JPH10102621A - Resonance sound absorbing mechanism - Google Patents
Resonance sound absorbing mechanismInfo
- Publication number
- JPH10102621A JPH10102621A JP8274188A JP27418896A JPH10102621A JP H10102621 A JPH10102621 A JP H10102621A JP 8274188 A JP8274188 A JP 8274188A JP 27418896 A JP27418896 A JP 27418896A JP H10102621 A JPH10102621 A JP H10102621A
- Authority
- JP
- Japan
- Prior art keywords
- sound absorbing
- resonator
- standing wave
- frequency
- resonance
- 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
Landscapes
- Building Environments (AREA)
- Soundproofing, Sound Blocking, And Sound Damping (AREA)
Abstract
Description
【０００１】[0001]
【発明の属する技術分野】この発明は、ＲＣ構造のマン
ション等の集合住宅、体育館、事務所ビル、学校の教室
等において、床衝撃音等の低減・吸収することができる
共鳴吸音機構に関するものである。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a resonance sound absorbing mechanism capable of reducing and absorbing floor impact noise in apartment buildings such as RC-structure apartments, gymnasiums, office buildings, school classrooms, and the like. is there.
【０００２】[0002]
【従来の技術】従来の吸音機構としては、床や天井等に
吸音材などを配設し、騒音の発生それ自体を抑制しよう
としていた。2. Description of the Related Art As a conventional sound absorbing mechanism, a sound absorbing material or the like is provided on a floor, a ceiling, or the like to suppress the generation of noise itself.
【０００３】また、これとは別に、ある特定周波数音の
低減（吸音）のために、レゾネータが開発され使用され
ている。このレゾネータを形成する場合には、あらかじ
め低減（吸音）対象周波数を特定し、この低減（吸音）
対象周波数に合わせて各種寸法などを予め理論的に計算
で求めたのち、具体的に形成される。[0003] Separately, a resonator has been developed and used for reducing (absorbing) sound of a specific frequency. When forming this resonator, the frequency to be reduced (sound absorption) is specified in advance, and this reduction (sound absorption) is specified.
After various dimensions and the like are theoretically calculated in advance in accordance with the target frequency, they are specifically formed.
【０００４】また、他からの音や振動で誘起されて発生
する固有の低周波数帯域の騒音、即ち定在波を低減（吸
音）する場合には、設置する部屋の広さ等に応じて生じ
る定在波の固有波長（λ）を計算することができるか
ら、その波長（λ）に合わせた最適なレゾネータが形成
できる。[0004] Further, in the case of reducing (absorbing) the noise in a specific low frequency band, that is, a standing wave, which is generated by being induced by sound or vibration from other sources, the noise is generated according to the size of the room in which the apparatus is installed. Since the characteristic wavelength (λ) of the standing wave can be calculated, an optimum resonator suitable for the wavelength (λ) can be formed.
【０００５】[0005]
【発明が解決しようとする課題】しかしながら、次のよ
うな問題を有している。 室内定在波の低減を図ろうとした場合、既に設置する
部屋が存在し、低減対象の定在波周波数が精度よく把握
されていればよいが、設置対象の部屋が未だ設計段階
で、図面上から定在波周波数を予測し、レゾネータを設
計した場合には、設置現場の状況（柱、梁、ドア等の入
り方）により、予測した周波数がずれてしまい、レゾネ
ータの効果がでない場合がある。However, there are the following problems. When trying to reduce indoor standing waves, it is only necessary that the room to be installed already exists and the standing wave frequency to be reduced be accurately grasped. When the standing wave frequency is predicted from the above and the resonator is designed, the predicted frequency is shifted depending on the situation of the installation site (how to enter columns, beams, doors, etc.), and the effect of the resonator may not be effective. .
【０００６】通常、部屋は、初期には空の状態だが、
人が住むようになると、家具などがおかれて、室内空間
の状態が変化し、定在波の周波数がずれた場合、レゾネ
ータの効果が失われてしまう場合がある。Normally, the room is initially empty,
When a person starts to live, furniture or the like is placed, the state of the indoor space changes, and when the frequency of the standing wave is shifted, the effect of the resonator may be lost.
【０００７】騒音源の変化（例えば、騒音源となって
いる機械、設備等が交換された場合など），設置環境の
変化（例えば、室内の棚、家具等の設置環境の変化な
ど）等による低減対象騒音の周波数がずれた場合、レゾ
ネータの効果失われてしまう場合がある。即ちこれは、
従来のレゾネータでは、一度設計（設定）された共振周
波数は固定されているため、変更することが困難であ
る。Changes in the noise source (for example, when a machine or equipment serving as the noise source is replaced), changes in the installation environment (for example, changes in the installation environment of indoor shelves, furniture, etc.), etc. If the frequency of the noise to be reduced is shifted, the effect of the resonator may be lost. That is,
In a conventional resonator, since the resonance frequency once designed (set) is fixed, it is difficult to change the resonance frequency.
