JP3227493B2 - Noise and airflow separation type silencer and low noise type equipment using the same - Google Patents

Description

【発明の詳細な説明】DETAILED DESCRIPTION OF THE INVENTION

【０００１】[0001]

【発明の属する技術分野】本発明は、騒音と気流が混在
して排出される設備装置、排気ダクト、吸気ダクト、喚
気扇、家庭電気製品等の騒音低減に効果を発揮し、工
場、事業所等の敷地境界と作業環境の騒音規制値の遵守
並びに快適な生活環境の確保に役立つ騒音と気流分離型
消音器及びこれを用いた低騒音型設備装置に関する。詳
しくは、工場、事業所等の主要騒音放出源である局部排
気設備、サイクロン、集塵機、冷暖房設備、機械設備等
の防音箱などの排気ダクト及び吸気ダクトから排出され
る騒音、家屋の換気扇、給湯器ボイラー、浄化槽ブロア
等の住宅設備、ヘアードライヤー、掃除機等の家庭電気
製品の騒音などに対し消音効果を発揮する騒音と気流分
離型消音器及びこれを用いた低騒音型設備装置に関す
る。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention is effective in reducing noise of equipment, exhaust ducts, intake ducts, loudspeakers, household electric appliances, etc., in which noise and airflow are mixed and discharged, and is used in factories and offices. The present invention relates to a noise and airflow separation type silencer that is useful for complying with noise regulation values of a site boundary and a work environment, and for ensuring a comfortable living environment, and a low noise type equipment using the same. For details, noise emitted from exhaust ducts and intake ducts such as soundproof boxes such as local exhaust equipment, cyclones, dust collectors, cooling and heating equipment, and mechanical equipment that are major sources of noise emission from factories and offices, house ventilation fans, hot water supply TECHNICAL FIELD The present invention relates to a noise and airflow separation type silencer which exerts a noise reduction effect on household equipment such as a household boiler and a septic tank blower, and a household electric appliance such as a hair dryer and a vacuum cleaner, and a low noise type equipment using the same.

【０００２】[0002]

【従来の技術】工場、事業所等における設備の運転騒音
の低減並びに住宅設備や家庭電気製品から発生する騒音
の低減は、作業環境と快適な生活環境を確保する上で重
要な課題である。作業環境や生活環境の許容騒音レベル
は、労働安全衛生規則、騒音規制法、特定工場における
騒音規制基準、特定建設作業における騒音規制基準、環
境基準、航空機騒音や新幹線鉄道に係る環境基準、都道
府県市町村条例等で、用途地域別、時間帯毎に規制又は
指導されている。2. Description of the Related Art Reducing the operating noise of equipment in factories, offices, and the like, and reducing the noise generated from household equipment and home electric appliances are important issues in securing a work environment and a comfortable living environment. The permissible noise levels in the working environment and living environment are as follows: Occupational Safety and Health Regulations, Noise Regulation Law, Noise Regulation Standards for Specific Factories, Noise Regulation Standards for Specific Construction Work, Environmental Standards, Environmental Standards for Aircraft Noise and Shinkansen Railways, Prefectures It is regulated or instructed by municipal ordinance, etc., by use area and by time of day.

【０００３】気流の特徴は気圧の低い方に流れる性質が
あるのに対し、騒音の特徴は、反射性と直進性があるこ
とである。さらに、単一点音源の騒音発生源近接ｒ₁ｍ
からｒ₂ｍまでの距離による減衰消音量は、（ｄＢ）＝
２０ｌｏｇｒ₂／ｒ₁に近似すること、同レベルの騒音源
が近接する場合の騒音は、単一の騒音源に比べ３ｄＢ増
加すること、騒音の多くは、卓越周波数が数百Ｈｚから
１ＫＨｚを中心とした幾つかの周波数帯の集合体である
こと、騒音レベルと生活感覚の関係は、７０ｄＢ前後で
会話が困難となり、５０ｄＢ前後で睡眠が妨害され、数
百Ｈｚ以下の低周波騒音は不快感を募らせることなどで
ある。また低周波騒音は、高周波騒音に比べ波長が長い
ことから障壁を越えて遠方まで到達しやすく、既存の消
音器では消音が難しいという問題がある。[0003] The characteristic of airflow is that it flows toward the lower pressure, whereas the characteristic of noise is that it has reflectivity and straightness. Furthermore, the noise source proximity r ₁ m of the single point sound source
The attenuation volume due to the distance from to r ₂ m is (dB) =
20 logr ₂ / r ₁ , noise when noise sources of the same level are close to each other increases by 3 dB compared to a single noise source, and most of the noise has a dominant frequency ranging from several hundred Hz to 1 kHz. The relationship between noise level and life sensation is that conversation becomes difficult at around 70 dB, sleep is disturbed at around 50 dB, and low-frequency noise below several hundred Hz is uncomfortable. And so on. In addition, low-frequency noise has a longer wavelength than high-frequency noise, so it is easy to reach a distant place over a barrier, and there is a problem that it is difficult to muffle sound with an existing silencer.

【０００４】例えば、１馬力のブロアから発生する騒音
は、設計上８２±５ｄＢと言われ、その多くは卓越周波
数が数百Ｈｚから１ＫＨｚの低周波である。従って、こ
のようなブロアを使用する工場、事業所の周辺では、快
適な生活環境と快適な作業環境が阻害されやすいことが
判る。このようなことから、工場事業所等の個々の排気
ダクトや吸気ダクトから排出される騒音並びに設備装置
から発生する騒音に対し、低周波領域にも消音効果が大
きく用途共用範囲が広い消音器の開発が強く望まれてい
る。同様に生活環境に密接する台所、浴室等の換気扇騒
音や浄化槽のブロア騒音、家庭電気製品等に対する消音
器も望まれている。For example, the noise generated from a 1-horsepower blower is said to be 82 ± 5 dB in design, and most of the noise has a dominant frequency of several hundred Hz to 1 KHz. Therefore, it is understood that a comfortable living environment and a comfortable working environment are likely to be hindered in the vicinity of a factory or a business using such a blower. For this reason, silencers that have a large noise reduction effect even in the low-frequency range and have a wide range of applications can be used for noise emitted from individual exhaust ducts and intake ducts at factory offices, etc., and noise generated from equipment. Development is strongly desired. Similarly, there is a need for a silencer for a ventilation fan noise in a kitchen or bathroom, a blower noise in a septic tank, a household electric appliance, etc., which are in close contact with the living environment.

【０００５】排気騒音を減らす消音器としては、従来か
らダクト用消音器がある。その原理は、電気の濾波回路
に相当するタイプと、電気の抵抗に相当し騒音エネルギ
ーを熱エネルギーに変換するタイプである。前者の例と
してはダクトに頸部と容積を持つ空洞型ダクト用消音器
がある。後者の例としてはダクト内にガラスマット等の
繊維質吸音材の層を設けた管状吸音型ダクト用消音器が
ある。しかしながらこれらのダクト用消音器はつぎのよ
うな欠点がある。As a muffler for reducing exhaust noise, there is a muffler for a duct conventionally. The principle is a type corresponding to an electric filtering circuit, and a type corresponding to electric resistance and converting noise energy into heat energy. An example of the former is a hollow duct silencer having a neck and a volume in the duct. As an example of the latter, there is a silencer for a tubular sound-absorbing duct in which a layer of a fibrous sound-absorbing material such as a glass mat is provided in the duct. However, these duct silencers have the following disadvantages.

