JPH0932796A - Blower - Google Patents
BlowerInfo
- Publication number
- JPH0932796A JPH0932796A JP18151095A JP18151095A JPH0932796A JP H0932796 A JPH0932796 A JP H0932796A JP 18151095 A JP18151095 A JP 18151095A JP 18151095 A JP18151095 A JP 18151095A JP H0932796 A JPH0932796 A JP H0932796A
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- Prior art keywords
- blower
- axial
- centrifugal
- air
- blade
- 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.)
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- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
Description
【０００１】[0001]
【発明の属する技術分野】本発明は一般産業用の送風機
に広く適用できる送風機に係り、特に、低圧から高圧ま
で、または小型から大型まで広く適用することができる
送風機に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a blower widely applicable to general industrial blowers, and more particularly to a blower widely applicable from low pressure to high pressure or from small size to large size.
【０００２】[0002]
【発明が解決しようとする課題】一般に、送風機には、
軸流形式と遠心形式とがある。軸流形式は大風量が出せ
るが低風圧であり、高い風圧を得ることができないの
で、軸流送風機は比較的低風圧で大風量を得る目的で広
く使われている。このような軸流送風機の低騒音化のた
めには主に翼形状の改良が行なわれ、かなりの低騒音化
に成功しており、現在、さらなる低騒音化、すなわち超
低騒音化を目指して研究開発が行なわれているが、今の
ところ革新的な成果は報告されていない。Generally, a blower has a
There are axial flow type and centrifugal type. Since the axial flow type can generate a large amount of air but has a low air pressure and cannot obtain a high air pressure, an axial blower is widely used for the purpose of obtaining a large air amount at a relatively low air pressure. In order to reduce the noise of such an axial blower, the blade shape was mainly improved, and it succeeded in considerably reducing the noise.At present, aiming for further noise reduction, that is, ultra-noise reduction. Research and development is ongoing, but so far no innovative results have been reported.
【０００３】一方、遠心形式は逆に送風流量は少ないが
高風圧が得られる。このような軸流、遠心形式とも騒音
低下のために多大の努力が払われてきたが、軸流形式と
遠心形式を個別に取り扱うことにほぼ限界がきている。On the other hand, in contrast to the centrifugal type, a high air pressure can be obtained although the air flow rate is small. Although great efforts have been made to reduce noise in both the axial flow type and the centrifugal type, there are almost limits to handling the axial type and the centrifugal type separately.
【０００４】そこで本発明の目的は、主に軸流送風機
と、遠心送風機とを組み合せる等により一段と低騒音化
することができる高性能の送風機を提供することにあ
る。Therefore, an object of the present invention is to provide a high-performance blower capable of further reducing noise by mainly combining an axial blower and a centrifugal blower.
【０００５】[0005]
【課題を解決するための手段】請求項１記載の発明は、
軸流送風機の回転軸に、その吹出側にて遠心送風機を取
り付けている。According to the first aspect of the present invention,
A centrifugal blower is attached to the rotating shaft of the axial blower on the outlet side thereof.
【０００６】請求項２記載の発明は、請求項１記載の発
明であって、遠心送風機は、軸流送風機の回転軸に同心
状に取り付けられた円板と、この円板の一面上に環状に
配設された複数の矩形平板状の翼とを具備し、これら各
翼の円板への取付角を、円板中心と各翼の内側端とを結
ぶ基準線と、各翼の軸直角線とのなす角度が円板回転方
向と反対方向へ０〜６０°の範囲に設定している。The invention according to claim 2 is the invention according to claim 1, wherein the centrifugal blower is a disk concentrically attached to the rotary shaft of the axial blower, and an annular ring is formed on one surface of the disk. And a plurality of rectangular flat-plate blades arranged on the blade, and the mounting angle of each blade to the disc is defined by the reference line connecting the center of the disc and the inner end of each blade and the axis perpendicular to each blade. The angle formed by the line is set in the range of 0 to 60 ° in the direction opposite to the disc rotation direction.
【０００７】請求項３記載の発明は、請求項２記載の発
明であって、遠心送風機の矩形平板状の各翼を、台形平
板状の翼に置換している。The invention according to claim 3 is the invention according to claim 2, wherein each of the rectangular flat blades of the centrifugal blower is replaced with a trapezoidal flat blade.
【０００８】請求項４記載の発明は、請求項２記載の発
明であって、遠心送風機の矩形平板状の各翼を、回転方
向に向けて凸状に湾曲する円弧状の翼に置換している。The invention according to claim 4 is the invention according to claim 2, wherein each blade of the rectangular flat plate of the centrifugal blower is replaced with an arc-shaped blade which is convexly curved in the rotational direction. There is.
【０００９】請求項５記載の発明は、軸流送風機の回転
軸に、その吹出側にて、円板を取り付け、この円板と上
記軸流送風機との間にて、この円板の遠心方向に吹出風
路を形成している。According to a fifth aspect of the present invention, a disc is attached to the rotary shaft of the axial blower on the blow-out side thereof, and the disc is mounted between the disc and the axial blower in the centrifugal direction of the disc. It forms a blowout air path.
