JPS60145498A - Centrifugal blower - Google Patents

Abstract

PURPOSE:To balance pressure by varying the width on the periphery on the motor side of the air blowing port of a casing according to the installation position of the motor in the direction perpendicular to the shaft of a motor, when the interval between the edge surface of the motor and the edge surface of a casing is smaller than the outside diameter of the vane wheel, in a suction type centrifugal blower. CONSTITUTION:When the interval L between the edge surface 3 of a casing 1 which covers the both multiblade vane wheels 6a and 6b for suction and the edge surface of a motor 8 is less than the outside diameter of the vane wheel 6, the blowing width d1 on the periphery on the opposite side to the motor 8 of a blowing port 7 and the width d2 on the periphery on the motor side of the blowing port are set so tht the relation d1>d2 is established, and the resistance for the suction into the vane wheel 6 is made equal, and the revolution of the vane wheel 6 is stabilized. Therefore, the resistance on the suction side is balanced, and the flow of air is stabilized, and the vibration and noise of the vane wheel 6 due to the difference of resistance on the suction side can be suppressed.

Description

【発明の詳細な説明】 産業上の利用分野 本発明は、空気調和機等に用いられている両吸込形遠心
送風機の送風性能の向上と運転騒音の低下に関するもの
である。DETAILED DESCRIPTION OF THE INVENTION Field of the Invention The present invention relates to improving the blowing performance and reducing operating noise of a double-suction type centrifugal blower used in an air conditioner or the like.

従来例の構成とその問題点 従来、両吸込形遠心送風機は、両吸込用多翼羽根車（以
下単に羽根車と略記する。）を駆動するためのモータな
どを両吸込形遠心送風機のケーシング近傍に設置する構
造となっているが、両吸込形遠心送風機の構造を簡便に
するため、モータの軸に直接羽根車を固定する構成が採
られている。Conventional structure and its problems Conventionally, a double-suction type centrifugal blower has been equipped with a motor for driving a double-suction multi-blade impeller (hereinafter simply referred to as an impeller) near the casing of the double-suction type centrifugal blower. However, in order to simplify the structure of the double-suction type centrifugal blower, the impeller is fixed directly to the motor shaft.

しかし、このような場合、羽根車の重量をモータの軸の
みで片持的に支える必要があり、そのだめ強度的９価格
的な面より軸の長さを可能た限り、短く設計、なければ
ならない。その結果、モータの取付ける位置は、両吸込
形遠心送風機のケーシングの両側板に設けられているノ
ズルの一方の側に近くなるため、空気を吸込む場合の抵
抗のアンバランスの原因となり、送風機の不安定や、振
動。However, in such a case, it is necessary to support the weight of the impeller in a cantilevered manner only by the shaft of the motor, so the length of the shaft must be designed to be as short as possible in terms of strength and cost. No. As a result, the motor is installed close to one side of the nozzle provided on both side plates of the casing of a double-suction centrifugal blower, which causes an imbalance in the resistance when drawing air, causing an imbalance in the blower. Stability and vibration.

騒音の増加を生じるなどの問題欠を有していた。It had some problems, such as an increase in noise.

発明の目的 本発明は、このような問題点を解決するもので、羽根車
駆動用のモータが、両吸込形遠心送風機のケーシング側
板に非常に近く取付けられた場合、あるいは、モータの
一部が羽根車の中へ入り込んだ場合にでも、安定した送
風性能を確保し、運転時の振動、騒音も、従来よシ増加
させないようにすることを目的とするものである。OBJECTS OF THE INVENTION The present invention solves these problems, and is aimed at solving problems when the impeller drive motor is installed very close to the casing side plate of a double-suction type centrifugal blower, or when a part of the motor The purpose is to ensure stable air blowing performance even if the impeller gets into the impeller, and to prevent vibration and noise during operation from increasing compared to conventional methods.

３、− 発明の構成 この目的を達成するために本発明は、両吸込形遠心送風
機のケーシングに設けられた空気吹出し口のモータ側近
辺の巾を、モータの軸と直角な方向に、モータの取付位
置によって変化させたものである。3.-Structure of the Invention In order to achieve this object, the present invention has the following features: The width of the air outlet provided in the casing of a double-suction type centrifugal blower near the motor side is adjusted in the direction perpendicular to the axis of the motor. It changes depending on the mounting position.