【０００６】（１）空洞型ダクト用消音器（参考分献：
守田栄著 騒音と騒音防止）は、２０ｄＢ低減するため
に、消音器の断面積は接続する排気ダクトの断面積の１
６倍必要とされる。周波数と消音効果の関係は、波長と
ダクト用消音器の長さ及び断面積に依存し、少なくも波
長より長い消音器でなければ効果を期待できない。従っ
て空洞型ダクト用消音器は大型とならざるを得ず、低周
波騒音ほど消音が困難となり、予め騒音発生源毎に周波
数分析を行い専用の寸法設計が必要であるなどの欠点が
ある。 （２）管状吸音型ダクト用消音器は、空洞型ダクト消音
器を、吸音材を使って小型化したものであるが、予め騒
音発生源毎に周波数分析と専用の寸法設計が必要である
ほか、一般に使用される繊維質吸音材は２５０Ｈｚ以下
の低周波騒音には効果が少く、塗料ミスト、油煙、ヒュ
ーム、粉塵等を排出するダクトでは、これらを吸着して
消音効果を減退し圧力損失を増大させるなどの欠点があ
る。さらに従来の消音器は、解体分解が困難な構造であ
ることから吸音材の交換が出来ないと言う欠点がある。(1) Silencer for hollow duct (Reference distribution:
To reduce the noise by 20 dB, the cross-sectional area of the silencer is one of the cross-sectional area of the exhaust duct to be connected.
Six times required. The relationship between the frequency and the silencing effect depends on the wavelength and the length and cross-sectional area of the duct silencer, and the effect cannot be expected unless the silencer is at least longer than the wavelength. Therefore, the muffler for a hollow duct has to be large in size, and it is difficult to muffle the sound with lower frequency noise, and there is a drawback that frequency analysis is performed in advance for each noise source and a special dimensional design is required. (2) The muffler for a tubular sound-absorbing duct is a miniaturized hollow duct muffler using a sound-absorbing material. However, frequency analysis and dedicated dimensional design are required for each noise source in advance. The generally used fibrous sound-absorbing material has little effect on low-frequency noise of 250Hz or less, and in ducts that discharge paint mist, oil smoke, fume, dust, etc. There are drawbacks such as an increase. Further, the conventional silencer has a disadvantage that the sound absorbing material cannot be replaced because the structure is difficult to disassemble and disassemble.

【０００７】（３）これら従来のダクト用消音器は、ダ
クトの先端から侵入する降雨を排出する機能がないた
め、ダクトの先端に取り付けることが出来ず、図９に示
すように排気流入口１から流入された騒音２、気流３等
が消音され、これらが放出される排気放出口４に雨傘５
を付けたり、図１０に示すように排気放出口４であるダ
クトの先端を下方に折り曲げ、降雨６の侵入を防止する
必要がある。このため雨傘５やダクトの曲り部に排気気
流が衝突して新たな騒音が発生し、消音器７の残存騒音
８と合体した騒音が下方に放出され、地上騒音の消音効
果が減退する欠点がある。 （４）従来のダクト用消音器は、大型一体構造で解体分
解が出来ない構造のため、高所への取付けや内部掃除な
どの作業性に欠点がある。(3) Since these conventional silencers for ducts do not have a function of discharging rainfall that enters from the end of the duct, they cannot be attached to the end of the duct, and as shown in FIG. The noise 2, the airflow 3 and the like flowing from the air are silenced, and the umbrella 5
In addition, as shown in FIG. 10, it is necessary to bend the tip of the duct which is the exhaust outlet 4 downward to prevent the rainfall 6 from entering. For this reason, the exhaust air current collides with the umbrella 5 or the bent portion of the duct, and new noise is generated. The noise combined with the residual noise 8 of the muffler 7 is emitted downward, and the noise reduction effect of the ground noise is reduced. is there. (4) Since the conventional silencer for ducts has a large integral structure and cannot be disassembled and disassembled, it has drawbacks in workability such as mounting at a high place and cleaning inside.

【０００８】[0008]

【発明が解決しようとする課題】請求項１及び２記載の
発明は、消音効果が大きく、圧力損失が少なく、用途共
用範囲が広く、消音器で消音できなかった残存騒音と排
気を垂直上空に排出することができるため地上騒音を大
幅に削減でき、かつ構造が簡易で、安価な騒音と気流分
離型消音器を提供する。請求項３記載の発明は、請求項
１及び２記載の発明に加えて、対象周波数帯の選択と気
流抵抗による新たな騒音発生の抑制と圧力損失の抑制の
最適化を図ることができる騒音と気流分離型消音器を提
供する。SUMMARY OF THE INVENTION According to the first and second aspects of the present invention, the noise reduction effect is large, the pressure loss is small, the application range is wide, and the residual noise and exhaust gas that could not be muffled by the muffler are positioned vertically above. Provided is an inexpensive noise and airflow separation type silencer that can significantly reduce ground noise because it can be discharged, and has a simple structure. According to the third aspect of the present invention, in addition to the first and second aspects of the invention, it is possible to optimize the selection of the target frequency band, the suppression of new noise generation due to airflow resistance, and the suppression of pressure loss. An airflow silencer is provided.

【０００９】請求項４記載の発明は、請求項１、２及び
３記載の発明に加えて、降雨を系外に排出することがで
きる全天候型の騒音と気流分離型消音器を提供する。請
求項５記載の発明は、請求項１、２、３及び４記載の発
明に加えて少ない空間容積で、かつ小型で消音効果に優
れる騒音と気流分離型消音器を提供する。請求項６記載
の発明は、請求項１、２、３、４及び５記載の発明に加
えて解体、運搬、組立て等の施工性と掃除、騒音反射
体、外殻等の交換作業性に優れる騒音と気流分離型消音
器を提供する。請求項７記載の発明は、請求項１、２、
３、４、５及び６記載の発明に加えて、従来使用してい
た降雨浸入防止又は浸入降雨の排出機能を有しない従来
の騒音と気流分離型消音器を併用して使用できる騒音と
気流分離型消音器を提供する。請求項８記載の発明は、
消音効果が大きく、圧力損失が少なく、用途共用範囲が
広く、構造が簡易で、安価な騒音と気流分離型消音器を
備えた低騒音型設備装置を提供する。According to a fourth aspect of the present invention, in addition to the first, second and third aspects of the present invention, there is provided an all-weather noise and airflow separation type silencer capable of discharging rainfall out of the system. The fifth aspect of the present invention provides a noise and airflow separation type silencer which has a small space volume, is small in size, and has an excellent noise reduction effect, in addition to the first, second, third and fourth aspects of the invention. The invention of claim 6 is excellent in the workability of disassembly, transportation, assembly, etc., and the workability of cleaning, noise reflectors, outer shells and the like in addition to the inventions of claims 1, 2, 3, 4 and 5. Provide a noise and airflow separation type silencer. The invention according to claim 7 is the invention according to claims 1, 2,
In addition to the inventions described in 3, 4, 5, and 6, noise and airflow separation that can be used by using a conventional noiseless and airflow separation type silencer that does not have a rainfall intrusion prevention or ingress rainfall discharge function that has been used conventionally Provide a type silencer. The invention according to claim 8 is
Provided is a low-noise facility device having a large noise reduction effect, a small pressure loss, a wide range of common use, a simple structure, a low-cost noise and an airflow separation type silencer.

