JP6512795B2 - Mute structure of natural ventilation opening - Google Patents

Mute structure of natural ventilation opening Download PDF

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JP6512795B2
JP6512795B2 JP2014230709A JP2014230709A JP6512795B2 JP 6512795 B2 JP6512795 B2 JP 6512795B2 JP 2014230709 A JP2014230709 A JP 2014230709A JP 2014230709 A JP2014230709 A JP 2014230709A JP 6512795 B2 JP6512795 B2 JP 6512795B2
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muffling
opening
tubular body
natural ventilation
sleeve tube
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井上　諭
諭 井上
羽染　武則
武則 羽染
菜穂美 井上
菜穂美 井上
志津子 西沢
志津子 西沢
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Tokyu Construction Co Ltd
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Description

本発明は、自然換気口の消音構造に関するものである。
The present invention relates to silencing structure of natural ventilation openings.

建築基準法の改正により２４時間換気システムの設置が義務化されたことにより、近年の住宅においては、自然換気のための換気口が取り付けられる。
一般的な自然換気口は、屋外側給気口のベントキャップ（フード）、スリーブ管（通気スリーブ）、および室内側給気口のレジスタによって構成する。（図１４）
このような構成の自然換気口において、スリーブ管は両端に開口を持つ共鳴管となるため、気柱共鳴と呼ばれる管状体特有の音波の共鳴現象が生じる。気柱共鳴が生じると、共鳴周波数において換気口内の音圧が増大し遮音性能が低下する。 With the revision of the Building Standard Law, the establishment of a 24-hour ventilation system is obligated, and in recent homes, a vent for natural ventilation is installed.
A general natural ventilation port is constituted by the vent cap (hood) of the outdoor side air supply port, the sleeve tube (aeration sleeve), and the register of the indoor side air supply port. (Figure 14)
In such a natural ventilation port, since the sleeve tube becomes a resonance tube having an opening at both ends, a resonance phenomenon of sound waves peculiar to the tubular body called air column resonance occurs. When air column resonance occurs, the sound pressure in the vent increases at the resonance frequency and the sound insulation performance decreases.

このような問題を改善するために従来、次のような消音構造が開発されていた。
＜１＞２４時間換気給気口の外部ガラリに迷路状の吸音材を設置して消音する、外付け型防音ガラリ構造
＜２＞全熱交換器型の給気ダクト内に吸音材を巻いて消音する、グラスダクトフレキシブル消音構造
＜３＞２４時間換気給気口のスリーブ管内に吸音材付きの装置をはめ込んで消音する、スリーブ内蔵型サイレンサー構造
＜４＞外壁と内壁との間に消音ダクトを設ける、消音ダクト挿入型構造（特許文献１、２） In order to improve such problems, conventionally, the following muffling structure has been developed.
<1> An external soundproof glaring structure in which a maze-like sound absorbing material is installed and muffled on the outer gully of the ventilation air supply port for 24 hours <2> Wrap the sound absorbing material in the air intake duct of total heat exchanger type Glass duct flexible muffling structure <3> A device with sound absorbing material is inserted into a sleeve tube of a 24 hour ventilation air inlet and muffled, a sleeve built-in silencer structure <4> a muffling duct between an outer wall and an inner wall Muffler duct insertion type structure (patent documents 1 and 2)

また、共鳴機構を利用した消音装置として、ヘルムホルツ共鳴器や管状体の共鳴器等が知られている。
とくに「片側開口−片側閉塞」の管状体を用いた共鳴器は、その長さが消音対象とする音波の波長の１／４程度（λ／４共鳴器）であることが特徴であり、多くの技術分野で使用されている。（特許文献３、４） In addition, Helmholtz resonators, resonators of a tubular body, and the like are known as silencers using a resonance mechanism.
In particular, a resonator using a “one side open-one side closed” tubular body is characterized in that its length is about 1⁄4 of the wavelength of the sound wave to be silenced (λ / 4 resonator), Used in the technical field of (Patent Documents 3 and 4)