この構成によって、両吸込形遠心送風機を運転した場合
、ケーシング両側板に設けられたそれぞれのノズルを通
って羽根車内に吸い込まれる空気は、吹出し口のモータ
側近辺の巾をモータの軸と直角な方向に小さく設定する
ことによって、吸込側の抵抗がバランスされて、空気の
流れは安定し、さらには、吸込側の抵抗差による羽根車
の振動も解消され、騒音増加も抑制することができると
いうものである０ 実施例の説明 以下、本発明をその一実施例を示す第１図〜第５図を参
考に説明するＯ 第１図において、１は両吸込形遠心送風機のケーシング
、２は前記両吸込形遠心送風機のケーシング１の側板Ａ
でモータを取り付けている側と反対の側板、３は前記両
吸込形遠心送風機のケーシング１の側板Ｂでモータを取
りつけている側の側板、４は前記側板Ａ２に設けられた
ノズル部分Ａ、５は前記側板Ｂ３に設けられたノズル部
分Ｂ、６は両吸込用多翼羽根車、７は吹出し口、８は前
記両吸込用多翼羽根車６を駆動するためのモータ、９は
前記モータ８の軸で前記羽根車６が固定されている。又
第２図は第１図のＡ−Ａ線における断面図を示し、第３
図は第１図の斜視図を示す。第４図は風量特性の結果、
第５図は６０ｋｌ（ｔ、２２０■での騒音特性の結果を
示す。第１図〜第３図中、Ｌは側板３とモータ８の端面
との最少間隔、Ｄは羽根車の外径、ｄｌ　は前記吹出し
ロアのモータ８と反対側近辺の吹出し巾、ｄ２は前記吹
出しロアのモータ８側近辺の吹出し巾を示している。With this configuration, when a double-suction type centrifugal blower is operated, the air sucked into the impeller through the respective nozzles provided on both sides of the casing is directed to the width of the outlet near the motor side, which is perpendicular to the motor axis. By setting it small in the direction, the resistance on the suction side is balanced, the air flow is stable, and furthermore, the vibration of the impeller due to the difference in resistance on the suction side is eliminated, and the increase in noise can be suppressed. 0 DESCRIPTION OF EMBODIMENTS The present invention will be described below with reference to FIGS. 1 to 5 showing one embodiment thereof. In FIG. Side plate A of casing 1 of double suction type centrifugal blower
3 is the side plate B of the casing 1 of the dual suction type centrifugal blower opposite to the side on which the motor is attached; 4 is the nozzle portion A provided on the side plate A2; 5 is a nozzle part B provided on the side plate B3, 6 is a multi-blade impeller for both suctions, 7 is an outlet, 8 is a motor for driving the multi-blade impeller 6 for both suctions, and 9 is the motor 8 The impeller 6 is fixed to the shaft. Also, FIG. 2 shows a cross-sectional view taken along line A-A in FIG.
The figure shows a perspective view of FIG. Figure 4 shows the results of air volume characteristics.
Figure 5 shows the results of noise characteristics at 60kl (t, 220mm). In Figures 1 to 3, L is the minimum distance between the side plate 3 and the end face of the motor 8, D is the outer diameter of the impeller, dl indicates the blowing width near the side opposite to the motor 8 of the blowing lower, and d2 indicates the blowing width near the motor 8 side of the blowing lower.

第１図〜第３図を用いて空気の流れについて説明する。Air flow will be explained using FIGS. 1 to 3.

モータ８の駆動により羽根車６が回転すると、空気はケ
ーシング１の側板Ａ２．Ｂ３に設けられたノズルＡ４．
Ｂ５を通って羽根車６内に５　＼− 吸い込まれケーシング内でエネルギーを与えられて吹出
しロアより吹出される。この場合、側板Ｂ３とモータ８
との間隔りが狭いと、空気の流動がモータ８によって阻
害されるため、ノズルＢ５を通過して羽根車６に吸い込
まれる空気の量は、ノズルＡ４を通過して羽根車６に吸
い込まれる空気の量に比較して少ない。この流動空気の
差が、羽根車６の不安定な回転の原因となり、更には、
圧力の差による軸方向への羽根車６の振動の原因ともな
るため、 Ｌ≦Ｄ の場合、吹出しロアのモータ８と反対側近辺の吹出し巾
ｄ１．吹出し口のモータ側近辺の吹出し巾ｄ２を ｄｌ〉ｄ２ のように設定し、羽根車６へ吸い込まれるまでの抵抗を
同じにして羽根車６の回転を安定させるという構造を用
いる０ この構造を用いた実験の結果が第４図および第６図であ
る。第４図は風量特性の結果であり、横６、− 軸は羽根車６０回転数（ｒ　ｐｍ　）、縦軸は風量ケβ
ｍ）である。寸だ、実線が上記実施例の場合で、破線は
従来例の場合である０この結果、前記実施例の方が風量
特性は多少良くなっていることがわかる０第６図は騒音
特性の結果で、上のグラフが従来例の場合、下のグラフ
が本実施例の場合であり、横軸は周波数（Ｂ７）、縦軸
は騒音レベル（ｄＢ）である。上のグラフで７００〜８
００Ｈｚ付近でレベルが極端に高くなっているが、下の
グラフではそれがほとんどわからなくなっている。この
７００〜８００）ｈ付近の騒音は、羽根車６の１枚の羽
根が風を切る時に出る特有の音で、羽根車６の不安定が
原因であり、前記構成を用いることによって羽根車６が
安定し、この特有の音が出なくなり、騒音が減少したと
言える。When the impeller 6 is rotated by the drive of the motor 8, air flows through the side plate A2 of the casing 1. Nozzle A4 provided in B3.
It passes through B5 and is sucked into the impeller 6, is given energy within the casing, and is blown out from the blowout lower. In this case, the side plate B3 and the motor 8
If the distance between the motor 8 and is small compared to the amount of This difference in flowing air causes unstable rotation of the impeller 6, and furthermore,
Since the difference in pressure causes vibration of the impeller 6 in the axial direction, when L≦D, the blowout width d1 near the side opposite to the motor 8 of the blowout lower. A structure is used in which the blowout width d2 near the motor side of the blowout port is set as dl>d2, and the rotation of the impeller 6 is stabilized by making the resistance until it is sucked into the impeller 6 the same.0 This structure is used. The results of the experiment were shown in Figures 4 and 6. Figure 4 shows the results of the air volume characteristics, where the horizontal axis is 60, the - axis is the impeller rotation speed (rpm), and the vertical axis is the air volume value β.
m). The solid line is for the above example, and the broken line is for the conventional example.0 As a result, it can be seen that the air volume characteristics are somewhat better in the above example.0 Figure 6 shows the results of the noise characteristics. The upper graph is for the conventional example, and the lower graph is for this embodiment, with the horizontal axis representing frequency (B7) and the vertical axis representing noise level (dB). 700-8 in the graph above
The level is extremely high near 00Hz, but this is hardly noticeable in the graph below. This noise around 700 to 800) h is a unique sound produced when one blade of the impeller 6 cuts the wind, and is caused by the instability of the impeller 6. It can be said that the noise level has stabilized, this characteristic sound no longer occurs, and the noise has decreased.

