JPH0979199A - Motor-driven air blower - Google Patents
Motor-driven air blowerInfo
- Publication number
- JPH0979199A JPH0979199A JP7234999A JP23499995A JPH0979199A JP H0979199 A JPH0979199 A JP H0979199A JP 7234999 A JP7234999 A JP 7234999A JP 23499995 A JP23499995 A JP 23499995A JP H0979199 A JPH0979199 A JP H0979199A
- Authority
- JP
- Japan
- Prior art keywords
- blower
- electric motor
- frequency
- resonance
- silencer
- 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
Links
Abstract
Description
【０００１】[0001]
【発明の属する技術分野】本発明は、汎用的に集塵や冷
却等に用いられる電動送風機に関するものである。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an electric blower generally used for dust collection, cooling and the like.
【０００２】[0002]
【従来の技術】従来の電動送風機の構成を図２を用いて
説明する。2. Description of the Related Art The structure of a conventional electric blower will be described with reference to FIG.
【０００３】図２は従来の電動送風機で、全体断面図を
示す。図２の左側軸方向から吸い込まれた流体は羽根車
１２により昇圧され、ケーシング１３により吐出口１４
まで案内され、流体の流れ３で示すように右側軸方向に
吐き出されている。電動送風機は、送風器部１と電動機
部２を枠５により包み込みこむことにより電動機外周に
吐出流路４を形成し、作動流体により電動機部２を冷却
する構造となっている。当該吐出流路４内には、送風機
開口部１４からの直接音や流体の乱流音の吸音のため、
吐出側と吸込側の枠５の内側流路内に、多孔質または発
泡樹脂材料を巻き抵抗型消音器７が形成されている。FIG. 2 is a conventional electric blower and shows an overall sectional view. The fluid sucked in from the axial direction on the left side of FIG.
And is discharged in the right axial direction as shown by the flow 3 of the fluid. The electric blower has a structure in which the blower unit 1 and the electric motor unit 2 are wrapped in a frame 5 to form a discharge passage 4 on the outer periphery of the electric motor, and the electric motor unit 2 is cooled by a working fluid. In the discharge flow path 4, because of the direct sound from the blower opening 14 and the absorption of the turbulent sound of the fluid,
A resistance type silencer 7 is formed by winding a porous or foamed resin material in the inner flow paths of the frame 5 on the discharge side and the suction side.
【０００４】[0004]
【発明が解決しようとする課題】上記従来技術におい
て、抵抗型消音器７は多孔質または発泡樹脂材料を枠５
の内側流路内に貼り、流体と材料が接している構造を取
っている。多孔質または発泡樹脂材料表面の吸音率とし
ては図３に示すように、1000Hz以上の比較的高い周波数
領域で優れているが、反面、それ以下の比較的中低程度
の周波数の騒音の吸音特性は著しく劣っている。本発明
が適用される電動送風機から発生する騒音の周波数特性
は、回転数を基本周波数とした成分が主成分で、例えば
電動機の極数が２で、この電動機をインバータ装置によ
り２５０Ｈｚで駆動した場合、騒音の基本周波数は約２
５０Ｈｚで２倍の高調は成分が約５００Ｈｚとなり（誘
導電動機の場合すべりがあるのでインバータ出力周波数
とは多少異なる）、比較的中低周波数の機械的騒音が含
まれている。回転に起因して電動送風機から発生する騒
音は回転周波数及びその整数倍の周波数が卓越してお
り、抵抗型消音器７では吸音出来ずにその成分が残り、
騒音レベルを下げるのは難しくなっていた。更に、取り
付け部との振動絶縁が為されていない場合、取り付け部
が新たな加振源となり、回転周波数の振動が伝搬し比較
的中低周波数の騒音が発生していた。In the above-mentioned prior art, the resistance silencer 7 is made of a porous or foamed resin material for the frame 5.
It is attached to the inside of the inner channel and has a structure in which the fluid and the material are in contact with each other. As shown in Fig. 3, the sound absorption coefficient of the surface of the porous or foamed resin material is excellent in the comparatively high frequency range of 1000 Hz or higher, but on the other hand, it is the sound absorption characteristic of the noise of the comparatively middle and low frequencies below that. Is significantly inferior. The frequency characteristic of noise generated from an electric blower to which the present invention is applied is mainly composed of a component having a fundamental frequency of rotation speed, for example, when the number of poles of the electric motor is 2, and the electric motor is driven at 250 Hz by an inverter device. , The fundamental frequency of noise is about 2
The component of the double harmonic at 50 Hz is about 500 Hz (it is slightly different from the inverter output frequency due to slippage in the case of an induction motor), and relatively low and medium frequency mechanical noise is included. The noise generated from the electric blower due to the rotation is excellent in the rotation frequency and the frequency that is an integral multiple thereof, and the component cannot be absorbed by the resistance silencer 7, and the component remains.
