JP6691521B2 - Muffling system - Google Patents
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- JP6691521B2 JP6691521B2 JP2017181231A JP2017181231A JP6691521B2 JP 6691521 B2 JP6691521 B2 JP 6691521B2 JP 2017181231 A JP2017181231 A JP 2017181231A JP 2017181231 A JP2017181231 A JP 2017181231A JP 6691521 B2 JP6691521 B2 JP 6691521B2
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Landscapes
- Building Environments (AREA)
- Soundproofing, Sound Blocking, And Sound Damping (AREA)
Description
本発明は、消音システムに関する。 The present invention relates to a silencing system.
換気口、空調用ダクトなど、室内と室外とを隔てる壁に設けられた、室内と室外とを貫通する管状部材において、室外からの騒音が室内に伝わるのを抑制するため、あるいは室内からの騒音が外部に伝わるのを抑制するために、管状部材内にウレタン、ポリエチレン等の吸音材を設置することが行なわれている。
しかしながら、ウレタンおよびポリエチレン等の吸音材を用いる場合には、８００Ｈｚ以下の低周波音の吸収率が極端に低くなるため、吸収率を大きくするためには体積を大きくする必要があるが、換気口、空調用ダクトなどの通気性を確保する必要があるため、吸音材の大きさには限度があり、高い通気性と防音性能とを両立することが難しいという問題があった。
In a tubular member that is provided on a wall that separates the room from the room, such as a ventilation port or an air-conditioning duct, that penetrates the room from the room to prevent noise from the room from being transmitted to the room or from the room. In order to suppress the transmission of heat to the outside, a sound absorbing material such as urethane or polyethylene is installed inside the tubular member.
However, when a sound absorbing material such as urethane and polyethylene is used, the absorption rate of low frequency sound of 800 Hz or less becomes extremely low. Therefore, it is necessary to increase the volume in order to increase the absorption rate. However, since it is necessary to ensure the air permeability of the air-conditioning duct, the size of the sound absorbing material is limited, and it is difficult to achieve both high air permeability and soundproof performance.
ここで、換気口および空調用ダクト等の管状部材における騒音として、管状部材の共鳴音が問題となる。特に、最低周波数の共鳴音が問題となる。この共鳴音が８００Ｈｚ以下の場合には、吸音材で防音するためには、吸音材の量が著しく増加してしまう。そのため、通気を犠牲にしたとしても、一般的に十分な防音性能を出すことは難しい。市販品を例にあげると、住宅用換気スリーブの内部に挿入する吸音材タイプの防音製品であるポリエチレン製防音スリーブ（株式会社新協和製 ＳＫ−ＢＯ７５）では、開口率が３６％となり大幅に通気量を低下させるにもかかわらず、８割以上の共鳴音が透過してしまう。
このような管状部材の共鳴音を消音するために、特定の周波数の音を消音する共鳴型の消音器が用いられる。
Here, resonance noise of the tubular member becomes a problem as noise in the tubular member such as the ventilation port and the air conditioning duct. In particular, the resonance sound of the lowest frequency becomes a problem. When the resonance sound is 800 Hz or less, the amount of the sound absorbing material is significantly increased in order to prevent the sound with the sound absorbing material. Therefore, it is generally difficult to provide sufficient soundproofing performance even if the ventilation is sacrificed. Taking a commercially available product as an example, a polyethylene soundproof sleeve (SK-BO75 manufactured by Shin-Kyowa Co., Ltd.), which is a sound-absorbing material type soundproof product to be inserted into a ventilation sleeve for a house, has an opening ratio of 36% and significantly vents air. Even though the amount is reduced, 80% or more of the resonance sound is transmitted.
In order to muffle the resonance sound of such a tubular member, a resonance muffler that muffles the sound of a specific frequency is used.
例えば、特許文献１には、第１空間と第２空間とを仕切る仕切部に、両空間相互の通気を図る通気スリーブが貫通状態に設けられ、通気スリーブの通過音に対する消音を図る共鳴型消音機構が通気スリーブに設けられている通気孔構造であって、共鳴型消音機構は、通気スリーブの筒軸芯方向における仕切部の外の位置で、且つ、仕切部と、仕切部に沿ってその表面から離間する状態に設けられた化粧板との間の位置で、通気スリーブの外周部に形成してある通気孔構造が記載されている。また、共鳴型消音機構として、サイドブランチ型消音器、ヘルムホルツ共鳴器が記載されている。 For example, in patent document 1, a ventilation sleeve that provides ventilation between the two spaces is provided in a partitioning portion that divides the first space and the second space in a penetrating state, and a resonance-type noise suppression that suppresses sound passing through the ventilation sleeve. The mechanism is a ventilation hole structure provided in the ventilation sleeve, wherein the resonance-type sound deadening mechanism is at a position outside the partition in the cylinder axis direction of the ventilation sleeve, and along the partition and the partition. The vent hole structure is formed in the outer peripheral portion of the ventilation sleeve at a position between the ventilation sleeve and the decorative plate provided in a state of being separated from the surface. Further, as the resonance type silencing mechanism, a side branch type silencer and a Helmholtz resonator are described.
また、特許文献２には、自然換気口のスリーブ管内に設置して用いる消音用管状体であって、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、一方の端部から開口部の中心までの長さが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する消音用管状体が記載されている。
また、特許文献２には、住宅、マンション等における外壁の厚さは、２００〜４００ｍｍ程度であり、この外壁に設けられるスリーブ管に生じる第一共鳴周波数（４００〜７００Ｈｚ程度）の周波数帯において遮音性能の低下が生じることが記載されている（特許文献２の図１５参照）。
Further, Patent Document 2 discloses a sound deadening tubular body that is used by being installed in a sleeve pipe of a natural ventilation port, in which at least one end is closed and an opening is provided near the other end, and one end is provided. A silencer tubular body is described in which the length from the portion to the center of the opening is approximately half the total length of the sleeve tube, and a porous material is arranged inside.
Further, in Patent Document 2, the thickness of the outer wall in a house, a condominium, etc. is about 200 to 400 mm, and the sound insulation is performed in the frequency band of the first resonance frequency (about 400 to 700 Hz) generated in the sleeve pipe provided on the outer wall. It is described that the performance is degraded (see FIG. 15 of Patent Document 2).
しかしながら、本発明者らの検討によれば、共鳴型の消音器を用いて、管状部材の最低共鳴周波数の音を消音する場合には、少なくとも共鳴周波数の波長の１／４の長さが必要となり、消音器のサイズが大型化してしまう。そのため、高い通気性と防音性能とを両立することが難しいという問題があった。 However, according to the study by the present inventors, in the case of using the resonance silencer to mute the sound of the lowest resonance frequency of the tubular member, at least ¼ of the wavelength of the resonance frequency is required. Therefore, the size of the silencer becomes large. Therefore, there is a problem that it is difficult to achieve both high air permeability and soundproof performance.
ここで、特許文献１には、消音器を壁と化粧板との間の空間に設置することが記載されている。これにより、通気路を塞ぐことなく、消音器を大型化することができることが記載されている。
しかしながら、共鳴型の消音器は、特定の周波数（周波数帯域）の音を選択的に消音するものである。管状部材の長さおよび形状等が異なると、管状部材の共鳴周波数も変わる。そのため、管状部材に合わせた設計が必要となり、汎用性が低いという問題があった。
Here, Patent Document 1 describes that a silencer is installed in a space between a wall and a decorative plate. It is described that it is possible to increase the size of the silencer without blocking the ventilation path.
However, the resonance-type silencer selectively silences the sound of a specific frequency (frequency band). When the length and shape of the tubular member differ, the resonance frequency of the tubular member also changes. Therefore, a design matching the tubular member is required, and there is a problem that the versatility is low.
また、管状部材の共鳴は複数の周波数で発生するが、共鳴型の消音器は特定の周波数の音を消音する。そのため、消音対象となる共鳴音は１つの周波数のみとなり、共鳴型の消音器が消音する周波数帯域は狭いので、他の周波数の共鳴音は消音できないという問題があった。 Further, the resonance of the tubular member occurs at a plurality of frequencies, but the resonance-type silencer silences the sound of a specific frequency. Therefore, there is a problem that the resonance sound to be silenced is only one frequency and the resonance silencer silences a narrow frequency band, so that the resonance sounds of other frequencies cannot be silenced.
本発明の課題は、上記従来技術の問題点を解消し、高い通気性と防音性能を両立することができ、また、複数の共鳴音を消音することができ、また、設置環境に合わせた設計が不要で汎用性の高い消音システムを提供することを課題とする。 An object of the present invention is to solve the above-mentioned problems of the conventional technology, to achieve both high breathability and soundproofing performance, to mitigate a plurality of resonance sounds, and to design according to the installation environment. It is an object of the present invention to provide a muffler system that does not require and is highly versatile.
本発明者らは、上記課題を解決すべく鋭意検討した結果、壁を貫通して設置された管状部材に、管状部材を通過する音を消音する消音装置が設置された消音システムであって、消音装置は、壁の一方の端面側に配置され、空洞部および空洞部と外部とを連通する開口部を有する１以上の消音器を有し、消音器の開口部の少なくとも１つは、消音システム内における管状部材の第一共鳴の音場空間に接続されており、消音器の空洞部内の少なくとも一部に、または、消音器の開口部の少なくとも一部を覆う位置に、音エネルギーを熱エネルギーに変換する変換機構が配置されており、消音器内の音波の進行方向における空洞部の深さＬdは、管状部材の軸方向における開口部の幅Ｌoよりも大きく、消音装置を含む消音システムにおける管状部材の第一共鳴の共鳴周波数における音波の波長をλとすると、空洞部の深さＬdは、０．０１１×λ＜Ｌd＜０．２５×λを満たし、消音装置は、管状部材の軸方向における消音器の長さを調整可能な長さ調整部を有することにより、上記課題を解決できることを見出し、本発明を完成させた。
すなわち、以下の構成により上記目的を達成することができることを見出した。
As a result of intensive studies to solve the above problems, the present inventors have found that a tubular member installed through a wall is a muffling system in which a muffling device that muffles the sound passing through the tubular member is installed. The silencer includes one or more silencers arranged on one end surface side of the wall and having a cavity and an opening communicating the cavity with the outside, and at least one of the openings of the silencer is a silencer. It is connected to the sound field space of the first resonance of the tubular member in the system and heats the sound energy to at least part of the cavity of the muffler or to a position covering at least part of the opening of the muffler. A conversion mechanism for converting into energy is arranged, and the depth L d of the cavity in the traveling direction of the sound wave in the silencer is larger than the width L o of the opening in the axial direction of the tubular member, and includes the silencer. Tubular member in silence system Suppose that the wavelength of the sound wave at the resonance frequency of the first resonance is λ, the depth L d of the cavity satisfies 0.011 × λ <L d <0.25 × λ, and the muffling device uses the axis of the tubular member. The present invention has been completed by finding that the above problems can be solved by having a length adjusting unit that can adjust the length of the silencer in the direction.
That is, it was found that the above object can be achieved by the following constitution.
［１］ 壁を貫通して設置された管状部材に、管状部材を通過する音を消音する消音装置が設置された消音システムであって、
消音装置は、壁の一方の端面側に配置され、空洞部および空洞部と外部とを連通する開口部を有する１以上の消音器を有し、
消音器の開口部の少なくとも１つは、消音システム内における管状部材の第一共鳴の音場空間に接続されており、
消音器の空洞部内の少なくとも一部に、または、消音器の開口部の少なくとも一部を覆う位置に、音エネルギーを熱エネルギーに変換する変換機構が配置されており、
消音器内の音波の進行方向における空洞部の深さＬdは、管状部材の軸方向における開口部の幅Ｌoよりも大きく、
消音装置を含む消音システムにおける管状部材の第一共鳴の共鳴周波数における音波の波長をλとすると、空洞部の深さＬdは、０．０１１×λ＜Ｌd＜０．２５×λを満たし、
消音装置は、管状部材の軸方向における消音器の長さを調整可能な長さ調整部を有する消音システム。
［２］ 壁の一方の面側に壁と平行に化粧板が配置されており、
消音装置は、壁と化粧板との間に配置され、
管状部材の軸方向における消音器の長さは、長さ調整部によって、壁と化粧板との間の距離に合わせて調整されている［１］に記載の消音システム。
［３］ 消音装置は、複数の消音器を有し、
複数の消音器は、管状部材の軸方向に配列されており、
軸方向に配列された消音器の合計長さが、長さ調整部によって、壁と化粧板との間の距離に合わせて調整されている［２］に記載の消音システム。
［４］ 長さ調整部は、軸方向に配列された消音器それぞれの長さを調整可能である［３］に記載の消音システム。
［５］ 管状部材の軸方向に平行な断面において、消音器は、軸方向に延在する空洞部と、空洞部の軸方向に平行な面の、軸方向の一方の端部側に開口部を有するＬ字型の形状を有し、
軸方向における空洞部の長さが、空洞部の深さＬdである［１］〜［４］のいずれかに記載の消音システム。
［６］ 消音器の開口部は、管状部材の中心軸側を向いて配置されている［１］〜［５］のいずれかに記載の消音システム。
［７］ 消音装置は、管状部材に接続される筒状の挿入部を有し、
挿入部は、中心軸を管状部材の中心軸に一致させて配置されており、
消音器は、挿入部の一方の端面に接続されている［１］〜［６］のいずれかに記載の消音システム。
［８］ 管状部材の軸方向に平行な断面において、空洞部の深さ方向に直交する方向の空洞部の幅Ｌwは、０．００１×λ＜Ｌw＜０．０６１×λを満たす［１］〜［７］のいずれかに記載の消音システム。
［９］ 変換機構は、吸音材であり、
吸音材の流れ抵抗σ1は、（１．２５−ｌｏｇ（０．１×Ｌd））／０．２４＜ｌｏｇ（σ1）＜５．６を満たす［１］〜［８］のいずれかに記載の消音システム。
［１０］ 消音器の空洞部は、管状部材の中心軸に垂直な断面で見た際に、円環状であり、
消音器の開口部は、空洞部の周方向に沿ってスリット状に形成されている［１］〜［９］のいずれかに記載の消音システム。
［１１］ 管状部材のいずれか一方の端部に設置されるカバー部材と、
管状部材の他方の端部に設置される風量調整部材と、を有し、
消音装置、カバー部材および風量調整部材を含む消音システムにおける管状部材の第一共鳴の共鳴周波数における音波の波長をλとすると、空洞部の深さＬdはλ／４よりも短い［１］〜［１０］のいずれかに記載の消音システム。
[1] A muffling system in which a muffling device that muffles sound passing through a tubular member is installed on a tubular member that is installed through a wall,
The silencer includes one or more silencers arranged on one end surface side of the wall and having a cavity and an opening communicating the cavity with the outside,
At least one of the openings of the silencer is connected to the sound field space of the first resonance of the tubular member in the silencer system,
At least a part of the cavity of the silencer, or at a position that covers at least a part of the opening of the silencer, a conversion mechanism for converting sound energy into heat energy is arranged,
The depth L d of the hollow portion in the traveling direction of the sound wave in the silencer is larger than the width L o of the opening portion in the axial direction of the tubular member,
When the wavelength of the sound wave at the resonance frequency of the first resonance of the tubular member in the sound deadening system including the sound deadening device is λ, the depth L d of the cavity satisfies 0.011 × λ <L d <0.25 × λ. ,
The silencer is a silencer system having a length adjuster capable of adjusting the length of the silencer in the axial direction of the tubular member.
[2] A decorative plate is arranged parallel to the wall on one side of the wall,
The silencer is arranged between the wall and the decorative board,
The silencer system according to [1], wherein the length of the silencer in the axial direction of the tubular member is adjusted by the length adjusting unit according to the distance between the wall and the decorative plate.
[3] The silencer has a plurality of silencers,
The plurality of silencers are arranged in the axial direction of the tubular member,
The silencer system according to [2], wherein the total length of the silencers arranged in the axial direction is adjusted by the length adjusting unit according to the distance between the wall and the decorative plate.
[4] The silencer system according to [3], wherein the length adjusting unit is capable of adjusting the length of each silencer arranged in the axial direction.
[5] In a cross section parallel to the axial direction of the tubular member, the muffler includes a cavity extending in the axial direction and an opening on one end side in the axial direction of a plane parallel to the axial direction of the cavity. Has an L-shape with
The sound deadening system according to any one of [1] to [4], wherein the length of the hollow portion in the axial direction is the depth L d of the hollow portion.
[6] The muffling system according to any one of [1] to [5], in which the opening of the silencer faces the central axis of the tubular member.
[7] The silencer has a tubular insertion portion connected to the tubular member,
The insertion portion is arranged with its central axis aligned with the central axis of the tubular member,
The silencer is the silencer system according to any one of [1] to [6], which is connected to one end surface of the insertion portion.
[8] In the cross section parallel to the axial direction of the tubular member, the width L w of the hollow portion in the direction orthogonal to the depth direction of the hollow portion satisfies 0.001 × λ <L w <0.061 × λ [ The silencing system according to any one of 1] to [7].
[9] The conversion mechanism is a sound absorbing material,
The flow resistance σ 1 of the sound absorbing material is any one of [1] to [8] satisfying (1.25-log (0.1 × L d )) / 0.24 <log (σ 1 ) <5.6. Silence system described in.
[10] The hollow part of the silencer has an annular shape when viewed in a cross section perpendicular to the central axis of the tubular member,
The muffling system according to any one of [1] to [9], in which the opening of the silencer is formed in a slit shape along the circumferential direction of the cavity.