特開平１０−２８１５１５号公報Unexamined-Japanese-Patent No. 10-281515 特開２０１３−１６４２２９号公報JP, 2013-164229, A 特開２０１４−５２５３９号公報JP, 2014-52539, A 特開平０６−１５９１７５号公報Unexamined-Japanese-Patent No. 06-159175 gazette

前記した従来の消音構造や消音装置にあっては、次のような問題点がある。
＜１＞通常、スリーブ管長は外壁厚に応じて変化し２００〜４００ｍｍ程度となる。このとき、スリーブ管に生じる気柱共鳴周波数は４００〜７００Ｈｚの範囲に表れ、換気口においてはこの気柱共鳴周波数を中心に１／３オクターブバンド幅以上の周波数帯域において大幅な遮音性能の欠損を生じる。（図１５）
＜２＞遮音性能の確保と、省スペース化を意図することによって、製品自体の寸法を小さくした製品が多い。そのために、吸音材を迷路状に配置して距離減衰や吸音面積を確保し、あるいは空気流入経路の気積を縮小するなどの処置がとられている。その結果、通気抵抗が増し、レンジフードの運転等による強制排気時には居室内外の圧力差が大きくなるため、玄関ドアやサッシの開閉が重くなる。
＜３＞以上のような、遮音性能確保と圧力差の解消という矛盾する２つの課題を満足することはできていない。特に直径が１５０Φの給気口に付属するものではＴ−４性能を確保するものが存在しない。
＜４＞上記問題を解消した消音ダクト挿入型構造（特許文献２）は、通気性能を損なうことなく、高い遮音性能を確保できるが、スリーブ管内で生じる気柱共鳴による遮音性能の欠損については、改善の余地がある。
＜５＞λ／４共鳴器は目標周波数の音を定めて消音させることが可能であるが、消音できる周波数帯域幅が小さいため、スリーブ管で生じている１／３オクターブバンド幅以上の周波数帯域での遮音性能の欠損をカバーすることができない。
＜６＞特許文献３におけるλ／４共鳴器の開口端に薄膜を貼り付ける構成は、共鳴周波数における吸音力を高めるためのものであり、吸音帯域幅を拡張するものではない。
＜７＞λ／４共鳴器は、その開口端をスリーブ管内の音圧振幅分布の腹部近傍に設置することが最も効果的であることは特許文献４にも記載されているが、実施例においては腹部近傍に設置することも、腹部の位置も明確に記載されておらず、実際に得られる効果は不明である。
＜８＞いずれの消音構造、消音装置においても、通気性能を確保し圧力損失を下げつつ、遮音性能を高めることについては配慮されていない。 The above-described conventional muffling structure and muffling apparatus have the following problems.
<1> Usually, the sleeve pipe length changes according to the outer wall thickness and becomes about 200 to 400 mm. At this time, the air column resonance frequency generated in the sleeve tube appears in the range of 400 to 700 Hz, and the ventilation opening largely loses the sound insulation performance in the frequency band of 1/3 octave bandwidth or more centered on the air column resonance frequency. It occurs. (Figure 15)
<2> There are many products in which the dimensions of the product itself are reduced by the purpose of securing the sound insulation performance and saving space. Therefore, measures are taken such as arranging the sound absorbing material in a maze shape to secure the distance attenuation and the sound absorbing area, or reducing the air volume of the air inflow path. As a result, the ventilation resistance is increased, and the pressure difference between the inside and the outside of the room becomes large at the time of forced exhaust by the operation of the range hood and the like, so that the opening and closing of the entrance door and the sash becomes heavy.
It has not been possible to satisfy the two contradictory tasks of securing the sound insulation performance and eliminating the pressure difference as described above in <3>. In particular, the one attached to the air inlet having a diameter of 150 mm does not exist to secure the T-4 performance.
<4> The muffling duct insertion type structure (PTL 2) that solves the above problems can ensure high sound insulation performance without impairing the ventilation performance, but the loss of the sound insulation performance due to air column resonance occurring in the sleeve tube is There is room for improvement.
The <5> λ / 4 resonator can determine and mute the sound of the target frequency, but the frequency band width that can be muffled is small, so a frequency band of 1/3 octave bandwidth or more generated by the sleeve tube Can not cover the loss of sound insulation performance in
The configuration in which the thin film is attached to the opening end of the λ / 4 resonator in <6> Patent Document 3 is for enhancing the sound absorption at the resonance frequency, and does not expand the sound absorption bandwidth.
Although it is described in Patent Document 4 that it is most effective to place the open end of the <7> λ / 4 resonator in the vicinity of the abdomen of the sound pressure amplitude distribution in the sleeve tube, it is described in Patent Document 4 The position of the abdomen is not clearly described, nor is the effect actually obtained obtained.
In any of the noise reduction structures and noise reduction devices of <8>, no consideration is given to enhancing the sound insulation performance while securing the ventilation performance and reducing the pressure loss.