【０００８】レゾネータは、首部の空気質量と空洞内
空気の共振現象を利用しているため、吸音効果の生じる
周波数帯域が非常に狭く、そのため例えば騒音源となっ
ている回転機械等の回転変動により生じる騒音周波数の
変動が大きいと、レゾネータの効果は大きく減少する。[0008] Since the resonator uses the resonance phenomenon of the mass of air in the neck and the air in the cavity, the frequency band in which the sound absorbing effect occurs is very narrow. If the fluctuation of the noise frequency that occurs is large, the effect of the resonator is greatly reduced.
【０００９】レゾネータの共鳴周波数は、理論式によ
り求められるが、この式は、理想的条件（形状、寸法、
材質など）の場合の式であり、実際に制作すると、寸法
誤差などのため、または、単純な形状でない場合に、共
鳴周波数が理論値からずれる場合がある。[0009] The resonance frequency of the resonator is obtained by a theoretical equation, which is based on ideal conditions (shape, dimensions,
Material)), and when actually produced, the resonance frequency may deviate from the theoretical value due to dimensional errors and the like or when the shape is not a simple shape.
【００１０】そこで、この発明は、上記した事情に鑑
み、個々の室内の状態に合わせて微妙に変化する定在波
の周波数に応じてきめ細かく低減（吸音）対象周波数を
変更・調整することができる共鳴吸音機構を提供するこ
とを目的とするものである。[0010] In view of the above circumstances, the present invention can finely change and adjust the frequency to be reduced (sound-absorbed) in accordance with the frequency of a standing wave that slightly changes according to the state of each room. It is an object of the present invention to provide a resonance sound absorbing mechanism.
【００１１】[0011]
【課題を解決するための手段】即ち、この請求項１に記
載の発明は、中空形状の空洞部分を有する本体部と、こ
の本体部に連通・連結され外部に向けて開口する通気路
を設けた首部とを備え、前記首部の通気路に存在する空
気の質量と前記空洞部分の空気のばね成分による共鳴現
象を利用し、設置する室内で発生する定在波を低減・吸
収する共鳴吸音機構であって、前記空洞部分の体積、首
部の通気路の長さ、首部の開口部断面積のうち、少なく
とも一つを変更可能とする可変構造を有するものであ
る。According to the first aspect of the present invention, there is provided a main body having a hollow hollow portion, and an air passage communicating with and connected to the main body and opening to the outside. And a resonance sound absorbing mechanism that reduces and absorbs a standing wave generated in an installation room by using a resonance phenomenon caused by a mass of air existing in an air passage of the neck and a spring component of air in the hollow portion. And having a variable structure that can change at least one of the volume of the hollow portion, the length of the ventilation path of the neck, and the cross-sectional area of the opening of the neck.
【００１２】また、この請求項２に記載の発明は、首部
及び／又は空洞部分に減衰機能を有するものである。The invention according to claim 2 has a damping function in the neck and / or the hollow portion.
【００１３】[0013]
【発明の実施の形態】まず、この定在波についてこの出
願に係る発明者によって詳しく検討・解析をしてみたと
ころ、次のような知見が得られた。BEST MODE FOR CARRYING OUT THE INVENTION First, the standing wave was examined and analyzed in detail by the inventor of the present application, and the following findings were obtained.
【００１４】そもそもこの室内定在波とは、残響室では
発生せず、実際の部屋のような、密閉された空間で、壁
と壁（または、天井と床）がほぼ平行に向かい合ってい
るような場合に、必ず発生するものである。この定在波
は、例えば図１に示すように向かい合った壁と壁、また
は、天井の床との間で音が反射しあい発生するもので、
部屋の中央部では音圧が最低（空気の粒子速度は最
高）、部屋の端部では音圧が最高（空気の粒子速度は最
低）となる。このため、通常、定在波が発生する周波数
帯域では、部屋の中央部と端では重量源床衝撃音は１０
dB以上の差がでてしまい、部屋全体の音圧レベルも定在
波が発生しない周波数帯域に比べて高くなってしまうこ
とになる。In the first place, this indoor standing wave does not occur in a reverberation room, but in a closed space such as an actual room, where walls and walls (or ceiling and floor) face each other almost in parallel. This is always what happens. This standing wave is generated by sound reflection between the walls facing each other, for example, as shown in FIG. 1, or the floor of the ceiling,
At the center of the room, the sound pressure is the lowest (the air particle velocity is the highest), and at the end of the room, the sound pressure is the highest (the air particle velocity is the lowest). For this reason, in the frequency band where a standing wave is generated, the weight source floor impact noise is usually 10 at the center and at the end of the room.
A difference of more than dB will occur, and the sound pressure level of the whole room will be higher than the frequency band where no standing wave is generated.
【００１５】図１を見てわかるように、平行する面の距
離Ｌがちょうど１／２波長（１／２λ）となる周波数
（Ｆ）で定在波が発生することになる。ここで、平行面
の距離をＬ、音速をＣとすると、 Ｃ＝λ・Ｆ となるから、この定在波の周波数Ｆは、 Ｆ＝Ｃ／２Ｌ …（1) であり、これは１次元のみを考えた場合の１次モードの
振動を行う定在波である。As can be seen from FIG. 1, a standing wave is generated at a frequency (F) at which the distance L between the parallel surfaces is exactly 波長 wavelength (1 / 2λ). Here, assuming that the distance between the parallel planes is L and the sound velocity is C, C = λ · F. Therefore, the frequency F of this standing wave is F = C / 2L (1), which is one-dimensional. This is a standing wave that oscillates in the first-order mode when considering only the case.