[11] A cover member installed at one end of the tubular member,
An air volume adjusting member installed at the other end of the tubular member,
When the wavelength of the sound wave at the resonance frequency of the first resonance of the tubular member in the muffling system including the muffling device, the cover member, and the air volume adjusting member is λ, the depth L d of the cavity is shorter than λ / 4 [1] to The muffling system according to any one of [10].
本発明によれば、高い通気性と防音性能を両立することができ、また、複数の共鳴音を消音することができ、また、設置環境に合わせた設計が不要で汎用性の高い消音システムを提供することができる。 According to the present invention, it is possible to achieve both high breathability and soundproofing performance, it is also possible to mute a plurality of resonance sounds, and a highly versatile muffling system that does not require a design according to the installation environment. Can be provided.
以下、本発明について詳細に説明する。
以下に記載する構成要件の説明は、本発明の代表的な実施態様に基づいてなされるが、本発明はそのような実施態様に限定されるものではない。
なお、本明細書において、「〜」を用いて表される数値範囲は、「〜」の前後に記載される数値を下限値および上限値として含む範囲を意味する。
また、本明細書において、「直交」および「平行」とは、本発明が属する技術分野において許容される誤差の範囲を含むものとする。例えば、「直交」および「平行」とは、厳密な直交あるいは平行に対して±１０°未満の範囲内であることなどを意味し、厳密な直交あるいは平行に対しての誤差は、５°以下であることが好ましく、３°以下であることがより好ましい。
本明細書において、「同一」、「同じ」は、技術分野で一般的に許容される誤差範囲を含むものとする。また、本明細書において、「全部」、「いずれも」または「全面」などというとき、１００％である場合のほか、技術分野で一般的に許容される誤差範囲を含み、例えば９９％以上、９５％以上、または９０％以上である場合を含むものとする。
Hereinafter, the present invention will be described in detail.
The description of the constituents described below is given based on the typical embodiment of the present invention, but the present invention is not limited to such embodiment.
In addition, in this specification, the numerical range represented using "-" means the range which includes the numerical values described before and after "-" as a lower limit and an upper limit.
Further, in the present specification, the terms “orthogonal” and “parallel” include the range of error allowed in the technical field to which the present invention belongs. For example, “orthogonal” and “parallel” mean that the angle is within ± 10 ° with respect to the exact orthogonal or parallel, and the error with respect to the exact orthogonal or parallel is 5 ° or less. Is preferable, and more preferably 3 ° or less.
In the present specification, “identical” and “identical” include an error range generally accepted in the technical field. Further, in the present specification, when referring to “all”, “any” or “entire surface” and the like, in addition to the case of 100%, the error range generally accepted in the technical field is included, for example, 99% or more, The case where it is 95% or more, or 90% or more is included.
［消音システム］
本発明の消音システムの構成について、図面を用いて説明する。
図１は、本発明の消音システムの好適な実施態様の一例を示す模式的な断面図である。
[Silent system]
The configuration of the silencing system of the present invention will be described with reference to the drawings.
FIG. 1 is a schematic sectional view showing an example of a preferred embodiment of the silencing system of the present invention.
図１に示すように、消音システム１０ａは、２つの空間を隔てる壁１６を貫通して設けられる、円筒状の管状部材１２の一方の端面側に、管状部材１２を通過する音を消音する消音装置１４が設置された構成を有する。 As shown in FIG. 1, the muffling system 10a is a muffler that silences a sound passing through the tubular member 12 on one end surface side of a cylindrical tubular member 12 that is provided to penetrate a wall 16 that separates two spaces. The device 14 is installed.
マンション等の住宅の壁は、例えば、コンクリート壁、石膏ボード、断熱材、化粧板、および、壁紙等を有して構成されており、これらを貫通して、例えば、換気口および空調用ダクト等の通気スリーブが設けられている。
コンクリート壁が、本発明における壁１６に相当し、換気口および空調用ダクト等の通気スリーブが、本発明における管状部材１２に相当する。
The wall of a house such as a condominium is configured to have, for example, a concrete wall, a gypsum board, a heat insulating material, a decorative board, and a wallpaper, and penetrates through these, for example, a ventilation port and an air conditioning duct. A ventilation sleeve is provided.
The concrete wall corresponds to the wall 16 in the present invention, and the ventilation sleeves such as the ventilation port and the air conditioning duct correspond to the tubular member 12 in the present invention.
図１に示すように、壁１６の一方の面側には、壁１６から所定距離離間して、壁１６と平行に化粧板４０が配置される。消音装置１４は、壁１６と化粧板４０の間に設置される。
また、消音装置１４の化粧板４０側には、風量調整部材２０が設置されている。風量調整部材２０は、従来公知のレジスター等である。
As shown in FIG. 1, on one surface side of the wall 16, a decorative plate 40 is arranged in parallel with the wall 16 at a predetermined distance from the wall 16. The silencer 14 is installed between the wall 16 and the decorative plate 40.
An air volume adjusting member 20 is installed on the decorative plate 40 side of the silencer 14. The air volume adjusting member 20 is a conventionally known register or the like.
消音装置１４は、挿入部２６と消音器２２とを有する。挿入部２６は、両端が開放された筒状の部材で、一方の端面に消音器２２が接続されている。また、挿入部２６の外径は、管状部材１２の内径と略同等で、管状部材１２内に挿入されている。すなわち、挿入部２６は、挿入部２６の中心軸を管状部材１２の中心軸と一致させて管状部材内に挿入されている。 The silencer 14 has an insertion portion 26 and a silencer 22. The insertion portion 26 is a tubular member whose both ends are open, and the silencer 22 is connected to one end surface of the insertion portion 26. The outer diameter of the insertion portion 26 is substantially the same as the inner diameter of the tubular member 12, and is inserted into the tubular member 12. That is, the insertion section 26 is inserted into the tubular member with the central axis of the insertion section 26 aligned with the central axis of the tubular member 12.
図２に、消音器２２の、管状部材１２の軸方向（以下、単に軸方向ともいう）に垂直な断面図を示す。
消音器２２は、軸方向に平行な断面において、軸方向に延在し、管状部材１２の外周面に沿って湾曲した略直方体形状で、内部に軸方向に延在する空洞部３０を有する。図２に示すように、空洞部３０は、軸方向に垂直な断面で見た際に円環状である。
また、消音器２２の管状部材１２側の面の、軸方向の一方の端部側には、空洞部３０と外部とを連通する開口部３２を有する。開口部３２は、周面方向に沿ったスリット状である。
すなわち、消音器２２は、軸方向に平行な断面において、Ｌ字型の空間を有する。開口部３２は挿入部２６の中心軸（管状部材１２の中心軸）を向くように配置されている。これにより、開口部３２は、消音システム１０ａにおける管状部材１２内に生じる第一共鳴の音場空間に接続されている。音場空間については後に説明する。
なお、以下の説明において、図１に示すようなＬ字型の空間を有する消音器２２をＬ字型の消音器ともいう。
FIG. 2 shows a cross-sectional view of the silencer 22 perpendicular to the axial direction of the tubular member 12 (hereinafter, also simply referred to as axial direction).
The silencer 22 has a substantially rectangular parallelepiped shape that extends in the axial direction and curves along the outer peripheral surface of the tubular member 12 in a cross section parallel to the axial direction, and has a hollow portion 30 that extends in the axial direction inside. As shown in FIG. 2, the hollow portion 30 has an annular shape when viewed in a cross section perpendicular to the axial direction.
Further, an opening 32 that communicates the cavity 30 with the outside is provided on one end side of the silencer 22 on the tubular member 12 side in the axial direction. The opening 32 has a slit shape along the circumferential surface direction.
That is, the muffler 22 has an L-shaped space in a cross section parallel to the axial direction. The opening 32 is arranged so as to face the central axis of the insertion portion 26 (the central axis of the tubular member 12). Thereby, the opening 32 is connected to the sound field space of the first resonance generated in the tubular member 12 of the silencing system 10a. The sound field space will be described later.
In the following description, the muffler 22 having the L-shaped space as shown in FIG. 1 is also referred to as an L-shaped muffler.
ここで、図１に示すように、消音器２２は、第１部材２１ａおよび第２部材２１ｂにより構成されている。本発明においては、第１部材２１ａと第２部材２１ｂとの軸方向の相対位置を調整することで、消音器２２の軸方向の長さを調整することができる。 Here, as shown in FIG. 1, the silencer 22 includes a first member 21a and a second member 21b. In the present invention, the axial length of the silencer 22 can be adjusted by adjusting the relative positions of the first member 21a and the second member 21b in the axial direction.
図３に、第１部材２１ａの斜視図を示す。図４に、第２部材２１ｂの斜視図を示す。
図３に示すように、第１部材２１ａは、一方の側面（底面）が開放された円筒状の外周部１０２と外周部１０２の他方の側面に配置される底面部１００とを有する。底面部１００の外周部１０２とは反対側の面の中心には挿入部２６が接続されており、挿入部２６の内径と同じ直径の開口が形成されている。外周部１０２の中心軸と挿入部２６の中心軸は一致する。
図１に示すように、第１部材２１ａの外周部１０２の内径は、管状部材１２の内径よりも大きい。
FIG. 3 shows a perspective view of the first member 21a. FIG. 4 shows a perspective view of the second member 21b.
As shown in FIG. 3, the first member 21a has a cylindrical outer peripheral portion 102 whose one side surface (bottom surface) is open, and a bottom surface portion 100 arranged on the other side surface of the outer peripheral portion 102. The insertion portion 26 is connected to the center of the surface of the bottom surface portion 100 opposite to the outer peripheral portion 102, and an opening having the same diameter as the inner diameter of the insertion portion 26 is formed. The central axis of the outer peripheral portion 102 and the central axis of the insertion portion 26 coincide with each other.
As shown in FIG. 1, the inner diameter of the outer peripheral portion 102 of the first member 21 a is larger than the inner diameter of the tubular member 12.
図４に示すように、第２部材２１ｂは、一方の側面が開放された円筒状の外周部１０６と、外周部１０６の内径よりも外径が小さく、外周部１０６と同心円状に配置される円筒状の内周部１０４と、外周部１０６および内周部１０４の他方の側面の外周部１０６と内周部１０４との間を閉塞する底面部１０８とを有する。外周部１０６の他方の側面と内周部１０４の他方の側面は、面一に配置されている。外周部１０６の底面部１０８からの高さ（軸方向の長さ）は、内周部１０４の高さよりも高い。
図１に示すように、第２部材２１ｂの外周部１０６の内径は、第１部材２１ａの外周部１０２の外径よりも大きい（略同じである）。また、内周部１０４の内径は、挿入部２６の内径と略同じである。また、内周部１０４の高さは、第１部材２１ａの外周部１０２の高さ（軸方向の長さ）よりも低い。
As shown in FIG. 4, the second member 21b is arranged in a concentric circle with the outer peripheral portion 106, which has a cylindrical outer peripheral portion 106 with one side surface open and whose outer diameter is smaller than the inner diameter of the outer peripheral portion 106. It has a cylindrical inner peripheral portion 104, an outer peripheral portion 106, and a bottom surface portion 108 that closes between the outer peripheral portion 106 and the inner peripheral portion 104 on the other side surface of the inner peripheral portion 104. The other side surface of the outer peripheral portion 106 and the other side surface of the inner peripheral portion 104 are arranged flush with each other. The height (axial length) of the outer peripheral portion 106 from the bottom surface portion 108 is higher than the height of the inner peripheral portion 104.
As shown in FIG. 1, the inner diameter of the outer peripheral portion 106 of the second member 21b is larger than the outer diameter of the outer peripheral portion 102 of the first member 21a (substantially the same). Further, the inner diameter of the inner peripheral portion 104 is substantially the same as the inner diameter of the insertion portion 26. The height of the inner peripheral portion 104 is lower than the height (axial length) of the outer peripheral portion 102 of the first member 21a.
このような形状の第１部材２１ａおよび第２部材２１ｂは、図１に示すように、第１部材２１ａの外周部１０２を、外周部１０２の開放面側から第２部材２１ｂの外周部１０６と内周部１０４との間に挿入されて、第１部材２１ａの底面部１００と外周部１０２と第２部材２１ｂの底面部１０８と内周部１０４とに囲まれた空間である空洞部３０、および、第１部材２１ａの底面部１００と第２部材２１ｂの内周部１０４との間隙である開口部３２を有する消音器２２を形成している。
図１に示す例では、第１部材２１ａの外周部１０２の開放面側の端面が第２部材２１ｂの底面部１０８に突き当たる状態にされている。第２部材２１ｂの内周部１０４の高さは、第１部材２１ａの外周部１０２の高さよりも低いので、第２部材２１ｂの内周部１０４の端面と第１部材２１ａの底面部１００は離間した状態となるため開口部３２が形成される。
すなわち、図１に示す例は、消音器２２の長さが最も短くなった状態である。以下、この状態を第１の状態ともいう。
In the first member 21a and the second member 21b having such a shape, as shown in FIG. 1, the outer peripheral portion 102 of the first member 21a is connected to the outer peripheral portion 106 of the second member 21b from the open surface side of the outer peripheral portion 102. A cavity 30, which is a space inserted between the inner peripheral portion 104 and the bottom surface portion 100 of the first member 21a, the outer peripheral portion 102, the bottom surface portion 108 of the second member 21b, and the inner peripheral portion 104, Further, the silencer 22 having the opening 32 which is a gap between the bottom surface portion 100 of the first member 21a and the inner peripheral portion 104 of the second member 21b is formed.
In the example shown in FIG. 1, the end surface on the open surface side of the outer peripheral portion 102 of the first member 21a abuts the bottom surface portion 108 of the second member 21b. Since the height of the inner peripheral portion 104 of the second member 21b is lower than the height of the outer peripheral portion 102 of the first member 21a, the end surface of the inner peripheral portion 104 of the second member 21b and the bottom surface portion 100 of the first member 21a are Since they are separated from each other, the opening 32 is formed.
That is, in the example shown in FIG. 1, the silencer 22 has the shortest length. Hereinafter, this state is also referred to as a first state.
ここで、前述のとおり、第１部材２１ａと第２部材２１ｂとの軸方向の相対位置を調整することで、消音器２２の軸方向の長さを調整することができる。
図５に、消音器２２の長さを伸ばした状態の消音システム１０ｂを示す。以下、図５に示す状態を第２の状態ともいう。
Here, as described above, the axial length of the muffler 22 can be adjusted by adjusting the relative positions of the first member 21a and the second member 21b in the axial direction.
FIG. 5 shows the muffling system 10b in a state where the length of the muffler 22 is extended. Hereinafter, the state shown in FIG. 5 is also referred to as the second state.
図５に示す消音システム１０ｂでは、壁１６と化粧板４０との距離が、図１の例と比較して長い。従って、消音装置１４は、壁１６と化粧板４０との間の距離に合わせて消音器２２の長さを調整されている。 In the muffling system 10b shown in FIG. 5, the distance between the wall 16 and the decorative plate 40 is longer than that in the example of FIG. Therefore, in the muffler 14, the length of the muffler 22 is adjusted according to the distance between the wall 16 and the decorative plate 40.
具体的には、図５に示すように、第１部材２１ａの外周部１０２の開放面側の端面と、第２部材２１ｂの底面部１０８との間に、両側面が開放された円筒状のスペーサー２１ｃが設置されている。スペーサー２１ｃは、内径および外径が第１部材２１ａの外周部１０２と略同じである。また、スペーサー２１ｃの高さ（軸方向の長さ）は壁１６と化粧板４０との間の距離に応じて適宜選択される。
第１部材２１ａ、第２部材２１ｂおよびスペーサー２１ｃは、本発明における長さ調整部に相当する。
Specifically, as shown in FIG. 5, between the end surface of the outer peripheral portion 102 of the first member 21a on the open surface side and the bottom surface portion 108 of the second member 21b, both side surfaces are open. The spacer 21c is installed. The spacer 21c has substantially the same inner diameter and outer diameter as the outer peripheral portion 102 of the first member 21a. Further, the height (length in the axial direction) of the spacer 21c is appropriately selected according to the distance between the wall 16 and the decorative plate 40.
The 1st member 21a, the 2nd member 21b, and the spacer 21c are equivalent to the length adjustment part in this invention.
なお、本発明において、『消音装置が壁と化粧板との間に配置される』とは、軸方向において、少なくとも消音器の２／３以上が、壁と化粧板との間に存在することを言う。従って、図１に示すように、消音器２２の一部が化粧板４０を貫通していてもよい。さらに、消音器２２の一部が、化粧板４０の、壁１６とは反対側の空間に存在していてもよい。また、消音装置１４の消音器２２以外の部位が、壁と化粧板との間以外の空間に存在していてもよい。例えば、図１に示す例では、消音装置１４は挿入部２６を有し、挿入部２６は、管状部材１２内に配置される。 In the present invention, "the silencer is arranged between the wall and the decorative plate" means that at least 2/3 or more of the silencer is present between the wall and the decorative plate in the axial direction. Say Therefore, as shown in FIG. 1, a part of the muffler 22 may penetrate the decorative plate 40. Furthermore, a part of the muffler 22 may be present in the space of the decorative plate 40 opposite to the wall 16. Further, the parts other than the muffler 22 of the muffling device 14 may be present in a space other than between the wall and the decorative plate. For example, in the example shown in FIG. 1, the muffling device 14 has an insertion portion 26, and the insertion portion 26 is arranged inside the tubular member 12.