It was difficult to reduce the noise level. Furthermore, when vibration isolation from the mounting portion is not performed, the mounting portion serves as a new vibration source, and vibrations at the rotational frequency propagate to generate noise at relatively low and medium frequencies.
【０００５】本発明は以上のような課題を解決するため
になされたもので、本発明の目的は、回転に起因する電
動送風機の騒音の主成分である回転周波数とその整数倍
の成分と、流れに起因する乱れの中低周波数成分の騒音
と、電動送風機表面からの放射音及び取り付け部からの
新たな騒音の静音化を行うことにある。The present invention has been made to solve the above problems, and an object of the present invention is to provide a rotation frequency which is a main component of noise of an electric blower caused by rotation and a component which is an integral multiple thereof. It is to reduce the noise of the low and middle frequency components caused by the flow, the noise emitted from the surface of the electric blower, and the new noise from the mounting portion.
【０００６】[0006]
【問題を解決するための手段】本発明では上記目的を達
成するために、以下のような技術的手段を採用した。 （１）内部に、羽根車を有する送風機部分と、この羽根
車を駆動する電動機部分により構成される電動送風機に
おいて、送風機部と電動機部を枠により包み込み、枠と
電動機部により構成される流路に共鳴型消音器を備える
ようにした。In order to achieve the above object, the present invention employs the following technical means. (1) In an electric blower composed of a blower part having an impeller inside and an electric motor part for driving the impeller, a fan part and an electric motor part are wrapped by a frame, and a flow path is formed by the frame and the electric motor part. It was equipped with a resonance silencer.
【０００７】（２）上記（１）に記載された電動送風機
において、複数の周波数が吸音できるように複数の共鳴
型消音器で構成した。(2) In the electric blower described in (1) above, a plurality of resonance type silencers are used so that a plurality of frequencies can be absorbed.
【０００８】（３）上記（１）に記載された電動送風機
において、当該共鳴型消音器と、抵抗型消音器を組み合
わせて構成した。(3) In the electric blower described in (1) above, the resonance type silencer and the resistance type silencer are combined.
【０００９】上記目的を達成するため用いた手段の作用
について説明する。The operation of the means used to achieve the above object will be described.
【００１０】送風機部分と電動機部分を枠により包み込
み、枠と電動機部外周により吐出流路を構成し、当該流
路内に共鳴型消音器形成することにより、送風機開口部
からの直接音と電動機部からの機械的、磁気的アンバラ
ンスに起因する騒音が吸収される。A blower part and an electric motor part are wrapped by a frame, and a discharge flow path is constituted by the frame and the outer periphery of the electric motor part, and a resonance type silencer is formed in the flow path, so that the direct sound from the blower opening part and the electric motor part are formed. The noise due to the mechanical and magnetic imbalance from is absorbed.
【００１１】共鳴型消音器は、任意の周波数の吸音特性
を予め規定することが出来、騒音の卓越周波数成分を特
定して効果的に吸音する事が出来る。共鳴型消音器の構
造としては、金属あるいは非金属の板に貫通孔をあけ、
板の背後に空気層をおいた吸音構造体となっており、こ
の孔の部分の空気と背後空気層とが一種のヘルムホルツ
共鳴器を構成している。この共鳴周波数が、共鳴型消音
器の減衰周波数となる。The resonance type silencer can predefine the sound absorption characteristic of an arbitrary frequency and can effectively absorb the sound by specifying the dominant frequency component of the noise. As the structure of the resonance silencer, a through hole is made in a metal or non-metal plate,
The sound absorbing structure has an air layer behind the plate, and the air in the hole and the back air layer form a kind of Helmholtz resonator. This resonance frequency becomes the attenuation frequency of the resonance silencer.
【００１２】共鳴型消音器の減衰周波数ｆｒに関して
は、下記の数１あるいは数２の関係式が一般に知られて
いる。Regarding the attenuation frequency fr of the resonance type silencer, the following relational expression of equation 1 or equation 2 is generally known.
【００１３】[0013]
【数１】 [Equation 1]
【００１４】[0014]
【数２】 [Equation 2]
【００１５】共鳴周波数ｆｒの規定は、上式に示される
ように、孔開き板の板厚ｔ、孔径ｄ、空洞の容積Ｖ、孔
の数ｎ、開口率ｐ、背後空気層の厚さＬにより設定され
る。The resonance frequency fr is defined as shown in the above equation: the plate thickness t of the perforated plate, the hole diameter d, the volume V of the cavity, the number n of holes, the aperture ratio p, and the thickness L of the rear air layer. Set by.
