブレード4bの端部に発生する空気渦、即
ち翼端渦を小さくすることができ、騒音発生を低減させ
ることができる。As a result, the air vortex generated at the end of each blade 4b, that is, the wing tip vortex can be reduced, and noise generation can be reduced.
更に、軸流ファン4の各ブレード4bをその回転方向X
へ前進させるように傾けたことと、前記のように軸流フ
ァン4を通過する空気を求心方向へ向けたこととが相俟
って、送風機における騒音低減の効果を更に向上させる
ことができる。Further, each blade 4b of the axial fan 4 is rotated in the rotation direction X
The effect of reducing the noise in the blower can be further improved by the fact that it is tilted so as to move forward and the air passing through the axial fan 4 is directed in the centripetal direction as described above.
この実施例の送風機では、各ブレードが前進・前傾の
形状ではない軸流ファンに比べて、約3dBの騒音低減を
実現することができた。即ち、この実施例の送風機で
は、前記第2従来例における前進・前傾タイプの軸流フ
ァン11を備えた送風機の騒音低減に匹敵する効果を実現
することができた。In the blower of this example, noise reduction of about 3 dB could be realized as compared with an axial fan in which each blade does not have a forward / forward tilted shape. That is, with the blower of this embodiment, an effect comparable to the noise reduction of the blower provided with the forward / forward tilt type axial flow fan 11 in the second conventional example could be realized.
従って、この実施例の送風機では、各ブレード4bの表
面に特殊な凹凸等の加工を何ら施すことなく騒音低減を
有効に行うことができる。Therefore, in the blower of this embodiment, noise reduction can be effectively performed without performing any processing such as special unevenness on the surface of each blade 4b.
尚、この発明は前記実施例に限定されるものではな
く、発明の趣旨を逸脱しない範囲において構成の一部を
適宜に変更して次のように実施することもできる。The present invention is not limited to the above-described embodiments, and a part of the configuration can be appropriately modified and carried out as follows without departing from the spirit of the invention.
(1)前記実施例では、軸流ファン4の前進量αを40mm
に設定したが、騒音低減の効果を損なわない範囲で前進
量αを適宜に増減してもよい。(1) In the above embodiment, the advance amount α of the axial fan 4 is 40 mm.
However, the advance amount α may be appropriately increased or decreased within a range that does not impair the noise reduction effect.
(2)前記実施例では、軸流ファン4の各ブレード4bの
前進角θ1を45度に設定したが、騒音低減の効果を損な
わない範囲で前進角θ1を適宜に増減してもよい。(2) In the above embodiment, the advancing angle θ1 of each blade 4b of the axial fan 4 is set to 45 degrees, but the advancing angle θ1 may be appropriately increased or decreased within a range that does not impair the noise reduction effect.
(3)前記実施例では、自動車のラジエタ冷却用の送風
機に具体化したが、家庭用空調装置の室外機用の送風機
に具体化してもよい。(3) In the above-described embodiment, the fan is used for cooling the radiator of the automobile, but it may be embodied as the fan for the outdoor unit of the home air conditioner.
(4)前記実施例では、軸流ファン4を回転させるため
の駆動源とモータ3を設けたが、自動車のエンジンを駆
動源として使用してもよい。(4) In the above embodiment, the drive source for rotating the axial fan 4 and the motor 3 are provided, but an automobile engine may be used as the drive source.
[発明の効果] 以上詳述したようにこの発明によれば、各ブレード表
面に特殊な加工を何ら施す必要がなく、又、開放部の前
後方向の寸法を略従来通りの大きさにしながら、軸流フ
ァンの後方に所定量のスペースを確保しつつ空気導通部
の前後幅を小さくでき、シュラウドの前後幅を小さくし
て送風機全体の前後方向の体格を小さくできるので、小
さなスペースで取付けることができて騒音低減を実現す
ることができるという優れた効果を発揮する。[Effects of the Invention] As described in detail above, according to the present invention, it is not necessary to perform any special processing on the surface of each blade, and the dimension of the open portion in the front-rear direction is substantially the same as the conventional one. The front and rear width of the air-conducting part can be reduced while ensuring a certain amount of space behind the axial fan, and the front and rear width of the blower can be reduced by reducing the front and rear width of the shroud. It has the excellent effect of being able to achieve noise reduction.
第1図はこの発明を具体化した一実施例を示す送風機の
部分破断側面図、第2図は同じく送風機の正面図、第3
図は同じく送風機の部分破断側面図、第4図は軸流ファ
ンのブレードの前進角と騒音発生の関係を示すグラフ、
第5図は軸流ファンのブレードの前傾角と騒音発生の関
係を示すグラフである。第6図は第2従来例の軸流ファ
ンの部分破断正面図、第7図は同じく軸流ファンの部分
破断側面図、第8図は第2従来例の軸流ファンを適用し
た送風機の部分破断側面図である。 図中、2はシュラウド、2aは空気導通部、2bは開放部、
3は駆動源としてのモータ、4は軸流ファン、4bはブレ
ード、4cは前端側、Lは回転軸線、Xは回転方向、θ1
は前進角、αは前進量である。FIG. 1 is a partially cutaway side view of a blower showing an embodiment of the present invention, and FIG. 2 is a front view of the blower, and FIG.