【００１６】これを図２に示す３次元空間に拡張する
と、次に（2)式のようになる。 Ｆr ＝（Ｃ／２）・〔（ｎX ／ＬX ）2 ＋（ｎY ／ＬY ）2 ＋（ｎZ ／ＬZ ）2 〕1/2 …（2) 〔ここで、ｎX ，ｎY ，ｎZ は自然数であってモード次
数、即ちモードの節の数を示す〕 実際には、１次の定在波の音圧が最も大きくなり、重量
源床衝撃音レベルを悪化させる一つの要因となる。即
ち、ｎX ＝ｎY ＝ｎZ ＝１の場合となり、（3)で求ま
る。 When this is extended to the three-dimensional space shown in FIG. 2, the following equation (2) is obtained. F r = (C / 2) · [(n x / L x ) 2 + (n y / L y ) 2 + (n z / L z ) 2 ] 1/2 (2) where n x , N Y , n Z are natural numbers and indicate the mode order, that is, the number of nodes of the mode.] In practice, the sound pressure of the first-order standing wave becomes the largest, and the weight source floor impact sound level is deteriorated. This is one factor. That becomes a case of n X = n Y = n Z = 1, obtained in (3).
【００１７】一般的な部屋について概算し、定在波の発
生する周波数を求めると、表１のようになる。Table 1 shows an approximate calculation of a general room and the frequency at which a standing wave is generated.
【００１８】[0018]
【表１】 [Table 1]
【００１９】表１よりわかるように、定在波の発生する
周波数については、ほとんどがＪＩＳ評価の６３Hzオク
ターブバンド（４５Hz〜９０Hz）内にはいっていること
がわかる。さらにほとんどの場合は、重量源床衝撃音で
最もＬ値が高く、問題となる周波数バンドがこの６３Hz
であることから、室内定在波を低減しなければ、重量源
床衝撃音の評価レベル（Ｌ値）は改善できないことにな
る。As can be seen from Table 1, most of the frequencies at which standing waves are generated fall within the 63 Hz octave band (45 Hz to 90 Hz) evaluated by JIS. Furthermore, in most cases, the L value is the highest in the floor impact sound of the weight source, and the frequency band of interest is this 63 Hz.
Therefore, unless the indoor standing wave is reduced, the evaluation level (L value) of the weight source floor impact sound cannot be improved.
【００２０】そこで、以下にこの発明に係る実施例につ
いて説明する。図３は、この発明に係る共鳴吸音機構を
示すものであり、共鳴吸音周波数の変更機構４を備えた
レゾネータ１で構成されており、床衝撃により発生する
室内定在波を低減・吸収できるようになっている。Therefore, an embodiment according to the present invention will be described below. FIG. 3 shows a resonance sound absorbing mechanism according to the present invention, which is constituted by a resonator 1 having a resonance sound absorbing frequency changing mechanism 4 so as to reduce and absorb indoor standing waves generated by floor impact. It has become.
【００２１】この実施例のレゾネータ１は、適宜の合成
樹脂で形成した大略中空円筒体２（内径Ｄ、長さＬ）で
構成されており、一方側端面には開口孔を設け、そこに
外部に向けて開口した開口部５を有する首部（内径ｄ、
長さｔ）３が連通するように取付けてある。The resonator 1 of this embodiment is composed of a substantially hollow cylindrical body 2 (inner diameter D, length L) formed of a suitable synthetic resin. A neck (inner diameter d,
It is attached so that length t) 3 communicates.
【００２２】このレゾネータ１の変更機構４は、内周面
に沿ってスライド可能な仕切板４１で構成されており、
シャフト４１Ａによって仕切板４１のスライド動作を行
い首部３側の体積を変更させ、定在波との共鳴吸音周波
数をチューニングできるようになっている。The changing mechanism 4 of the resonator 1 is composed of a partition plate 41 slidable along the inner peripheral surface.
The sliding operation of the partition plate 41 is performed by the shaft 41A to change the volume on the neck 3 side, so that the resonance sound absorption frequency with the standing wave can be tuned.
【００２３】なお、この共鳴吸音周波数の変更機構であ
る仕切板４１のスライド方法としては、シャフト４１Ａ
を用いる他に、例えば図４に示すようなねじ孔２Ａに螺
合する雄ねじが切られたシャフト４１Ｂを使用してもよ
い。また、この他の共鳴吸音周波数の変更機構として
は、例えば図５に示す角筒体２１を仕切板４２で仕切る
ことにより、首部３１側の角筒体２１の体積Ｖを変更さ
せるものでもよい。As a method of sliding the partition plate 41 which is a mechanism for changing the resonance sound absorbing frequency, a shaft 41A is used.
In addition to the above, for example, a shaft 41B with a male thread cut into the screw hole 2A as shown in FIG. 4 may be used. As another mechanism for changing the resonance sound absorbing frequency, for example, the volume V of the rectangular cylindrical body 21 on the neck 31 side may be changed by partitioning the rectangular cylindrical body 21 shown in FIG.