第１部材２１ａと第２部材２１ｂとの間にスペーサー２１ｃを配置した第２の状態では、第１部材２１ａの底面部１００から第２部材２１ｂの底面部１０８までの距離が、第１の状態の場合に比べて長くなる。すなわち、第２の状態における消音器２２の軸方向の長さが第１の状態に比べて長くなり、また、空洞部３０の体積が大きくなる。
このように、消音器２２の長さを調整可能とすることで、壁１６と化粧板４０との間の距離に応じて消音器２２の長さ（空洞部３０の体積）を最大化することができる。
共鳴型の消音器の場合には、消音器の長さを変えると消音できる周波数帯域が変化してしまう。これに対して、後に詳述するが、本発明における消音器２２は、共鳴によって吸音するものではなく、吸収によって吸音するものである。そのため、消音器２２の長さを変えても吸音する周波数帯が変わることなく、広い周波数帯域で吸音することができる。また、空洞部３０の体積が大きいと防音性能が高くなる。
従って、本発明の消音システムにおいては、設置する空間に合わせて消音器２２の長さを変えて簡単に設置できる。また、その際、消音性能を最大化するようにすることもできる。例えば、壁１６と化粧板４０との間の距離が異なる、種々の構成の壁に対して、壁１６と化粧板４０との間の距離に応じて、消音器２２の長さを変えることで種々の構成の壁に設置することが可能である。また、その際、空洞部３０の体積を最大化することによって、消音器２２による防音性能を最大化することができる。また、消音器２２の内部に配置する吸音材２４の大きさを調整した消音器２２の長さに合わせて変更することによって、防音性能をより高くすることができる。
すなわち、本発明の消音システムは、設置環境に合わせた設計が不要で汎用性が高い。
In the second state in which the spacer 21c is arranged between the first member 21a and the second member 21b, the distance from the bottom surface portion 100 of the first member 21a to the bottom surface portion 108 of the second member 21b is the first state. It will be longer than in the case of. That is, the length in the axial direction of the muffler 22 in the second state is longer than that in the first state, and the volume of the cavity 30 is large.
In this way, by making the length of the silencer 22 adjustable, the length of the silencer 22 (volume of the cavity 30) is maximized according to the distance between the wall 16 and the decorative plate 40. You can
In the case of a resonance-type silencer, changing the length of the silencer changes the frequency range in which the silence can be performed. On the other hand, as described later in detail, the muffler 22 of the present invention does not absorb sound by resonance but absorbs sound by absorption. Therefore, even if the length of the silencer 22 is changed, the frequency band to be absorbed does not change, and the sound can be absorbed in a wide frequency band. Further, if the volume of the hollow portion 30 is large, the soundproof performance is improved.
Therefore, in the muffling system of the present invention, the length of the muffler 22 can be changed according to the space where the muffler is installed, and the muffler 22 can be easily installed. Further, at that time, the silencing performance can be maximized. For example, by changing the length of the muffler 22 according to the distance between the wall 16 and the decorative plate 40 for walls having various configurations in which the distance between the wall 16 and the decorative plate 40 is different. It can be installed on walls of various configurations. Further, at that time, by maximizing the volume of the cavity 30, the soundproof performance of the silencer 22 can be maximized. Further, by changing the size of the sound absorbing material 24 arranged inside the muffler 22 according to the length of the muffler 22, the soundproofing performance can be further enhanced.
That is, the silencing system of the present invention does not need to be designed according to the installation environment and is highly versatile.
空洞部３０内には、吸音材２４が配置されている。吸音材２４は、本発明における、音エネルギーを熱エネルギーに変換する変換機構である。なお、変換機構としては、吸音材２４に限定はされず、消音器２２の壁面近傍における流体の粘性、壁面の凹凸（表面粗さ）、および、微細な貫通孔を複数有するシート状の微細穿孔板等であってもよい。 The sound absorbing material 24 is arranged in the hollow portion 30. The sound absorbing material 24 is a conversion mechanism for converting sound energy into heat energy in the present invention. The converting mechanism is not limited to the sound absorbing material 24, and the viscosity of the fluid in the vicinity of the wall surface of the silencer 22, the unevenness (surface roughness) of the wall surface, and the sheet-shaped fine perforation having a plurality of fine through holes. It may be a plate or the like.
図６に、消音器の空洞部の深さＬdと幅Ｌwと、開口部の幅Ｌoを説明するための図を示す。
本発明においては、図６に示すように、消音器２２の空洞部３０内の音波の進行方向における空洞部３０の深さをＬdとし、管状部材１２の軸方向（以下、単に軸方向ともいう）における消音器２２の開口部３２の幅をＬoとすると、空洞部３０の深さＬdは、開口部３２の幅Ｌoよりも大きい。
空洞部３０内の音波の進行方向は、シミュレーションにより求めることができる。図６に示す例においは、空洞部３０は軸方向に延在しているため、空洞部３０内の音波の進行方向は軸方向（図中左右方向）である。従って、空洞部３０の深さＬdは、軸方向における開口部３２の中心位置から空洞部３０の遠い側の端面までの長さである。なお、位置によって空洞部３０の深さが異なる場合には、空洞部３０の深さＬdは、各位置での深さの平均値である。また、位置によって開口部３２の幅が異なる場合には、開口部３２の幅Ｌoは、各位置での幅の平均値である。
FIG. 6 is a diagram for explaining the depth L d and width L w of the cavity of the silencer and the width L o of the opening.
In the present invention, as shown in FIG. 6, the depth of the hollow portion 30 in the traveling direction of the sound wave in the hollow portion 30 of the silencer 22 is L d, and the axial direction of the tubular member 12 (hereinafter, simply referred to as the axial direction). When the width of the opening 32 of the muffler 22 in () is set to L o , the depth L d of the cavity 30 is larger than the width L o of the opening 32.
The traveling direction of the sound wave in the cavity 30 can be obtained by simulation. In the example shown in FIG. 6, since the hollow portion 30 extends in the axial direction, the traveling direction of the sound waves in the hollow portion 30 is the axial direction (the horizontal direction in the drawing). Therefore, the depth L d of the cavity 30 is the length from the center position of the opening 32 in the axial direction to the end surface of the cavity 30 on the far side. In addition, when the depth of the cavity 30 differs depending on the position, the depth L d of the cavity 30 is an average value of the depths at the respective positions. When the width of the opening 32 differs depending on the position, the width L o of the opening 32 is an average value of the widths at the respective positions.
また、消音システム１０ａ内における管状部材１２内に生じる第一共鳴の共鳴周波数における音波の波長をλ（ｍｍ）とすると、消音器２２の空洞部３０の深さＬd（ｍｍ）は、０．０１１×λ＜Ｌd＜０．２５×λを満たす。すなわち、空洞部３０の深さはＬdは、λ／４よりも小さく、消音器２２は、共鳴によって消音するものではない。 When the wavelength of the sound wave at the resonance frequency of the first resonance generated in the tubular member 12 in the silencer system 10a is λ (mm), the depth L d (mm) of the cavity 30 of the silencer 22 is 0. 011 × λ <L d <0.25 × λ is satisfied. That is, the cavity 30 has a depth L d smaller than λ / 4, and the muffler 22 does not muffle by resonance.
前述のとおり、共鳴型の消音器を用いて管状部材の最低共鳴周波数の音を消音する場合には、少なくとも共鳴周波数の波長λの１／４の長さが必要となり、消音器のサイズが大型化してしまう。そのため、高い通気性と防音性能とを両立することが難しいという問題があった。
また、共鳴型の消音器は、特定の周波数（周波数帯域）の音を選択的に消音するものである。そのため、管状部材の共鳴周波数に合わせた設計が必要となり、汎用性が低いという問題があった。
また、管状部材の共鳴は複数の周波数で発生するが、共鳴型の消音器は特定の周波数の音を消音する。そのため、消音対象となる共鳴音は１つの周波数のみとなり、また、共鳴型の消音器が消音する周波数帯域は狭いので、他の周波数の共鳴音は消音できないという問題があった。
As described above, when the sound of the lowest resonance frequency of the tubular member is silenced by using the resonance type silencer, at least 1/4 of the wavelength λ of the resonance frequency is required, and the size of the silencer is large. Will turn into. Therefore, there is a problem that it is difficult to achieve both high air permeability and soundproof performance.
Further, the resonance-type silencer selectively silences a sound of a specific frequency (frequency band). Therefore, it is necessary to design the tubular member according to the resonance frequency, and there is a problem that the versatility is low.
Further, the resonance of the tubular member occurs at a plurality of frequencies, but the resonance-type silencer silences the sound of a specific frequency. Therefore, there is a problem that the resonance sound to be silenced has only one frequency, and the resonance silencer silences a narrow frequency band, so that the resonance sounds of other frequencies cannot be silenced.
これに対して、本発明は、空洞部３０と開口部３２とを有し、消音器内の音波の進行方向における空洞部３０の深さＬdが、管状部材の軸方向における開口部の幅Ｌoよりも大きく、管状部材１２の第一共鳴の共鳴周波数における音波の波長をλとすると、空洞部の深さＬdが、０．０１１×λ＜Ｌd＜０．２５×λを満たす消音器２１を、管状部材１２の第一共鳴の音場空間に接続して配置する構成とする。 On the other hand, in the present invention, the cavity 30 and the opening 32 are provided, and the depth L d of the cavity 30 in the traveling direction of the sound wave in the silencer is the width of the opening in the axial direction of the tubular member. When the wavelength of the sound wave that is larger than L o and is at the resonance frequency of the first resonance of the tubular member 12 is λ, the cavity depth L d satisfies 0.011 × λ <L d <0.25 × λ. The silencer 21 is connected to the sound field space of the first resonance of the tubular member 12 and arranged.
ここで、消音器２２の開口部３２の幅Ｌoが空洞部３０の深さＬdよりも小さいことによって、管状部材１２内の音波が消音器２２内に流入する際に、音圧を保ったまま気体（空気）分子の移動速度が速くなる。変換機構による音エネルギーから熱エネルギーへの変換効率は、音圧および気体分子の移動速度に依存する。そのため、音圧を保ったまま気体分子の移動速度が速くなることによって、変換機構による音エネルギーから熱エネルギーへの変換効率が高くなる。
この消音の原理は消音器の共鳴を利用しないので、空洞部３０の深さＬdが管状部材１２の第一共鳴の共鳴周波数における波長λの１／４よりも小さくても、高い防音性能を発現することができる。従って、消音器２２を小型化して管状部材１２の通気性を維持しつつ、高い防音性能を得ることができる。
Here, since the width L o of the opening 32 of the muffler 22 is smaller than the depth L d of the hollow portion 30, the sound pressure is maintained when the sound wave in the tubular member 12 flows into the muffler 22. The moving speed of gas (air) molecules increases as it is. The conversion efficiency from sound energy to heat energy by the conversion mechanism depends on the sound pressure and the moving speed of gas molecules. Therefore, the moving speed of the gas molecules is increased while maintaining the sound pressure, so that the conversion efficiency of the sound energy into the heat energy by the conversion mechanism is increased.
Since the principle of this muffling does not utilize the resonance of the muffler, even if the depth L d of the cavity 30 is smaller than ¼ of the wavelength λ at the resonance frequency of the first resonance of the tubular member 12, high soundproof performance is obtained. Can be expressed. Therefore, it is possible to reduce the size of the silencer 22 and maintain the air permeability of the tubular member 12, while obtaining high soundproof performance.
また、消音器２２による消音の原理は、音圧の大きさに依存するので、管状部材１２の長さおよび形状等が異なって、問題となる音圧の大きな音波の波長が異なる場合でも、その問題の波長の音波に対して高い防音性能を発現することができ、共鳴型消音器のような管状部材１２に合わせた共鳴構造設計が不要であり汎用性が高い。
また、消音器２２による消音の原理は消音器の共鳴が主要な消音原理ではないので、広い周波数帯域の音を消音することができる。
Further, since the principle of silencing by the silencer 22 depends on the magnitude of sound pressure, even if the length and shape of the tubular member 12 are different and the wavelength of a sound wave having a large sound pressure is different, High sound insulation performance can be exhibited for sound waves of the wavelength in question, and there is no need for a resonance structure design matching the tubular member 12 such as a resonance silencer, which is highly versatile.
Further, since the principle of silencing by the muffler 22 is not the main silencing principle due to resonance of the muffler, it is possible to mute sounds in a wide frequency band.
また、前述のとおり、消音器２２による消音の原理は、管状部材１２内の音波が消音器２２内に流入する際に、音圧を保ったまま気体（空気）分子の移動速度が速くなることを利用して変換機構による音エネルギーから熱エネルギーへの変換効率を高めるものである。従って、消音器２２の長さを変えても共鳴型のように強く吸音する周波数帯が急激に変わることなく、広い周波数帯域で吸音することができる。また、空洞部３０の体積が大きいと防音性能が高くなる。従って、壁１６と化粧板４０との間の距離が異なる、種々の構成の壁に対して、壁１６と化粧板４０との間の距離に応じて、空洞部３０の体積を最大化して、消音器２２による防音性能を最大化することができる。すなわち、設置環境に合わせた設計が不要で汎用性が高い。 Further, as described above, the principle of silencing by the muffler 22 is that when sound waves in the tubular member 12 flow into the muffler 22, the moving speed of gas (air) molecules increases while maintaining the sound pressure. Is used to increase the conversion efficiency of sound energy into heat energy by the conversion mechanism. Therefore, even if the length of the muffler 22 is changed, a strongly absorbing frequency band unlike the resonance type does not suddenly change, and sound can be absorbed in a wide frequency band. Further, if the volume of the hollow portion 30 is large, the soundproof performance is improved. Therefore, for walls having various configurations in which the distance between the wall 16 and the decorative plate 40 is different, the volume of the cavity 30 is maximized according to the distance between the wall 16 and the decorative plate 40, The soundproof performance of the muffler 22 can be maximized. That is, there is no need to design according to the installation environment, and the versatility is high.
また、消音器２２をＬ字型の空間を有する形状とすることで、消音器２２の実効外径、すなわち、消音システムの外径をより小さくすることができる。なお、実効外径は、円相当直径であり、断面が円形ではない場合、その断面積と同じ円の直径を実効外径とした。 Further, by forming the silencer 22 into a shape having an L-shaped space, it is possible to further reduce the effective outer diameter of the silencer 22, that is, the outer diameter of the silencer system. The effective outer diameter is the equivalent circle diameter, and when the cross section is not circular, the diameter of the circle having the same cross-sectional area was taken as the effective outer diameter.
ここで、消音システム１０ａ内における管状部材１２の第一共鳴の音場空間について図７を用いて説明する。
図７は、２つの空間を隔てる壁１６を貫通して設けられる管状部材１２の第一共鳴モードにおける音圧の分布をシミュレーションによって求めたものである。図７からわかるように、管状部材１２の第一共鳴の音場空間は、管状部材１２内、および、開口端補正距離内の空間である。周知のとおり、開口端補正の距離だけ音場の定在波の腹が管状部材１２の外側にはみ出している。なお、円筒形の管状部材１２の場合の開口端補正距離は、大凡１．２×管直径で与えられる。
すなわち、本発明の消音システムにおいては、消音器２２は、壁１６の一方の端面側、すなわち、管状部材１２の外側に配置されるので、消音器２２の開口部３２は開口端補正距離内の空間に配置されて、管状部材１２の第一共鳴の音場空間に接続される。
Here, the sound field space of the first resonance of the tubular member 12 in the silencing system 10a will be described with reference to FIG. 7.
FIG. 7 shows the distribution of the sound pressure in the first resonance mode of the tubular member 12 that penetrates the wall 16 that separates the two spaces and is obtained by simulation. As can be seen from FIG. 7, the sound field space of the first resonance of the tubular member 12 is a space within the tubular member 12 and within the opening end correction distance. As is well known, the antinode of the standing wave of the sound field protrudes outside the tubular member 12 by the distance of the opening end correction. In addition, the opening end correction distance in the case of the cylindrical tubular member 12 is given by about 1.2 × tube diameter.
That is, in the muffling system of the present invention, since the muffler 22 is arranged on one end surface side of the wall 16, that is, outside the tubular member 12, the opening 32 of the muffler 22 is within the opening end correction distance. It is arranged in space and is connected to the sound field space of the first resonance of the tubular member 12.
ここで、図８に示すように、消音器２２の空洞部３０の面積をＳ0とし、開口部３２の面積をＳ1とすると、開口部３２の面積Ｓ1は、空洞部３０の面積Ｓ0よりも小さいのが好ましい。
図８は、消音装置の消音器の空洞部の面積Ｓ0と開口部の面積Ｓ1とを説明するための図である。
開口部３２の面積Ｓ1を、空洞部３０の面積Ｓ0よりも小さくすることで、管状部材１２内の音波が消音器２２内に流入する際に、音圧を保ったまま気体（空気）分子の移動速度を速くすることができるため、変換機構による音エネルギーから熱エネルギーへの変換効率をより高くすることができる。
ここで、空洞部３０の面積Ｓ0および開口部３２の面積Ｓ1はそれぞれ、空洞部３０または開口部３２を通る管状部材１２の中心軸を軸とする円周面における面積である。
なお、管状部材１２の半径方向の位置によって空洞部３０の面積が異なる場合には、空洞部３０の面積Ｓ0は、各位置での面積の平均値である。
また、開口部３２の面積Ｓ1は、開口が最小となる面積である。
Here, as shown in FIG. 8, when the area of the cavity portion 30 of the muffler 22 and S 0, the area of the opening 32 and S 1, the area S 1 of the opening 32, the area of the cavity 30 S It is preferably smaller than 0 .