上記目的を達成するためになされた本願の第１発明は、屋外の給気口と、室内の給気口とをスリーブ管によって接続する、自然換気口の消音構造であって、前記スリーブ管内に設置する消音用管状体を有し、前記消音用管状体は、少なくとも一方の端部を閉止し、他方の端部付近に開口部を設け、前記一方の端部から前記開口部の中心までの長さが前記スリーブ管の全長の略半分の長さを有し、内部には多孔質材を配置し、前記スリーブ管内に前記消音用管状体を、前記消音用管状体の開口部が前記スリーブ管の内部空間に向かって開口するように配置し、前記消音用管状体の前記開口部の、前記スリーブ管の中央からの、前記スリーブ管の長手方向の長さに対するずれを４０％以内とすることを特徴とする、自然換気口の消音構造を提供する。
本願の第２発明は、第１発明の自然換気口の消音構造において、前記消音用管状体の前記開口部は、前記他方の端部の長手方向端面に設けることを特徴とする、自然換気口の消音構造を提供する。
本願の第３発明は、第１発明の自然換気口の消音構造において、前記消音用管状体の前記他方の端部を閉止し、前記開口部を前記他方の端部の側面に設けることを特徴とする、自然換気口の消音構造を提供する。
本願の第４発明は、第１発明乃至第３発明の何れかの自然換気口の消音構造において、前記消音用管状体は、断面を前記スリーブ管の内周に沿う弓状とし、前記開口部を長手方向端面または弦をなす面に設けることを特徴とする、自然換気口の消音構造を提供する。
本願の第５発明は、第１発明乃至第４発明の何れかの自然換気口の消音構造において、前記スリーブ管と前記室内の給気口との間に消音ダクトを設けることを特徴とする、自然換気口の消音構造を提供する。
The first shot Ming application has been made in order to achieve the above object, outdoor and air inlets of the indoor air inlets connected by a sleeve tube, a muffling structure of a natural ventilation opening, the sleeve tube And the muffling tubular body closes at least one end and provides an opening near the other end, from the one end to the center of the opening has an approximately half the total length of the length the sleeve tube, inside placing a porous material, said sound-absorbing tubular body to said sleeve tube, the openings of the sound-absorbing tubular body wherein It is arranged to open toward the inner space of the sleeve tube, and the deviation of the opening of the muffling tubular body from the center of the sleeve tube with respect to the longitudinal length of the sleeve tube is within 40%. characterized in that it, to provide a muffling structure of a natural ventilation opening .
According to a second invention of the present application, in the noise reduction structure of the natural ventilation opening according to the first invention, the opening of the muffling tubular body is provided on a longitudinal end surface of the other end. Provide a silent structure.
According to a third aspect of the present invention, in the noise reduction structure of the natural ventilation port according to the first aspect, the other end of the muffling tubular body is closed and the opening is provided on the side of the other end. To provide a noise reduction structure for natural ventilation openings.
According to a fourth invention of the present application, in the noise reduction structure of the natural ventilation port according to any one of the first invention to the third invention, the muffling tubular body has an arc-shaped cross section along the inner periphery of the sleeve tube; The present invention provides a noise reduction structure of a natural ventilation opening, characterized in that the longitudinal ventilation end surface or the surface making a chord is provided.
According to a fifth aspect of the present invention, in the noise reduction structure according to any one of the first to fourth aspects, a noise reduction duct is provided between the sleeve pipe and the air supply opening in the chamber. Provide a noise reduction structure for the natural ventilation port.