【００１０】請求項６記載の発明は、軸流送風機と、こ
の軸流送風機からの送風を受けて、その軸流送風機の遠
心方向外方へ送風させる風向手段と、を具備している。The invention according to claim 6 is provided with an axial blower and wind direction means for receiving air from the axial blower and blowing the air outward in the centrifugal direction of the axial blower.
【００１１】そして、請求項１〜４の各発明において
は、送風圧は低いが、送風流量の大きい軸流送風機と、
送風圧は高いが送風流量の少ない遠心送風機とを１本の
回転軸により同軸に結合しているので、これら両者は同
時に同一方向かつ単位時間当り同一回転数で回転し、軸
流送風機からの送風を再び遠心送風機により昇圧して遠
心方向外方へ送風する。In each of the first to fourth aspects of the invention, there is provided an axial blower having a low blast pressure but a large blast flow rate.
The centrifugal blower, which has a high blower pressure but a small blown flow rate, is coaxially connected by a single rotating shaft, so both of them simultaneously rotate in the same direction and at the same number of revolutions per unit time, and the blower from the axial blower Is again boosted by a centrifugal blower and blown outward in the centrifugal direction.
【００１２】このために、軸流送風機又は遠心送風機の
みの場合に比してＰ（圧力）−Ｑ（流量）特性を向上さ
せることができると共に、送風騒音を低減することがで
きる。Therefore, the P (pressure) -Q (flow rate) characteristics can be improved and the blast noise can be reduced as compared with the case of using only the axial blower or the centrifugal blower.
【００１３】請求項２の発明においては、遠心送風機の
各翼を矩形平板状に形成し、請求項３の発明において
は、遠心送風機の各翼を台形平板状に形成しており、翼
形状が共に単純であるので、翼の製作コストを低減する
ことができる。According to the invention of claim 2, each blade of the centrifugal blower is formed in a rectangular flat plate shape, and in the invention of claim 3, each blade of the centrifugal blower is formed in a trapezoidal flat plate shape. Since both are simple, the manufacturing cost of the blade can be reduced.
【００１４】請求項５の発明においては、軸流送風機と
円板とが同時に連動して、軸流送風機からの送風が円板
の遠心方向の吹出風路を通って外部へ送風される。In the fifth aspect of the invention, the axial blower and the disc are simultaneously operated, and the blown air from the axial blower is blown to the outside through the blowout passage in the centrifugal direction of the disc.
【００１５】これによっても、軸流送風機のみの場合に
比してＰ−Ｑ特性を向上させることができると共に、送
風騒音を低減することができる。Also by this, it is possible to improve the PQ characteristics and to reduce the blowing noise as compared with the case where only the axial blower is used.
【００１６】請求項６の発明においては、軸流送風機か
らの送風を風向手段により遠心方向外方へ案内させて外
部へ送風させるが、これによっても、軸流送風機のみの
場合に比してＰ−Ｑ特性の向上と送風騒音の低減とを共
に図ることができる。In the invention of claim 6, the air blown from the axial blower is guided to the outside in the centrifugal direction by the wind direction means and blown to the outside. It is possible to improve the -Q characteristic and reduce blast noise.
【００１７】[0017]
【発明の実施の形態】以下、本発明の実施の形態を図１
〜図１２に基づいて説明する。なお、図１〜図１２中、
同一または相当部分には同一符号を付している。BEST MODE FOR CARRYING OUT THE INVENTION Embodiments of the present invention will be described below with reference to FIG.
This will be described with reference to FIG. In addition, in FIGS.
The same or corresponding parts are designated by the same reference numerals.
【００１８】図１は本発明の第１の実施形態の要部側面
図であり、この図１において、送風機１は軸流送風機２
の回転軸３に、その吹出側４にて遠心送風機５のボス部
５ａを接続しており、この回転軸３の先端部（図１では
右端部）には図示しないモータの出力軸を結合し、１本
の回転軸３により軸流ファン２と遠心送風機５とを同時
に同一方向へ、かつ単位時間当り同一回転数で回転させ
るようになっている。FIG. 1 is a side view of an essential part of a first embodiment of the present invention. In FIG. 1, the blower 1 is an axial flow blower 2.
The boss 5a of the centrifugal blower 5 is connected to the rotary shaft 3 of the rotary blower 3 at the blow-out side 4, and the output shaft of the motor (not shown) is connected to the tip end (the right end in FIG. 1) of the rotary shaft 3. The single rotating shaft 3 allows the axial fan 2 and the centrifugal blower 5 to rotate simultaneously in the same direction and at the same number of revolutions per unit time.
【００１９】軸流送風機２は例えばプロペラファン等の
ように空気を軸方向に吸い込み、かつ送風する送風機で
あって、その外周側には空気流の吸い込みと送風方向と
を案内する釣鐘状のベルマウス６を設けている。The axial-flow blower 2 is a blower such as a propeller fan that sucks air in the axial direction and blows the air, and a bell-shaped bell that guides the suction and the blowing direction of the air flow on the outer peripheral side thereof. A mouse 6 is provided.