Similarly, the figure is a partially broken side view of the blower, and FIG. 4 is a graph showing the relationship between the advancing angle of the blade of the axial fan and noise generation.
FIG. 5 is a graph showing the relationship between the forward inclination angle of the blade of the axial fan and noise generation. FIG. 6 is a partially cutaway front view of the axial fan of the second conventional example, FIG. 7 is a partially cutaway side view of the axial fan of the same, and FIG. 8 is a blower part to which the axial fan of the second conventional example is applied. It is a fracture | rupture side view. In the figure, 2 is a shroud, 2a is an air conducting part, 2b is an open part,
3 is a motor as a drive source, 4 is an axial fan, 4b is a blade, 4c is a front end side, L is a rotation axis, X is a rotation direction, and θ1
Is the advance angle, and α is the advance amount.
Claims (1)
え、その軸流ファンの後方に所定量のスペースを確保し
つつ当該軸流ファンを内包する管状の空気導通部と、同
軸流ファン前方の広範囲の空気を前記空気導通部へ導く
ために前記空気導通部に連続して軸流ファンの前方へ開
放される開放部とからなるシュラウドを備えた送風機に
おいて、 前記シュラウドの前記開放部を前記空気導通部へ収束さ
せるように斜状に形成し、前記軸流ファンの各ブレード
を、その回転方向へ前進させるように傾けて設ける一
方、軸流ファンの回転軸線に対しては当該軸線方向にお
いて各ブレードの前縁部が略垂直となるようにし、その
軸流ファンの回転軸方向の前端側を前記空気導通部と開
放部との境目から前記開放部へ所定量だけ前進させて配
置したことを特徴とする送風機。1. A tubular air conducting portion including an axial fan that is rotated by a drive source, the tubular air conducting portion including the axial fan while ensuring a predetermined amount of space behind the axial fan, and the front of the coaxial fan. A blower provided with a shroud that is open to the front of the axial fan and that is continuous with the air-conducting part to guide a wide range of air to the air-conducting part. The blade is formed in a slanted shape so as to converge to the air-conducting portion, and each blade of the axial fan is provided so as to be inclined so as to advance in the rotation direction thereof, while in the axial direction with respect to the rotation axis of the axial fan. The front edge portion of each blade is made substantially vertical, and the front end side of the axial fan in the rotation axis direction is arranged by advancing by a predetermined amount from the boundary between the air conducting portion and the opening portion to the opening portion. To Characterized blower.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP63221086A JP2560793B2 (en) | 1988-09-02 | 1988-09-02 | Blower |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP63221086A JP2560793B2 (en) | 1988-09-02 | 1988-09-02 | Blower |
Publications (2)
Publication Number | Publication Date |
---|---|
JPH0270998A JPH0270998A (en) | 1990-03-09 |
JP2560793B2 true JP2560793B2 (en) | 1996-12-04 |
Family
ID=16761269
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP63221086A Expired - Lifetime JP2560793B2 (en) | 1988-09-02 | 1988-09-02 | Blower |
Country Status (1)
Country | Link |
---|---|
JP (1) | JP2560793B2 (en) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US10550855B2 (en) | 2014-02-14 | 2020-02-04 | Mitsubishi Electric Corporation | Axial flow fan |
US10563751B2 (en) | 2017-04-19 | 2020-02-18 | Excel Industries, Inc. | Cooling apparatus for continuously variable transmissions |
Families Citing this family (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US7585149B2 (en) * | 2006-08-07 | 2009-09-08 | Deere & Company | Fan variable immersion system |
JP4613181B2 (en) * | 2007-05-10 | 2011-01-12 | 株式会社スイデン | Air blower |
Family Cites Families (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS619596U (en) * | 1984-06-21 | 1986-01-21 | 三菱電機株式会社 | Air blower |
JPS62143096U (en) * | 1986-03-04 | 1987-09-09 | ||
JPS62169295U (en) * | 1986-04-04 | 1987-10-27 | ||
JPS62282198A (en) * | 1986-05-30 | 1987-12-08 | Mitsubishi Electric Corp | Axial fan |
-
1988
- 1988-09-02 JP JP63221086A patent/JP2560793B2/en not_active Expired - Lifetime
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US10550855B2 (en) | 2014-02-14 | 2020-02-04 | Mitsubishi Electric Corporation | Axial flow fan |
DE112014006367B4 (en) | 2014-02-14 | 2024-08-01 | Mitsubishi Electric Corporation | AXIAL FLOW FANS |
US10563751B2 (en) | 2017-04-19 | 2020-02-18 | Excel Industries, Inc. | Cooling apparatus for continuously variable transmissions |
Also Published As
Publication number | Publication date |
---|---|
JPH0270998A (en) | 1990-03-09 |
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