本発明は、上記した課題を解決するための手段により、次のような効果の少なくとも一つを得ることができる。
＜１＞スリーブ管と消音用管状体との１次の固有振動数を一致させるとともに、スリーブ管と消音用管状体の音圧特性をずらすことにより、スリーブ管の気柱共鳴を弱めることができる。
＜２＞気柱共鳴を弱めることにより、遮音性能が向上する。
＜３＞スリーブ管端部や給気経路内の吸音処理ではなく、スリーブ管中央部に消音用管状体を配置するものであるため、通気性能を確保し圧力損失を下げつつ、遮音性能を高めることができる。
＜４＞消音用管状体内に吸音材を充填することにより、吸音帯域幅を拡張し、気柱共鳴によって遮音性能の欠損が生じる周波数帯域音を効率よく吸収することができる。
＜５＞消音用管状体の開口部の配置位置を明確にすることにより、効果的に遮音性能を高めることができる。 In the present invention, at least one of the following effects can be obtained by means for solving the problems described above.
The air column resonance of the sleeve tube can be weakened by matching the primary natural frequencies of the sleeve tube and the tube for muffling, and shifting the sound pressure characteristics of the sleeve tube and the tube for muffling .
The sound insulation performance is improved by weakening the air column resonance.
<3> Instead of sound absorption processing in the end of the sleeve pipe or in the air supply path, the muffling tubular body is disposed at the center of the sleeve pipe. Therefore, the sound insulation performance is enhanced while securing the ventilation performance and reducing the pressure loss. be able to.
By filling the sound absorbing material in the <4> sound absorbing tubular body, it is possible to expand the sound absorption bandwidth and efficiently absorb the frequency band noise that causes the loss of the sound insulation performance by air column resonance.
The sound insulation performance can be effectively enhanced by clarifying the arrangement position of the opening of the tubular body for noise reduction.

本発明の自然換気口の消音構造の説明図Explanatory drawing of the muffling structure of the natural ventilation port of the present invention 消音ダクトを有する本発明の自然換気口の消音構造の説明図Explanatory drawing of the muffling structure of the natural ventilation port of this invention which has a muffling duct スリーブ管中の音圧振幅分布の概念図Conceptual diagram of sound pressure amplitude distribution in a sleeve tube 消音用管状体の説明図Explanatory drawing of the tubular body for muffling 消音用管状体中の音圧振幅分布の概念図A conceptual diagram of sound pressure amplitude distribution in a muffle tube スリーブ管と消音用管状体との配置の概念図と音圧振幅の概念図A conceptual view of the arrangement of the sleeve tube and the muffle tube and a conceptual view of the sound pressure amplitude 消音用管状体の設置位置による遮音性能の違いを示す図（消音ダクト有り）Diagram showing the difference in sound insulation performance depending on the installation position of the sound deadening pipe (with sound deadening duct) 消音用管状体の設置位置を示す図The figure which shows the installation position of the tubular body for muffling 消音用管状体の占有率による遮音性能の違いを示す図（消音ダクト有り）Diagram showing the difference in sound insulation performance due to the occupancy rate of the tube for muffling (with muffling duct) 消音用管状体の圧力損失特性を示す図（消音ダクト有り）Diagram showing the pressure drop characteristics of the sound deadening pipe (with sound deadening duct) 吸音材の物性による遮音性能の違いを示す図（消音ダクト有り）Diagram showing the difference in sound insulation performance due to the physical properties of the sound absorbing material (with a silencer duct) その他実施例にかかる消音用管状体の説明図Explanatory drawing of the pipe | tube body for muffling concerning the other Example その他実施例にかかる自然換気口の消音構造の説明図Explanation of the noise reduction structure of the natural ventilation port according to other examples 一般的な自然換気口の説明図An illustration of a typical natural vent 従来の自然換気口の遮音性能を示す図（消音ダクト有り）Diagram showing the sound insulation performance of a conventional natural ventilation port (with a silencer duct)

以下、図面を参照しながら本発明の実施の形態について説明する。   Hereinafter, embodiments of the present invention will be described with reference to the drawings.