【００１６】本発明では、減衰周波数を電動送風機の騒
音の主成分である、回転周波数とその整数倍の周波数
と、流れに起因する乱流音の中低周波数成分の静音化を
図っている。さらに孔開き板構造体の共鳴周波数の吸音
特性は孔の配置により変えている。回転周波数など特定
周波数が卓越し変動が小さい場合には、孔を集中させる
と減衰周波数に対して吸音特性が先鋭化し減衰量は大き
くなる。回転数が負荷条件などにより変動する場合や、
流れに起因する中低周波数成分の乱流音を吸音したい場
合には、孔を等間隔ピッチにすると、減衰量は小さくな
るが吸音特性は減衰周波数を中心として比較的なだらか
な特性となり、ある幅の周波数範囲の減音には効果的と
なる。共鳴型消音器はこのように単一の周波数の減音に
優れているので、電動送風機のように特定の周波数の騒
音が卓越している電動送風機の静音化には、減音周波数
が異なる複数の共鳴型消音器を組み合わせることによ
り、効果的に静音化を図ることができ、本発明では枠内
側の吐出流路面に構成された複数の共鳴型消音器によ
り、回転周波数とその整数倍の周波数、および流れに起
因する乱れの中低周波数成分の静音化を図っている。In the present invention, the damping frequency is the main component of the noise of the electric blower, the rotation frequency is an integral multiple of the rotation frequency, and the low and middle frequency components of the turbulent sound caused by the flow are made quiet. Furthermore, the sound absorption characteristics of the resonant frequency of the perforated plate structure are changed depending on the arrangement of the holes. When the specific frequency such as the rotation frequency has a predominantly small variation, if the holes are concentrated, the sound absorption characteristic becomes sharper with respect to the attenuation frequency and the attenuation amount increases. When the rotation speed changes due to load conditions,
If you want to absorb the turbulent sound of mid-low frequency component caused by the flow, if you make the holes at regular intervals, the amount of attenuation will be smaller, but the sound absorption characteristics will be a comparatively gentle characteristic centered on the attenuation frequency, It is effective for sound reduction in the frequency range of. Since the resonance type silencer is excellent in reducing the noise of a single frequency in this way, it is necessary to reduce the noise of multiple frequencies with different noise reduction levels in order to reduce the noise of an electric blower in which noise of a specific frequency is dominant such as an electric blower. It is possible to effectively reduce the noise by combining the resonance type silencers of the present invention, and in the present invention, by the plurality of resonance type silencers configured on the discharge flow passage surface inside the frame, the rotation frequency and the frequency that is an integer multiple thereof. , And the low and middle frequency components of the turbulence caused by the flow are reduced.
【００１７】さらに、送風機部分と電動機部分を枠によ
り包み込み、枠と電動機部の振動絶縁を行うことで、枠
表面からの放射音及び、取り付け部からの新たな騒音の
発生を防止している。Further, the blower part and the electric motor part are wrapped by a frame, and the frame and the electric motor part are vibration-insulated to prevent radiation noise from the surface of the frame and generation of new noise from the mounting part.
【００１８】以上の作用により、電動送風機の騒音の主
成分である回転周波数とその整数倍の成分と、流れに起
因する乱れの中低周波数成分の騒音と、電動送風機表面
からの放射音及び取り付け部からの新たな騒音が低減さ
れる。With the above operation, the rotational frequency which is the main component of the noise of the electric blower and its integral multiple component, the noise of the middle and low frequency components of the turbulence caused by the flow, the radiated sound from the surface of the electric blower and the installation New noise from the department is reduced.
【００１９】[0019]
【発明の実施の形態】以下、発明の位置実施例を図１、
及び図４〜図８に基づいて説明する。BEST MODE FOR CARRYING OUT THE INVENTION A position embodiment of the invention is shown in FIG.
And it demonstrates based on FIGS.