FIG. 8 is a diagram for explaining the area S 0 of the cavity and the area S 1 of the opening of the silencer of the silencer.
By making the area S 1 of the opening 32 smaller than the area S 0 of the cavity 30, when the sound wave in the tubular member 12 flows into the muffler 22, gas (air) is maintained while maintaining the sound pressure. Since the moving speed of molecules can be increased, the conversion efficiency of sound energy to thermal energy by the conversion mechanism can be further increased.
Here, each area S 1 of the area S 0 and the opening 32 of the cavity 30 is the area in the circumferential surface of the central axis of the tubular member 12 passing through the hollow portion 30 or the opening 32 and the shaft.
When the area of the hollow portion 30 differs depending on the radial position of the tubular member 12, the area S 0 of the hollow portion 30 is an average value of the areas at the respective positions.
The area S 1 of the opening 32 is the area where the opening is the smallest.
気体分子の移動速度を速くする観点では開口部３２の面積Ｓ1が小さいほど好ましいが、開口部３２の面積Ｓ1が小さすぎると音波が空洞部３０内に流入しにくくなるため防音性能が低くなってしまう。以上の観点から、開口部３２の面積Ｓ1は空洞部３０の面積Ｓ0の０.１％＜Ｓ1／Ｓ0＜４０％が好ましく、０.３％＜Ｓ1／Ｓ0＜３５％がより好ましく、０．５％＜Ｓ1／Ｓ0＜３０％がより好ましい。 From the viewpoint of increasing the moving speed of gas molecules, the smaller the area S 1 of the opening 32 is, the better. However, if the area S 1 of the opening 32 is too small, it is difficult for sound waves to flow into the cavity 30, and the soundproof performance is low. turn into. From the above viewpoint, the area S 1 of the opening 32 is preferably 0.1% <S 1 / S 0 <40% of the area S 0 of the cavity 30, and 0.3% <S 1 / S 0 <35%. Is more preferable, and 0.5% <S 1 / S 0 <30% is more preferable.
また、防音性能および通気性の観点から、消音器２２の空洞部３０の深さＬdは、０．０１１×λ＜Ｌd＜０．２５×λを満たし、０．０１６×λ＜Ｌd＜０．２５×λを満たすのが好ましく、０．０２１×λ＜Ｌd＜０．２５×λを満たすのがより好ましい。
また、軸方向に平行な断面において、空洞部３０の深さ方向に直交する方向の空洞部３０の幅Ｌw（図６参照）は、０．００１×λ＜Ｌw＜０．０６１×λを満たすのが好ましく、０．００１×λ＜Ｌw＜０．０５１×λを満たすのが好ましく、０．００１×λ＜Ｌw＜０．０４１×λを満たすのがより好ましい。
From the viewpoint of soundproofing performance and air permeability, the depth L d of the cavity 30 of the silencer 22 satisfies 0.011 × λ <L d <0.25 × λ, and 0.016 × λ <L d. It is preferable to satisfy <0.25 × λ, and it is more preferable to satisfy 0.021 × λ <L d <0.25 × λ.
Further, in the cross section parallel to the axial direction, the width L w (see FIG. 6) of the cavity 30 in the direction orthogonal to the depth direction of the cavity 30 is 0.001 × λ <L w <0.061 × λ Is preferably satisfied, 0.001 × λ <L w <0.051 × λ is preferable, and 0.001 × λ <L w <0.041 × λ is more preferable.
この点について図９を用いて説明する。
図９は、（空洞部３０の深さＬd／消音対象の音波の波長λ）と、（空洞部３０の幅Ｌw／消音対象の音波の波長λ）と、気体分子の平均粒子速度ｖおよび平均音圧Ｐの乗算値（｜ｖ｜×｜Ｐ｜）との関係を表すグラフである。（｜ｖ｜×｜Ｐ｜）は、空洞部３０の体積当たりの吸収に比例する値である。
This point will be described with reference to FIG.
Figure 9 is a (wavelength lambda of depth L d / mute target sound wave cavity 30), and (wavelength width L w / mute target wave cavity 30 lambda), the average particle velocity v of the gas molecules 3 is a graph showing the relationship between the average sound pressure P and the multiplication value (| v | × | P |). (| V | × | P |) is a value proportional to the absorption per volume of the cavity 30.
粒子速度ｖおよび音圧Ｐは、有限要素法計算ソフトCOMSOL ver5.3（ＣＯＭＳＯＬ社）の音響モジュールを用いて、空洞部３０の深さＬdと空洞部３０の幅Ｌwとを種々変更して求めた。シミュレーションにおいて壁１６と化粧板４０とその間の空間との合計長さ（厚み）は２００ｍｍとし、内径１００ｍｍの管状部材１２および消音装置１４が貫通する構成とした。
消音器２２の空洞部３０は軸方向が深さ方向とした。開口部３２は管状部材１２の周面方向にスリット状に配置した。開口部３２の幅は１０ｍｍとした。開口部３２は軸方向において、空洞部３０の壁側の端部に配置した。また、空洞部３０内には流れ抵抗１３０００［Ｐａ・ｓ／ｍ2］の吸音材２４が配置されるものとした。
管状部材１２の最低共鳴周波数は４６０Ｈｚである。消音対象の音波の周波数は４６０Ｈｚとした。
For the particle velocity v and the sound pressure P, the depth L d of the cavity 30 and the width L w of the cavity 30 are variously changed by using the acoustic module of the finite element method calculation software COMSOL ver5.3 (COMSOL). I asked. In the simulation, the total length (thickness) of the wall 16, the decorative plate 40, and the space between them was 200 mm, and the tubular member 12 having an inner diameter of 100 mm and the silencer 14 were configured to penetrate therethrough.
The cavity 30 of the muffler 22 has an axial direction in the depth direction. The openings 32 are arranged in a slit shape in the circumferential direction of the tubular member 12. The width of the opening 32 was 10 mm. The opening 32 is arranged at the wall-side end of the cavity 30 in the axial direction. In addition, the sound absorbing material 24 having a flow resistance of 13000 [Pa · s / m 2 ] is arranged in the cavity 30.
The lowest resonance frequency of the tubular member 12 is 460 Hz. The frequency of the sound wave to be silenced was 460 Hz.
図１０に示すように、壁で仕切られた一方の空間の半球状の面から音波を入射させ、他方の空間の半球状の面に到達する音波の単位体積あたりの振幅を求めた。半球状の面は、管状部材の開口面の中心位置を中心とした半径５００ｍｍの半球状の面である。入射させる音波は単位体積あたりの振幅を１とした。 As shown in FIG. 10, a sound wave was made incident from a hemispherical surface of one space partitioned by a wall, and the amplitude per unit volume of the sound wave reaching the hemispherical surface of the other space was determined. The hemispherical surface is a hemispherical surface having a radius of 500 mm centered on the center position of the opening surface of the tubular member. The incident sound wave had an amplitude of 1 per unit volume.
図９から、吸収に比例する（｜ｖ｜×｜Ｐ｜）の値は、空洞部３０の幅Ｌwと深さＬdがある範囲で、高くなることがわかる。 From FIG. 9, it can be seen that the value of (| v | × | P |), which is proportional to the absorption, increases in a range where the width L w and the depth L d of the cavity 30 are in a certain range.
また、本発明の消音システムは、消音器２２の空洞部３０の内壁の表面積Ｓdに対する開口部３２の面積Ｓ1の比率Ｓ1／Ｓdを０＜Ｓ1／Ｓd＜４０％とすることで、吸音材２４等変換機構の表面積に対して音波が入射する面の面積の割合を小さくして、高い音圧Ｐを保ったまま吸音材２４等の変換機構に流入する音波に対応する気体分子の移動速度を速くして防音性能を高めることができる。
気体分子の移動速度を速くする観点では開口部３２の面積Ｓ1（比率Ｓ1／Ｓd）は小さいほど好ましいが、開口部３２の面積Ｓ1が小さすぎると音波が空洞部３０内に流入しにくくなるため防音性能が低くなってしまう。以上の観点から、空洞部３０の内壁の表面積Ｓdに対する開口部３２の面積Ｓ1は０.１％＜Ｓ1／Ｓd＜４０％が好ましく、０.３％＜Ｓ1／Ｓd＜３５％がより好ましく、０．５％＜Ｓ1／Ｓd＜３０％がより好ましい。
なお、空洞部３０の内壁の表面積Ｓdは、分解能を１ｍｍとして測定する。すなわち、１ｍｍ未満の凹凸等の微細構造を有する場合には、これを平均化して表面積Ｓdを求めればよい。
Further, in the sound deadening system of the present invention, the ratio S 1 / S d of the area S 1 of the opening 32 to the surface area S d of the inner wall of the cavity 30 of the muffler 22 is 0 <S 1 / S d <40%. As a result, the ratio of the area of the surface on which the sound wave is incident to the surface area of the sound absorbing material 24 or the like converting mechanism is reduced, and it corresponds to the sound wave flowing into the sound absorbing material 24 or other converting mechanism while maintaining a high sound pressure P. The moving speed of gas molecules can be increased to improve the soundproof performance.
From the viewpoint of increasing the moving speed of gas molecules, the smaller the area S 1 (ratio S 1 / S d ) of the opening 32 is, the more preferable. However, if the area S 1 of the opening 32 is too small, the sound wave flows into the cavity 30. Since it is difficult to do so, the soundproofing performance will be poor. From the above viewpoint, the area S 1 of the opening 32 with respect to the surface area S d of the inner wall of the cavity 30 is preferably 0.1% <S 1 / S d <40%, and 0.3% <S 1 / S d < 35% is more preferable, and 0.5% <S 1 / S d <30% is more preferable.
The surface area S d of the inner wall of the cavity 30 is measured with a resolution of 1 mm. That is, in the case of having a fine structure such as unevenness of less than 1 mm, the surface area S d may be obtained by averaging the fine structure.
この点について、図１０に示すシミュレーションモデルと同様のモデルを用いてシミュレーションを行なった。
空洞部３０の深さＬdは８０ｍｍ、幅Ｌwは１０ｍｍとした。
開口部の幅Ｌoを１０ｍｍ（１ｃｍ）〜７０ｍｍ（７ｃｍ）に変更することで、面積比率Ｓ1／Ｓdを５．３％〜５４．７％に変更して、それぞれ透過音圧を算出した。図１１中面積割合５．３％が１ｃｍに対応し、１７．９％が３ｃｍに対応し、２５．３％が４ｃｍに対応し、３３．８％が５ｃｍに対応し、５４．７％が７ｃｍに対応する。なお、透過音圧は、消音器を設置しなかった場合の透過音圧のピーク（第一共鳴周波数の透過音圧）を１として規格化した。消音器を設置しない場合の管状部材内の第一共鳴周波数は４６０Ｈｚであるので、４６０Ｈｚにおける透過音圧がピーク音圧である。
結果を図１１および図１２に示す。
With respect to this point, simulation was performed using a model similar to the simulation model shown in FIG.
The cavity portion 30 had a depth L d of 80 mm and a width L w of 10 mm.
By changing the width L o of the opening to 10 mm (1 cm) to 70 mm (7 cm), the area ratio S 1 / S d is changed to 5.3% to 54.7%, and the transmitted sound pressure is calculated. did. In FIG. 11, the area ratio 5.3% corresponds to 1 cm, 17.9% corresponds to 3 cm, 25.3% corresponds to 4 cm, 33.8% corresponds to 5 cm, and 54.7% corresponds to Corresponds to 7 cm. The transmitted sound pressure was standardized with the peak of transmitted sound pressure (transmitted sound pressure at the first resonance frequency) being 1 when the silencer was not installed. Since the first resonance frequency in the tubular member when the silencer is not installed is 460 Hz, the transmitted sound pressure at 460 Hz is the peak sound pressure.
The results are shown in FIGS. 11 and 12.
図１１は、周波数と透過音圧との関係を表すグラフであり、図１２は、開口面積の割合と透過音圧のピークとの関係を表すグラフである。
図１１および図１２からわかるように、吸音材の体積は同じであるにも関わらず、開口部の面積比率Ｓ1／Ｓdが小さいほど、共鳴周波数の透過音圧は小さくなることがわかる。なお、消音器無しの場合に対して、消音器を設置した場合の共鳴周波数が低周波側にシフトしているのは音波が存在できる体積が増えたためである。
FIG. 11 is a graph showing the relationship between frequency and transmitted sound pressure, and FIG. 12 is a graph showing the relationship between the ratio of the opening area and the peak of transmitted sound pressure.
As can be seen from FIGS. 11 and 12, although the volume of the sound absorbing material is the same, the smaller the area ratio S 1 / S d of the openings, the smaller the transmitted sound pressure at the resonance frequency. It should be noted that the resonance frequency when the silencer is installed is shifted to the lower frequency side as compared with the case where the silencer is not installed because the volume where sound waves can exist is increased.
また、音エネルギーを熱エネルギーに変換する変換機構は、前述のとおり、消音器の壁面近傍における流体の粘性、消音器の壁面の凹凸（表面粗さ）、消音器内に配置された吸音材、あるいは、図１３および図１４に示すような微細な貫通孔６４を多数有するシート状の微細穿孔板６０等である。変換機構としては、吸音材を用いることが好ましい。
吸音材２４および微細穿孔板等の変換機構は、消音器２２の空洞部３０内の少なくとも一部に配置される構成とすればよい。あるいは、図１５に示す消音システム１０ｈのように、吸音材２４（変換機構）は消音器２２の開口部３２の少なくとも一部を覆うように配置される構成としてもよい。
Further, the conversion mechanism for converting sound energy into heat energy is, as described above, the viscosity of the fluid in the vicinity of the wall surface of the silencer, the unevenness (surface roughness) of the wall surface of the silencer, the sound absorbing material arranged in the silencer, Alternatively, it is a sheet-like fine perforated plate 60 having a large number of fine through holes 64 as shown in FIGS. 13 and 14. It is preferable to use a sound absorbing material as the conversion mechanism.
The sound absorbing material 24 and the conversion mechanism such as the fine perforated plate may be arranged in at least a part of the hollow portion 30 of the silencer 22. Alternatively, as in the sound deadening system 10h shown in FIG. 15, the sound absorbing material 24 (conversion mechanism) may be arranged so as to cover at least a part of the opening 32 of the muffler 22.
吸音材２４は、単位厚さ当たりの流れ抵抗σ1［Pa・s/m2］が（１．２５−ｌｏｇ（Ｌd））／０．２４＜ｌｏｇ（σ1）＜５．６を満たすことが好ましく、（１．３２−ｌｏｇ（Ｌd））／０．２４＜ｌｏｇ（σ1）＜５．２］を満たすことがより好ましく、（１．３９−ｌｏｇ（Ｌd））／０．２４＜ｌｏｇ（σ1）＜４．７を満たすことがさらに好ましい。なお、上記式において、Ｌdの単位は［ｍｍ］であり、ｌｏｇは自然対数である。吸音材の流れ抵抗は、１ｃｍ厚の吸音材の垂直入射吸音率を測定し、Ｍｉｋｉモデル（Ｊ． Ａｃｏｕｓｔ． Ｓｏｃ． Ｊｐｎ．， １１（１） ｐｐ．１９−２４ （１９９０））でフィッティングすることで評価した。または「ＩＳＯ ９０５３」に従って評価してもよい。 In the sound absorbing material 24, the flow resistance σ 1 [Pa · s / m 2 ] per unit thickness satisfies (1.25−log (L d )) / 0.24 <log (σ 1 ) <5.6. It is preferable that (1.32-log (L d )) / 0.24 <log (σ 1 ) <5.2] is satisfied, and (1.39-log (L d )) / 0 is satisfied. It is more preferable to satisfy the following condition: 24.24 <log (σ 1 ) <4.7. In the above formula, the unit of L d is [mm], and log is the natural logarithm. The flow resistance of the sound absorbing material is measured by measuring the normal incidence sound absorption coefficient of the sound absorbing material having a thickness of 1 cm, and fitting with a Miki model (J. Aust. Soc. Jpn., 11 (1) pp.19-24 (1990)). It was evaluated by. Alternatively, it may be evaluated according to "ISO 9053".
吸音材２４としては、特に限定はなく、従来公知の吸音材が適宜利用可能である。例えば、発泡ウレタン、軟質ウレタンフォーム、木材、セラミックス粒子焼結材、フェノールフォーム等の発泡材料および微小な空気を含む材料；グラスウール、ロックウール、マイクロファイバー（３Ｍ社製シンサレートなど）、フロアマット、絨毯、メルトブローン不織布、金属不織布、ポリエステル不織布、金属ウール、フェルト、インシュレーションボードおよびガラス不織布等のファイバーおよび不織布類材料；木毛セメント板；シリカナノファイバーなどのナノファイバー系材料；石膏ボード；種々の公知の吸音材が利用可能である。 The sound absorbing material 24 is not particularly limited, and a conventionally known sound absorbing material can be appropriately used. For example, foamed materials such as urethane foam, soft urethane foam, wood, ceramic particles sintered material, phenol foam, and materials containing minute air; glass wool, rock wool, microfiber (thin-slate etc. manufactured by 3M), floor mat, carpet. Fiber, non-woven materials such as meltblown non-woven fabric, metal non-woven fabric, polyester non-woven fabric, metal wool, felt, insulation board and glass non-woven fabric; wood wool cement board; nanofiber material such as silica nanofiber; plasterboard; various known materials Sound absorbing material is available.