【００２０】一方、遠心送風機５は例えばうず巻ファン
や多翼ファン（シロッコファン）等遠心力を利用した送
風機であって、ボス部５ａを形成した環状、または円板
状の基板７の内側面（図１では左側面）に、矩形平板状
の多数の矩形翼８を周方向に所定のピッチを置いて環状
に配設し、遠心方向外方へ送風するようになっている。On the other hand, the centrifugal blower 5 is a blower utilizing centrifugal force such as a spiral fan or a multi-blade fan (sirocco fan), and the inner surface of the annular or disc-shaped substrate 7 having the boss portion 5a formed therein. A large number of rectangular blades 8 in the shape of a rectangular flat plate are annularly arranged (at a left side in FIG. 1) at a predetermined pitch in the circumferential direction, and air is blown outward in the centrifugal direction.
【００２１】図２は各矩形翼８の基板７への取付角θを
示しており、この取付角θは、基板７の中心Ｏと各翼８
の内側端とを直線で結ぶ基準線Ｏｓに対して、各矩形翼
８の軸直角軸８ａがなす角が基板７の回転方向に対して
反対方向へ０°〜６０°の範囲に設定されている。FIG. 2 shows the attachment angle θ of each rectangular blade 8 to the substrate 7. The attachment angle θ is the center O of the substrate 7 and each blade 8.
The angle formed by the axis perpendicular to the axis 8a of each rectangular wing 8 with respect to the reference line Os that connects the inner end of the substrate with a straight line is set in the range of 0 ° to 60 ° in the opposite direction to the rotation direction of the substrate 7. There is.
【００２２】なお、各矩形翼８は図２で示す円弧翼９に
置換してもよい。この円弧翼９はその軸直角断面形状が
基板７の回転方向に向かって凸状に湾曲する円弧形に形
成されているものである。The rectangular blades 8 may be replaced with arcuate blades 9 shown in FIG. The arcuate blade 9 has a cross-sectional shape perpendicular to its axis formed in an arcuate shape that is convexly curved in the rotation direction of the substrate 7.
【００２３】したがって、このように構成された送風機
１においては、図示しないファンモータにより回転軸３
が回転すると、軸流送風機２と遠心送風機５とが同時に
連動して、同一方向に同一回転数で回転する。Therefore, in the blower 1 thus constructed, the rotating shaft 3 is driven by the fan motor (not shown).
When is rotated, the axial blower 2 and the centrifugal blower 5 are simultaneously interlocked and rotate in the same direction at the same rotation speed.
【００２４】このために、外気がベルマウス６から内方
へ吸い込まれてから、軸流送風機２により、その軸方向
下流側へ圧送されて吹出側４へ所定風量と風圧で吹き出
される。さらに、この吹出風は遠心送風機５により、そ
の遠心方向外方へ所定風量と風圧で圧送されて、吹出風
路から外部へ送風される。Therefore, after the outside air is sucked inward from the bell mouth 6, the outside air is blown by the axial blower 2 to the downstream side in the axial direction and blown out to the blowing side 4 with a predetermined air volume and wind pressure. Further, this blown air is pressure-fed outward by the centrifugal blower 5 in the centrifugal direction at a predetermined air volume and wind pressure, and is blown to the outside from the blowout air passage.
【００２５】図３中ａ線はこのように矩形翼８を具備し
た送風機１の送風圧力Ｐと流量ＱとのＰ−Ｑ特性を示
し、ｂ線は従来の軸流ファン２のみの送風機を同一条件
で運転したときのＰ−Ｑ特性を示している。したがって
本発明の送風機１のＰ−Ｑ特性の方が従来の軸流ファン
２のみのＰ−Ｑ特性よりも優れていることが判明した。The line a in FIG. 3 shows the PQ characteristics of the blower pressure P and the flow rate Q of the blower 1 having the rectangular blades 8 as described above, and the line b is the same as that of the conventional blower having only the axial fan 2. The P-Q characteristic at the time of driving on condition is shown. Therefore, it has been found that the PQ characteristics of the blower 1 of the present invention are superior to the PQ characteristics of the conventional axial flow fan 2 alone.
【００２６】図４は上記送風機１の減音特性図であり、
これは送風機１の送風圧力上昇Ｐを例えば２．３mmＡｑ
に固定すると共に、１分間当りの送風流量を１２．０ｍ
3 ／minに固定し、遠心送風機５のボス部５ａの中心か
ら矩形翼８の先端までの半径ｒ2 および軸流送風機２の
ボス部２ａ中心から翼先端までの半径ｒ1 の半径比ｒ2
／ｒ1 と、送風機１の減音量（ｄＢ）との関係を示して
いる。FIG. 4 is a sound reduction characteristic diagram of the blower 1.
This means that the blower pressure increase P of the blower 1 is, for example, 2.3 mmAq.
Fixed to 1 and the air flow rate per minute is 12.0 m.
Fixed at 3 / min, the radius ratio r2 from the center of the boss portion 5a of the centrifugal blower 5 to the tip of the rectangular blade 8 and the radius ratio r2 of the radius r1 from the center of the boss portion 2a of the axial blower 2 to the blade tip.
/ R1 and the volume reduction (dB) of the blower 1 are shown.