＜１＞自然換気口の消音構造の構成。
本発明の自然換気口の消音構造は、屋外側給気口に設けるベントキャップ１と、室内側給気口に設けるレジスタ２と、ベントキャップ１とレジスタ２とを繋ぐスリーブ管３と、スリーブ管３内に配置する消音用管状体４と、からなる。（図１）
また、スリーブ管３とレジスタ２との間に、消音ダクト５を設けても良い。（図２） <1> Configuration of the noise reduction structure of the natural ventilation port.
The noise reduction structure of the natural ventilation port according to the present invention comprises a vent cap 1 provided at the outdoor side air supply port, a register 2 provided at the indoor side air supply port, a sleeve pipe 3 connecting the vent cap 1 and the register 2, and a sleeve pipe And muffling tubular body 4 disposed in 3. (Figure 1)
Further, the muffle duct 5 may be provided between the sleeve pipe 3 and the register 2. (Figure 2)

＜２＞スリーブ管による気柱共鳴。
スリーブ管３によって生じる気柱共鳴による音波の固有振動数fnは次式で表される。
fn = n・c / 2L [Hz] (n=1,2,3,・・・・)……（１）
これに対応する音波の波長λnは（２）式のとおり表される。
λn = 2L/n ……（２）
c：音速、L：スリーブ管長さ、n：次数（節数）
そして、遮音性能上特に問題となるのは、n=1のときの1次の固有振動、fn =c / 2L[Hz]、λn = 2L の条件である。
このときの音圧振幅の分布は図３のように、スリーブ管３の長手方向中央部に音圧振幅の「腹」（音圧極大点）が生じる。 Air column resonance by <2> sleeve tube.
The natural frequency fn of the sound wave due to air column resonance generated by the sleeve tube 3 is expressed by the following equation.
fn = n · c / 2 L [Hz] (n = 1, 2, 3, ...) ... (1)
The wavelength λ n of the sound wave corresponding to this is expressed by equation (2).
λ n = 2 L / n (2)
c: sound velocity, L: sleeve tube length, n: order (number of nodes)
Further, what is particularly a problem in the sound insulation performance is the condition of the first-order natural vibration when n = 1, fn = c / 2L [Hz], λn = 2L.
The distribution of the sound pressure amplitude at this time is such that the "antinode" (sound pressure maximum point) of the sound pressure amplitude is generated at the central portion in the longitudinal direction of the sleeve tube 3 as shown in FIG.

＜３＞消音用管状体。
本発明の消音用管状体４は、一方の端部側に開口部４１を有し、もう一方の端部は閉止端４２とした管体からなる。（図４ａ）
消音用管状体４は、金属、木材、樹脂等の、音波の共鳴現象が生じるに足る剛性および質量を備える材料により構成する。
消音用管状体４の断面形状は極端な扁平でない限り、円、楕円、方形、多角形等、任意の形状でよい。
また、消音用管状体４の管の長手方向についても、直線状であってもよいし、折れ曲がりがあってもよい。 <3> A tubular body for muffling.
The pipe 4 for muffling of the present invention comprises an opening 41 at one end and a closed end 42 at the other end. (Figure 4a)
The muffling tubular body 4 is made of a material such as metal, wood, resin, etc., which has sufficient rigidity and mass to cause a resonance phenomenon of sound waves.
As long as the cross-sectional shape of the muffling tubular body 4 is not extremely flat, it may be any shape such as a circle, an ellipse, a square, or a polygon.
Further, the longitudinal direction of the pipe of the tubular body 4 for muffling may be linear or may be bent.