吸音材２４の厚みは空洞部３０内あるいは開口部近傍に配置可能であれば限定はない。吸音性能等の観点から、吸音材２４の厚みは０．０１ｍｍ〜５００ｍｍが好ましく、０．１ｍｍ〜１００ｍｍがより好ましい。 The thickness of the sound absorbing material 24 is not limited as long as it can be arranged inside the cavity 30 or in the vicinity of the opening. From the viewpoint of sound absorbing performance and the like, the thickness of the sound absorbing material 24 is preferably 0.01 mm to 500 mm, more preferably 0.1 mm to 100 mm.
微細穿孔板６０は、シート状部材６２に微細な貫通孔６４を多数有するものである。微細穿孔板６０は、音波が貫通孔６４を通過する際の摩擦によって音エネルギーを熱エネルギーに変換して吸音する。
貫通孔の平均開口径としては、１〜２５０μｍであるのが好ましく、１〜１００μｍであるのがより好ましい。貫通孔の平均開口率としては、０．１〜２０％が好ましく、０．５〜１０％がより好ましい。
また、シート状部材６２の厚みとしては、５μｍ〜５００μｍが好ましく、１０μｍ〜３００μｍがより好ましい。
The fine perforated plate 60 has a large number of fine through holes 64 in the sheet-shaped member 62. The fine perforated plate 60 converts sound energy into heat energy due to friction when sound waves pass through the through holes 64 and absorbs sound.
The average opening diameter of the through holes is preferably 1 to 250 μm, and more preferably 1 to 100 μm. The average aperture ratio of the through holes is preferably 0.1 to 20%, more preferably 0.5 to 10%.
The thickness of the sheet member 62 is preferably 5 μm to 500 μm, more preferably 10 μm to 300 μm.
なお、貫通孔の平均開口径は、微細穿孔板の一方の面から、高分解能走査型電子顕微鏡（ＳＥＭ 株式会社日立ハイテクテクノロジーズ製：FE-SEM S-4100）を用いて微細穿孔板の表面を倍率２００倍で撮影し、得られたＳＥＭ写真において、周囲が環状に連なっている貫通孔を２０個抽出し、その開口径を読み取って、これらの平均値を平均開口径として算出する。もし、１枚のＳＥＭ写真内に貫通孔が２０個未満の場合は、周辺の別の位置でＳＥＭ写真を撮影し、合計個数が２０個になるまでカウントする。
なお、開口径は、貫通孔部分の面積をそれぞれ計測し、同一の面積となる円に置き換えたときの直径(円相当直径)を用いて評価した。すなわち、貫通孔の開口部の形状は略円形状に限定はされないので、開口部の形状が非円形状の場合には、同一面積となる円の直径で評価した。従って、例えば、２以上の貫通孔が一体化したような形状の貫通孔の場合にも、これを１つの貫通孔とみなし、貫通孔の円相当直径を開口径とする。
これらの作業は、例えば「Image J」（https://imagej.nih.gov/ij/）を用いて、Analyze Particlesにより円相当直径、開口率などを全て計算することができる。
The average opening diameter of the through-holes is measured from one surface of the micro-perforated plate by using a high-resolution scanning electron microscope (FE-SEM S-4100 manufactured by Hitachi High-Tech Technologies, SEM Corporation). Photographed at a magnification of 200 times, in the obtained SEM photograph, 20 through-holes each having a ring-shaped periphery are extracted, their opening diameters are read, and their average value is calculated as the average opening diameter. If there are less than 20 through holes in one SEM photograph, SEM photographs are taken at other peripheral positions and counted until the total number reaches 20.
The opening diameter was evaluated using the diameter (circle equivalent diameter) obtained by measuring the areas of the through holes and replacing them with circles having the same area. That is, since the shape of the opening of the through hole is not limited to a substantially circular shape, when the shape of the opening is non-circular, the diameter of the circle having the same area was used for evaluation. Therefore, for example, even in the case of a through hole having a shape in which two or more through holes are integrated, this is regarded as one through hole, and the circle equivalent diameter of the through hole is set as the opening diameter.
For these operations, for example, "Image J" (https://imagej.nih.gov/ij/) can be used to calculate all the circle equivalent diameters, aperture ratios, etc. by Analyze Particles.
また、平均開口率は、高分解能走査型電子顕微鏡（ＳＥＭ）を用いて微細穿孔板の表面を真上から倍率２００倍で撮影し、得られたＳＥＭ写真の３０ｍｍ×３０ｍｍの視野（５箇所）について、画像解析ソフト等で２値化して貫通孔部分と非貫通孔部分を観察し、貫通孔の開口面積の合計と視野の面積（幾何学的面積）とから、比率（開口面積／幾何学的面積）を算出し、各視野（５箇所）における平均値を平均開口率として算出する。 Further, the average aperture ratio was obtained by photographing the surface of the micro perforated plate at a magnification of 200 from directly above using a high resolution scanning electron microscope (SEM), and a 30 mm × 30 mm visual field (5 locations) of the obtained SEM photograph. , The through-hole and non-through-hole are observed by binarizing with image analysis software, and the ratio (opening area / geometry) is calculated from the total opening area of the through holes and the field of view (geometric area). Target area), and the average value in each field (5 locations) is calculated as the average aperture ratio.
また、シート状部材６２の材料としては、膜状にできる樹脂材料、箔状にできる金属材料、その他繊維状の膜になる材質の材料、不織布、ナノサイズのファイバーを含むフィルム、薄く加工したポーラス材料、薄膜構造に加工したカーボン材料、および、ゴム材料等、薄い構造を形成できる材質又は構造等を挙げることができる。具体的には、金属材料としては、アルミニウム、チタン、ニッケル、パーマロイ、４２アロイ、コバール、ニクロム、銅、ベリリウム、リン青銅、黄銅、洋白、錫、亜鉛、鉄、タンタル、ニオブ、モリブデン、ジルコニウム、金、銀、白金、パラジウム、鋼鉄、タングステン、鉛、イリジウム等の各種金属、および、これら金属の合金を挙げることができる。また、樹脂材料としては、ＰＥＴ（ポリエチレンテレフタレート）、ＴＡＣ（トリアセチルセルロース）、ポリ塩化ビニルデン、ポリエチレン、ポリ塩化ビニル、ポリメチルベンテン、ＣＯＰ（シクロオレフィンポリマー）、ポリカーボネート、ゼオノア、ＰＥＮ（ポリエチレンナフタレート）、ポリプロピレン、および、ポリイミド等の樹脂材料等が利用可能である。その他繊維状の膜になる材質の材料としては、例えば紙、および、セルロース等を挙げることができる。薄く加工したポーラス材料としては、例えば薄く加工したウレタン、および、シンサレート等を挙げることができる。さらに、薄膜ガラスなどのガラス材料、ＣＦＲＰ（炭素繊維強化プラスチック：Ｃａｒｂｏｎ Ｆｉｂｅｒ Ｒｅｉｎｆｏｒｃｅｄ Ｐｌａｓｔｉｃｓ）、および、ＧＦＲＰ（ガラス繊維強化プラスチック：Ｇｌａｓｓ Ｆｉｂｅｒ Ｒｅｉｎｆｏｒｃｅｄ Ｐｌａｓｔｉｃｓ）のような繊維強化プラスチック材料を用いることもできる。また、ゴム材料としては、例えば、シリコーンゴム、および、天然ゴムをあげることができる。
また、微細穿孔板１２の材料として、繊維状の材料を用いる場合には、繊維状のものが重なりあったもの、または繊維が編まれたもの（網）でもよく、平面視した際に繊維間にできる開口の平均開口径が０．１μｍ以上２５０μｍ以下となるようにすれるのが好ましい。
また、微細穿孔板１２は、これらの材料からなる膜を積層した構成としてもよい。
Further, as the material of the sheet-like member 62, a resin material that can be formed into a film, a metal material that can be formed into a foil, a material that forms a fibrous film, a nonwoven fabric, a film containing nano-sized fibers, a thinly processed porous material. Examples of the material include a material, a carbon material processed into a thin film structure, and a rubber material, which are capable of forming a thin structure. Specifically, as the metal material, aluminum, titanium, nickel, permalloy, 42 alloy, kovar, nichrome, copper, beryllium, phosphor bronze, brass, nickel silver, tin, zinc, iron, tantalum, niobium, molybdenum, zirconium. , Various metals such as gold, silver, platinum, palladium, steel, tungsten, lead and iridium, and alloys of these metals. Further, as the resin material, PET (polyethylene terephthalate), TAC (triacetyl cellulose), polyvinyl vinyl chloride, polyethylene, polyvinyl chloride, polymethyl bentene, COP (cycloolefin polymer), polycarbonate, zeonoa, PEN (polyethylene naphthalate) ), Polypropylene, and resin materials such as polyimide can be used. Examples of the material of the material that forms the fibrous film include paper and cellulose. As the thinly processed porous material, for example, thinly processed urethane, thinsulate and the like can be mentioned. Further, a glass material such as thin film glass, a fiber reinforced plastic material such as CFRP (Carbon Fiber Reinforced Plastics), and a GFRP (Glass Fiber Reinforced Plastics) can be used. Further, examples of the rubber material include silicone rubber and natural rubber.
When a fibrous material is used as the material of the fine perforated plate 12, fibrous materials may be overlapped with each other or braided fibers (mesh) may be used. The average opening diameter of the openings that can be formed is preferably 0.1 μm or more and 250 μm or less.
Further, the fine perforated plate 12 may have a structure in which films made of these materials are laminated.
また、貫通孔の形成方法は、微細穿孔板の形成材料等に応じて、公知の方法で行えばよい。
例えば、微細穿孔板としてＰＥＴフィルム等の樹脂フィルムを用いる場合には、レーザー加工などのエネルギを吸収する加工方法、もしくはパンチング、および、針加工などの物理的接触による機械加工方法で貫通孔を形成することができる。また、微細穿孔板としてアルミニウム等の金属材料を用いる場合には、エッチングなどで貫通孔を形成することができる。
The method of forming the through holes may be a known method depending on the material for forming the fine perforated plate and the like.
For example, when a resin film such as a PET film is used as the fine perforated plate, the through holes are formed by a processing method such as laser processing that absorbs energy, or a mechanical processing method by physical contact such as punching and needle processing. can do. When a metal material such as aluminum is used for the fine perforated plate, the through holes can be formed by etching or the like.
また、図５に示す例では、第１部材２１ａと第２部材２１ｂとの間にスペーサー２１ｃを配置して、消音器２２の長さを調整する構成としたが、これに限定はされない。
例えば、図１６に示す消音システム１０ｃのように、第１部材２１ａの外周部１０２にリング状のストッパー２１ｄを固定し、このストッパー２１ｄに第２部材２１ｂの外周部１０６の端面が突き当たるようにして、第１部材２１ａと第２部材２１ｂとの軸方向における相対位置を調整する。第１部材２１ａの外周部１０２上におけるストッパー２１ｄの位置を適宜、変更することで、消音器２２の長さを調整することができる。
図１６に示す消音システム１０ｃにおいて、第１部材２１ａ、第２部材２１ｂおよびストッパー２１ｄが長さ調整部に相当する。
In the example shown in FIG. 5, the spacer 21c is arranged between the first member 21a and the second member 21b to adjust the length of the silencer 22, but the present invention is not limited to this.
For example, as in the sound deadening system 10c shown in FIG. 16, a ring-shaped stopper 21d is fixed to the outer peripheral portion 102 of the first member 21a, and the end surface of the outer peripheral portion 106 of the second member 21b abuts on this stopper 21d. , The relative position of the first member 21a and the second member 21b in the axial direction is adjusted. By appropriately changing the position of the stopper 21d on the outer peripheral portion 102 of the first member 21a, the length of the silencer 22 can be adjusted.
In the silencing system 10c shown in FIG. 16, the first member 21a, the second member 21b, and the stopper 21d correspond to the length adjusting unit.
あるいは、図１７に示す消音システム１０ｄのように、第１部材２１ａと第２部材２１ｂとを所望の相対位置に粘着テープ２１ｅで固定して、消音器２２の長さを調整するようにしてもよい。
図１７に示す消音システム１０ｄにおいて、第１部材２１ａ、第２部材２１ｂおよび粘着テープ２１ｅが長さ調整部に相当する。
粘着テープ２１ｅとしては、遮音テープ（大建工業株式会社製 粘着遮音シート 100N等）、クラフトテープ（積水化学工業株式会社製 No.500 K51X13など）、布テープ（積水化学工業株式会社製 布テープNo.600M等）、金属テープ（アルミ、銅、ステンレス、など）、養生テープ（ニチバン株式会社製 養生用布テープ108-30など）、カプトンテープ（東レ・デュポン株式会社製 カプトン（登録商標）等）等の市販の粘着テープを用いることができる。
Alternatively, like the silencer system 10d shown in FIG. 17, the length of the silencer 22 may be adjusted by fixing the first member 21a and the second member 21b at desired relative positions with the adhesive tape 21e. Good.
In the sound deadening system 10d shown in FIG. 17, the first member 21a, the second member 21b, and the adhesive tape 21e correspond to the length adjusting unit.
As the adhesive tape 21e, sound insulation tape (adhesive sound insulation sheet 100N manufactured by Daiken Kogyo Co., Ltd.), kraft tape (No.500 K51X13 manufactured by Sekisui Chemical Co., Ltd.), cloth tape (Cloth tape No. manufactured by Sekisui Chemical Co., Ltd.) .600M, etc.), metal tape (aluminum, copper, stainless steel, etc.), curing tape (Nichiban Co., Ltd. curing cloth tape 108-30 etc.), Kapton tape (Toray DuPont Kapton (registered trademark) etc.) Commercially available adhesive tapes such as
また、図１８に示す消音システム１０ｅでは、第１部材２１ａの外周部１０２の外周面に非貫通の穴部２１ｆが複数、軸方向に設けられている。また、第２部材２１ｂの外周部１０６の内周面の先端側（底面部１０８とは反対側）には突起部２１ｇが設けられている。突起部２１ｇが１つの穴部２１ｆに嵌合することで、第１部材２１ａと第２部材２１ｂとの軸方向における相対位置を調整する。突起部２１ｇが嵌合する穴部２１ｆを変えることで、消音器２２の長さを調整することができる。
図１８に示す消音システム１０ｅにおいて、第１部材２１ａ、第２部材２１ｂ、孔部２１ｆおよび突起部２１ｇが長さ調整部に相当する。
Further, in the sound deadening system 10e shown in FIG. 18, a plurality of non-penetrating holes 21f are axially provided on the outer peripheral surface of the outer peripheral portion 102 of the first member 21a. A protrusion 21g is provided on the inner peripheral surface of the outer peripheral portion 106 of the second member 21b at the tip side (opposite to the bottom surface portion 108). By fitting the protrusion 21g into the one hole 21f, the relative position of the first member 21a and the second member 21b in the axial direction is adjusted. The length of the silencer 22 can be adjusted by changing the hole 21f into which the protrusion 21g is fitted.
In the silencing system 10e shown in FIG. 18, the first member 21a, the second member 21b, the hole 21f, and the protrusion 21g correspond to the length adjusting unit.
図１９に示す消音システム１０ｆでは、軸方向の長さが長い吸音材２４を用いて、第１部材２１ａの底面部１００と第２部材２１ｂの底面部１０８とをそれぞれ吸音材２４に接触させることで、第１部材２１ａの底面部１００と第２部材２１ｂの底面部１０８との間の距離、すなわち、第１部材２１ａと第２部材２１ｂとの軸方向における相対位置を調整する。軸方向の長さの異なる吸音材２４を用いることで、消音器２２の長さを調整することができる。
図１９に示す消音システム１０ｆにおいて、第１部材２１ａ、第２部材２１ｂおよび吸音材２４が長さ調整部に相当する。
In the sound deadening system 10f shown in FIG. 19, the bottom surface portion 100 of the first member 21a and the bottom surface portion 108 of the second member 21b are brought into contact with the sound absorbing material 24 by using the sound absorbing material 24 having a long axial length. Then, the distance between the bottom surface portion 100 of the first member 21a and the bottom surface portion 108 of the second member 21b, that is, the relative position of the first member 21a and the second member 21b in the axial direction is adjusted. By using the sound absorbing material 24 having different axial lengths, the length of the muffler 22 can be adjusted.
In the sound deadening system 10f shown in FIG. 19, the first member 21a, the second member 21b, and the sound absorbing material 24 correspond to the length adjusting unit.
図２０に示す消音システム１０ｇにおいては、第１部材２１ａの外周部１０２の外周面に雄ネジが形成されており、第２部材２１ｂの外周部１０６の内周面に雌ネジが形成されており、雄ネジと雌ネジを噛み合わせることによって、第１部材２１ａと第２部材２１ｂとの軸方向における相対位置を調整する。ネジ部２１ｈの嵌合長さを変えることで、消音器２２の長さを調整することができる。
図２０に示す消音システム１０ｇにおいて、第１部材２１ａ、第２部材２１ｂおよびネジ部２１ｈが長さ調整部に相当する。
In the sound deadening system 10g shown in FIG. 20, a male screw is formed on the outer peripheral surface of the outer peripheral portion 102 of the first member 21a, and a female screw is formed on the inner peripheral surface of the outer peripheral portion 106 of the second member 21b. The relative position in the axial direction of the first member 21a and the second member 21b is adjusted by engaging the male screw and the female screw. The length of the silencer 22 can be adjusted by changing the fitting length of the screw portion 21h.