【００２７】ここで、減音量とは送風圧力Ｐと流量Ｑと
を同一にした場合に、軸流送風機２単独のときの騒音
と、この軸流送風機２と矩形翼遠心送風機５とを連結し
た送風機１の騒音との差をいう。図３に示すように本発
明の送風機１によれば、上記半径比ｒ2 ／ｒ1 の増大に
比例して減音量（ｄＢ）を増大させることができる。ま
た、図１で示す軸流送風機２の吹出面と遠心送風機５の
基板７の内側面との間隔Ｌは減音をより効果的にするた
めには低圧に行くほど長くしなければならないことが判
明した。Here, the volume reduction means that when the blower pressure P and the flow rate Q are the same, the noise generated when the axial blower 2 alone is connected to the axial blower 2 and the rectangular blade centrifugal blower 5. The difference from the noise of the blower 1. As shown in FIG. 3, according to the blower 1 of the present invention, the volume reduction (dB) can be increased in proportion to the increase of the radius ratio r2 / r1. Further, the distance L between the blowing surface of the axial blower 2 and the inner surface of the substrate 7 of the centrifugal blower 5 shown in FIG. 1 must be made longer as the pressure becomes lower in order to make the noise reduction more effective. found.
【００２８】図５は本発明の第２の実施形態に係る送風
機１Ａの要部側面図であり、この送風機１Ａは上記遠心
送風機５の各矩形翼８を、台形平板状の台形翼１０に置
換した点に特徴がある。これによっても、上記送風機１
Ａとほぼ同様の作用効果を得ることができる。FIG. 5 is a side view of a main part of a blower 1A according to a second embodiment of the present invention. In this blower 1A, each rectangular blade 8 of the centrifugal blower 5 is replaced with a trapezoidal trapezoidal blade 10. The point is that it was done. Also by this, the blower 1
It is possible to obtain substantially the same action and effect as in A.
【００２９】図６は本発明の第３の実施形態に係る送風
機１Ｂの要部側面図であり、この送風機１Ｂは上記遠心
送風機５の各矩形翼８または台形翼１０を省略して、基
板５のみを、軸流送風機２と同一方向かつ同一回転数で
回転する回転円板５ｂに構成した点に特徴がある。FIG. 6 is a side view of an essential part of a blower 1B according to a third embodiment of the present invention. In this blower 1B, the rectangular blades 8 or trapezoidal blades 10 of the centrifugal blower 5 are omitted and the substrate 5 is omitted. It is characterized in that only the rotary disk 5b is configured to rotate in the same direction and at the same rotational speed as the axial blower 2.
【００３０】図７はこの送風機１ＢのＰ−Ｑ特性を一点
鎖線ｃで示しており、この特性線ｃは図２でも示す従来
の軸流送風機２のみのＰ−Ｑ特性線ｂと、上記第１の実
施形態のＰ−Ｑ特性線ａとのほぼ中間の性能を示してい
る。FIG. 7 shows the P-Q characteristic of the blower 1B by a one-dot chain line c. The characteristic line c is the P-Q characteristic line b of only the conventional axial blower 2 shown in FIG. The performance is almost in the middle of the PQ characteristic line a of the first embodiment.
【００３１】図８は本発明の第４の実施形態に係る送風
機１Ｃの要部側面図であり、この送風機１Ｃは図６で示
す送風機１Ｂの回転円板５ｂを、断面形状がほぼ三角形
の回転しない風向板１１に置換した点に特徴がある。FIG. 8 is a side view of an essential part of a blower 1C according to a fourth embodiment of the present invention. This blower 1C rotates a rotating disk 5b of the blower 1B shown in FIG. It is characterized in that the wind direction plate 11 is replaced.
【００３２】風向板１１は軸流送風機２の回転軸３を貫
通せしめる中心部を、軸流送風機２側へくの字状に突出
する頂部とする一方、外径方向に先細の三角形をなし、
その先細外端部外周に、図中白矢印で示す空気流の吹出
方向を案内する吹出風路１２を形成している。風向板１
１の背面軸心部には回転軸３を回転駆動するファンモー
タ１３を取り付けている。この送風機１Ｃによっても上
記送風機１，１Ａ，１Ｂと同様にファン性能を従来例よ
りも向上させることができる。The air flow direction plate 11 has a central portion through which the rotary shaft 3 of the axial flow fan 2 penetrates as a top portion projecting in a V shape toward the axial flow fan 2 side, while forming a tapered triangle in the outer diameter direction,
On the outer circumference of the tapered outer end portion, a blowout air passage 12 for guiding the blowout direction of the airflow shown by a white arrow in the drawing is formed. Wind vane 1
A fan motor 13 that rotationally drives the rotary shaft 3 is attached to the rear-side center of the shaft 1. With this blower 1C, the fan performance can be improved more than that of the conventional example, as in the case of the blowers 1, 1A and 1B.
【００３３】図９は本発明の第５の実施形態に係る送風
機１Ｄの要部側面図であり、この送風機１Ｄは図８で示
す送風機１Ｃの風向板１１を単なる平板の風向板１１Ａ
に置換すると共に、前面側の吹出側４にファンモータ１
３を配設した点に特徴がある。FIG. 9 is a side view of an essential part of a blower 1D according to a fifth embodiment of the present invention. This blower 1D is a simple flat wind vane 11A instead of the wind vane 11 of the blower 1C shown in FIG.
And the fan motor 1 on the blow-out side 4 on the front side.
The feature is that 3 is provided.