【００１０】[0010]

【課題を解決するための手段】本発明は、騒音と気流が
混在する排気の流入口と放出口を有する角型状又は筒状
の外殻の中に、騒音を一定方向に反射して気流から分離
し、かつ騒音を吸音減衰消音、衝突減衰消音、振動減衰
消音及び位相差減衰消音する機能を有する騒音反射体及
び閉塞空間を設けてなる騒音と気流分離型消音器に関す
る。また、本発明は、円盤状の外殻の中に中空の閉塞空
間を形成し、該円盤状の外殻の片側に排気流入口と反対
側に排気放出口を設け、該閉塞空間に風車状に襞を有す
る多角錐の騒音反射体を下端を排気放出口を覆うように
密着させ、先端を排気放出口の中央になる位置に取付
け、該騒音反射体の円盤状の中心に向かう襞をくり抜い
て気流の通路とし、この襞の内側端部から次の襞の外側
端部につながる襞は残存騒音を閉塞空間の外殻に反射す
る役割を持たせ、該騒音反射体、該閉塞空間、該外殻に
より、吸音減衰消音、衝突減衰消音、振動減衰消音及び
位相差減衰消音を繰り返し行う騒音と気流分離型消音器
に関する。また、本発明は、騒音反射体と閉塞空間の角
度及び距離を調節可能とした騒音と気流分離型消音器に
関する。SUMMARY OF THE INVENTION According to the present invention, there is provided a rectangular or cylindrical outer shell having an inlet and an outlet for exhaust gas in which noise and air flow coexist. The present invention relates to a noise reflector and a noise and airflow separation type silencer having a function of separating sound from noise, and having a function of absorbing, attenuating, attenuating a collision, attenuating a vibration, and attenuating a phase difference. The present invention also provides a hollow closed space inside a disk-shaped outer shell.
A space is formed between one side of the disk-shaped outer shell and the exhaust inlet.
Side with an exhaust outlet, and the closed space has a fold like a windmill
Polygonal pyramid noise reflector with lower end covering exhaust outlet
Attach at the position where the tip is in the center of the exhaust outlet
Cut out the fold toward the disc-shaped center of the noise reflector
Air flow path, from the inner end of this fold to the outside of the next fold
End folds reflect residual noise to the outer shell of the enclosed space
The noise reflector, the closed space, and the outer shell.
From sound absorption damping, collision damping, vibration damping,
The present invention relates to a noise and airflow separation type silencer that repeatedly performs phase difference attenuation silencing . The present invention also relates to a noise and airflow separation type silencer in which the angle and distance between the noise reflector and the closed space can be adjusted.

【００１１】また、本発明は、騒音反射体の下端又はこ
れに相対する外殻の下端に、降雨の排出口を設けてなる
騒音と気流分離型消音器に関する。また、本発明は、閉
塞空間の外周部分が騒音反射体を兼ね、かつこれらが連
続一体化されたものである騒音と気流分離型消音器に関
する。また、本発明は、外殻、騒音反射体及び閉塞空間
が分割構造である騒音と気流分離型消音器に関する。ま
た、本発明は、上記の騒音と気流分離型消音器の下部に
降雨浸入防止又は浸入した降雨の排出機能を有しない騒
音と気流分離型消音器を接続するか又は両者を連結一体
化してなる騒音と気流分離型消音器に関する。さらに、
本発明は、上記の騒音と気流分離型消音器を騒音発生源
の設備装置の内部に備えてなる低騒音型設備装置に関す
る。[0011] The present invention also relates to a noise and air flow separation type silencer in which a rainfall outlet is provided at a lower end of a noise reflector or a lower end of an outer shell opposed thereto. The present invention also relates to a noise and airflow separation type silencer in which an outer peripheral portion of a closed space also functions as a noise reflector and these are continuously integrated. Further, the present invention relates to a noise and airflow separation type silencer in which an outer shell, a noise reflector, and a closed space have a divided structure. In addition, the present invention connects the noise and the airflow separation type silencer which does not have the function of preventing rainfall intrusion or the inflow of rainfall to the lower part of the noise and the airflow separation type silencer, or connects and integrates both. It relates to noise and airflow separation type silencers. further,
The present invention relates to a low-noise facility apparatus including the noise and airflow separation type silencer described above inside a noise source facility apparatus.

【００１２】[0012]

【発明の実施の形態】以下、本発明の騒音と気流分離型
消音器を、図面を用いて詳述する。図１の（ａ）、
（ｂ）、図２の（ａ）、（ｂ）、（ｃ）及び図３の
（ａ）、（ｂ）は、本発明の騒音と気流分離型消音器の
消音原理図であり、図１において排気流入口１から流入
された騒音２と気流３を混在する排気は、騒音反射体９
の表面にある吸音材層１０に衝突し、気流３は気圧の低
い排気放出口４に向かって流れ消音器の系外に排出され
る。一方騒音２は吸音材層１０の内部に進入し吸音され
る。これを吸音減衰消音と呼称する。ついで騒音２は制
振吸音材１１に衝突し減衰する。これを衝突減衰消音と
呼称する。また、制振吸音材１１は吸音減衰消音の機能
も有する。衝突によって生じる騒音反射体９の振動は制
振吸音材１１によって制振され再騒音化が防止される。
これを振動減衰消音と呼称する。また騒音反射体９での
残存騒音８は、衝突する際の入射角度と同程度の反射角
度で反射し、吸音材層１０′に到達して吸音減衰消音が
行われる。DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Hereinafter, a noise and airflow separation type silencer according to the present invention will be described in detail with reference to the drawings. FIG. 1 (a),
(B), (a), (b) and (c) of FIG. 2 and (a) and (b) of FIG. 3 are noise suppression principle diagrams of the noise and airflow separation type silencer of the present invention. , The exhaust gas mixed with the noise 2 and the air flow 3 flowing from the exhaust inlet 1 is mixed with the noise reflector 9.
The air stream 3 collides with the sound absorbing material layer 10 on the surface of the air flow, and flows toward the exhaust outlet 4 having a low atmospheric pressure, and is discharged out of the muffler. On the other hand, the noise 2 enters the sound absorbing material layer 10 and is absorbed. This is called sound absorption attenuation muffling. Next, the noise 2 collides with the vibration damping sound absorbing material 11 and is attenuated. This is called collision damping silencing. Further, the vibration damping sound absorbing material 11 also has a function of sound absorption attenuation and silencing. Vibration of the noise reflector 9 caused by the collision is damped by the damping sound absorbing material 11, so that noise reduction is prevented.
This is called vibration damping silencing. The residual noise 8 at the noise reflector 9 is reflected at a reflection angle substantially equal to the incident angle at the time of collision, reaches the sound absorbing material layer 10 ', and is subjected to sound absorption attenuation and silencing.