＜４＞開口部
開口部４１は消音用管状体４の長さ方向の端面または側面の最端部に形成する。（図４ａ、ｂ）開口部４１を側面に形成する場合には、消音用管状体４は両端が閉止端４２となる。
開口部４１の面積は、消音用管状体４の断面積と略同一とする。
開口部４１の形状は、円、楕円、方形、多角形等、任意の形状でよい。 <4> Opening The opening 41 is formed at the end of the end surface or the side surface of the sound absorption tubular body 4 in the longitudinal direction. When the opening 41 is formed on the side surface, both ends of the muffling tubular body 4 are closed ends 42 (FIG. 4a, b).
The area of the opening 41 is approximately the same as the cross-sectional area of the muffling tubular body 4.
The shape of the opening 41 may be any shape such as a circle, an ellipse, a square, or a polygon.

＜５＞消音用管状体の効果。
本発明では一方の端部側に開口部４１を有し、もう一方の端部は閉止端４２とした消音用管状体４をスリーブ管３内に配置する。
消音用管状体４は、開口部４１に音波が入射すると気柱共鳴が発生する。その固有振動数fm、波長λmは次のとおりに表される。
fm =c (2m-1)/ 4D [Hz] (m=1,2,3,・・・・)……（３）
λm = 4D/(2m-1) ……（４）
但し、c：音速、D：消音用管状体の長さ（開口部中心から反対側の閉止端までの長さ）、m：次数（節数）
ここでm=1、すなわち、1次の固有振動は振動数fm =c / 4D [Hz]、波長λm = 4Dとなり、その音圧振幅の分布は図５のように表され、消音用管状体４の開口端４１には、音圧振幅の「節」（音圧極小部）が生じる。
そして、スリーブ管３内の音場制御にあたっては、スリーブ管３と消音用管状体４との１次の固有振動数を一致させる。すなわち、消音用管状体４の長さ（開口部４１の中心から反対側の閉止端までの長さ）Dを制御対象とする音波の波長（λn＝λm）の約1/4相当、スリーブ管３の長さＬの約1/2とする。
消音用管状体４の設置位置は、開口部４１がスリーブ管３の長手方向の中央付近に位置するようにすることにより、スリーブ管３内の中央部の音圧の「腹」に消音用管状体４の開口部４１の「節」が近接する（図６）。この配置はスリーブ管３と消音用管状体４の音圧特性が一致しないように企図されたものであり、これにより、消音用管状体４の1次の共鳴を最も弱める効果を発揮する。 The effect of the tubular body for <5> sound absorption.
In the present invention, the end of the sleeve tube 3 has the opening 41 at one end, and the other end has the closed end 42 in the sleeve tube 3.
When the sound wave enters the opening 41, air column resonance occurs in the sound absorption tubular body 4. The natural frequency fm and the wavelength λm are expressed as follows.
fm = c (2m-1) / 4D [Hz] (m = 1, 2, 3, ...) ... (3)
λ m = 4D / (2 m-1) (4)
However, c: sound velocity, D: length of the tube for muffling (length from the opening center to the opposite closed end), m: order (number of nodes)
Here, m = 1, that is, the first-order natural vibration has frequency fm = c / 4D [Hz] and wavelength λm = 4D, and the distribution of the sound pressure amplitude is represented as shown in FIG. At the open end 41 of 4, the "node" (sound pressure minimum portion) of the sound pressure amplitude occurs.
Then, in controlling the sound field in the sleeve tube 3, the primary natural frequencies of the sleeve tube 3 and the muffling tubular body 4 are made to match. That is, the sleeve tube corresponds to about 1/4 of the wavelength (λ n = λ m) of the sound wave whose length is to be controlled (the length from the center of the opening 41 to the opposite closed end) D It is about 1/2 of the length L of 3.
The installation position of the muffling tubular body 4 is such that the opening 41 is located near the center of the sleeve tube 3 in the longitudinal direction, so that the muffling tubular can be installed on the "belly side" of the sound pressure of the central portion in the sleeve tube 3. The "nodes" of the opening 41 of the body 4 approach (Fig. 6). This arrangement is intended to make the sound pressure characteristics of the sleeve tube 3 and the muffling tubular body 4 not coincide with each other, thereby exerting the effect of most weakening the primary resonance of the muffling tubular body 4.