【００３４】この送風機１Ｄは軸流送風機２と平板風向
板１１Ａとの間隔Ｌを適宜選択することによりファン特
性を改善することができる。例えば高圧特性を改善する
ときは間隔Ｌを軸流送風機２の直径の例えば約６％程度
に設定し、中圧特性を改善するときは間隔Ｌを軸流送風
機２の直径の約１５％位に設定するとよい。In this blower 1D, the fan characteristic can be improved by appropriately selecting the distance L between the axial blower 2 and the flat airflow direction plate 11A. For example, when improving the high pressure characteristics, the interval L is set to, for example, about 6% of the diameter of the axial blower 2. When improving the intermediate pressure characteristics, the interval L is set to about 15% of the diameter of the axial blower 2. Good to set.
【００３５】図１０はこの送風機１ＤのＰ−Ｑ特性を示
しており、図中ｅは軸流送風機２のみの従来例のＰ−Ｑ
特性を示し、ｆは間隔Ｌを小さく設定し、ｇは間隔Ｌを
大きく設定したときのＰ−Ｑ特性を示している。FIG. 10 shows the P-Q characteristic of this blower 1D, and e in the figure is the P-Q of the conventional example in which only the axial blower 2 is used.
The characteristics are shown, f shows the PQ characteristics when the interval L is set small, and g shows the PQ characteristics when the interval L is set large.
【００３６】図１１は本発明の第５の実施形態に係る空
気調和機の室外機１５の一例の部分縦断面図であり、こ
の室外機１５は図１２で示す従来の遠心送風機１４に代
えて図１で示す送風機１を室外ファンとして内蔵した点
に特徴がある。FIG. 11 is a partial vertical cross-sectional view of an example of an outdoor unit 15 of an air conditioner according to a fifth embodiment of the present invention. The outdoor unit 15 is replaced with the conventional centrifugal blower 14 shown in FIG. A feature is that the blower 1 shown in FIG. 1 is incorporated as an outdoor fan.
【００３７】室外機１５は送風機１と共に室外熱交換器
１６や図示しない圧縮機等を内蔵し、送風機１により外
気を吸込口１７から室外機１５内へ吸い込むと共に、こ
の外気を室外熱交換器１６へ送風することにより、この
室外熱交換器１６内を通る冷媒と外気との熱交換を効率
的に行なうものである。なお、図１１中、符号１５ａは
支持板であり、これはファンモータ１３を取り付けると
共に、吹出風の吹出方向を案内するものである。The outdoor unit 15 incorporates an outdoor heat exchanger 16 and a compressor (not shown) together with the blower 1, sucks the outside air into the outdoor unit 15 from the suction port 17 by the blower 1, and at the same time, the outside air is exchanged with the outdoor heat exchanger 16. By blowing air into the outdoor heat exchanger 16, heat exchange between the refrigerant passing through the outdoor heat exchanger 16 and the outside air is efficiently performed. In addition, in FIG. 11, reference numeral 15a is a support plate, which is used for mounting the fan motor 13 and for guiding the blowing direction of the blowing air.
【００３８】図１２で示す従来の遠心送風機１４は、図
示しないファンモータの回転軸が結合されるボス部１８
ａを突設している円板状の基板１８の一面の外周部上
に、複数の翼１９を周方向に所定のピッチで環状に配設
し、ベルマウス２０の吸込口２０ａから空気を吸い込
み、図中矢印に示すように隣り合う各翼１９同士間の間
隙から遠心方向外方へ送風するものである。The conventional centrifugal blower 14 shown in FIG. 12 has a boss portion 18 to which a rotating shaft of a fan motor (not shown) is coupled.
A plurality of blades 19 are annularly arranged at a predetermined pitch in the circumferential direction on the outer peripheral portion of one surface of the disk-shaped substrate 18 projecting a, and air is sucked from the suction port 20a of the bell mouth 20. The air is blown outward in the centrifugal direction from the gap between the adjacent blades 19 as shown by the arrow in the figure.
【００３９】一方、図１で示す送風機１はこの従来の遠
心送風機１４よりも送風性能で優れているうえに低騒音
であるので、室外機１５内の室外熱交換器１６による熱
交換性能を向上させることができるうえに、静粛性を高
めることができる。On the other hand, the blower 1 shown in FIG. 1 is superior in blowing performance to this conventional centrifugal blower 14 and has low noise, so that the heat exchange performance by the outdoor heat exchanger 16 in the outdoor unit 15 is improved. Not only can it be done, but also quietness can be enhanced.
【００４０】また、この送風機１を室外送風機として室
外機１５内に内蔵する場合には、遠心送風機５の背後に
ファンモータ１３を配置して、その半径方向に吹出風路
１２を適宜形成することができるので、室外機１５を、
その後板２１が図示しない建屋等の外壁等に密着するよ
うに屋外に設置することができる。これにより、室外機
１５の設置スペースの節約を図ることができる。When the blower 1 is built in the outdoor unit 15 as an outdoor blower, the fan motor 13 is arranged behind the centrifugal blower 5 and the blowout air passage 12 is appropriately formed in the radial direction. Since it is possible to use the outdoor unit 15,
After that, the plate 21 can be installed outdoors so as to be in close contact with an outer wall of a building or the like (not shown). As a result, the installation space for the outdoor unit 15 can be saved.