発明の効果 上記実施例からも明らかなように、本発明における両吸
込形遠心送風機の２つの空気吸込側の抵抗の大小によっ
て、吹出し口の巾をモータ側近辺とモータの反対側近辺
とで相違させ、安定した両吸込形遠心送風機を確保する
ことができる。Effects of the Invention As is clear from the above embodiments, depending on the magnitude of the resistance on the two air suction sides of the double suction type centrifugal blower of the present invention, the width of the outlet can be different between the vicinity of the motor side and the vicinity of the opposite side of the motor. This makes it possible to ensure a stable dual-suction type centrifugal blower.

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

第１図は本発明の一実施例である両吸込形遠心送風機の
正面図、第２図は前記第１図のＡ−Ａ線における側面断
面図、第３図は第１図の外観斜視図、第４図は同風量特
性を示す特性図、第５図Ａは従来の騒音特性図、第５図
Ｂは本発明の一実施例での騒音特性図である。 １・・・・・ケーシング、２・・・・・・ケーシングの
側板Ａ１３・・・・・・ケーシングの側板Ｂ、４・・・
・・・ノズルＡ１５・・・・・・ノズルＢ、６・・・・
・・両吸込用多翼羽根車、７・・・・・・吹出し口、８
・・・・・・モータ、９・・・・・・軸、ｄｌ、ｄ２・
・・・・・吹出し巾。 代理人の氏名　弁理士　中　尾　敏　男　ほか１名菓　
１　□□□ 第２図 第３図 ４図 乙Ｐｍ Ｓ図Fig. 1 is a front view of a double suction type centrifugal blower which is an embodiment of the present invention, Fig. 2 is a side sectional view taken along line A-A in Fig. 1, and Fig. 3 is an external perspective view of Fig. 1. , FIG. 4 is a characteristic diagram showing the same air volume characteristics, FIG. 5A is a conventional noise characteristic diagram, and FIG. 5B is a noise characteristic diagram in one embodiment of the present invention. 1...Casing, 2...Casing side plate A13...Casing side plate B, 4...
...Nozzle A15...Nozzle B, 6...
...Multi-blade impeller for both suctions, 7...Blowout port, 8
...Motor, 9...Axis, dl, d2.
...Blowout width. Name of agent: Patent attorney Toshio Nakao and one other name
1 □□□ Figure 2 Figure 3 Figure 4 Figure O Pm S Figure

Claims (1)

【特許請求の範囲】[Claims] 前記両吸込用多翼羽根車を駆動するためのモータの端面
と、ケーシングの側板の前記モータに相対する側の端面
との最少間隔が、前記両吸込用多翼羽根車の外径寸法よ
り小さい場合、前記ケーシングに設けられた空気吹出し
口のモータ側近辺の巾をモータの軸と直角な方向に小さ
く設定した遠心送風機。The minimum distance between the end face of the motor for driving the dual suction multiblade impeller and the end face of the side plate of the casing on the side facing the motor is smaller than the outer diameter dimension of the dual suction multiblade impeller. In the case of a centrifugal blower, the width of the air outlet provided in the casing near the motor side is set small in a direction perpendicular to the axis of the motor.