In the muffling system 10g shown in FIG. 20, the first member 21a, the second member 21b, and the screw portion 21h correspond to the length adjusting portion.
また、図１に示す例では、１つの消音器２２を有する構成としたが、これに限定はされず、軸方向に２以上の消音器２２を有する構成としてもよい。例えば、図２１に示す消音システム１０ｉのように、軸方向に２つの消音器２２を配置した構成としてもよい。 Further, in the example shown in FIG. 1, the configuration has one silencer 22, but the configuration is not limited to this, and a configuration having two or more silencers 22 in the axial direction may be adopted. For example, as in the silencer system 10i shown in FIG. 21, two silencers 22 may be arranged in the axial direction.
図２１に示す消音システム２０ｉにおいて、消音装置１４は、軸方向に挿入部２６と、消音器２２ａと、消音器２２ｂとを有する。消音器２２ａおよび消音器２２ｂは、第１部材２３ａと第２部材２３ｂと第３部材２３ｃとによって構成されている。 In the silencer system 20i shown in FIG. 21, the silencer 14 has an insertion portion 26, a silencer 22a, and a silencer 22b in the axial direction. The silencer 22a and the silencer 22b are composed of a first member 23a, a second member 23b, and a third member 23c.
具体的には、第１部材２３ａは、第１部材２１ａと同様の形状で、外周部の内径が第２部材２３ｂおよび第３部材２３ｃの外周部の外径よりも大きい（略同じである）。第２部材２３ｂおよび第３部材２３ｃは、第２部材２１ｂと同様の形状で、外周部の外径が第１部材２３ａの外周部の内径よりも小さい。また、第１部材２３ａの外周部の高さ（軸方向の長さ）は、第２部材２３ｂの外周部の高さ、および、第３部材２３ｃの外周部の高さの合計と略同じである。また、第２部材２３ｂおよび第３部材２３ｃはいずれも、内周部の高さが外周部の高さよりも低い形状である。
第２部材２３ｂおよび第３部材２３ｃは、軸方向にこの順に第１部材２３ａの外周部内に挿入されている。図２１に示す状態では、第２部材２３ｂは、第２部材２３ｂの外周部が第１部材２３ａの底面部に突き当たるように配置され、第３部材２３ｃは、第３部材の外周部が第２部材２３ｂの底面部の外側面に突き当たるように配置されている。これにより、第１部材２３ａの底面部と第２部材２３ｂの外周部と底面部と内周部とによって囲まれる空洞部３０ａが形成され、第１部材２３ａの底面部と第２部材２３ｂの内周部との間に開口部３２ａが形成されて消音器２２ａが構成される。また、第２部材２３ｂの底面部と第３部材２３ｃの外周部と底面部と内周部とによって囲まれる空洞部３０ｂが形成され、第２部材２３ｂの底面部と第３部材２３ｃの内周部との間に開口部３２ｂが形成されて消音器２２ｂが構成される。
Specifically, the first member 23a has the same shape as the first member 21a, and the inner diameter of the outer peripheral portion is larger than the outer diameters of the outer peripheral portions of the second member 23b and the third member 23c (almost the same). . The second member 23b and the third member 23c have the same shape as the second member 21b, and the outer diameter of the outer peripheral portion is smaller than the inner diameter of the outer peripheral portion of the first member 23a. The height of the outer peripheral portion of the first member 23a (the length in the axial direction) is substantially the same as the sum of the height of the outer peripheral portion of the second member 23b and the height of the outer peripheral portion of the third member 23c. is there. Further, both the second member 23b and the third member 23c have a shape in which the height of the inner peripheral portion is lower than the height of the outer peripheral portion.
The second member 23b and the third member 23c are inserted into the outer peripheral portion of the first member 23a in this order in the axial direction. In the state shown in FIG. 21, the second member 23b is arranged such that the outer peripheral portion of the second member 23b abuts the bottom surface portion of the first member 23a, and the third member 23c has the outer peripheral portion of the third member second. It is arranged so as to abut the outer surface of the bottom surface of the member 23b. As a result, a cavity portion 30a surrounded by the bottom surface portion of the first member 23a, the outer peripheral portion, the bottom surface portion, and the inner peripheral portion of the second member 23b is formed, and the bottom surface portion of the first member 23a and the inner portion of the second member 23b are formed. An opening 32a is formed between the silencer 22a and the peripheral portion to form the silencer 22a. Further, a cavity portion 30b surrounded by the bottom surface portion of the second member 23b, the outer peripheral portion of the third member 23c, the bottom surface portion and the inner peripheral portion is formed, and the bottom surface portion of the second member 23b and the inner peripheral portion of the third member 23c are formed. The muffler 22b is formed by forming an opening 32b between the muffler and the part.
このように構成される消音器２２ａおよび消音器２２ｂは、第１部材２３ａ、第２部材２３ｂおよび第３部材２３ｃの軸方向の相対位置を調整することで、軸方向の長さを調整することができる。従って、軸方向に複数の消音器を有する場合にも、壁１６と化粧板４０との間の距離に合わせて消音器の長さを調整して消音器を配置することができる。
第１部材２３ａ、第２部材２３ｂおよび第３部材２３ｃの軸方向の相対位置の調整方法としては、前述と同様の方法を用いることができる。
The muffler 22a and the muffler 22b configured as described above adjust the axial length by adjusting the relative positions of the first member 23a, the second member 23b, and the third member 23c in the axial direction. You can Therefore, even when a plurality of mufflers are provided in the axial direction, the muffler can be arranged by adjusting the length of the muffler according to the distance between the wall 16 and the decorative plate 40.
As a method of adjusting the relative positions of the first member 23a, the second member 23b, and the third member 23c in the axial direction, the same method as described above can be used.
すなわち、例えば、図２２に示す消音システム１０ｊのように、第１部材２３ａの底面部と第２部材２３ｂの外周部の端面との間に、両側面が開放された円筒状のスペーサー２３ｄを設置することで消音器２２ａの長さを調整し、第２部材２３ｂの底面部と第３部材２３ｃの外周部の端面との間に、両側面が開放された円筒状のスペーサー２３ｅを設置することで消音器２２ｂの長さを調整することができる。 That is, for example, as in the sound deadening system 10j shown in FIG. 22, a cylindrical spacer 23d having open both side surfaces is provided between the bottom surface of the first member 23a and the end surface of the outer peripheral portion of the second member 23b. By adjusting the length of the silencer 22a, a cylindrical spacer 23e having both open sides is installed between the bottom surface of the second member 23b and the end surface of the outer peripheral portion of the third member 23c. The length of the silencer 22b can be adjusted with.
あるいは、図２３に示す消音システム１０ｋのように、消音器２２ｂの内部に配置される吸音体２４ｂとして軸方向の長さが長い吸音体を用いて、第２部材２３ｂの底面部と第３部材２３ｃの底面部とをそれぞれ吸音材２４ｂに接触させることで、第２部材２３ｂの底面部と第３部材２３ｃの底面部との間の距離、すなわち、第２部材２３ｂと第３部材２３ｃとの軸方向における相対位置を調整して、消音器２２ｂの長さを調整することができる。 Alternatively, as in the muffling system 10k shown in FIG. 23, a sound absorbing body having a long axial length is used as the sound absorbing body 24b arranged inside the muffler 22b, and the bottom surface portion of the second member 23b and the third member 23b are used. The bottom surface of 23c is brought into contact with the sound absorbing material 24b, so that the distance between the bottom surface of the second member 23b and the bottom surface of the third member 23c, that is, the distance between the second member 23b and the third member 23c. The length of the silencer 22b can be adjusted by adjusting the relative position in the axial direction.
なお、２以上の消音器を有する場合には、少なくとも１つの消音器の長さが調整可能であればよく、また、複数の消音器の長さが調整可能な場合には、全ての消音器の長さをそれぞれ調整してもよく、あるいは、少なくとも１つの消音器の長さを調整するのみであってもよい。 In the case of having two or more silencers, the length of at least one silencer may be adjustable, and when the lengths of a plurality of silencers are adjustable, all silencers may be used. May be adjusted individually, or only the length of the at least one silencer may be adjusted.
また、複数の消音器を有する構成の場合には、それぞれの空洞部内に配置される吸音材の音響特性は同じであっても異なっていてもよい。
例えば、図２１に示す消音システム１０ｉにおいては、消音器２２ａの空洞部３０ａに配置される吸音材２４ａと、消音器２２ｂの空洞部３０ｂに配置される吸音材２４ｂとの吸音特性が互いに異なっていてもよい。
Further, in the case of the configuration having a plurality of silencers, the acoustic characteristics of the sound absorbing material arranged in each cavity may be the same or different.
For example, in the sound deadening system 10i shown in FIG. 21, the sound absorbing material 24a arranged in the hollow portion 30a of the silencer 22a and the sound absorbing material 24b arranged in the hollow portion 30b of the silencer 22b have different sound absorbing characteristics. May be.
また、消音器および挿入部を有する消音装置を管状部材内に挿入して設置する構成とすることで、既存の換気口および空調ダクト等に大規模な工事等を行うことなく簡易に設置することが可能となる。従って、消音器が劣化あるいは破損した時の交換が簡易である。また、住宅の換気スリーブなどに使用する場合は、コンクリート壁の貫通穴径を変える必要がなく施工が簡易である。また、リノベーション時に後付けで設置することが簡易である。 In addition, by installing a silencer and a silencer having an insertion part inside the tubular member, it is possible to easily install it in an existing ventilation port, air conditioning duct, etc. without performing large-scale construction. Is possible. Therefore, when the muffler is deteriorated or damaged, it is easy to replace it. Further, when used as a ventilation sleeve of a house, it is not necessary to change the through hole diameter of the concrete wall, and the construction is simple. In addition, it is easy to retrofit it when renovating.
なお、図１に示す例では、消音装置１４の挿入部２６を管状部材１２内に挿入して、消音装置１４を管状部材１２の開口部に配置する構成としたが、これに限定はされない。
例えば、図２４に示す消音システム１０ｎのように、消音装置１４が挿入部を有さず、壁１６に接着剤等で貼り付ける構成としてもよい。
あるいは、図２５に示す消音システム１０ｐのように、消音装置１４の挿入部２６の内径を壁１６に配置された管状部材１２の外径と略同じ径として、消音装置１４の挿入部２６内に管状部材１２を挿入して、消音装置１４を設置する構成としてもよい。挿入部２６は、管状部材１２と壁１６との間に配置される。
あるいは、図２６に示す消音システム１０ｑのように、消音装置１４の挿入部２６の内径を管状部材１２の外径よりも大きくして、挿入部２６が壁１６内に配置される構成としてもよい。
図２４〜図２６に示すような構成にすることにより、挿入部２６を管状部材１２に挿入することによる開口率の低下を抑制でき、管状部材１２の通気性を向上できる。
なお、図２４〜図２６においては、消音器の長さを調整する機構（第１部材、第２部材等）の図示は省略した。以下、図２７〜図３４においても同様である。
In the example shown in FIG. 1, the silencing device 14 is inserted into the tubular member 12 and the silencing device 14 is arranged in the opening of the tubular member 12. However, the present invention is not limited to this.
For example, as in the sound deadening system 10n shown in FIG. 24, the sound deadening device 14 does not have an insertion portion and may be attached to the wall 16 with an adhesive or the like.
Alternatively, as in the sound deadening system 10p shown in FIG. The tubular member 12 may be inserted and the silencer 14 may be installed. The insert 26 is arranged between the tubular member 12 and the wall 16.
Alternatively, as in the sound deadening system 10q shown in FIG. 26, the inner diameter of the insertion portion 26 of the sound deadening device 14 may be made larger than the outer diameter of the tubular member 12, and the insertion portion 26 may be arranged in the wall 16. .
With the configuration shown in FIGS. 24 to 26, it is possible to suppress a decrease in the aperture ratio due to the insertion of the insertion portion 26 into the tubular member 12, and improve the air permeability of the tubular member 12.
24 to 26, the mechanism (first member, second member, etc.) for adjusting the length of the muffler is not shown. The same applies to FIGS. 27 to 34.
なお、図２５および図２６に示すように、挿入部２６を壁１６内に配置する構成とする場合には、挿入部２６の大きさおよび形状に合わせて、壁１６に挿入部２６を配置するための溝を形成すればよい。あるいは、壁１６を作製する際に、あらかじめ消音装置１４（および管状部材１２）を設置しておき、コンクリートを流し込んで壁１６を作製してもよい。 As shown in FIGS. 25 and 26, when the insertion portion 26 is arranged in the wall 16, the insertion portion 26 is arranged in the wall 16 in accordance with the size and shape of the insertion portion 26. It is sufficient to form a groove for this. Alternatively, when the wall 16 is manufactured, the muffling device 14 (and the tubular member 12) may be installed in advance, and the wall 16 may be manufactured by pouring concrete.
また、消音システムは、管状部材のいずれか一方の端面に設置されるカバー部材および他方の端部に設置される風量調整部材の少なくとも一方を有していてもよい。カバー部材は、換気口および空調用ダクト等に設置される従来公知の、ルーバ、ガラリ等である。また、風量調整部材は、従来公知のレジスター等である。
また、カバー部材および風量調整部材は、管状部材の消音装置が設置された側の端面に設置されてもよいし、消音装置が設置されていない側の端面に設置されてもよい。
また、例えば、図１に示すように、風量調整部材２０が消音装置１４側に設置される場合には、軸方向から見た際に、風量調整部材２０が消音装置１４を全て覆うように設置されるのが好ましい。カバー部材が消音装置１４側に設置される場合も同様である。
Further, the muffling system may include at least one of a cover member installed on one end surface of the tubular member and an air volume adjusting member installed on the other end portion. The cover member is a conventionally known louver, louver or the like installed in a ventilation port, an air conditioning duct, or the like. The air volume adjusting member is a conventionally known register or the like.
Further, the cover member and the air volume adjusting member may be installed on the end surface of the tubular member on the side where the muffler is installed, or may be installed on the end surface on the side where the muffler is not installed.
Further, for example, as shown in FIG. 1, when the air volume adjusting member 20 is installed on the silencer 14 side, the air volume adjusting member 20 is installed so as to cover the entire silencer 14 when viewed from the axial direction. Preferably. The same applies when the cover member is installed on the silencer 14 side.
また、図１に示す例においては、消音装置１４は化粧板４０側の端面が、化粧板４０の壁１２とは反対側の面と面一に配置される構成とした。すなわち、化粧板４０に形成される貫通孔を消音装置１４の外径と略同じにして、化粧板４０の貫通孔に消音装置１４を挿通させる構成としたが、図２７に示すように、消音装置１４は化粧板４０側の端面が、化粧板４０の壁１２側の面よりも壁１６側に配置される構成としてもよい。あるいは、図１に示す例では、消音装置１４は化粧板４０側の端面と、化粧板４０の壁１２とは反対側の面とが面一となる構成としたが、これに限定はされず、消音装置１４の一部が、化粧版４０がある平面上に存在する構成であってもよい。
化粧板４０の貫通孔に消音装置１４を挿通させる構成とすることで、消音装置の設置、交換等が容易になる点で好ましい。
Further, in the example shown in FIG. 1, the silencer 14 is configured such that the end surface of the decorative plate 40 side is flush with the surface of the decorative plate 40 opposite to the wall 12. That is, the through hole formed in the decorative plate 40 is made substantially the same as the outer diameter of the muffling device 14, and the muffling device 14 is inserted into the through hole of the decorative plate 40. However, as shown in FIG. The device 14 may be configured such that the end surface on the decorative plate 40 side is arranged closer to the wall 16 than the surface on the wall 12 side of the decorative plate 40. Alternatively, in the example shown in FIG. 1, the muffling device 14 has a configuration in which the end surface on the decorative plate 40 side and the surface on the opposite side of the wall 12 of the decorative plate 40 are flush with each other, but the invention is not limited to this. The part of the muffling device 14 may be present on the plane where the makeup plate 40 is present.
It is preferable that the silencer 14 be inserted into the through hole of the decorative plate 40, because installation and replacement of the silencer are easy.
消音装置１４の消音器２２は、サイズが大きいほど消音性能が高くなる。
ここで、図１に示すように、消音装置１４は化粧板４０側の端面が、化粧板４０の壁１２とは反対側の面と面一に配置される構成の場合には、消音器２２のサイズが大きいと、化粧板４０側にレジスターのような風量調整部材２０を設置しても、室内から化粧板４０に形成した貫通孔（消音装置１４と化粧板４０との境界）が視認されてしまうおそれがある。従って、図２８に示すように、風量調整部材２０と化粧板４０および消音装置１４との間に、境界カバー４２を設置するのが好ましい。これにより、室内側（風量調整部材２０側）から見た際に、図２９に示すように、化粧板４０の貫通孔が境界カバー４２によって隠れるので、意匠性を高めることができる。
The larger the size of the muffler 22 of the muffler 14, the higher the muffling performance.
Here, as shown in FIG. 1, in the silencer 14, when the end surface on the decorative plate 40 side is arranged flush with the surface of the decorative plate 40 opposite to the wall 12, the silencer 22 If the size is large, even if the air volume adjusting member 20 such as a register is installed on the decorative plate 40 side, the through hole (the boundary between the silencer 14 and the decorative plate 40) formed in the decorative plate 40 is visually recognized from the room. There is a risk that Therefore, as shown in FIG. 28, it is preferable to install the boundary cover 42 between the air volume adjusting member 20 and the decorative plate 40 and the muffling device 14. As a result, when viewed from the indoor side (air volume adjusting member 20 side), the through hole of the decorative plate 40 is hidden by the boundary cover 42 as shown in FIG. 29, so that the designability can be improved.