＜６＞消音用管状体の配置位置。
消音用管状体４は上記のとおり、開口部４１がスリーブ管３の長手方向の中央に位置することが最適である。
ただし、図７の結果に示す通り、図８のように開口部４１の、スリーブ管３の中央からの、スリーブ管３の長さＬに対するずれが最大４０％（０．４Ｌ）までは許容し、２７％（０．２７Ｌ）までが好適である。
このとき、消音用管状体４の開口部４１はスリーブ管３の内部空間に向かって開口していれば良く、開口部４１や消音用管状体４の方向は特定されない。 Arrangement position of the tubular body for <6> sound absorption.
As described above, it is optimal that the opening 41 be located at the longitudinal center of the sleeve tube 3 as described above.
However, as shown in the results of FIG. 7, as shown in FIG. 8, the deviation of the opening 41 from the center of the sleeve tube 3 with respect to the length L of the sleeve tube 3 is allowed up to 40% (0.4 L) Up to 27% (0.27 L) is preferred.
At this time, the opening 41 of the muffling tubular body 4 may be opened toward the internal space of the sleeve tube 3, and the directions of the opening 41 and the muffling tubular body 4 are not specified.

＜７＞消音用管状体の占有率。
消音用管状体４は、断面形状は問わないが、スリーブ管３の断面に対する消音用管状体４の占有率が高くなると、遮音性能は高まる（図９）が、通気経路が狭くなり、内外圧差が大きくなる。
そこで、図９の結果より消音用管状体のスリーブ管の断面積に対する占有率が２０〜２５％以上となるようにすれば遮音性能は確保できる。
占有率を２５％とした場合、図１０のようにスリーブ管３の大きさに関わらず、圧力損失特性に及ぼす影響が小さく、換気性能に及ぼす影響を最小限にとどめることができる。 <7> Occupancy rate of the tubular body for muffling.
Although the cross-sectional shape of the muffling tubular body 4 is not limited, the sound insulation performance is enhanced when the occupancy rate of the muffling tubular body 4 with respect to the cross-section of the sleeve tube 3 is increased (FIG. 9). Becomes larger.
Therefore, according to the result of FIG. 9, the sound insulation performance can be secured by setting the occupancy rate to the cross-sectional area of the sleeve pipe of the tubular body for noise reduction to 20 to 25% or more.
When the occupancy rate is 25%, the influence on the pressure loss characteristic is small regardless of the size of the sleeve tube 3 as shown in FIG. 10, and the influence on the ventilation performance can be minimized.

＜８＞吸音材。
消音用管状体４の内部には吸音材６を全体に充填する。
吸音材６は、グラスウールやポリエステル吸音体等の多孔質材を用いる。
吸音材６は、流れ抵抗１６００Ns/m4程度（密度８ｋｇ／ｍ３程度）とすることにより、気柱共鳴によって遮音性能の欠損が生じる周波数帯域音を効率よく吸収することができる（図１１）。
<8> Sound absorbing material.
Inside the sound absorbing tubular body 4, the sound absorbing material 6 is entirely filled.
The sound absorbing material 6 uses a porous material such as glass wool or a polyester sound absorber.
By setting the flow resistance to about 1600 Ns / m 4 (density about 8 kg / m 3 ), the sound absorbing material 6 can efficiently absorb frequency band noise that causes loss of sound insulation performance due to air column resonance (FIG. 11) .

＜９＞その他実施例。
消音用管状体４は断面形状を、弓の弧をスリーブ管３の内周に沿わせた弓状としてもよい。このとき、開口部４１は端面または弦をなす面に形成する（図１２）。開口部４１を弦をなす面に形成する場合には、開口部４１を設けた側の端面も閉止される。
そして、消音用管状体４は、開口部４１が上記＜６＞の条件に当てはまるように配置するが、閉止端４２をベントキャップ１側の端部に合わせることで、屋外からスリーブ管３内へ浸入する雨水の流入を防止する止水板としての機能を持たせることができる。（図１３） <9> Other Examples.
The muffling tubular body 4 may have a cross-sectional shape in which the arc of the bow is formed along the inner periphery of the sleeve 3. At this time, the opening 41 is formed on an end face or a chordal face (FIG. 12). In the case where the opening 41 is formed in a chordal surface, the end face on the side where the opening 41 is provided is also closed.
Then, the muffling tubular body 4 is disposed so that the opening 41 satisfies the above condition <6>, but by fitting the closed end 42 to the end on the vent cap 1 side, it is possible to enter the sleeve tube 3 from the outside. It can have a function as a water stop plate which prevents the inflow of the rainwater which infiltrates. (Figure 13)