【００１３】次に吸音材層１０′及び閉塞空間１３を通
過した残存騒音８は吸音材層１０″、制振吸音材１１で
吸音減衰消音と振動減衰消音される。さらに残存騒音８
は残存騒音の反射距離調節体１６に到達し入射角度と同
程度の反射角度で反射し、前述の経路と逆経路で消音さ
れ騒音反射体９に再び衝突するが、排気流入口１と騒音
反射体９との間及び騒音反射体９と残存騒音の反射距離
調節体１６との間で生じる騒音音波の位相のずれが合体
して消音する。これを位相差減衰消音と呼称する。騒音
のエネルギーは、一つの角型状又は筒状の外殻１２の中
で前述の４種類の消音原理で複合消音され、最終的には
熱エネルギーに変換し消費される。なお残存騒音の反射
距離調節体１６の外側の外殻１２が、位相差消音に適す
る距離の場合は、残存騒音の反射距離調節体１６と外殻
１２とを合体した構造とすることができる。Next, the remaining noise 8 that has passed through the sound absorbing material layer 10 'and the closed space 13 is sound-absorbed and damped by the sound-absorbing material layer 10 "and the vibration-damping sound absorbing material 11. Further, the remaining noise 8
Arrives at the reflection distance adjuster 16 for the residual noise and is reflected at a reflection angle substantially equal to the incident angle, is muffled in the reverse path to the above-mentioned path, and collides with the noise reflector 9 again. The phase shift of the noise sound wave generated between the noise reflector 9 and the noise reflector 9 and the reflection distance adjuster 16 for the residual noise is united and silenced. This is called phase difference attenuation muffling. The noise energy is compounded in one square or cylindrical outer shell 12 based on the above-described four types of noise reduction principles, and is finally converted to heat energy and consumed. Note the outer shell 12 of the reflector distance adjusting member 16 of the residual noise, when the distance suitable for the phase difference silenced may be a structure in which combined a reflection distance adjusting member 16 and the outer shell 12 of the residual noise .

【００１４】ここにおいて、騒音と気流が混在する排気
流入口１と騒音反射体９の角度は、閉塞空間１３におけ
る吸音減衰消音と衝突減衰消音と振動減衰消音及び位相
差減衰消音を高めることができる。また、気流の抵抗に
よる新たな騒音の発生や圧力損失を予防するための重要
な要素でもある。それゆえ消音器の消音性能と共用範囲
を広げるためには、排気流入口１と騒音反射体９との角
度と距離および騒音反射体９と吸音材層１０′との角度
と距離並びに騒音反射体９と底部の外殻１２との角度と
距離の何れかは調節出来る構造とすることが好ましい。
これによって消音器を設置後に排気放出口４から排出す
る残存騒音８の周波数分析を行いながら、位相差減衰消
音の対象周波数の選択と気流３による新たな騒音の発生
と圧力損失の関係を勘案し、最適角度と位置に調節し
て、消音性能を最大限に引き出すことが可能となる。こ
れによって、消音器の用途共用範囲が広くなり、騒音源
毎の専用消音器の設計は不要となる。Here, the angle between the exhaust inlet 1 where the noise and the air flow are mixed and the noise reflector 9 can enhance the sound absorption attenuation, the collision attenuation, the vibration attenuation and the phase difference attenuation in the closed space 13. . It is also an important factor for preventing the generation of new noise and pressure loss due to airflow resistance. Therefore, in order to increase the silencing performance and the common use range of the silencer, the angle and distance between the exhaust inlet 1 and the noise reflector 9, the angle and distance between the noise reflector 9 and the sound absorbing material layer 10 ', and the noise reflector It is preferable that any one of the angle and the distance between 9 and the outer shell 12 at the bottom can be adjusted.
Thus, while performing frequency analysis of the residual noise 8 discharged from the exhaust outlet 4 after the muffler is installed, selection of the target frequency of the phase difference attenuation noise reduction and the relationship between the generation of new noise due to the air flow 3 and the pressure loss are taken into consideration. By adjusting the angle and the position to the optimum, the noise reduction performance can be maximized. As a result, the range of common use of the muffler is widened, and it becomes unnecessary to design a dedicated muffler for each noise source.

【００１５】なお騒音反射体９と閉塞空間１３の角度は
ある特定周波数帯を低減するときは、適宜選定して角度
を調整するが、その角度は例えば２０〜３５度が好まし
く、２５〜３０度であることがさらに好ましい。但し、
オールパス騒音で最大の効果を有する角度は２７．５度
であることが好ましい。また、騒音反射体９と閉塞空間
１３の距離は、位相差消音の効率に影響するが、通常消
音対象設備機器の大きさから制約を受けるのでその都度
適宜選定する。さらに、騒音反射体９と閉塞空間１３の
入り口の吸音材層１０′を湾曲させることは、新たな騒
音発生の予防と気流３の圧力損失を低減するために重要
である。なお、図１の（ａ）及び（ｂ）では、騒音反射
体９と閉塞空間１３の配置の原形を示したが、多面体の
騒音反射体９の周囲に閉塞空間１３を配置したり、閉塞
空間１３に吸音材層１０を設けたり、重層構造にしても
差し支えない。In order to reduce a specific frequency band, the angle between the noise reflector 9 and the closed space 13 is appropriately selected and adjusted, and the angle is preferably, for example, 20 to 35 degrees, and is preferably 25 to 30 degrees. Is more preferable. However,
It is preferable that the angle having the maximum effect on the all-pass noise is 27.5 degrees. Further, the distance between the noise reflector 9 and the closed space 13 affects the efficiency of the phase difference noise reduction. However, the distance is usually limited by the size of the equipment targeted for noise reduction. Furthermore, it is important to bend the noise reflector 9 and the sound absorbing material layer 10 ′ at the entrance of the closed space 13 in order to prevent the generation of new noise and reduce the pressure loss of the airflow 3. Although FIGS. 1A and 1B show the original arrangement of the noise reflector 9 and the closed space 13, the closed space 13 is arranged around the polyhedral noise reflector 9, 13 may be provided with the sound absorbing material layer 10 or may have a multilayer structure.

【００１６】排気放出口４から侵入する降雨６は、騒音
反射体９で捕集し降雨排出口１４から排出する。これに
よって排気放出口４は下方に向けたり雨傘を付ける必要
がなくなり、垂直方向など任意の方向に向けることがで
き、排気放出口４の残存騒音８は垂直方向などの距離に
よって減衰消音し、残存騒音８による地上への影響をな
くすることができる。なお図１の（ａ）及び（ｂ）にお
いて１５は気流の通路、１６は残存騒音の反射距離調節
体及び１７は角度、距離の調節固定部である。The rainfall 6 entering from the exhaust outlet 4 is collected by the noise reflector 9 and discharged from the rainfall outlet 14. This eliminates the need for the exhaust outlet 4 to be directed downward or to attach an umbrella, and allows the exhaust outlet 4 to be directed in any direction such as the vertical direction. The influence on the ground by the noise 8 can be eliminated. In FIGS. 1A and 1B, reference numeral 15 denotes an airflow passage, reference numeral 16 denotes a reflection distance adjusting body for remaining noise, and reference numeral 17 denotes an angle and distance adjustment and fixing portion.

【００１７】図２の（ａ）、（ｂ）及び（ｃ）は、図１
の原理の騒音反射体９を多面体とし周囲に閉塞空間１３
を配置したものである。気流は気圧の低い排気放出口４
に進行し、騒音２は騒音反射体９に衝突し、減衰し、次
いで反射して制振吸音材１１に衝突し、以下反射と直進
性を利用して溝状に構成した一つの閉塞空間１３を無限
長に活用して吸音減衰消音、衝突減衰消音、振動減衰消
音及び位相差減衰消音を繰り返し行うもので、消音器の
小型高性能化に役立つ。FIGS. 2 (a), (b) and (c) show FIG.
The noise reflector 9 of the principle of the above is made into a polyhedron, and the surrounding space 13 is enclosed.
Is arranged. Air flow is low exhaust pressure exhaust outlet 4
The noise 2 collides with the noise reflector 9, attenuates, and then reflects and collides with the vibration damping / absorbing material 11. Hereinafter, one closed space 13 formed in a groove shape using reflection and straightness is used. This is used for infinite length to repeat sound absorption attenuation, collision attenuation, vibration attenuation, and phase difference attenuation, which is useful for miniaturization and high performance of silencers.