なお、図２８に示す例では、消音装置１４と境界カバー４２とを別部材としたが、消音装置１４と境界カバー４２を一体的に形成してもよい。すなわち、消音装置１４にフリンジを設けてもよい。 Note that, in the example shown in FIG. 28, the silencer 14 and the boundary cover 42 are separate members, but the silencer 14 and the boundary cover 42 may be integrally formed. That is, the silencer 14 may be provided with a fringe.
また、図１等に示す例においては、消音装置１４の内径は、管状部材１２と略同じ径で一様としたが、これに限定はされない。図３０に示す消音システム１０ｒのように、消音器２２部分の内径を挿入部２６の内径よりも大きく、すなわち、管状部材１２の内径よりも大きくしてもよい。
消音器２２部分の内径を管状部材１２の内径よりも大きくすることで、管状部材１２の径よりも大きい径の管状部材用の、大きな風量調整部材２０を用いることができる。大きな風量調整部材２０を用いることで、化粧板４０の貫通孔が風量調整部材２０によって隠れるので、意匠性を高めることができる。
Further, in the example shown in FIG. 1 and the like, the inner diameter of the muffling device 14 is substantially the same as that of the tubular member 12, but is not limited to this. As in the silencer system 10r shown in FIG. 30, the inner diameter of the silencer 22 portion may be larger than the inner diameter of the insertion portion 26, that is, larger than the inner diameter of the tubular member 12.
By making the inner diameter of the silencer 22 portion larger than the inner diameter of the tubular member 12, it is possible to use the large air volume adjusting member 20 for the tubular member having a diameter larger than the diameter of the tubular member 12. By using the large air volume adjusting member 20, the through hole of the decorative plate 40 is hidden by the air volume adjusting member 20, so that the designability can be improved.
また、図３１に示す消音システム１０ｓのように、消音装置１４と風量調整部材２０とを一体化してもよい。
図１等に示すように、市販のレジスター等の風量調整部材２０は、差込部を有し、差込部を消音装置１４に差し込んで設置される。しかしながら、市販のレジスターの差し込み部は、接続時の剛性および密閉性確保のため、長さが５ｃｍ程度あり、消音装置１４の設計が制限されるおそれがある。これに対して、図３１のように、消音装置１４と風量調整部材２０とを一体化することで、消音装置１４の設計自由度が高くなり、また、施工も簡易化される点で好ましい。
Further, as in the muffling system 10s shown in FIG. 31, the muffling device 14 and the air volume adjusting member 20 may be integrated.
As shown in FIG. 1 and the like, a commercially available air flow rate adjusting member 20 such as a register has an insertion portion, and the insertion portion is installed by being inserted into the silencer 14. However, the insertion portion of the commercially available register has a length of about 5 cm in order to secure the rigidity and the airtightness at the time of connection, which may limit the design of the silencer 14. On the other hand, as shown in FIG. 31, by integrating the muffling device 14 and the air volume adjusting member 20, the degree of freedom in designing the muffling device 14 is increased, and the construction is also preferable, which is preferable.
なお、消音システムが、カバー部材および風量調整部材を有する場合には、管状部材内に生じる第一共鳴は、カバー部材、風量調整部材および消音装置を含む消音システムにおける管状部材の第一共鳴である。従って、消音器の空洞部の長さＬdは、カバー部材、風量調整部材および消音装置を含む消音システムにおける管状部材の第一共鳴の共鳴周波数における音波の波長λの１／４よりも短い。 When the muffling system has the cover member and the air volume adjusting member, the first resonance generated in the tubular member is the first resonance of the tubular member in the muffling system including the cover member, the air volume adjusting member, and the muffling device. . Therefore, the length L d of the cavity of the muffler is shorter than 1/4 of the wavelength λ of the sound wave at the resonance frequency of the first resonance of the tubular member in the muffling system including the cover member, the air volume adjusting member, and the muffling device.
消音器２２および消音装置１４の形成材料としては、金属材料、樹脂材料、強化プラスチック材料、および、カーボンファイバ等を挙げることができる。金属材料としては、例えば、アルミニウム、チタン、マグネシウム、タングステン、鉄、スチール、クロム、クロムモリブデン、ニクロムモリブデン、および、これらの合金等の金属材料を挙げることができる。また、樹脂材料としては、例えば、アクリル樹脂、ポリメタクリル酸メチル、ポリカーボネート、ポリアミドイド、ポリアリレート、ポリエーテルイミド、ポリアセタール、ポリエーテルエーテルケトン、ポリフェニレンサルファイド、ポリサルフォン、ポリエチレンテレフタラート、ポリブチレンテレフタラート、ポリイミド、および、トリアセチルセルロース等の樹脂材料を挙げることができる。また、強化プラスチック材料としては、炭素繊維強化プラスチック（ＣＦＲＰ：Carbon Fiber Reinforced Plastics）、および、ガラス繊維強化プラスチック（ＧＦＲＰ：Glass Fiber Reinforced Plastics）を挙げることができる。
ここで、消音器２２および消音装置１４は、排気口等に利用可能な点から、難燃材料より耐熱性の高い材料からなることが好ましい。耐熱性は、例えば、建築基準法施行令の第百八条の二各号を満たす時間で定義することができる。建築基準法施行令の第百八条の二各号を満たす時間が５分間以上１０分間未満の場合が難燃材料であり、１０分間以上２０分間未満の場合が準不燃材料であり、２０分間以上の場合が不燃材料である。ただし耐熱性は各分野ごとで定義されることが多い。そのため、消音システムを利用する分野に合わせて、消音器２２および消音装置１４を、その分野で定義される難燃性相当以上の耐熱性を有する材料からなるものとすればよい。
Examples of the material for forming the silencer 22 and the silencer 14 include a metal material, a resin material, a reinforced plastic material, and carbon fiber. Examples of the metal material include metal materials such as aluminum, titanium, magnesium, tungsten, iron, steel, chromium, chromium molybdenum, nichrome molybdenum, and alloys thereof. Further, as the resin material, for example, acrylic resin, polymethyl methacrylate, polycarbonate, polyamideide, polyarylate, polyetherimide, polyacetal, polyether ether ketone, polyphenylene sulfide, polysulfone, polyethylene terephthalate, polybutylene terephthalate, Examples of the resin material include polyimide and triacetyl cellulose. Further, as the reinforced plastic material, carbon fiber reinforced plastics (CFRP: Carbon Fiber Reinforced Plastics) and glass fiber reinforced plastics (GFRP: Glass Fiber Reinforced Plastics) can be mentioned.
Here, the muffler 22 and the muffler 14 are preferably made of a material having higher heat resistance than the flame-retardant material from the viewpoint that it can be used for the exhaust port and the like. The heat resistance can be defined, for example, by the time for satisfying each item of Article 108-2 of the Enforcement Order of the Building Standards Act. Flame-retardant material when the time to meet each item of Article 108-2 of the Building Standards Act is 5 minutes or more and less than 10 minutes, quasi-incombustible material when the time is 10 minutes or more and less than 20 minutes, and 20 minutes The above cases are non-combustible materials. However, heat resistance is often defined for each field. Therefore, the muffler 22 and the muffling device 14 may be made of a material having heat resistance equal to or higher than flame retardancy defined in the field, depending on the field in which the muffling system is used.
また、図３２に示す消音システム１０ｔのように、各消音器２２の開口部３２が、音波は透過し、空気（風）は遮蔽する防風用フィルム４４によって覆われているのが好ましい。
消音器２２の空洞部３０内に空気が流入可能な構成の場合には、直管の場合に比べて、消音システム全体としての圧力損失が大きくなる。そのため、通気量が少なくなってしまうおそれがある。これに対して、各消音器２２の開口部３２を防風用フィルム４４で覆う構成とすることで、防風用フィルム４４が音波を透過するため、消音器２２による消音の効果は得られ、かつ、防風用フィルム４４が空気を遮蔽するため、空洞部３０内に空気が流入するのを抑制して圧力損失を低減することができる。
Further, as in the muffling system 10t shown in FIG. 32, it is preferable that the opening 32 of each muffler 22 be covered with a windbreak film 44 that transmits sound waves and shields air (wind).
In the case of a structure in which air can flow into the cavity 30 of the silencer 22, the pressure loss of the silencer system as a whole becomes larger than that in the case of a straight pipe. Therefore, there is a possibility that the amount of ventilation is reduced. On the other hand, by making the opening 32 of each silencer 22 covered with the windbreak film 44, the windbreak film 44 transmits sound waves, so that the silencer 22 has a sound deadening effect, and Since the windbreak film 44 shields air, it is possible to suppress the inflow of air into the cavity 30 and reduce the pressure loss.
防風用フィルム４４は、非通気のフィルムであってもよく、通気性の低いフィルムであってもよい。
非通気の防風用フィルム４４の材料としては、ポリメタクリル酸メチル（ＰＭＭＡ）などのアクリル樹脂、ポリエチレンテレフタレート（ＰＥＴ）、ポリカーボネート、ポリアミドイド、ポリアリレート、ポリエーテルイミド、ポリアセタール、ポリエーテルエーテルケトン、ポリフェニレンサルファイド、ポリサルフォン、ポリブチレンテレフタラート、ポリイミド、トリアセチルセルロース等の樹脂材料、が利用可能である。
低通気性の防風用フィルム４４の材料としては、上記樹脂からなる多孔質フィルム、不織布（レジンボンド不織布、サーマルボンド不織布、スパンボンド不織布、スパンレース不織布、ナノファイバー不織布）、織布、紙等が利用可能である。
防風用フィルム４４の厚みは、材質にもよるが、１μｍ〜５００μｍが好ましく、３μｍ〜３００μｍがより好ましく、５μｍ〜１００μｍがより好ましい。
The windbreak film 44 may be a non-breathable film or a film having low breathability.
Examples of the material of the non-ventilating windproof film 44 include acrylic resin such as polymethylmethacrylate (PMMA), polyethylene terephthalate (PET), polycarbonate, polyamideide, polyarylate, polyetherimide, polyacetal, polyetheretherketone, and polyphenylene. Resin materials such as sulfide, polysulfone, polybutylene terephthalate, polyimide and triacetyl cellulose can be used.
Examples of the material of the low-permeability windbreak film 44 include porous films made of the above resins, non-woven fabrics (resin-bonded non-woven fabrics, thermal-bonded non-woven fabrics, spun-bonded non-woven fabrics, spun-laced non-woven fabrics), woven fabrics, papers, and the like. It is available.
Although depending on the material, the thickness of the windbreak film 44 is preferably 1 μm to 500 μm, more preferably 3 μm to 300 μm, and further preferably 5 μm to 100 μm.
また、本発明の消音システムにおいて、他の市販の防音部材を有していてもよい。
例えば、図３３に示す消音システム１０ｕのように、管状部材１２の一方の端部には、本発明における消音装置１４が配置され、管状部材１２の内部には、内挿型消音器５０が配置される構成としてもよい。
また、図３４に示す消音システム１０ｖのように、管状部材１２の一方の端部には、本発明における消音装置１４が配置され、管状部材１２の他方の端部には、野外設置型の防音フード５２が配置される構成としてもよい。
あるいは、管状部材１２の一方の端部には、本発明における消音装置１４が配置され、管状部材１２の内部には、内挿型消音器５０が配置され、管状部材１２の他方の端部には、野外設置型の防音フード５２が配置される構成としてもよい。
このように、他の防音部材と組み合わせることで、より広い帯域で高い防音性能を得られる。
Further, the sound deadening system of the present invention may have another commercially available soundproof member.
For example, like the silencing system 10u shown in FIG. 33, the silencing device 14 of the present invention is disposed at one end of the tubular member 12, and the insertion silencer 50 is disposed inside the tubular member 12. It may be configured to be.
Further, as in the sound deadening system 10v shown in FIG. 34, the sound deadening device 14 of the present invention is arranged at one end of the tubular member 12, and the outdoor soundproofing is installed at the other end of the tubular member 12. The hood 52 may be arranged.
Alternatively, the silencer 14 according to the present invention is disposed at one end of the tubular member 12, the insertion silencer 50 is disposed inside the tubular member 12, and the other end of the tubular member 12 is disposed. The field-installed soundproof hood 52 may be arranged.
In this way, by combining with another soundproofing member, high soundproofing performance can be obtained in a wider band.
内挿型消音器５０としては、種々の公知の防音スリーブが利用可能である。例えば、株式会社新協和製：防音スリーブ（SK-BO100等）、大建プラスチックス株式会社製：防音スリーブ（100NS2等）、西邦工業株式会社製 自然換気用サイレンサー（SEIHO NPJ100等）、株式会社ユニックス製：サイレンサー（UPS100SA等）、株式会社建友製：サイレントスリーブＰ（HMS-K等）等を用いることができる。
野外設置型の防音フード５２としては、種々の公知の防音スリーブが利用可能である。例えば、株式会社ユニックス製：防音フード（SSFW-A10M等）、株式会社シルファー製：防音型フード（BON-TS等）等を用いることができる。
Various known soundproof sleeves can be used as the insertion silencer 50. For example, Shinkyowa Co., Ltd .: Soundproof sleeve (SK-BO100 etc.), Daiken Plastics Co., Ltd .: Soundproof sleeve (100NS2 etc.), Seiho Kogyo Co., Ltd. natural ventilation silencer (SEIHO NPJ100 etc.), Inc. A silencer (UPS100SA etc.) manufactured by Unix, a silent sleeve P (HMS-K etc.) manufactured by Kentou Co., Ltd. can be used.
As the outdoor-installed soundproof hood 52, various known soundproof sleeves can be used. For example, a soundproof hood (SSFW-A10M etc.) manufactured by Unix Co., Ltd., a soundproof hood (BON-TS etc.) manufactured by Sylfer, Inc. can be used.
以下に実施例に基づいて本発明をさらに詳細に説明する。以下の実施例に示す材料、使用量、割合、処理内容、処理手順等は、本発明の趣旨を逸脱しない限り適宜変更することができる。したがって、本発明の範囲は以下に示す実施例により限定的に解釈されるべきものではない。 Hereinafter, the present invention will be described in more detail based on examples. Materials, usage amounts, ratios, processing contents, processing procedures, and the like shown in the following examples can be appropriately changed without departing from the spirit of the present invention. Therefore, the scope of the present invention should not be limitedly interpreted by the following examples.
［シミュレーション］
まず、本発明の消音システムについてシミュレーションを行なった結果を説明する。
シミュレーションは、有限要素法計算ソフトCOMSOL ver5.3（ＣＯＭＳＯＬ社）の音響モジュールを用いて行なった。
[simulation]
First, the result of a simulation performed on the silencing system of the present invention will be described.
The simulation was performed using an acoustic module of the finite element method calculation software COMSOL ver5.3 (COMSOL).
［参考例］
まず、リファレンスとして、消音器を設置しない場合の管状部材を透過する音波についてシミュレーションを行なった。シミュレーションにおいて壁１６と化粧板４０とその間の空間との合計長さ（厚み）は２００ｍｍとし、内径１００ｍｍの管状部材１２が貫通する構成とした。シミュレーションによって、管状部材を透過して一方の空間から他方の空間に伝搬する音波の音圧（透過音圧）と周波数との関係を算出した。結果を図３５に示す。なお、透過音圧は、第一次共鳴周波数の透過音圧を１として規格化した値である。
図３５に示すように、消音器を設置しない場合には、管状部材に生じる共鳴の共鳴周波数で透過音圧が高くなっている。第一共鳴周波数は６３０Ｈｚ、第二共鳴周波数は１３４０Ｈｚ、第三共鳴周波数は２１４０Ｈｚである。
[Reference example]
First, as a reference, a simulation was carried out on a sound wave passing through a tubular member when a silencer was not installed. In the simulation, the total length (thickness) of the wall 16, the decorative plate 40, and the space between them is 200 mm, and the tubular member 12 having an inner diameter of 100 mm penetrates. By simulation, the relationship between the sound pressure (transmitted sound pressure) of sound waves transmitted through the tubular member and propagating from one space to the other space was calculated. Results are shown in FIG. The transmitted sound pressure is a value standardized with the transmitted sound pressure of the first resonance frequency set to 1.
As shown in FIG. 35, when the silencer is not installed, the transmitted sound pressure is high at the resonance frequency of the resonance generated in the tubular member. The first resonance frequency is 630 Hz, the second resonance frequency is 1340 Hz, and the third resonance frequency is 2140 Hz.
［実施例１］
次に、実施例１として、図１０に示すように、壁１６と化粧板４０との間の空間の化粧板４０側に消音器２２を配置した構成についてシミュレーションを行なった。
なお、図１０は消音器２２を１つ配置した例であるが、以下のシミュレーションにおいては消音器２２は軸方向に２つ配置した。壁１６側の消音器を消音器２２ａとし、化粧板４０側の消音器を消音器２２ｂとする。
消音器２２ａおよび消音器２２ｂは、Ｌ字型の消音器であり、周面方向において管状部材１２の外周面の全周に沿った円環状であり、開口部３２が周面方向に沿ったスリット状に形成された形状である。また、消音器２２ａおよび消音器２２ｂの空洞部３０内には吸音材２４が配置される構成とした。
[Example 1]
Next, as Example 1, as shown in FIG. 10, a simulation was performed for a configuration in which the silencer 22 was arranged on the decorative plate 40 side in the space between the wall 16 and the decorative plate 40.