【００２０】図１は、第一の実施例の断面図であり、図
４は共鳴型消音器６の詳細断面図、図５は図４を上方か
ら見た視図である。図６は枠５と送風機部１と電動機部
２の取り付け部分の詳細断面図である。図１より、送風
機部１と電動機部２はこれらの最外径よりも大きい枠５
に包み込まれ、電動機部ハウジング２２と枠５により吐
出流路４が形成されている。枠５内側の吐出流路４内に
は、孔開き板６１及び、背後の空気層６２により共鳴型
消音器６が形成されており、減衰周波数を変えた複数の
共鳴型消音器６は軸方向後方に構成されている。共鳴型
消音器６の孔開き板６３の孔６４の配置は、流れの乱れ
の中低周波数成分の吸音と負荷変動による回転数変動を
考慮し、等間隔ピッチに配置され、減衰周波数の回りに
なだらかな傾斜を持つ吸音特性になっている。羽根車１
２により昇圧され、ケーシング１３により吐出口１４に
案内された流れ３が、吐出流路４を通り、軸右方向に吐
き出される。吐出口１４からの直接音や電動機部２から
の音は吐出流路４内に設けられた共鳴型消音器６を複数
の減衰周波数の共鳴型消音器６−１、６−２、６−３に
分けてそれぞれ効果的に吸音される。共鳴型消音器６の
一つの詳細構造を図４〜５の詳細図を用いて説明する。
図４より枠５の内側に背後空気層６２があり、それを挟
むように孔開き板６３がある。孔開き板６３の板厚ｔ、
孔６４の直径ｄ、孔６４の開孔率ｐ、背後空気層６２の
厚さＬ等の各々の寸法は、減衰周波数により決定され、
数１、数２に基づいて求めることができる。２極の電動
機をインバータ装置により２５０Ｈｚで駆動した実施例
の具体的数値例をあげると、共鳴型消音器６−３は、減
衰周波数ｆｒ＝２５０Ｈｚ，空洞の容積Ｖ＝０．０００
９６立方ｍｍ、背後空気層の厚さＬ＝０．０８７ｍｍ、
Ｃ０＝０．０２、孔の長さｔ＝５ｍｍ、孔の直径ｄ＝４
ｍｍ、開孔率０．０８％、孔の数ｎ＝１３となり、共鳴
型消音器６−１は、減衰周波数ｆｒ＝５００Ｈｚ，空洞
の容積Ｖ＝０．０００９６立方ｍｍ、背後空気層の厚さ
Ｌ＝０．０８７ｍｍ、Ｃ０＝０．０８、孔の長さｔ＝５
ｍｍ、孔の直径ｄ＝１０ｍｍ、開孔率０．５％、孔の数
ｎ＝１３となる。なお、流れに起因する乱れの中低周波
数成分の騒音と、電動送風機表面からの放射音及び取り
付け部からの新たな騒音を低減する為の共鳴型消音器６
−２は、これらに起因する騒音の大きい周波数帯を実験
などのより求め、この付近に減衰周波数ｆｒを設定す
る。このように減衰周波数ｆｒは、電動送風機の騒音の
主成分である回転周波数とその整数倍の周波数と、流れ
３の乱れの中低周波数成分を取り静音化を図っている。FIG. 1 is a sectional view of the first embodiment, FIG. 4 is a detailed sectional view of the resonance silencer 6, and FIG. 5 is a view of FIG. 4 seen from above. FIG. 6 is a detailed cross-sectional view of the mounting portion of the frame 5, the blower unit 1, and the electric motor unit 2. As shown in FIG. 1, the blower unit 1 and the electric motor unit 2 have a frame 5 larger than their outermost diameters.
The discharge passage 4 is formed by the electric motor housing 22 and the frame 5. A resonance type silencer 6 is formed in the discharge flow path 4 inside the frame 5 by a perforated plate 61 and a back air layer 62, and the resonance type silencers 6 having different attenuation frequencies are arranged in the axial direction. It is configured in the rear. The holes 64 of the perforated plate 63 of the resonance silencer 6 are arranged at equal pitches in consideration of sound absorption of low and middle frequency components of flow turbulence and rotation speed fluctuation due to load fluctuation, and are arranged around the attenuation frequency. It has sound absorption characteristics with a gentle slope. Impeller 1
The flow 3 pressurized by 2 and guided to the discharge port 14 by the casing 13 passes through the discharge flow path 4 and is discharged in the axial right direction. For the direct sound from the discharge port 14 and the sound from the electric motor section 2, the resonance type silencer 6 provided in the discharge flow path 4 is set to the resonance type silencers 6-1, 6-2, 6-3 having a plurality of attenuation frequencies. The sound is effectively absorbed by dividing into. One detailed structure of the resonance silencer 6 will be described with reference to the detailed views of FIGS.
As shown in FIG. 4, there is a back air layer 62 inside the frame 5, and there is a perforated plate 63 so as to sandwich it. The thickness t of the perforated plate 63,
The dimensions of the diameter d of the hole 64, the opening ratio p of the hole 64, the thickness L of the back air layer 62, etc. are determined by the damping frequency,
It can be calculated based on Equations 1 and 2. To give a specific numerical example of an embodiment in which a two-pole motor is driven by an inverter device at 250 Hz, the resonance silencer 6-3 has a damping frequency fr = 250 Hz and a cavity volume V = 0.000.