【００１８】図３の（ａ）及び（ｂ）は、騒音反射体９
の騒音反射機能などを、湾曲した閉塞空間１３の外周部
分で兼用発揮するもので、上記と同様に吸音減衰消音、
衝突減衰消音、振動減衰消音及び位相差減衰消音を繰り
返し行うもので、少風量の排気の消音に適する。なお閉
塞空間１３を螺旋状に構成しても本発明の目的を達成す
ることができる。FIGS. 3A and 3B show the noise reflector 9.
The noise reflection function and the like are also exerted in the outer peripheral portion of the curved closed space 13, and the sound absorption attenuation damping and silencing as described above,
It repeats collision damping, vibration damping, and phase difference damping, and is suitable for silencing exhaust with small airflow. The object of the present invention can be achieved even if the closed space 13 is formed in a spiral shape.

【００１９】本発明においては、図１、図２及び図３に
示す騒音と気流分離型消音器を重層構造にしたり、本発
明になる騒音と気流分離型消音器の下部に降雨浸入防止
又は浸入降雨の排出機能を有しない従来の騒音と気流分
離型消音器を接続するか又は両者を連結一体化して用い
てもよい。なお本発明になる騒音と気流分離型消音器
は、騒音発生源の設備装置の内部に組み込めば、別々に
制作するものに比較して小型化できるので好ましい。In the present invention, the noise and airflow separation type silencer shown in FIGS. 1, 2 and 3 may have a multi-layer structure, or the noise and airflow separation type silencer according to the present invention may be prevented from entering rainfall or entering the lower part. A conventional noise having no function of discharging rainfall and an airflow separation type silencer may be connected, or both may be connected and integrated. It is preferable that the noise and airflow separation type silencer according to the present invention be incorporated in the equipment of the noise source because the size can be reduced as compared with those separately manufactured.

【００２０】本発明における騒音と気流分離型消音器
は、騒音反射体９と閉塞空間１３の角度及び距離、騒音
反射体９から吸音材層１０′、制振吸音材１１、又は外
殻１２までの距離若しくは閉塞空間１３の外周部分を兼
ねた騒音反射体の曲率、直径、幅等を適正に調節するこ
とによって、位相差減衰消音周波数帯の選択や、効率的
な吸音減衰消音、衝突減衰消音、振動減衰消音が得られ
る。また、排気流入口１から排気放出口４までの間の気
流３の流速は、１０ｍ／秒を越える場合には新たな騒音
が発生したり、圧力損失が増大し易くなる。従って、排
気流入口１の断面積に対する気流の通路１５の断面積の
比は、このことを考慮して気流３の流速を１０ｍ／秒以
下に設計することが好ましい。The noise and airflow separation type silencer according to the present invention includes the angle and distance between the noise reflector 9 and the closed space 13, from the noise reflector 9 to the sound absorbing material layer 10 ′, the vibration damping sound absorbing material 11, or the outer shell 12. By properly adjusting the curvature, diameter, width, etc. of the noise reflector which also serves as the distance of the noise or the outer peripheral portion of the closed space 13, selection of the phase difference attenuation noise reduction frequency band, efficient sound absorption attenuation noise reduction, collision attenuation noise reduction, etc. Thus, vibration damping and silencing can be obtained. If the flow velocity of the air flow 3 from the exhaust inlet 1 to the exhaust outlet 4 exceeds 10 m / sec, new noise is generated and the pressure loss tends to increase. Therefore, the ratio of the cross-sectional area of the airflow passage 15 to the cross-sectional area of the exhaust inlet 1 is preferably designed so that the flow velocity of the airflow 3 is 10 m / sec or less in consideration of this.

【００２１】次に本発明の騒音と気流分離型消音器を構
成する部材の材質について説明する。排気流入口１、騒
音反射体９、排気放出口４、外殻１２等は、鋼板、鍍金
鋼板、ステンレス、アルミ合金、強化プラスチック、木
材、木質ボード類等の材質の中から、排気気流の温度、
含有成分等を考慮して選択する。一般に、質量の大きい
材質ほど消音効果が大きいが、鋼板の間に制振材をサン
ドイッチ状に介在した制振鋼板も有効である。Next, the material of the members constituting the noise and airflow separation type silencer of the present invention will be described. The exhaust inlet 1, the noise reflector 9, the exhaust outlet 4, the outer shell 12 and the like are made of a material such as a steel plate, a plated steel plate, a stainless steel, an aluminum alloy, a reinforced plastic, wood, a wooden board, etc. ,
The selection is made in consideration of the contained components and the like. In general, a material having a larger mass has a greater sound deadening effect, but a damping steel sheet in which a damping material is sandwiched between steel sheets is also effective.

【００２２】吸音材層１０に用いられる吸音材は、無機
質系のガラス繊維、ロックウール、金属繊維、セラミッ
ク繊維、マイカ片、有機質系の人造繊維、パルプ、天然
繊維、炭化物等をマット状、織布、不織布等にしたもの
を、パンチングメタル、エキスパンジョンメタル、金
網、孔付き強化プラスチック等で固定する。これらは、
排気温度や排気に含まれる物質によって耐熱性、耐薬品
性、耐溶剤（有機）性、耐水性等を考慮して選択する。
塗料ミスト、油煙、各種ヒューム、粉塵等を排出する用
途の場合は、これら物質の吸着状態によって解体掃除、
吸音材の交換を行う。また、臭気を伴う排気の場合は、
活性炭や臭気吸着機能を有する多孔質セラミックスなど
を吸音材兼脱臭材として活用することもできる。このた
め消音器は、嵌合い構造やビス止め、ナット止め構造な
ど、簡単に解体組立てできる構造が望ましい。The sound-absorbing material used for the sound-absorbing material layer 10 is made of inorganic glass fiber, rock wool, metal fiber, ceramic fiber, mica chips, organic artificial fiber, pulp, natural fiber, carbide, etc. in a mat-like or woven form. The cloth or nonwoven fabric is fixed with a punching metal, an expansion metal, a wire mesh, a reinforced plastic with holes, or the like. They are,
The selection is made in consideration of heat resistance, chemical resistance, solvent resistance (organic) resistance, water resistance and the like depending on the exhaust temperature and the substances contained in the exhaust.
For applications that emit paint mist, oil fumes, various fumes, dust, etc., dismantling cleaning,
Replace the sound absorbing material. In the case of exhaust with odor,
Activated carbon, porous ceramics having an odor adsorption function, and the like can also be used as a sound absorbing material and a deodorizing material. For this reason, it is desirable that the silencer has a structure that can be easily disassembled and assembled, such as a fitting structure, a screw fixing structure, and a nut fixing structure.