【００２４】また、このレゾネータとして、この実施例
のような樹脂材料で形成するもの以外に、例えば各種の
金属、セラミックス、その他のものが適用可能であり、
要は空気等の通気性のないものであればよい。なお、弾
性率、密度等については特に制限はない。さらに、この
レゾネータの形状としては、円筒形、角筒形に限るもの
ではなく、例えば円錐形、円錐台形、球形等、種々の形
状（例えば図６など複雑な形状でもよい）が可能であ
る。また、この実施例では首部を１箇所設けてあるが、
特にこれに限るものではなく、２箇所以上でもよい。As the resonator, for example, various metals, ceramics, and others can be applied in addition to the resonator made of a resin material as in this embodiment.
In short, any material that does not have air permeability such as air may be used. There are no particular restrictions on the elastic modulus, density, and the like. Further, the shape of the resonator is not limited to a cylindrical shape or a rectangular tube shape, but may be various shapes (for example, a complicated shape as shown in FIG. 6) such as a conical shape, a truncated conical shape, and a spherical shape. In this embodiment, one neck is provided.
The invention is not particularly limited to this, and two or more locations may be used.
【００２５】次に、この実施例に係るレゾネータの原理
について説明する。この実施例に係るレゾネータは、変
更機構を用いて共鳴吸音周波数を正確に（微）調整する
ことにより、発生する室内定在波を低減・吸収できるよ
うになっているが、レゾネータの共鳴とは、図７におい
て、機械系におけるばね−マス系の共振現象と同様に、
首部３３での空気の質量Ｓ・ｔ・ρ（機械系のマスＭに
相当）と、空洞内の空気のばね成分ρ・Ｃ2 ・Ｓ／Ｖ
（機械系ばねＫに相当）による共鳴現象のことをいう。
ここで、Ｓは開口部の面積、ｔは首部長さ、ρは空気の
密度、Ｃは空気中の音速、Ｖは空洞部の体積である。Next, the principle of the resonator according to this embodiment will be described. The resonator according to this embodiment can reduce (absorb) the generated indoor standing wave by precisely (finely) adjusting the resonance sound absorption frequency using the changing mechanism. In FIG. 7, similar to the resonance phenomenon of the spring-mass system in the mechanical system,
The mass S · t · ρ of the air at the neck 33 (corresponding to the mass M of the mechanical system) and the spring component ρ · C 2 · S / V of the air in the cavity
(Equivalent to the mechanical spring K).
Here, S is the area of the opening, t is the length of the neck, ρ is the density of air, C is the speed of sound in air, and V is the volume of the cavity.
【００２６】一般に図７における（4)式、即ちレゾネー
タの共鳴吸音周波数（Ｆ0 ）は Ｆ0 ＝（Ｃ／２π）・〔Ｓ／Ｖ（ｔ＋０．８ｄ）〕1/2 … （4) （ただし、ｄ：連通路の内径）で一義的に計算されるか
ら、この周波数Ｆ0 を前述の式（3)で求まる定在波に正
しくチューニング（同調）することにより、定在波を効
果的に低減できることがわかる。In general, equation (4) in FIG. 7, that is, the resonance sound absorption frequency (F 0 ) of the resonator is F 0 = (C / 2π) · [S / V (t + 0.8d)] 1/2 (4) ( However, since it is uniquely calculated by d: the inner diameter of the communication path, the standing wave is effectively tuned (tuned) by properly tuning this frequency F 0 to the standing wave obtained by the above-mentioned equation (3). It can be seen that it can be reduced.
【００２７】一方、３次元の定在波を１次モードのみ全
て改善するためには、（3)式，（4)式より３種類のレゾ
ネータ（Ｆ0X，Ｆ0Y，Ｆ0Z）を用意する必要がある。ま
たレゾネータの吸音周波数Ｆ0 の調整のためには、（4)
式でわかるように、Ｖ，ｔ，Ｓ（又はｄ）のパラメータ
のうち少なくともどれか１要素以上を可変にしておけば
よいことが分かる。従って、実際の設置場所での定在波
周波数が設置する現場によっては（3)式等の見積りから
ずれる場合、Ｖ，ｔ，Ｓ（又はｄ）を変更すればよい。
なおゾネータの吸音周波数Ｆ0 の見積りには、上式（4)
以外に、ＦＥＭ（有限要素法），ＢＥＭ（境界要素法）
等の数値解析による方法もあり、より複雑な形状に対応
可能であるが、実験値と対応づけたデータベースの蓄積
が必要となる。On the other hand, in order to improve only the first-order mode of the three-dimensional standing wave, three types of resonators (F 0X , F 0Y , F 0Z ) are prepared from equations (3) and (4). There is a need. In order to adjust the sound absorption frequency F 0 of the resonator, (4)
As can be seen from the equation, at least one or more of the parameters of V, t, S (or d) should be variable. Therefore, if the standing wave frequency at the actual installation location deviates from the estimation based on Equation (3) depending on the installation site, V, t, S (or d) may be changed.
The above equation (4) is used to estimate the sound absorption frequency F 0 of the zonator.
Besides, FEM (Finite Element Method), BEM (Boundary Element Method)
There is also a method based on numerical analysis such as this, and it is possible to cope with more complicated shapes, but it is necessary to accumulate a database in association with experimental values.