96 cubic mm, back air layer thickness L = 0.087 mm,
C0 = 0.02, hole length t = 5 mm, hole diameter d = 4
mm, open area ratio 0.08%, number of holes n = 13, resonance type silencer 6-1 has a damping frequency fr = 500 Hz, cavity volume V = 0.0096 cubic mm, thickness of back air layer L = 0.087 mm, C0 = 0.08, hole length t = 5
mm, hole diameter d = 10 mm, open area ratio 0.5%, and number of holes n = 13. It should be noted that the resonance-type silencer 6 for reducing the noise in the low and middle frequency components caused by the flow, the radiated sound from the surface of the electric blower, and the new noise from the mounting portion.
In the case of -2, a frequency band where noise due to these is large is found by experiments and the attenuation frequency fr is set in the vicinity thereof. In this way, the damping frequency fr takes the rotational frequency that is the main component of the noise of the electric blower, the frequency that is an integral multiple thereof, and the low and middle frequency components of the turbulence of the flow 3 to reduce noise.
【００２１】図５に孔６４の配置を示す。孔６４は、減
衰周波数に対して領域をもって吸音するように、等間隔
ピッチで配置されている。FIG. 5 shows the arrangement of the holes 64. The holes 64 are arranged at equal pitches so as to absorb sound in a region with respect to the attenuation frequency.
【００２２】送風機部１と電動機部２を枠５に包み込む
ことにより、開口部からの直接音と、電動機部２からの
騒音の静音化を消音器により図っているが、更に、送風
機部１、電動機部２と枠５の取り付けの振動絶縁を行
い、枠表面からの放射音と取り付け部からの新たな騒音
の発生を防止している。図６の枠５と電動機部２との取
り付け部分の詳細断面図より、本実施例では、枠５を取
り付け部分５１を別ピースとし、取り付け部分と電動機
部２の間に絶縁用のゴム５２をいれ、取り付け部分と固
定用のネジ５３が絶縁用ゴム５２を介して接するように
なっている。By enclosing the blower unit 1 and the electric motor unit 2 in the frame 5, a silencer is used to suppress the direct sound from the opening and the noise from the electric motor unit 2 by the silencer. Vibration insulation of the attachment of the motor unit 2 and the frame 5 is performed to prevent radiation noise from the frame surface and generation of new noise from the attachment unit. From the detailed cross-sectional view of the mounting portion between the frame 5 and the electric motor portion 2 in FIG. 6, in the present embodiment, the frame 5 is a separate piece and the insulating rubber 52 is provided between the mounting portion and the electric motor portion 2. The mounting portion and the fixing screw 53 are in contact with each other via the insulating rubber 52.
【００２３】図７は、上記第一の実施例に対し、共鳴型
消音器６を構成する孔開き板構造体６３の孔６４を集中
させ吸音特性を変更した場合の、第二の実施例の共鳴型
消音器６の詳細断面図で、図８は上方から見た場合の視
図である。回転周波数など特定周波数が卓越し変動が小
さい場合、共鳴型消音器６の孔６４を集中させることに
より、減衰周波数に対して吸音特性を先鋭化させ減衰量
を大きくしている。FIG. 7 shows a second embodiment in which the sound absorbing characteristics are changed by concentrating the holes 64 of the perforated plate structure 63 constituting the resonance type silencer 6 with respect to the first embodiment. FIG. 8 is a detailed cross-sectional view of the resonance silencer 6, and FIG. 8 is a perspective view when viewed from above. When the specific frequency such as the rotation frequency has a small variation, the holes 64 of the resonance silencer 6 are concentrated to sharpen the sound absorption characteristic with respect to the attenuation frequency and increase the attenuation amount.
【００２４】図９は、上記第一の実施例に対し、減衰周
波数が異なる共鳴型消音器６を周方向に分割して各々配
した場合の、第三の実施例であり、共鳴型消音器６を孔
６４の中心を含んで軸に垂直に断面した図である。騒音
は、吐出口１４や電動機部２から放射されるので、円周
方向に配置しても同様の効果が得られる。本実施例によ
り、共鳴器部の軸方向寸法を減衰波長に比べて長くとれ
る場合は、閉管の共鳴が加わって、第２次第３次の共鳴
周波数が現れるので、減衰周波数を回転周波数としてい
るので、回転周波数の第２、第３次成分の減衰が図れ
る。本実施例についても、共鳴型消音器６の孔６４の配
置を騒音の周波数特性に対して変更できる。FIG. 9 shows a third embodiment in which the resonance type silencers 6 having different attenuation frequencies are divided in the circumferential direction and are arranged in comparison with the first embodiment. FIG. 6 is a cross-sectional view of 6 including the center of a hole 64 and perpendicular to the axis. Since noise is radiated from the discharge port 14 and the electric motor unit 2, the same effect can be obtained even if the noise is arranged in the circumferential direction. According to the present embodiment, when the axial dimension of the resonator portion can be set longer than the attenuation wavelength, the resonance of the closed tube is added and the third-order resonance frequency appears gradually. Therefore, the attenuation frequency is the rotation frequency. The attenuation of the second and third order components of the rotation frequency can be achieved. Also in this embodiment, the arrangement of the holes 64 of the resonance silencer 6 can be changed with respect to the frequency characteristic of noise.