Although FIG. 10 shows an example in which one silencer 22 is arranged, two silencers 22 are arranged in the axial direction in the following simulation. The muffler on the wall 16 side is the muffler 22a, and the muffler on the decorative plate 40 side is the muffler 22b.
The muffler 22a and the muffler 22b are L-shaped mufflers, and are ring-shaped along the entire circumference of the outer peripheral surface of the tubular member 12 in the circumferential direction, and the opening 32 is a slit along the circumferential direction. It is a shape formed into a shape. Further, the sound absorbing material 24 is arranged in the hollow portion 30 of the muffler 22a and the muffler 22b.
消音器２２ａの空洞部３０の幅Ｌwは１８ｍｍ、長さＬd1は４０ｍｍとし、軸方向の開口部３２の幅Ｌoは１５ｍｍとした。すなわち、空洞部３０の深さＬdは３２．５ｍｍである。
消音器２２ｂの空洞部３０の幅Ｌwは１８ｍｍとし、軸方向の開口部３２の幅Ｌoは空洞部３０の長さに連動して変化するとした。これは図５に示すように、消音器２２の長さを調整する際に、第２部材２１ｂの位置を変えた場合に、開口部３２の幅が広がるためである。
なお、消音器２２ａおよび消音器２２ｂ共に、開口部３２は軸方向において、空洞部３０の壁側の端部に配置した。
また、吸音材２４は、消音器２２ａおよび消音器２２ｂそれぞれの空洞部３０の全域に充填されるものとした。吸音材２４の流れ抵抗は４００００［Ｐａ・ｓ／ｍ2］とした。以下の実施例においても特に記載がない場合は、吸音材２４は空洞部３０の全域に充填されるものとし、吸音材２４の流れ抵抗は４００００［Ｐａ・ｓ／ｍ2］としてシミュレーションを行った。
消音器２２ｂの空洞部３０の長さＬd１を、４０ｍｍ（開口幅Ｌo＝１０ｍｍ）、５０ｍｍ（開口幅Ｌo＝２０ｍｍ）、６０ｍｍ（開口幅Ｌo＝３０ｍｍ）としてそれぞれシミュレーションを行なった。
結果を図３５に示す。なお、透過音圧は、リファレンスの第一次共鳴周波数の透過音圧を１として規格化した値である。
また、図３６には、周波数帯域（オクターブバンド周波数）ごとに透過損失の平均値を求めた結果を示す。
図３５および図３６に示すように、本発明の実施例は、リファレンスに対して、共鳴周波数での透過音圧が低くなっていることがわかる。また、空洞部３０の深さＬdが深いほど（消音器の長さが長いほど）、透過音圧が低くなることがわかる。従って、壁１６と化粧板４０との間に配置する消音器の長さを、壁１６と化粧板４０との間の距離に合わせて調整して最大化することで、防音性能を最大化することができることがわかる。
The width L w of the cavity 30 of the muffler 22a was 18 mm, the length L d1 was 40 mm, and the width L o of the opening 32 in the axial direction was 15 mm. That is, the depth L d of the cavity 30 is 32.5 mm.
The width L w of the hollow portion 30 of the silencer 22b is set to 18 mm, and the width L o of the opening 32 in the axial direction changes in association with the length of the hollow portion 30. This is because, as shown in FIG. 5, when the length of the muffler 22 is adjusted, the width of the opening 32 becomes wider when the position of the second member 21b is changed.
Note that both the muffler 22a and the muffler 22b have the opening 32 arranged at the wall-side end of the cavity 30 in the axial direction.
The sound absorbing material 24 is filled in the entire cavity 30 of each of the muffler 22a and the muffler 22b. The flow resistance of the sound absorbing material 24 was set to 40,000 [Pa · s / m 2 ]. Also in the following examples, unless otherwise specified, the sound absorbing material 24 is assumed to be filled in the entire cavity 30, and the flow resistance of the sound absorbing material 24 is set to 40,000 [Pa · s / m 2 ] for simulation. .
The simulation was performed by setting the length L d1 of the cavity portion 30 of the silencer 22b to 40 mm (opening width L o = 10 mm), 50 mm (opening width L o = 20 mm), and 60 mm (opening width L o = 30 mm).
Results are shown in FIG. The transmitted sound pressure is a value standardized with the transmitted sound pressure at the primary resonance frequency of the reference being 1.
Further, FIG. 36 shows the result of obtaining the average value of the transmission loss for each frequency band (octave band frequency).
As shown in FIGS. 35 and 36, it can be seen that in the example of the present invention, the transmitted sound pressure at the resonance frequency is lower than that of the reference. It is also understood that the deeper the depth L d of the cavity 30 (the longer the length of the silencer), the lower the transmitted sound pressure. Therefore, the length of the muffler arranged between the wall 16 and the decorative plate 40 is adjusted to be maximum according to the distance between the wall 16 and the decorative plate 40, thereby maximizing the soundproof performance. You can see that you can.
次に、消音器２２の空洞部３０内に配置される吸音材２４の流れ抵抗についてシミュレーションを行なった結果について説明する。
実施例１のモデルにおいて、吸音材２４の流れ抵抗を種々変更してシミュレーションを行なった結果を図３７に示す。空洞部の深さＬdは８０ｍｍ、空洞部の幅Ｌwは１０ｍｍ、開口部の幅Ｌoは１０ｍｍ、面積割合Ｓ1／Ｓdは５．５％、軸方向における開口部の位置は中央である。
図３７から流れ抵抗には最適な範囲があることがわかる。これは、流れ抵抗が大きくなりすぎると吸音材２４内を通過しにくくなり、吸音材２４による音エネルギーから熱エネルギーへの変換効率が低くなってしまうためである。
Next, the result of simulation of the flow resistance of the sound absorbing material 24 arranged in the cavity 30 of the silencer 22 will be described.
FIG. 37 shows the result of simulation performed by changing the flow resistance of the sound absorbing material 24 variously in the model of the first embodiment. The depth L d of the cavity is 80 mm, the width L w of the cavity is 10 mm, the width L o of the opening is 10 mm, the area ratio S 1 / S d is 5.5%, and the position of the opening in the axial direction is the center. Is.
It can be seen from FIG. 37 that the flow resistance has an optimum range. This is because if the flow resistance becomes too large, it will be difficult for the sound absorbing material 24 to pass through, and the efficiency of conversion of sound energy into heat energy by the sound absorbing material 24 will be low.
また、以上のシミュレーション結果に基づいて、空洞部３０の深さＬdと吸音材の流れ抵抗との組み合わせに対して、透過音圧を測定した結果を図３８および図３９に示す。図３８は、空洞部３０の深さＬdが１０ｍｍ（１ｃｍ）〜１４０ｍｍ（１４ｃｍ）それぞれの場合の、吸音材２４の流れ抵抗と透過音圧のピーク値との関係を表すグラフである。図３９は、空洞部３０の深さＬdと吸音材２４の流れ抵抗に対する透過音圧のピーク値を表すグラフである。
図３８および図３９に示すように、吸音材２４の流れ抵抗は、空洞部３０の深さＬdに応じて好適な範囲があることがわかる。この結果から、本発明の共鳴音を選択的に吸音する効果が表れる流れ抵抗の範囲は、（ｌｏｇ（０．１×Ｌd）−１．２５）／０．２４＜ｌｏｇ（σ1）＜５．６が好ましく、（ｌｏｇ（（０．１×Ｌd））−１．３２）／０．２４＜ｌｏｇ（σ1）＜５．２がより好ましく、（ｌｏｇ（（０．１×Ｌd））−１．３９）／０．２４＜ｌｏｇ（σ1）＜４．７がさらに好ましい。なお、上記式において、Ｌdの単位は［ｍｍ］であり、流れ抵抗σ1の単位は［Ｐａ・ｓ／ｍ2］であり、ｌｏｇは自然対数である。
以上の結果より本発明の効果は明らかである。
38 and 39 show the results of measuring the transmitted sound pressure for the combination of the depth L d of the cavity 30 and the flow resistance of the sound absorbing material based on the above simulation results. FIG. 38 is a graph showing the relationship between the flow resistance of the sound absorbing material 24 and the peak value of the transmitted sound pressure when the depth L d of the hollow portion 30 is 10 mm (1 cm) to 140 mm (14 cm). FIG. 39 is a graph showing the peak value of the transmitted sound pressure with respect to the depth L d of the hollow portion 30 and the flow resistance of the sound absorbing material 24.
As shown in FIGS. 38 and 39, it can be seen that the flow resistance of the sound absorbing material 24 has a suitable range according to the depth L d of the cavity 30. From this result, the range of the flow resistance in which the effect of selectively absorbing the resonance sound of the present invention appears is (log (0.1 × L d ) −1.25) /0.24 <log (σ 1 ) < 5.6 is preferable, (log ((0.1 × L d )) − 1.32) /0.24 <log (σ 1 ) <5.2 is more preferable, and (log ((0.1 × L d d ))-1.39) /0.24 <log ([sigma] 1 ) <4.7 is more preferable. In the above equation, the unit of L d is [mm], the unit of flow resistance σ 1 is [Pa · s / m 2 ], and log is the natural logarithm.
From the above results, the effect of the present invention is clear.
１０ａ〜１０ｖ 消音システム
１２ 管状部材
１４ 消音装置
１６ 壁
１８ カバー部材
２０ 風量調整部材
２１ａ、２３ａ 第１部材
２１ｂ、２３ｂ 第２部材
２１ｃ、２３ｄ、２３ｅ スペーサー
２１ｄ ストッパー
２１ｅ 粘着テープ
２１ｆ 穴部
２１ｇ 突起部
２１ｈ ねじ部
２２、２２ａ、２２ｂ 消音器
２３ｃ 第３部材
２４、２４ａ、２４ｂ 吸音材
２６ 挿入部
３０、３０ａ、３０ｂ 空洞部
３２、３２ａ、３２ｂ 開口部
４０ 化粧板
４２ 境界カバー
４４ 防風用フィルム
５０ 内挿型消音器
５２ 防音フード
６０ 微細穿孔板
６２ シート部材
６４ 貫通孔
１００、１０８ 底面部
１０２、１０６ 外周部
１０４ 内周部
10a-10v Silencer system 12 Tubular member 14 Silencer 16 Wall 18 Cover member 20 Air volume adjustment member 21a, 23a 1st member 21b, 23b 2nd member 21c, 23d, 23e Spacer 21d Stopper 21e Adhesive tape 21f Hole 21g Projection 21h Screw part 22, 22a, 22b Muffler 23c Third member 24, 24a, 24b Sound absorbing material 26 Insertion part 30, 30a, 30b Cavity part 32, 32a, 32b Opening 40 Decorative plate 42 Boundary cover 44 Windproof film 50 Insertion Mold silencer 52 Soundproof hood 60 Micro perforated plate 62 Sheet member 64 Through holes 100, 108 Bottom part 102, 106 Outer peripheral part 104 Inner peripheral part
Claims (11)
前記消音装置は、前記壁の一方の端面側において、前記管状部材の外側に配置され、空洞部および前記空洞部と外部とを連通する開口部を有する１以上の消音器を有し、
前記消音器の開口部の少なくとも１つは、前記消音システム内における前記管状部材の第一共鳴の音場空間に接続されており、
前記消音器の前記空洞部内の少なくとも一部に、または、前記消音器の前記開口部の少なくとも一部を覆う位置に、音エネルギーを熱エネルギーに変換する変換機構が配置されており、
前記消音器内の音波の進行方向における前記空洞部の深さＬdは、前記管状部材の軸方向における前記開口部の幅Ｌoよりも大きく、
前記消音装置を含む前記消音システムにおける前記管状部材の第一共鳴の共鳴周波数における音波の波長をλとすると、前記空洞部の深さＬdは、０．０１１×λ＜Ｌd＜０．２５×λを満たし、
前記消音装置は、前記管状部材の軸方向における前記消音器の長さを調整可能な長さ調整部を有する消音システム。 A muffling system in which a muffling device that muffles the sound passing through the tubular member is installed in the tubular member that is installed through the wall,
The silencer includes one or more silencers, which are disposed outside the tubular member on one end surface side of the wall and have a cavity and an opening communicating the cavity with the outside,
At least one of the openings of the silencer is connected to a sound field space of the first resonance of the tubular member in the silencer system,
At least a part of the hollow portion of the silencer, or at a position that covers at least a portion of the opening of the silencer, a conversion mechanism for converting sound energy into heat energy is arranged.
The depth L d of the hollow portion in the traveling direction of the sound wave in the silencer is larger than the width L o of the opening portion in the axial direction of the tubular member,
When the wavelength of the sound wave at the resonance frequency of the first resonance of the tubular member in the silencing system including the silencing device is λ, the depth L d of the cavity is 0.011 × λ <L d <0.25. Satisfies × λ,
The silencer is a silencer system having a length adjusting unit capable of adjusting a length of the silencer in an axial direction of the tubular member.
前記消音装置は、前記壁と前記化粧板との間に配置され、
前記管状部材の軸方向における前記消音器の長さは、前記長さ調整部によって、前記壁と前記化粧板との間の距離に合わせて調整されている請求項１に記載の消音システム。 A decorative plate is arranged in parallel with the wall on one surface side of the wall,
The silencer is arranged between the wall and the decorative board,
The silencer system according to claim 1, wherein a length of the silencer in an axial direction of the tubular member is adjusted by the length adjusting unit according to a distance between the wall and the decorative plate.
複数の前記消音器は、前記管状部材の軸方向に配列されており、
軸方向に配列された前記消音器の合計長さが、前記長さ調整部によって、前記壁と前記化粧板との間の距離に合わせて調整されている請求項２に記載の消音システム。 The silencer has a plurality of silencers,
A plurality of the silencers are arranged in the axial direction of the tubular member,
The silencer system according to claim 2, wherein a total length of the silencers arranged in the axial direction is adjusted by the length adjusting unit according to a distance between the wall and the decorative plate.
軸方向における前記空洞部の長さが、前記空洞部の深さＬdである請求項１〜４のいずれか一項に記載の消音システム。 In a cross section parallel to the axial direction of the tubular member, the muffler includes the cavity extending in the axial direction and a surface parallel to the axial direction of the cavity on one end side in the axial direction. It has an L-shape with an opening,
The length of the hollow portion in the axial direction, silencer system according to any one of claims 1 to 4 the depth L d is the cavity.
前記挿入部は、中心軸を前記管状部材の中心軸に一致させて配置されており、
前記消音器は、前記挿入部の一方の端面に接続されている請求項１〜６のいずれか一項に記載の消音システム。 The silencer has a tubular insertion portion connected to the tubular member,
The insertion portion, the central axis is arranged to match the central axis of the tubular member,
The said silencer is a silencer system as described in any one of Claims 1-6 connected to one end surface of the said insertion part.
前記吸音材の流れ抵抗σ1は、（１．２５−ｌｏｇ（０．１×Ｌd））／０．２４＜ｌｏｇ（σ1）＜５．６を満たす請求項１〜８のいずれか一項に記載の消音システム。 The conversion mechanism is a sound absorbing material,
The flow resistance σ 1 of the sound absorbing material satisfies (1.25-log (0.1 × L d )) / 0.24 <log (σ 1 ) <5.6. The muffling system described in the item.
前記消音器の前記開口部は、前記空洞部の周方向に沿ってスリット状に形成されている請求項１〜９のいずれか一項に記載の消音システム。 The cavity of the silencer is annular when viewed in a cross section perpendicular to the central axis of the tubular member,
The silencing system according to any one of claims 1 to 9, wherein the opening of the silencer is formed in a slit shape along a circumferential direction of the cavity.
前記管状部材の他方の端部に設置される風量調整部材と、を有し、
前記消音装置、前記カバー部材および前記風量調整部材を含む消音システムにおける前記管状部材の第一共鳴の共鳴周波数における音波の波長をλとすると、前記空洞部の深さＬdはλ／４よりも短い請求項１〜１０のいずれか一項に記載の消音システム。
A cover member installed at one end of the tubular member,
An air volume adjusting member installed at the other end of the tubular member,
Assuming that the wavelength of the sound wave at the resonance frequency of the first resonance of the tubular member in the silencing system including the silencer, the cover member, and the air volume adjusting member is λ, the depth L d of the cavity is greater than λ / 4. A silencer system according to any one of the preceding claims, which is short.
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| JPS57142432A (en) * | 1981-08-10 | 1982-09-03 | Naka Tech Lab | Sound-shielding cylinder for use in vent-port |
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| JP3693521B2 (en) * | 1999-04-21 | 2005-09-07 | 松下エコシステムズ株式会社 | Silent air inlet |
| JP2002242651A (en) * | 2001-02-19 | 2002-08-28 | Hitachi Ltd | Variable reactance type noise eliminator |
| JP3664675B2 (en) * | 2001-10-24 | 2005-06-29 | 株式会社長谷工コーポレーション | Silent ventilation |
| JP4484820B2 (en) * | 2003-04-23 | 2010-06-16 | 小西 幹子 | Ventilation structure with silencer cartridge |
| JP2005344956A (en) * | 2004-06-01 | 2005-12-15 | Univ Kanagawa | Noise reduction ventilating hole |
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| JP6391529B2 (en) * | 2015-04-24 | 2018-09-19 | 三菱電機株式会社 | Silencer |
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