【００４１】図１３は本発明の第６の実施形態に係る空
気清浄機２２の概略構成図であり、この空気清浄機２２
は、その本体ケース２３内に、空気をろ過するエアーフ
ィルタ２４等と共に上記送風機１を内蔵しており、送風
機１の運転により外気を吸込口２５から本体ケース２３
内へ吸い込み、その吸込み空気をエアーフィルタ２４内
に通風して浄化し、各吹出風路１２から再び外部へ送風
することにより空気を浄化するようになっている。FIG. 13 is a schematic structural diagram of an air cleaner 22 according to the sixth embodiment of the present invention.
The air blower 1 is built in the main body case 23 together with an air filter 24 for filtering air, and the operation of the blower 1 draws the outside air from the suction port 25 to the main body case 23.
The air is sucked in, and the sucked air is ventilated into the air filter 24 to purify the air, and the air is blown from the blowout air passages 12 to the outside again to purify the air.
【００４２】従来のこの種の空気清浄機は送風機として
送風圧は高いが小送風量の例えばシロッコファン（多翼
遠心送風機）を使用している。このため、単位容積当り
の空気清浄に要する時間が長かった。The conventional air purifier of this type uses, for example, a sirocco fan (multi-blade centrifugal blower) having a high blowing pressure but a small blowing amount as a blower. Therefore, it takes a long time to clean the air per unit volume.
【００４３】しかし、この空気清浄機２２によれば、高
い送風圧で大流量かつ低騒音の送風機１を使用している
ので、空気清浄を短時間で効率よくかつ低騒音で行なう
ことができる。However, according to the air purifier 22, since the blower 1 having a high blowing pressure and a large flow rate and low noise is used, the air cleaning can be performed efficiently in a short time and with low noise.
【００４４】図１３は本発明の第７の実施形態に係るＯ
Ａ機器２６の概略構成図であり、このＯＡ機器２６は複
写機やファクシミリ等であって、本体ケース２７内に、
複数の電子電気部品２８等と共に送風機１を冷却ファン
として内蔵し、通電時に発熱する電子電気部品２８に、
送風機１により本体ケース２７内に吸い込んだ外気を送
風して冷却するようになっている。FIG. 13 shows the O according to the seventh embodiment of the present invention.
FIG. 2 is a schematic configuration diagram of an A device 26, which is a copying machine, a facsimile, etc.
The blower 1 is built-in as a cooling fan together with a plurality of electronic / electrical components 28, and the electronic / electrical components 28 that generate heat when energized are
The blower 1 blows the outside air sucked into the main body case 27 to cool it.
【００４５】このＯＡ機器２６によっても、高い送風圧
で大流量かつ低騒音の送風機１を使用しているので、各
電子電気部品２８を高効率かつ低騒音で冷却することが
できるうえに、吹出風路１２を本体ケース２７の半径方
向に適宜形成することができる。このために、本体ケー
ス２７の後板２７ａに図示しない吹出孔を必ず設ける必
要がなく、その吹出孔の配置の自由度を増大させること
ができるうえに、後板２７ａを例えば室内の内壁に密着
させて設置することができるので、その設置スペースを
節約することができる。Since the OA device 26 also uses the blower 1 having a high flow rate and a large flow rate and low noise, it is possible to cool the electronic / electrical parts 28 with high efficiency and low noise, and The air passage 12 can be appropriately formed in the radial direction of the main body case 27. For this reason, it is not necessary to necessarily provide a blowout hole (not shown) in the rear plate 27a of the main body case 27, the degree of freedom in arranging the blowout hole can be increased, and the rear plate 27a is closely attached to the inner wall of the room, for example. Since it can be installed by itself, the installation space can be saved.
【００４６】なお、上記実施形態では送風機として図１
で示す送風機１を空気調和機の室外機１５や空気清浄機
２２，ＯＡ機器２６に適用する場合について説明した
が、本発明はこれに限定されるものではなく、これら各
種機器に他の送風機１Ａ〜１Ｄを使用してもよく、さら
に、これらの適用機器としては、換気扇やレンジファ
ン，パイプファンおよび工業用有圧ファン等送風機を組
み込む機器一般に適用することができる。In the above embodiment, the blower shown in FIG.
The case where the blower 1 shown in FIG. 2 is applied to the outdoor unit 15 of the air conditioner, the air purifier 22, and the OA device 26 has been described, but the present invention is not limited to this and other blowers 1A for these various devices. .About.1D may be used, and as applicable equipment for these, general equipment incorporating a blower such as a ventilation fan, a range fan, a pipe fan and an industrial pressure fan can be applied.
【００４７】[0047]
【発明の効果】以上説明したように、請求項１〜４の各
発明においては、送風圧は低いが、送風流量の大きい軸
流送風機と、送風圧は高いが送風流量の少ない遠心送風
機とを１本の回転軸により同軸に結合しているので、こ
れら両者は同時に同一方向かつ単位時間当り同一回転数
で回転し、軸流送風機からの送風を再び遠心送風機によ
り昇圧して遠心方向外方へ送風する。As described above, in each of the first to fourth aspects of the invention, an axial blower having a low blast pressure but a large blast flow rate and a centrifugal blower having a high blast pressure but a small blast flow rate are provided. Since they are coaxially connected by a single rotating shaft, both of them rotate in the same direction and at the same number of revolutions per unit time at the same time, and the air from the axial blower is boosted again by the centrifugal blower to the outside in the centrifugal direction. Blow air.