【００２３】制振吸音材１１は、自動車の振動制振など
に使用されるダンピングシート、メルシート等が優れた
効果を発揮する。これらは、騒音反射体９や外殻１２の
内面、即ち騒音が衝突する面に使用すると、制振機能の
他吸音機能を発揮する。また騒音反射体９や外殻１２の
外面に使用すると制振機能と遮音機能を発揮する。制振
吸音材１１は、アスファルト、ゴム、エポキシ樹脂など
の各種樹脂の混合物に、パルプ、ガラス繊維等の各種繊
維質と炭酸カルシウム、マイカ粉、フライアッシュ、籾
殻灰、鉄粉などの鉱物質充填材を加え混練りしてシート
状やコンパウンド状にしたもので、騒音反射体９や外殻
１２に加熱融着するか接着剤、両面粘着テープ等で固定
するか、それ自体を加圧又は溶融成形して使用する。こ
のほか、ゴム、塩化ビニル等の合成樹脂に鉱物質の充填
材を加えた遮音材も使用できる。As the vibration damping / absorbing material 11, a damping sheet, a mel sheet, or the like used for vibration damping of an automobile or the like exhibits an excellent effect. When these are used on the inner surface of the noise reflector 9 or the outer shell 12, that is, on the surface where the noise collides, they exhibit a sound absorbing function in addition to a vibration damping function. Also, when used on the outer surface of the noise reflector 9 or the outer shell 12, it exerts a vibration damping function and a sound insulating function. The vibration damping / absorbing material 11 is a mixture of various resins such as asphalt, rubber and epoxy resin, and various kinds of fibers such as pulp and glass fiber and mineral substances such as calcium carbonate, mica powder, fly ash, chaff ash and iron powder. It is made by adding materials and kneading to form a sheet or a compound. It is heat-sealed to the noise reflector 9 or the outer shell 12, fixed with an adhesive, double-sided adhesive tape, or the like, or pressed or melted itself. Mold and use. In addition, a sound insulating material obtained by adding a filler of a mineral substance to a synthetic resin such as rubber or vinyl chloride can also be used.

【００２４】一般に、騒音と気流分離型消音器を構成す
る各部材は、それぞれ異なる共振特性やコインシデンス
効果、即ち消音効果陥没周波数帯がある。そこで構成す
る部材の選択に当たっては、このことを考慮して、予め
材質特性を確認するか、異質の部材を組み合わせて相互
補完する構成とすることが好ましい。前述の制振吸音材
１１のダンピングシートなどは、各種素材を混合して各
種部材のコインシデンス効果を小さくするよう設計した
もので、良好な制振特性と吸音特性が得られる。In general, the members constituting the noise and airflow separation type silencers have different resonance characteristics and coincidence effects, ie, a frequency band where the noise reduction effect is depressed. Considering this, when selecting the components to be configured, it is preferable to confirm the material characteristics in advance, or to complement each other by combining different components. The damping sheet and the like of the vibration-damping and sound-absorbing material 11 are designed to reduce the coincidence effect of various members by mixing various materials, and good vibration-damping characteristics and sound-absorbing characteristics can be obtained.

【００２５】以下本発明の実施例を説明する。 実施例１ 図４の（ａ）は、本発明の一実施例になる騒音と気流分
離型消音器の断面図、（ｂ）はそのＣ−Ｃ線断面図及び
図５は、本発明の実施例になる騒音と気流分離型消音器
を集塵機上に設置した状態を示す斜視図である。図４の
（ａ）及び（ｂ）に示す騒音と気流分離型消音器は、寸
法が５０mm×５０mmのＬ鋼を溶接して構成した幅（寸法
イ）４５０mm×長さ（寸法ロ）９００mm×高さ（寸法
ハ）４５０mmのＬ鋼枠に、厚さが１．６mmの鋼板をビス
止めして外殻１２を構成した角型状の上下の端部に、直
径（寸法ニ）が３００mm（φ）の排気流入口１と排気放
出口４を設け、排気流入口１の端部からちょうつがい２
０を介して斜めに立ち上がる騒音反射体９を厚さが１．
６mm×幅４４５mm×長さ４００mmの鋼板で構成した。こ
の騒音反射体９の長手方向の一端を端部から５０mmまで
の部分をＲ（寸法ホ）を７５mmの曲率に湾曲させ、その
湾曲部分の内側先端に直径１０mm（φ）×長さ４６０mm
のボルトを溶接し、ボルトの両端部分に当たる外殻１２
の側面にちょうつがい２０を支点としてボルトが上下に
曲率移動するための溝（図示せず）を設け、騒音反射体
９の角度を調節できるようにし、ボルトの一端をナット
で固定する構造とした。なお、上記外殻１２の側面の余
分な溝は、外殻１２の内側のボルトに溝塞ぎ用鋼板（図
示せず）を付けて塞ぐ構造とした。Hereinafter, embodiments of the present invention will be described. Embodiment 1 FIG. 4A is a cross-sectional view of a noise and airflow separation type silencer according to an embodiment of the present invention, FIG. 4B is a cross-sectional view taken along line CC of FIG. It is a perspective view which shows the state which installed the example noise and airflow separation type silencer on the dust collector. The noise and airflow separation type silencer shown in FIGS. 4A and 4B has a width (dimension a) 450 mm × length (dimension B) 900 mm × welded L steel having dimensions of 50 mm × 50 mm. A steel plate having a thickness of 1.6 mm is screwed to an L steel frame having a height (dimension c) of 450 mm, and the upper and lower ends of a rectangular shape which forms the outer shell 12 are 300 mm in diameter (dimension d). φ), an exhaust inlet 1 and an exhaust outlet 4 are provided.
The noise reflector 9 which rises obliquely through the line 0 has a thickness of 1.
It consisted of a steel plate of 6 mm x 445 mm x 400 mm in length. One end in the longitudinal direction of the noise reflector 9 is bent from the end to 50 mm at a radius R (dimension E) of 75 mm curvature, and the inner end of the curved portion has a diameter of 10 mm (φ) × length 460 mm.
Of the outer shell 12 which comes into contact with both ends of the bolt
A groove (not shown) for the bolt to move vertically up and down with the hinge 20 as a fulcrum is provided on the side surface of the so that the angle of the noise reflector 9 can be adjusted, and one end of the bolt is fixed with a nut. . An extra groove on the side surface of the outer shell 12 is closed by attaching a groove closing steel plate (not shown) to a bolt inside the outer shell 12.

【００２６】また、騒音反射体９の底部に面する外殻１
２の下部に幅３５０mm×高さ２mmの降雨排出口１４を設
けた。一方上記の騒音反射体９の上下面と外殻１２の内
側に厚さが２．５mmのダンピングシート制振吸音材１１
を貼付け、さらに騒音反射体９の騒音反射面側に厚さが
２５mmのガラスマット吸音材を開孔率が６０％のパンチ
ングメタルで固定して吸音材層１０を形成すると共に、
外殻１２の騒音反射面の裏側（騒音反射面に対し反対
側）の上方に上記と同様の厚さ２５mmのガラスマット吸
音材を開孔率が６０％のパンチングメタルで固定して吸
音材層１０を上部の幅が下部に比較して狭くなるように
傾斜させて固定し、その表面に厚さが１．６mmの鋼板、
さらに鋼板の表面に厚さが２．５mmのダンピングシート
制振吸音材１１を貼付けた。The outer shell 1 facing the bottom of the noise reflector 9
2, a rain discharge port 14 having a width of 350 mm and a height of 2 mm was provided. On the other hand, the upper and lower surfaces of the noise reflector 9 and the inside of the outer shell 12 have a damping sheet having a thickness of 2.5 mm.
And a 25 mm thick glass mat sound absorbing material is fixed on the noise reflecting surface side of the noise reflecting body 9 with a punching metal having an aperture ratio of 60% to form a sound absorbing material layer 10.
Above the back side of the noise reflection surface of the outer shell 12 (opposite to the noise reflection surface), a glass mat sound absorbing material having a thickness of 25 mm similar to the above is fixed with a punching metal having a porosity of 60% and a sound absorbing material layer. 10 is tilted and fixed so that the width of the upper part is smaller than that of the lower part, and a 1.6 mm thick steel plate
Further, a damping sheet vibration damping sound absorbing material 11 having a thickness of 2.5 mm was attached to the surface of the steel sheet.