【００２８】そこで、この実施例では、空洞部の体積Ｖ
を変更させるように構成してある。なお、レゾネータの
吸音効果は、Ｖ、Ｓが大きい程大きくなるが、レゾネー
タの内部の一辺が低減したい周波数の波長（λ）の１／
４以上となると、レゾネータ内で別の共鳴現象が起こ
り、逆にレゾネータから発音してしまう恐れがあるの
で、レゾネータの最長辺の長さを（Ｌmax ）とすると、
次式を満たす必要がある。 Ｌmax ≦（１／４）λ＝（１／４）Ｃ／Ｆ0 …（5)Therefore, in this embodiment, the volume V of the cavity is
Is configured to be changed. Note that the sound absorbing effect of the resonator increases as V and S increase, but one side of the resonator has one side of the wavelength (λ) of the frequency to be reduced.
If it is more than 4, another resonance phenomenon occurs in the resonator, and on the contrary, there is a possibility that sound is emitted from the resonator. Therefore, when the length of the longest side of the resonator is (L max ),
The following equation must be satisfied. Lmax ≦ (１ ／) λ = (１ ／) C / F 0 (5)
【００２９】例えば人間の最低可聴周波数２０Hzを考え
ると、 Ｌmax ≦（１／４）（３４０／２０）≒４．２５ｍ よって、実用上は、レゾネータの各辺（長さ）寸法は
４．２５ｍ以下とする必要がある。また、レゾネータの
配置（設置）については、図８のように、部屋の一方向
について、レゾネータの位置を１〜４まで変えて改善量
をプロットすると図９のようになった。[0029] For example, consider a human lowest audible frequency 20Hz, L max ≦ (1/4) (340/20) ≒ 4.25m Thus, practically, each side (length) of the resonator dimensions 4.25M It is necessary to: In addition, as for the arrangement (installation) of the resonators, as shown in FIG. 8, when the position of the resonator is changed from 1 to 4 in one direction of the room, the improvement amount is plotted as shown in FIG.
【００３０】部屋の定在波低減のためには、定在波の音
圧が高い部分にレゾネータを配置する程大きな効果が得
られることがわかった。実際には、理想的な位置、部屋
のはじ、すみに設置できない場合は、改善量が少なくな
るが、その分、レゾネータの個数を増やす、またはＶ、
Ｓを増加し、レゾネータ自体の吸音力を増加させる等で
対応することが可能である。In order to reduce the standing wave in the room, it has been found that the greater the arrangement of the resonator in the portion where the sound pressure of the standing wave is high, the greater the effect can be obtained. Actually, if it cannot be installed at the ideal position, at the edge of the room, or near the corner, the amount of improvement will be small, but the number of resonators will be increased accordingly, or V,
This can be dealt with by increasing S and increasing the sound absorbing power of the resonator itself.
【００３１】次に、この実施例に係るレゾネータ１を設
置場合に合わせた最適体積Ｖに調整して４階建の集合住
宅の３階に配置しておき、ＪＩＳ Ａ１４１８にのっと
り、２，３階を使用して、タイヤ落下評価実験を行なっ
た。なお、このときのレゾネータ１については、 のような図３に示したレゾネータを用いた。ここで、体
積Ｖを可変とし、実際の部屋の定在波周波数に微調整を
行った。Next, the resonator 1 according to this embodiment is adjusted to the optimum volume V in accordance with the case where it is installed, and is arranged on the third floor of a four-story apartment house, and according to JIS A1418, on the second and third floors. Was used to perform a tire drop evaluation experiment. In addition, about the resonator 1 at this time, The resonator shown in FIG. 3 was used. Here, the volume V was made variable, and fine adjustment was made to the standing wave frequency of the actual room.