【００２５】図１０は、上記第一の実施例に対し抵抗型
消音器７を併用した場合で、共鳴型消音器６の軸方向後
方部に抵抗型消音器７が形成されている第四の実施例の
断面図である。吐出口直後に第一の実施例に示した孔開
き板構造体６１により共鳴型消音器６が形成され、その
軸方向後方に枠５の内側に多孔質または発泡樹脂材料を
貼り付けることにより抵抗型消音器７を形成し、広範囲
の周波数の静音化が図っている。本実施例についても、
共鳴型消音器６の孔６４の配置を騒音の周波数特性に対
して変更し広範囲の騒音周波数に対応できる。FIG. 10 shows a case in which the resistance silencer 7 is used in combination with the first embodiment, and the resistance silencer 7 is formed in the axial rear portion of the resonance silencer 6 in the fourth embodiment. It is sectional drawing of an Example. Immediately after the discharge port, the resonant silencer 6 is formed by the perforated plate structure 61 shown in the first embodiment, and a porous or foamed resin material is attached to the inside of the frame 5 axially rearward thereof to reduce resistance. The muffler 7 is formed to reduce the noise over a wide range of frequencies. Also for this embodiment,
The arrangement of the holes 64 of the resonance silencer 6 can be changed with respect to the frequency characteristics of noise to cope with a wide range of noise frequencies.
【００２６】図１１は、上記第四の実施例に対し抵抗型
消音器７と共鳴型消音器６を周方向に分割して各々配し
た場合の第五の実施例であり、共鳴型消音器６を孔６４
の中心を含んで軸に垂直に断面した図である。本実施例
についても、共鳴型消音器６の孔６４の配置を騒音の周
波数特性に対して変更し広範囲の騒音周波数に対応でき
る。FIG. 11 is a fifth embodiment in which the resistance silencer 7 and the resonance silencer 6 are divided in the circumferential direction and are arranged in comparison with the fourth embodiment, and the resonance silencer is shown. 6 through 64
It is the figure which included the center of and crossed perpendicularly to an axis. Also in this embodiment, the arrangement of the holes 64 of the resonance silencer 6 can be changed with respect to the frequency characteristics of noise to cope with a wide range of noise frequencies.
【００２７】図１２は、共鳴型消音器６の孔６４の配置
を、インバータ装置で２５０Ｈｚ駆動したとき回転に起
因する騒音基本波周波数２５０Ｈｚに合わせた共鳴型消
音器６−３と２倍の周波数５００Ｈｚにあわせて集中さ
せた共鳴型消音器６−１と、流れに起因する乱れの中低
周波数成分の騒音や電動送風機表面からの放射音、取り
付け部からの新たな騒音に対応したなだらかな吸音特性
の等間隔の共鳴型消音器６−２とを混在させたものであ
る。このように構成するとそれぞれの騒音特性に合わせ
てを効果的に吸収することができる。FIG. 12 shows a resonance type silencer 6-3 in which the holes 64 of the resonance type silencer 6 are adjusted to a noise fundamental wave frequency 250 Hz caused by rotation when driven by an inverter device at 250 Hz and a frequency twice as high as that of the resonance silencer 6-3. Resonance type silencer 6-1 concentrated to 500Hz and gentle absorption of noise of low and middle frequency components of turbulence caused by flow, radiated sound from electric blower surface, and new noise from mounting part A resonance type silencer 6-2 having a characteristic equal interval is mixed. With this configuration, it is possible to effectively absorb the noise according to each noise characteristic.
【００２８】[0028]
【発明の効果】本発明により、電動送風機の騒音の主成
分である回転周波数とその整数倍の成分と、流れに起因
する乱れの中低周波数成分の騒音と、電動送風機表面か
らの放射音及び取り付け部からの新たな騒音の静音化を
行うことができる。According to the present invention, the rotational frequency which is the main component of the noise of the electric blower and its integral multiple component, the noise of the low and middle frequency components of the turbulence caused by the flow, the radiated sound from the surface of the electric blower, and New noise from the mounting part can be reduced.
【図１】本発明による第一の実施例の断面図である。FIG. 1 is a sectional view of a first embodiment according to the present invention.
【図２】従来の電動送風機の構造の例を示し、抵抗型消
音器を内蔵している場合の例の断面図である。FIG. 2 is a cross-sectional view of an example of a structure of a conventional electric blower, in which a resistance silencer is incorporated.