【００２７】さらに、騒音反射体９の上部先端から気流
３が通過する分の空白を開けて１００mmの曲率で湾曲し
たガラスマット吸音材を開孔率が６０％のパンチングメ
タルで固定し、最小部分の厚さが１００mmの吸音材層１
０′を設けた。次いでこの奥に閉塞空間１３を設け、さ
らにその奥に上記と同様の方法で厚さが１００mmの吸音
材層１０″厚さが２．５mmのダンピングシート制振吸音
材１１及び厚さが１．６mmの鋼板を残存騒音の反射距離
調節体１６として設け、その奥にさらに閉塞空間１３を
設け騒音と気流分離型消音器を得た。なお残存騒音の反
射距離調節体１６の取付け構造は、騒音反射体９の角度
調節機構と同様に、前後に移動できるようにし、ボルト
の一端をナットで固定する構造とした。Further, a space for the air flow 3 to pass therethrough is opened from the upper end of the noise reflector 9 and a glass mat sound absorbing material curved with a curvature of 100 mm is fixed with a punching metal having an opening ratio of 60% to form a minimum part. Sound absorbing material layer 1 with a thickness of 100 mm
0 'was provided. Next, a closed space 13 is provided in the back, and further in the back, a sound absorbing material layer 10 having a thickness of 100 mm and a damping sheet vibration damping sound absorbing material 11 having a thickness of 2.5 mm and a thickness of 1. A 6 mm steel plate was provided as a reflection distance adjuster 16 for the residual noise, and a closed space 13 was further provided in the back thereof to obtain a noise and airflow separation type silencer. Like the angle adjusting mechanism of the reflector 9, the reflector 9 can be moved back and forth, and one end of a bolt is fixed with a nut.

【００２８】次に図５に示すように上記で得た本発明に
なる騒音と気流分離型消音器１９を、下記仕様の集塵機
１８上に設置したものと、図９に示す従来の高さが１．
５ｍ雨傘付き吸音型ダクト用消音器を上記と同様に設置
したものについて排気騒音を測定しその比較を行つた。
その結果を表１に示す。なお測定は、普通型騒音計を使
用し、Ａ測定した。（以下の実施例についても同じであ
る）。 集塵機の仕様と騒音周波数域 排気口 ：３００ｍｍ（¢） 排気気流の流速 ：１１ｍ／秒 排気騒音の周波数域：６３Ｈｚから２０００Ｈｚ 卓越周波数帯 ：５００ＨｚNext, as shown in FIG. 5, the noise and airflow separation type silencer 19 according to the present invention obtained above is installed on a dust collector 18 having the following specifications, and the conventional height shown in FIG. 1.
Exhaust noise was measured for a muffler for a sound-absorbing duct equipped with a 5 m umbrella in the same manner as described above, and a comparison was made.
Table 1 shows the results. In addition, the measurement was performed using a normal sound level meter, and A was measured. (The same applies to the following examples). Dust collector specifications and noise frequency range Exhaust port: 300 mm (¢) Exhaust air flow velocity: 11 m / sec Exhaust noise frequency range: 63 Hz to 2000 Hz Dominant frequency band: 500 Hz

【００２９】[0029]

【表１】 [Table 1]

【００３０】表１に示されるように、地上６ｍ、放出口
より１ｍの排気放出口の騒音は、本発明品は７１ｄＢ、
これに対し消音器なしは８５ｄＢ及び従来品は７７ｄＢ
であった。この結果から本発明品は、消音器なしに対し
て１４ｄＢ及び従来品に対して６ｄＢの消音効果があっ
た。また地上１ｍの騒音最大値は、本発明品は６６ｄ
Ｂ、これに対し消音器なしは８２ｄＢ及び従来品は７４
ｄＢであった。この結果から本発明品は、消音器なしに
対して１６ｄＢ及び従来品に対して８ｄＢの消音効果が
あった。さらに本発明品は気流の入口と出口間の圧力損
失は３mmＨ₂Ｏであり、無視できるレベルであった。な
お表１の本発明品で７１ｄＢが得られた条件は、下記の
通りである。 騒音反射体９の角度：２７．５度 残存騒音の反射距離調節体１６と排気流入口１の端部と
の距離：４３０mm。As shown in Table 1, the noise of the exhaust outlet 6 m above the ground and 1 m from the outlet is 71 dB for the product of the present invention.
On the other hand, 85dB without silencer and 77dB with conventional products
Met. From these results, the product of the present invention had a noise reduction effect of 14 dB with no muffler and 6 dB with the conventional product. The maximum noise level at 1m above the ground is 66d for the product of the present invention.
B, on the other hand, 82dB without silencer and 74 for conventional products
dB. From these results, the product of the present invention had a noise reduction effect of 16 dB with no muffler and 8 dB with the conventional product. Further, in the product of the present invention, the pressure loss between the inlet and the outlet of the air flow was 3 mmH ₂ O, which was a negligible level. The conditions for obtaining 71 dB with the product of the present invention in Table 1 are as follows. Angle of noise reflector 9: 27.5 degrees Distance between reflector 16 for reflecting residual noise and end of exhaust inlet 1: 430 mm.

【００３１】また上記仕様の集塵機１８単体及び集塵機
１８上に本発明になる騒音と気流分離型消音器１９を設
置したものについて、それぞれの排気口から上方１ｍの
排気騒音並びにそれぞれの集塵機１８の操作面側から横
１ｍ、地上１．２ｍの位置の集塵機側面から発する騒音
の比較を行なった。その結果を表２に示す。なお測定
は、１／１オクターバンド騒音計を使用し、Ａ測定し
た。Further, with respect to the dust collector 18 of the above specification and the noise and airflow separation type silencer 19 according to the present invention installed on the dust collector 18, the exhaust noise 1 m upward from each exhaust port and the operation of each dust collector 18. A comparison was made of the noise emitted from the side of the dust collector 1 m from the surface side and 1.2 m above the ground. Table 2 shows the results. In addition, A measurement was performed using a 1/1 octave band noise meter.