【００３２】図１０に示すバングマシン５にて、３階床
の５点を加振し、その時の騒音を、２階５点でそれぞれ
計測し、平均としたときのデータを求めた。部屋の寸法
は、６帖相当で約３．６×２．７ｍ、高さ２．４ｍであ
る。スラブ＝１５０mm厚、各方向の定在波を概算すると
（3)式より、 ＬX （３．６ｍ）＝Ｃ／２ＬX ≒４７Hz ＬY （２．７ｍ）＝Ｃ／２ＬY ≒６３Hz ＬZ （２．４ｍ）＝Ｃ／２ＬZ ≒７１Hz となる。この部屋の床衝撃音を計測してみると、特にＸ
方向の定在波による騒音が最もレベルが大きいことがわ
かった。これは、部屋のドアや窓の配置の影響と考えら
れる。そこで、ここではＸ方向についての実験を行っ
た。実際の部屋の定在波は、音の計測より、４６Hzと、
上記（3)式からの概算値４７Hzからずれていたが、レゾ
ネータの体積Ｖ（実際には、図３の仕切板４１を動かし
て調整した）を変え、４６Hzに調整したレゾネータを用
いた。 (1) オクターブバンド分析結果については、共鳴吸音機
構を備えていない場合に比べ、図１１に示すように、６
３Hzバンドで４dBの改善、すなわち、遮音等級（Ｌ値）
が１ランクアップした。 (2) 狭帯域スペクトル分析結果については、共鳴吸音機
構を備えていない場合に比べ、図１２に示すように、４
６Hzのピーク値において約１０dB程度の低減が見られ
た。 (3) 時系列波形分析結果については、共鳴吸音機構を備
えていない場合に比べ、図１３に示すように、減衰時間
が大幅に低減した。なお、（2)，（3)については、中央
マイク以外のマイクから計測された結果である。With the bang machine 5 shown in FIG. 10, five points on the third floor were vibrated, and the noise at that time was measured at five points on the second floor, respectively, and the average data was obtained. The size of the room is about 3.6 x 2.7m, which is equivalent to 6 quires, and the height is 2.4m. Slab = 150 mm thickness and to approximate the standing wave in each direction (3) from the equation, L X (3.6m) = C / 2L X ≒ 47Hz L Y (2.7m) = C / 2L Y ≒ 63Hz L Z a (2.4m) = C / 2L Z ≒ 71Hz. When we measure the floor impact sound of this room, especially X
It was found that the noise due to the standing wave in the direction had the highest level. This is thought to be due to the arrangement of doors and windows in the room. Therefore, an experiment in the X direction was performed here. The standing wave of the actual room is 46Hz from the sound measurement,
Although it deviated from the approximate value of 47 Hz from the above equation (3), the resonator V was adjusted to 46 Hz by changing the volume V of the resonator (actually adjusted by moving the partition plate 41 in FIG. 3). (1) Regarding the octave band analysis result, as shown in FIG.
4dB improvement in 3Hz band, ie sound insulation grade (L value)
Increased by one rank. (2) As shown in FIG. 12, the result of the narrow band spectrum analysis was 4 times smaller than the case without the resonance sound absorbing mechanism.
At a peak value of 6 Hz, a reduction of about 10 dB was observed. (3) As for the result of the time-series waveform analysis, as shown in FIG. 13, the decay time was significantly reduced as compared with the case where the resonance sound absorbing mechanism was not provided. Note that (2) and (3) are results measured from microphones other than the central microphone.
【００３３】また、この実施例では、体積Ｖの変更・調
整を行う構成としてあるが、これ以外に例えば図１４に
示すように、首部３にキャップ３Ａをスライド可能に装
着させたり、図１５に示すようにねじを切った首部３Ｂ
とキャップ３Ｃとを螺合させ、それぞれスライドさせた
り回転させて、首部３の長さｔを可変構造としてもよ
い。同様に、首部を蛇腹状として伸縮性を付与する構造
としてもよい。また、図１６に示すように、首部３に、
内径寸法ｄの異なるキャップ３Ｄ〜３Ｆを選択的にセッ
トさせて首部３の内径ｄを変更させてもよい。In this embodiment, the volume V is changed / adjusted. In addition, for example, as shown in FIG. 14, a cap 3A can be slidably mounted on the neck 3, or as shown in FIG. Neck 3B threaded as shown
The length t of the neck 3 may be made variable by screwing the cap 3 </ b> C and the cap 3 </ b> C and sliding or rotating the cap 3 </ b> C. Similarly, the neck portion may have a bellows shape to provide elasticity. In addition, as shown in FIG.
The inner diameter d of the neck 3 may be changed by selectively setting the caps 3D to 3F having different inner diameters d.
【００３４】さらに、図１７及び図１８に示すように、
カメラのシャッタの絞りのような構造として、内径寸法
ｄを変更させてもよい。さらに、これらレゾネータの体
積Ｖ、首部（通気路）の長さｔ、首部の通気路の開口断
面積Ｓのいずれか２つ若しくは全てを可変構造としても
よい。Further, as shown in FIGS. 17 and 18,
The inner diameter d may be changed as a structure like a diaphragm of a camera shutter. Further, any two or all of the volume V of these resonators, the length t of the neck (air passage), and the opening cross-sectional area S of the air passage of the neck may be variable.
【００３５】さらに、首部の連通路内壁面に空気抵抗材
を組み込んで（例えば貼着する）、空気抵抗による減衰
機能を付与したり、首部開口端面に通気性のある綿、ガ
ーゼ、ウレタン、布、メッシュ材などを取り付けるなど
として、同様に減衰機能を付与するのもよい。さらにこ
の他に、レゾネータの空洞部分に水等の液体、粘度等の
固体、砂等の粒体を収容させて体積Ｖの変更・調整を行
う構成としてもよい。Further, an air resistance material is incorporated (for example, attached) on the inner wall surface of the communication passage of the neck to provide an attenuating function by air resistance, or air-permeable cotton, gauze, urethane, cloth, etc. Similarly, a damping function may be provided by attaching a mesh material or the like. In addition to this, the volume V may be changed and adjusted by storing a liquid such as water, a solid such as viscosity, and a granular material such as sand in the cavity of the resonator.