【図３】抵抗型消音器の周波数に対する吸音特性であ
る。FIG. 3 is a sound absorption characteristic with respect to the frequency of the resistance silencer.
【図４】本発明による第一の実施例で使われている共鳴
型消音器の詳細断面図である。FIG. 4 is a detailed cross-sectional view of a resonance silencer used in the first embodiment of the present invention.
【図５】図４を上方から見た場合の視図である。FIG. 5 is a perspective view of FIG. 4 when viewed from above.
【図６】本発明による第二の実施例で使われている枠と
送風機部と電動機部の取り付け部分の詳細断面図であ
る。FIG. 6 is a detailed cross-sectional view of a frame, a blower section, and an attachment section of an electric motor section used in a second embodiment of the present invention.
【図７】本発明による第二の実施例で使われている共鳴
型消音器の詳細断面図である。FIG. 7 is a detailed sectional view of a resonance silencer used in a second embodiment of the present invention.
【図８】図７を上方から見た場合の視図である。FIG. 8 is a perspective view when FIG. 7 is viewed from above.
【図９】減衰周波数が異なる共鳴型消音器を周方向に分
割して各々配した本発明による第三の実施例図である。FIG. 9 is a diagram of a third embodiment according to the present invention in which resonance type silencers having different attenuation frequencies are divided in the circumferential direction and arranged.
【図１０】共鳴型消音器と抵抗型消音器を併用した本発
明による第四の実施例図である。FIG. 10 is a diagram of a fourth embodiment according to the present invention in which a resonance type silencer and a resistance type silencer are used together.
【図１１】抵抗型消音器と共鳴型消音器を周方向に分割
して各々配した本発明による第五の実施例図である。FIG. 11 is a diagram of a fifth embodiment according to the present invention in which a resistance silencer and a resonance silencer are divided and arranged in the circumferential direction.
【図１２】共鳴型消音器の吸音特性を複数種類組み合わ
せた本発明による第六の実施例図である。FIG. 12 is a diagram of a sixth embodiment according to the present invention in which a plurality of types of sound absorbing characteristics of the resonance silencer are combined.
１…送風器部、２…電動機部、３…流体の流れ、５…
枠、６…共鳴型消音器、７…抵抗型消音器、１２…羽根
車、１３…ケーシング、１４…吐出口、２２…電動機ハ
ウジング、５１…取り付け部分、５２…絶縁用ゴム、５
３…固定用ネジ、６１…孔開き板、６２…背後の空気
層、６３…孔開き板、６４…孔。1 ... Blower part, 2 ... Electric motor part, 3 ... Fluid flow, 5 ...
Frame, 6 ... Resonance silencer, 7 ... Resistance silencer, 12 ... Impeller, 13 ... Casing, 14 ... Discharge port, 22 ... Motor housing, 51 ... Mounting portion, 52 ... Insulating rubber, 5
3 ... Fixing screw, 61 ... Perforated plate, 62 ... Rear air layer, 63 ... Perforated plate, 64 ... Hole.
Claims (5)
を備えた電動送風機において、前記送風機と前記電動機
を一体的に覆う枠と、前記枠と前記電動機の外周との間
に形成され前記送風機により送風される流体を通過させ
る流路と、前記流路に共鳴型消音器を備えたことを特徴
とする電動送風機。1. An electric blower comprising a blower and an electric motor for rotationally driving the blower, the blower being formed between a frame integrally covering the blower and the electric motor, and an outer periphery of the frame and the electric motor. An electric blower, comprising: a flow passage through which a fluid blown by the air passage is passed; and a resonance silencer provided in the flow passage.
きるように減衰周波数が異なる複数の共鳴型消音器で構
成されていることを特徴とする請求項１記載の電動送風
機。2. The electric blower according to claim 1, wherein the resonance-type silencer comprises a plurality of resonance-type silencers having different attenuation frequencies so that a plurality of frequencies can be absorbed.
を備えた電動送風機において、前記送風機と前記電動機
を一体的に覆う枠と、前記枠と前記電動機の外周との間
に形成され前記送風機により送風される流体を通過させ
る流路と、前記流路に共鳴型消音器と抵抗型消音器を備
えたことを特徴とする電動送風機。3. An electric blower comprising a blower and an electric motor for rotationally driving the blower, the blower being formed between a frame integrally covering the blower and the electric motor, and an outer periphery of the frame and the electric motor. An electric blower, comprising: a flow passage through which a fluid blown by the air passage is passed; and a resonance silencer and a resistance silencer provided in the flow passage.