【００４８】このために、軸流送風機又は遠心送風機の
みの場合に比してＰ（圧力）−Ｑ（流量）特性を向上さ
せることができると共に、送風騒音を低減することがで
きる。Therefore, the P (pressure) -Q (flow rate) characteristics can be improved and the blast noise can be reduced as compared with the case of using only the axial blower or the centrifugal blower.
【００４９】請求項２の発明においては、遠心送風機の
各翼を矩形平板状に形成し、請求項３の発明において
は、遠心送風機の各翼を台形平板状に形成しており、翼
形状が共に単純であるので、翼の製作コストを低減する
ことができる。In the invention of claim 2, each blade of the centrifugal blower is formed in a rectangular flat plate shape, and in the invention of claim 3, each blade of the centrifugal blower is formed in a trapezoidal flat plate shape. Since both are simple, the manufacturing cost of the blade can be reduced.
【００５０】請求項５の発明においては、軸流送風機と
円板とが同時に連動して、軸流送風機からの送風が円板
の遠心方向の吹出風路を通って外部へ送風される。According to the fifth aspect of the invention, the axial blower and the disc are simultaneously operated, and the blown air from the axial blower is blown to the outside through the blowout air passage in the centrifugal direction of the disc.
【００５１】これによっても、軸流送風機のみの場合に
比してＰ−Ｑ特性を向上させることができると共に、送
風騒音を低減することができる。Also by this, the PQ characteristics can be improved and the blowing noise can be reduced as compared with the case of using only the axial blower.
【００５２】請求項６の発明においては、軸流送風機か
らの送風を風向手段により遠心方向外方へ案内させて外
部へ送風させるが、これによっても、軸流送風機のみの
場合に比してＰ−Ｑ特性の向上と送風騒音の低減とを共
に図ることができる。In the invention of claim 6, the air blown from the axial blower is guided to the outside in the centrifugal direction by the wind direction means and blown to the outside. It is possible to improve the -Q characteristic and reduce blast noise.
【図１】本発明の第１の実施形態に係る送風機の要部側
面図。FIG. 1 is a side view of a main part of a blower according to a first embodiment of the present invention.
【図２】図１で示す遠心送風機の各翼の取付角を示す平
面図。FIG. 2 is a plan view showing a mounting angle of each blade of the centrifugal blower shown in FIG.
【図３】図１で示す送風機のＰ−Ｑ特性図。FIG. 3 is a PQ characteristic diagram of the blower shown in FIG. 1.
【図４】図１で示す送風機の減音特性図。FIG. 4 is a noise reduction characteristic diagram of the blower shown in FIG. 1.
【図５】本発明の第２の実施形態に係る送風機の要部側
面図。FIG. 5 is a side view of a main part of a blower according to a second embodiment of the present invention.
【図６】本発明の第３の実施形態に係る送風機の要部側
面図。FIG. 6 is a side view of a main part of a blower according to a third embodiment of the present invention.
【図７】図６で示す送風機のＰ−Ｑ特性図。7 is a PQ characteristic diagram of the blower shown in FIG.
【図８】本発明の第４の実施形態に係る送風機の要部側
面図。FIG. 8 is a side view of a main part of a blower according to a fourth embodiment of the present invention.
【図９】本発明の第５の実施形態に係る送風機の要部側
面図。FIG. 9 is a side view of a main part of a blower according to a fifth embodiment of the present invention.
【図１０】図９で示す送風機のＰ−Ｑ特性図。FIG. 10 is a PQ characteristic diagram of the blower shown in FIG. 9.
【図１１】図１で示す送風機を室外ファンとして組み込
む空気調和機の室外機の概略構成図。FIG. 11 is a schematic configuration diagram of an outdoor unit of an air conditioner in which the blower shown in FIG. 1 is incorporated as an outdoor fan.
【図１２】従来の多翼遠心送風機の概略斜視図。FIG. 12 is a schematic perspective view of a conventional multiblade centrifugal blower.
【図１３】図１で示す送風機を内蔵する空気洗浄機の概
略構成図。FIG. 13 is a schematic configuration diagram of an air cleaner including the blower shown in FIG.
【図１４】図１で示す送風機を内蔵するＯＡ機器の概略
構成図。FIG. 14 is a schematic configuration diagram of an OA device including the blower shown in FIG.
１，１Ａ，１Ｂ，１Ｃ，１Ｄ 送風機 ２ 軸流送風機 ３ 回転軸 ４ 吹出側 ５ 遠心送風機 ６ ベルマウス ７ 基板 ８ 矩形平板翼 ９ 円弧翼 １０ 台形平板翼 １１ 風向板 １２ 吹出風路 １３ ファンモータ １５ 空気調和機の室外機 １６ 室外熱交換器 ２２ 空気清浄機 ２６ ＯＡ機器 1, 1A, 1B, 1C, 1D Blower 2 Axial blower 3 Rotating shaft 4 Blow-off side 5 Centrifugal blower 6 Bell mouth 7 Substrate 8 Rectangular flat blade 9 Arc blade 10 Trapezoidal flat blade 11 Airflow vane 12 Blow-off air path 13 Fan motor 15 Air conditioner outdoor unit 16 Outdoor heat exchanger 22 Air purifier 26 OA equipment
Claims (6)
遠心送風機を取り付けていることを特徴とする送風機。1. A blower characterized in that a centrifugal blower is attached to the rotary shaft of the axial blower on the blow-out side thereof.