【００３６】次に、この発明にかかる他の実施例の共鳴
吸音機構について説明する。図１９は、この発明にかか
る共鳴吸音機構を示すものであり、この共鳴吸音機構
は、適宜の部材や部位（例えば、ドア、壁、柱、家具、
室内具、梁、床、その他の建物の内外のいずれのもので
も可能）に形成されており、空洞部分を有する本体部２
０と、この本体部２０に連通する通気路を設けた首部３
０と、首部３０の外部にむけて開口する開口部５０と、
共鳴吸音周波数の変更機構（図略）とを備えている。な
お、この変更機構としては、先の実施例のもののいずれ
であってもよい。Next, a resonance sound absorbing mechanism according to another embodiment of the present invention will be described. FIG. 19 shows a resonance sound absorbing mechanism according to the present invention. The resonance sound absorbing mechanism includes appropriate members and parts (for example, doors, walls, columns, furniture,
The main body 2 having a hollow portion, which is formed of a room tool, a beam, a floor, and any other object inside or outside the building.
0 and a neck 3 provided with an air passage communicating with the main body 20.
0, an opening 50 that opens toward the outside of the neck 30,
A resonance sound absorption frequency changing mechanism (not shown). The change mechanism may be any one of the above embodiments.
【００３７】[0037]
【発明の効果】以上説明してきたように、この発明によ
れば、共鳴吸音機構の空洞部分の体積、首部の通気路の
長さ、首部の開口部断面積のうち、少なくとも一つを変
更可能とする可変構造としたから、例えば設置場所の大
きさに合わせて計算（理論）上定められている吸音周波
数帯域を、設置する個々の室内の状況（例えば実際の梁
や柱等の寸法にずれ等）や家具の配置等に合わせて最適
値にきめ細かく変更・調整することができるようにな
り、延いては高品質の共鳴吸音機構を提供することがで
きる。さらに、最良な吸音周波数帯域は一定に維持させ
たまま、設置する場所のスペースに合わせて部分的な寸
法の変更調節を行うことも可能である。As described above, according to the present invention, it is possible to change at least one of the volume of the hollow portion of the resonance sound absorbing mechanism, the length of the ventilation path of the neck, and the sectional area of the opening of the neck. Therefore, for example, the sound absorption frequency band calculated (theoretical) according to the size of the installation location is changed to the situation in the individual room where the installation is performed (for example, deviation from the actual dimensions of beams, columns, etc.). And the like, and the arrangement of furniture can be finely changed and adjusted to an optimum value, thereby providing a high-quality resonance sound absorbing mechanism. Furthermore, it is also possible to adjust the partial size change according to the space of the installation place while keeping the best sound absorption frequency band constant.
【００３８】さらに、この請求項２に記載の発明によれ
ば、共鳴吸音機構に減衰機能を付与してあるから、本質
的には極く狭い範囲のみをカバーしている吸音周波数帯
域を拡大させることができる。Further, according to the second aspect of the present invention, since the resonance sound absorbing mechanism is provided with an attenuating function, the sound absorbing frequency band essentially covering only a very narrow range is expanded. be able to.
【図１】定在波を示す説明図。FIG. 1 is an explanatory diagram showing a standing wave.
【図２】３次元的に定在波を説明するための説明図。FIG. 2 is an explanatory diagram for describing a standing wave three-dimensionally.
【図３】この発明にかかる共鳴吸音機構を示す概略斜視
図。FIG. 3 is a schematic perspective view showing a resonance sound absorbing mechanism according to the present invention.
【図４】同機構の変形例を示す要部断面図。FIG. 4 is a sectional view of a main part showing a modification of the mechanism.
【図５】他の共鳴吸音機構を示す斜視図。FIG. 5 is a perspective view showing another resonance sound absorbing mechanism.
【図６】さらに他の共鳴吸音機構を示す斜視図。FIG. 6 is a perspective view showing still another resonance sound absorbing mechanism.
【図７】この発明の共鳴吸音機構を説明する原理図。FIG. 7 is a principle diagram illustrating a resonance sound absorbing mechanism of the present invention.
【図８】共鳴吸音機構の配置状態を示す説明図。FIG. 8 is an explanatory diagram showing an arrangement state of a resonance sound absorbing mechanism.
【図９】定在波の低減についての改善量を示すグラフ。FIG. 9 is a graph showing the amount of improvement in the reduction of standing waves.
【図１０】タイヤ落下評価実験を示す説明図。FIG. 10 is an explanatory diagram showing a tire drop evaluation experiment.
【図１１】オクターブバンド分析結果を示すグラフ。FIG. 11 is a graph showing an octave band analysis result.
【図１２】狭帯域スペクトルの分析結果を示すグラフ。FIG. 12 is a graph showing an analysis result of a narrow band spectrum.
【図１３】時系列波形の分析結果を示すグラフ。FIG. 13 is a graph showing an analysis result of a time-series waveform.
【図１４】共鳴吸音周波数の変更機構を示す要部断面
図。FIG. 14 is an essential part cross-sectional view showing a mechanism for changing the resonance sound absorbing frequency.
【図１５】変更機構の変形例を示す要部断面図。FIG. 15 is a sectional view of a main part showing a modification of the change mechanism.
【図１６】変更機構の他の変形例を示す断面図。FIG. 16 is a sectional view showing another modification of the change mechanism.
【図１７】変更機構のさらに他の変形例を示す概略斜視
図。FIG. 17 is a schematic perspective view showing still another modified example of the changing mechanism.