因する騒音の基本周波数にほぼ一致した減衰周波数と、
該基本周波数の整数倍にほぼ一致した減衰周波数を有す
る複数の共鳴型消音器を組み合わせて構成されたことを
特徴とする請求項１乃至請求項３記載の電動送風機。4. The resonance type silencer has an attenuation frequency which substantially matches a fundamental frequency of noise caused by rotation of the electric motor,
4. The electric blower according to claim 1, wherein the electric blower is configured by combining a plurality of resonance silencers having an attenuation frequency that is substantially equal to an integral multiple of the fundamental frequency.
を備えた電動送風機において、前記送風機と前記電動機
を一体的に覆う枠と、前記枠と前記電動機の外周との間
に形成され前記送風機により送風される流体を通過させ
る流路と、前記流路に共鳴型消音器と、前記電動機を駆
動するインバータ装置とを備え、前記共鳴型消音器はそ
の減衰周波数をほぼ前記インバータの出力周波数とその
整数倍の周波数に設定した共鳴型消音器を複数組み合わ
せて構成されていることを特徴とする電動送風機。5. An electric blower comprising a blower and an electric motor for rotationally driving the blower, wherein the blower is formed between a frame integrally covering the blower and the electric motor, and an outer periphery of the frame and the electric motor. A flow path for passing a fluid blown by, a resonance silencer in the flow path, and an inverter device for driving the electric motor, and the resonance silencer has an attenuation frequency substantially equal to the output frequency of the inverter. An electric blower, which is configured by combining a plurality of resonance-type silencers set to a frequency that is an integral multiple thereof.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP7234999A JPH0979199A (en) | 1995-09-13 | 1995-09-13 | Motor-driven air blower |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP7234999A JPH0979199A (en) | 1995-09-13 | 1995-09-13 | Motor-driven air blower |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH0979199A true JPH0979199A (en) | 1997-03-25 |
Family
ID=16979572
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP7234999A Pending JPH0979199A (en) | 1995-09-13 | 1995-09-13 | Motor-driven air blower |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH0979199A (en) |
Cited By (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2000013909A (en) * | 1998-06-17 | 2000-01-14 | Nissan Diesel Motor Co Ltd | Hybrid drive system |
| JP2008106645A (en) * | 2006-10-24 | 2008-05-08 | Matsushita Electric Ind Co Ltd | Electric blower and vacuum cleaner using the same |
| JP2008138687A (en) * | 2008-01-28 | 2008-06-19 | Mitsui Eng & Shipbuild Co Ltd | Method for mounting device for muffling blower exhaust noise |
| JP2012137095A (en) * | 2005-10-28 | 2012-07-19 | Resmed Ltd | Single-stage blower or multi-stage blower, and nested volute chamber and/or impeller for the volute chamber |
| JP2013113190A (en) * | 2011-11-28 | 2013-06-10 | Fulta Electric Machinery Co Ltd | Small blower device of double-cylinder structure |
| JP2016142426A (en) * | 2015-01-30 | 2016-08-08 | 株式会社日立産機システム | Ventilator, manufacturing method thereof, and support material for ventilator |
| JP2017195730A (en) * | 2016-04-22 | 2017-10-26 | ミネベアミツミ株式会社 | motor |
| JP2020105992A (en) * | 2018-12-28 | 2020-07-09 | 三菱重工業株式会社 | Centrifugal compressor |
| JP2021134751A (en) * | 2020-02-28 | 2021-09-13 | 公立大学法人 富山県立大学 | Fan unit and blower using the same |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2000013909A (en) * | 1998-06-17 | 2000-01-14 | Nissan Diesel Motor Co Ltd | Hybrid drive system |
| US9512729B2 (en) | 2005-10-28 | 2016-12-06 | Resmed Motor Technologies Inc. | Single or multiple stage blower and nested volute(s) and/or impeller(s) therefor |
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| JP2008138687A (en) * | 2008-01-28 | 2008-06-19 | Mitsui Eng & Shipbuild Co Ltd | Method for mounting device for muffling blower exhaust noise |
| JP2013113190A (en) * | 2011-11-28 | 2013-06-10 | Fulta Electric Machinery Co Ltd | Small blower device of double-cylinder structure |
| JP2016142426A (en) * | 2015-01-30 | 2016-08-08 | 株式会社日立産機システム | Ventilator, manufacturing method thereof, and support material for ventilator |
| JP2017195730A (en) * | 2016-04-22 | 2017-10-26 | ミネベアミツミ株式会社 | motor |
| JP2020105992A (en) * | 2018-12-28 | 2020-07-09 | 三菱重工業株式会社 | Centrifugal compressor |
| JP2021134751A (en) * | 2020-02-28 | 2021-09-13 | 公立大学法人 富山県立大学 | Fan unit and blower using the same |
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Free format text: JAPANESE INTERMEDIATE CODE: A02 Effective date: 20061226 |