風機は、軸流送風機の回転軸に同心状に取り付けられた
円板と、この円板の一面上に環状に配設された複数の矩
形平板状の翼とを具備し、これら各翼の円板への取付角
を、円板中心と各翼の内側端とを結ぶ基準線と、各翼の
軸直角線とのなす角度が円板回転方向と反対方向へ０〜
６０°の範囲に設定していることを特徴とする送風機。2. The blower according to claim 1, wherein the centrifugal blower is a disk that is concentrically attached to the rotary shaft of the axial blower, and a plurality of rectangles that are annularly arranged on one surface of the disk. A flat plate-shaped blade, and the angle formed between the reference line connecting the center of the disk and the inner end of each blade and the line perpendicular to the axis of each blade 0 to the opposite direction of rotation
A blower characterized by being set in a range of 60 °.
風機の矩形平板状の各翼を、台形平板状の翼に置換して
いることを特徴とする送風機。3. The blower according to claim 2, wherein each of the rectangular flat blades of the centrifugal blower is replaced with a trapezoidal flat blade.
風機の矩形平板状の各翼を、回転方向に向けて凸状に湾
曲する円弧状の翼に置換していることを特徴とする送風
機。4. The blower according to claim 2, wherein each of the rectangular flat blades of the centrifugal blower is replaced with an arcuate blade that is convexly curved in the rotation direction.
て、円板を取り付け、この円板と上記軸流送風機との間
にて、この円板の遠心方向に吹出風路を形成しているこ
とを特徴とする送風機。5. A disc is attached to the rotary shaft of the axial blower at its blow-out side, and a blowout air passage is formed in the centrifugal direction of the disc between the disc and the axial blower. A blower characterized by having.
風を受けて、その軸流送風機の遠心方向外方へ送風させ
る風向手段と、を具備していることを特徴とする送風
機。6. An air blower comprising: an axial flow blower; and a wind direction means for receiving the air blow from the axial flow blower and blowing the air outward in the centrifugal direction of the axial flow blower.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP18151095A JPH0932796A (en) | 1995-07-18 | 1995-07-18 | Blower |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP18151095A JPH0932796A (en) | 1995-07-18 | 1995-07-18 | Blower |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH0932796A true JPH0932796A (en) | 1997-02-04 |
Family
ID=16102029
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP18151095A Pending JPH0932796A (en) | 1995-07-18 | 1995-07-18 | Blower |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH0932796A (en) |
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2005163598A (en) * | 2003-12-02 | 2005-06-23 | Hitachi Ltd | Pipe fan |
| KR101222529B1 (en) * | 2012-10-31 | 2013-01-15 | (주) 토네이도테크 | Vortex type bentilator with bell mouth |
| CN104524879A (en) * | 2015-01-14 | 2015-04-22 | 安徽德赫斯曼环保设备科技有限公司 | Air purifying device |
| JP2015095361A (en) * | 2013-11-12 | 2015-05-18 | 富士重工業株式会社 | Temperature adjustment device |
| JP2015132174A (en) * | 2014-01-09 | 2015-07-23 | 株式会社デンソー | Fluid circulation apparatus |
| CN106971039A (en) * | 2017-03-29 | 2017-07-21 | 首钢京唐钢铁联合有限责任公司 | Capacity expansion transformation method of axial-flow blower |
| EP3199675A1 (en) * | 2016-01-29 | 2017-08-02 | Rieter Ingolstadt GmbH | Spinning machine with a suction device |
-
1995
- 1995-07-18 JP JP18151095A patent/JPH0932796A/en active Pending
Cited By (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2005163598A (en) * | 2003-12-02 | 2005-06-23 | Hitachi Ltd | Pipe fan |
| JP4512352B2 (en) * | 2003-12-02 | 2010-07-28 | 株式会社日立製作所 | Pipe fan |
| KR101222529B1 (en) * | 2012-10-31 | 2013-01-15 | (주) 토네이도테크 | Vortex type bentilator with bell mouth |
| JP2015095361A (en) * | 2013-11-12 | 2015-05-18 | 富士重工業株式会社 | Temperature adjustment device |
| JP2015132174A (en) * | 2014-01-09 | 2015-07-23 | 株式会社デンソー | Fluid circulation apparatus |
| CN104524879A (en) * | 2015-01-14 | 2015-04-22 | 安徽德赫斯曼环保设备科技有限公司 | Air purifying device |
| EP3199675A1 (en) * | 2016-01-29 | 2017-08-02 | Rieter Ingolstadt GmbH | Spinning machine with a suction device |
| CN107119359A (en) * | 2016-01-29 | 2017-09-01 | 立达英格尔施塔特有限公司 | With the spinning machine for suctioning out equipment |
| CN107119359B (en) * | 2016-01-29 | 2022-03-15 | 立达英格尔施塔特有限公司 | Spinning machine with suction device |
| CN106971039A (en) * | 2017-03-29 | 2017-07-21 | 首钢京唐钢铁联合有限责任公司 | Capacity expansion transformation method of axial-flow blower |
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