【図１８】図１７の変更機構を絞った状態を示すが概略
斜視図。FIG. 18 is a schematic perspective view showing a state in which the change mechanism of FIG. 17 is narrowed.
【図１９】この発明に係る他の共鳴吸音機構を示す概略
断面図。FIG. 19 is a schematic sectional view showing another resonance sound absorbing mechanism according to the present invention.
１ 共鳴吸音機構（レゾネータ） ２，２０，２１，２２ 本体部 ３，３０，３１，３２ 首部 ４，４０ 変更機構 ５，５０ 開口部 1 Resonant sound absorbing mechanism (resonator) 2,20,21,22 Main body 3,30,31,32 Neck 4,40 Changing mechanism 5,50 Opening
Claims (2)
部の空洞部に連通・する通気路を画成するとともに本体
部に連結する首部と、この首部の外部に向けて開口する
開口部とを備え、前記首部の通気路に存在する空気の質
量と前記空洞部分の空気のばね成分とによる共鳴現象を
利用し、設置する室内で発生する定在波等の低周波数騒
音を低減・吸収する共鳴吸音機構であって、 前記空洞部分の体積、首部の通気路の長さ、開口部断面
積のうち、少なくとも一つを変更可能とする可変構造を
有することを特徴とする共鳴吸音機構。1. A main body having a predetermined volume, a neck defining an air passage communicating with a cavity of the main body and connecting to the main body, and an opening opening to the outside of the neck. Utilizing a resonance phenomenon caused by the mass of air present in the air passage of the neck and the spring component of air in the cavity, reduces and absorbs low frequency noise such as standing waves generated in a room where the air conditioner is installed. A resonance sound absorbing mechanism having a variable structure that allows at least one of a volume of the hollow portion, a length of an air passage in a neck portion, and a cross-sectional area of an opening to be changed.
することを特徴とする請求項１に記載の共鳴吸音機構。2. The resonance sound absorbing mechanism according to claim 1, wherein the neck and / or the cavity has a damping function.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP8274188A JPH10102621A (en) | 1996-09-25 | 1996-09-25 | Resonance sound absorbing mechanism |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP8274188A JPH10102621A (en) | 1996-09-25 | 1996-09-25 | Resonance sound absorbing mechanism |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH10102621A true JPH10102621A (en) | 1998-04-21 |
Family
ID=17538269
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP8274188A Pending JPH10102621A (en) | 1996-09-25 | 1996-09-25 | Resonance sound absorbing mechanism |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH10102621A (en) |
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|---|---|---|---|---|
| KR20020049129A (en) * | 2000-12-19 | 2002-06-26 | 류정열 | Resonator tuning method |
| KR20030092306A (en) * | 2002-05-29 | 2003-12-06 | 전환표 | A Control Module Of An Indoor Reverberation And Control Device Of The Control Module |
| US7337877B2 (en) * | 2004-03-12 | 2008-03-04 | Visteon Global Technologies, Inc. | Variable geometry resonator for acoustic control |
| ITMI20110902A1 (en) * | 2011-05-20 | 2012-11-21 | Consorzio Intellimech | DEVICE FOR FITTING PRESSURE WAVES |
| WO2013114807A1 (en) * | 2012-02-03 | 2013-08-08 | 三菱電機株式会社 | Active noise control device |
| GB2565033A (en) * | 2017-05-23 | 2019-02-06 | Kp Acoustics Ltd | Acoustic resonators |
| CN110322868A (en) * | 2019-06-06 | 2019-10-11 | 江苏科技大学 | A kind of driving frequency-conversion Helmholz resonance device and its frequency modulation noise-reduction method |
| CN111883350A (en) * | 2020-07-21 | 2020-11-03 | 武汉大学 | Transformer substation noise frequency selection suppression device considering temperature factors and frequency selection method |
| CN113738476A (en) * | 2021-08-16 | 2021-12-03 | 安徽江淮汽车集团股份有限公司 | Air pipe assembly, noise elimination system and noise elimination method |
| WO2024019277A1 (en) * | 2022-07-22 | 2024-01-25 | (주)새론건설 | Noise prevention resonator and installation method therefor |
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Cited By (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR20020049129A (en) * | 2000-12-19 | 2002-06-26 | 류정열 | Resonator tuning method |
| KR20030092306A (en) * | 2002-05-29 | 2003-12-06 | 전환표 | A Control Module Of An Indoor Reverberation And Control Device Of The Control Module |
| US7337877B2 (en) * | 2004-03-12 | 2008-03-04 | Visteon Global Technologies, Inc. | Variable geometry resonator for acoustic control |
| ITMI20110902A1 (en) * | 2011-05-20 | 2012-11-21 | Consorzio Intellimech | DEVICE FOR FITTING PRESSURE WAVES |
| WO2013114807A1 (en) * | 2012-02-03 | 2013-08-08 | 三菱電機株式会社 | Active noise control device |
| GB2565033A (en) * | 2017-05-23 | 2019-02-06 | Kp Acoustics Ltd | Acoustic resonators |
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| CN110322868A (en) * | 2019-06-06 | 2019-10-11 | 江苏科技大学 | A kind of driving frequency-conversion Helmholz resonance device and its frequency modulation noise-reduction method |
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