１ ベントキャップ
２ レジスタ
３ スリーブ管
４ 消音用管状体
４１ 開口端
４２ 閉止端
５ 消音ダクト
６ 吸音材 DESCRIPTION OF SYMBOLS 1 Vent cap 2 Register 3 Sleeve tube 4 Tubular body 41 for muffling Opening end 42 Closed end 5 muffling duct 6 Sound absorbing material

Claims (5)

屋外の給気口と、室内の給気口とをスリーブ管によって接続する、自然換気口の消音構造であって、
前記スリーブ管内に設置する消音用管状体を有し、
前記消音用管状体は、
少なくとも一方の端部を閉止し、他方の端部付近に開口部を設け、
前記一方の端部から前記開口部の中心までの長さが前記スリーブ管の全長の略半分の長さを有し、
内部には多孔質材を配置し、
前記スリーブ管内に前記消音用管状体を、前記消音用管状体の開口部が前記スリーブ管の内部空間に向かって開口するように配置し、
前記消音用管状体の前記開口部の、前記スリーブ管の中央からの、前記スリーブ管の長手方向の長さに対するずれを４０％以内とすることを特徴とする、
自然換気口の消音構造。 A noise reduction structure of a natural ventilation port, which connects an outdoor air supply port and an indoor air supply port by a sleeve pipe,
A muffling tubular body installed in the sleeve tube;
The muffling tubular body is
Closing at least one end and providing an opening near the other end;
The length from the one end to the center of the opening has a length approximately half that of the entire length of the sleeve tube,
Place porous material inside,
The sound-absorbing tubular body to said sleeve tube, and arranged so that the opening of the muffler for the tubular body is open toward the inner space of the sleeve,
Deviation from the center of the sleeve tube with respect to the longitudinal length of the sleeve tube from the center of the sleeve tube is 40% or less .
Mute structure of natural ventilation opening. 請求項１に記載の自然換気口の消音構造において、In the noise reduction structure of the natural ventilation port according to claim 1,
前記消音用管状体の前記開口部は、前記他方の端部の長手方向端面に設けることを特徴とする、  The opening of the muffling tubular body is provided on a longitudinal end surface of the other end,
自然換気口の消音構造。Mute structure of natural ventilation opening. 請求項１に記載の自然換気口の消音構造において、In the noise reduction structure of the natural ventilation port according to claim 1,
前記消音用管状体の前記他方の端部を閉止し、前記開口部を前記他方の端部の側面に設けることを特徴とする、Closing the other end of the muffling tubular body, and providing the opening on the side surface of the other end;
自然換気口の消音構造。Mute structure of natural ventilation opening. 請求項１乃至請求項３の何れか一項に記載の自然換気口の消音構造において、In the noise reduction structure of the natural ventilation port according to any one of claims 1 to 3,
前記消音用管状体は、The muffling tubular body is
断面を前記スリーブ管の内周に沿う弓状とし、Cross-sections are arcuate along the inner periphery of the sleeve tube,
前記開口部を長手方向端面または弦をなす面に設けることを特徴とする、Providing the opening at a longitudinal end face or a chordal surface;
自然換気口の消音構造。Mute structure of natural ventilation opening. 請求項１乃至請求項４の何れか一項に記載の自然換気口の消音構造において、
前記スリーブ管と前記室内の給気口との間に消音ダクトを設けることを特徴とする、自然換気口の消音構造。 In the sound deadening structure of a natural ventilation port according to any one of claims 1 to 4 ,
A muffling structure for a natural ventilation port, comprising a muffling duct between the sleeve pipe and the air supply port in the room.
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