【００３２】[0032]

【表２】 [Table 2]

【００３３】表２に示されるように、排気口から上方１
ｍのオールパス騒音は、本発明品は６９．５ｄＢ、これ
に対し集塵機単体は８３．２ｄＢであった。この結果か
ら本発明品は、集塵機単体に対して１３．７ｄＢの消音
効果があった。また６３〜８０００Hzの各周波数帯の消
音効果は１２．４〜２０．５ｄＢであった。以上の結
果、本発明品は、低周波数帯から高周波数帯まで満遍な
く消音効果が大きいことが明らかである。一方、集塵機
の操作面側から１ｍ、地上１．２ｍの位置の集塵機側面
から発する騒音は、本発明品は７０．６ｄＢ、これに対
し集塵機単体は７７．３ｄＢであった。この結果から本
発明品は、集塵機単体に対して６．７ｄＢの消音効果が
あった。また６３〜８０００Hzの各周波数帯の消音効果
は２．６〜１６．８ｄＢであった。以上の結果、本発明
品は、集塵機側面から発する騒音に対しても消音効果が
大きいことが明らかである。As shown in Table 2, 1
The m of the all-pass noise was 69.5 dB for the product of the present invention, and 83.2 dB for the dust collector alone. From this result, the product of the present invention had a noise reduction effect of 13.7 dB with respect to the dust collector alone. The silencing effect in each frequency band from 63 to 8000 Hz was 12.4 to 20.5 dB. From the above results, it is apparent that the product of the present invention has a large noise reduction effect uniformly from a low frequency band to a high frequency band. On the other hand, the noise generated from the side of the dust collector 1 m from the operation surface side of the dust collector and 1.2 m above the ground was 70.6 dB for the product of the present invention, and 77.3 dB for the dust collector alone. From this result, the product of the present invention has a noise reduction effect of 6.7 dB with respect to the dust collector alone. The silencing effect in each frequency band from 63 to 8000 Hz was 2.6 to 16.8 dB. As a result, it is clear that the product of the present invention has a large noise-reducing effect even with respect to noise generated from the side of the dust collector.

【００３４】実施例２ 図６の（ａ）は、本発明の他の一実施例になる騒音と気
流分離型消音器の断面図及び（ｂ）はそのＤ−Ｄ線断面
図であり、実施例１で用いた図４に示す騒音と気流分離
型消音器を、２基重層構造にしたものである。次に上記
で得た本発明になる騒音と気流分離型消音器及び図９に
示す従来の高さが１．５ｍ雨傘付き吸音型ダクト用消音
器を、仕様が実施例１と同様の図５に示す集塵機１８上
にそれぞれ設置して排気騒音を測定しその比較を行っ
た。その結果を表３に示す。Embodiment 2 FIG. 6A is a cross-sectional view of a noise and airflow separation type silencer according to another embodiment of the present invention, and FIG. The noise and airflow separation type silencer shown in FIG. 4 used in Example 1 has a two-layer structure. Next, the noise and airflow separation type silencer according to the present invention obtained above and the conventional silencer for a sound absorbing duct with a 1.5 m height umbrella shown in FIG. The exhaust noise was measured by installing each on the dust collector 18 shown in FIG. Table 3 shows the results.

【００３５】[0035]

【表３】 [Table 3]

【００３６】表３に示されるように、地上６ｍ、放出口
より１ｍの排気放出口の騒音は、本発明は６５ｄＢ、こ
れに対し消音器なしは８５ｄＢ及び従来品は７７ｄＢで
あった。この結果から本発明品は、消音器なしに対して
２０ｄＢ及び従来品に対して１２ｄＢの消音効果があっ
た。また本発明品は気流の入口と出口間の圧力が６mmＨ
₂Ｏであり、無視できるレベルであった。As shown in Table 3, the noise at the exhaust outlet 6 m above the ground and 1 m from the outlet was 65 dB in the present invention, 85 dB without the silencer, and 77 dB in the conventional product. From this result, the product of the present invention had a noise reduction effect of 20 dB with no muffler and 12 dB with the conventional product. The product of the present invention has a pressure between the inlet and outlet of the airflow of 6 mmH.
₂ O, a negligible level.

【００３７】実施例３ 図７の（ａ）は、本発明の他の一実施例になる騒音と気
流分離型消音器の断面図、（ｂ）はその側面図及び
（ｃ）は騒音反射体の拡大図であり、厚さ１．６ｍｍの
鋼板で作成した直径（寸法ヘ）１６０ｍｍ（¢）×厚さ
（寸法ト）６０ｍｍの円盤状の外殻１２の中に、厚さが
０．５ｍｍのダンピングシート制振吸音材１１を貼付け
て直径（寸法チ）１５０ｍｍ（¢）×空間厚さ（寸法
リ）５０ｍｍの中空の閉塞空間１３を形成し、さらに円
盤状の外殻１２の片側中央部に直径（寸法ヌ）５０ｍｍ
（¢）の排気流入口１と反対側に直径（寸法ル）５５ｍ
ｍ（¢）の排気放出口４を設けた。さらに閉塞空間１３
の内部中央部に厚さが１．６ｍｍの鋼板にダンピングシ
ート制振吸音材１１を貼付け、風車状に襞を有する多角
錐の騒音反射体９を取付けた。Embodiment 3 FIG. 7A is a cross-sectional view of a noise and air flow separation type silencer according to another embodiment of the present invention, FIG. 7B is a side view thereof, and FIG. 7C is a noise reflector. FIG. 3 is an enlarged view of a disk-shaped outer shell 12 having a diameter (dimension F) of 160 mm (¢) × thickness (dimension G) of 60 mm made of a steel plate having a thickness of 1.6 mm.
A 0.5 mm damping sheet damping sound absorbing material 11 is attached to form a hollow closed space 13 having a diameter (dimension) of 150 mm (寸 法) × space thickness (dimension) of 50 mm, and a disk-shaped outer shell 12. 50mm in diameter (dimensions) in the center of one side of
(¢) 55m in diameter (dimensions) on the side opposite to the exhaust inlet 1
m (¢) exhaust outlet 4 was provided. Furthermore, the closed space 13
A damping sheet vibration-absorbing and sound-absorbing material 11 was adhered to a 1.6 mm-thick steel plate at the center of the inside, and a polygonal pyramid noise reflector 9 having windmill-shaped folds was attached.

【００３８】この騒音反射体９の襞は、円盤状の中心に
向かう８個の襞と、この襞の内側端部から次の襞の外側
端部につながる８個の襞で構成した。前者の襞の最大高
さ（寸法ヲ）は１５mmで、これをくり抜いて排気流入口
１の２倍の開口面積を設け、気流３の通路１５とし、後
者の襞の最大幅（寸法ワ）は３０mmで、騒音２を吸音減
衰消音、衝突減衰消音及び振動減衰消音させた後、残存
騒音８を閉塞空間１３の外殻１２に対し角度を持って反
射する役割を持たせた。この騒音反射体９は、下端を排
気放出口４を覆うように密着させ、先端を排気流入口１
の中央になる位置とした。この構成を１ユニットとし、
これを３ユニットの重層構造とした。騒音反射体９の襞
から反射された残存騒音８は、騒音反射体９を取り巻く
閉塞空間１３の外殻１２を構成する制振吸音材１１に繰
り返し衝突し、吸音減衰消音、衝突減衰消音及び振動減
衰消音が行われる他、残存騒音８の位相のずれが合体し
位相差減衰消音が行われる。なお、閉塞空間１３の制振
吸音材１１に対する騒音２の入射角を変更する場合は、
角度の異なる騒音反射体に交換する方法などがある。The folds of the noise reflector 9 were composed of eight folds toward the center of the disk, and eight folds from the inner end of this fold to the outer end of the next fold. The maximum height (dimension ヲ) of the former fold is 15 mm, which is hollowed out to provide an opening area twice as large as that of the exhaust inlet 1 to form a passage 15 for the air flow 3, and the maximum width (dimension ワ) of the latter fold is After the noise 2 was absorbed and attenuated, the collision attenuated, and the vibration attenuated at 30 mm, the remaining noise 8 was reflected at an angle to the outer shell 12 of the closed space 13. The noise reflector 9 has a lower end adhered so as to cover the exhaust outlet 4, and a tip located at the exhaust inlet 1.
At the center. With this configuration as one unit,
This was made into a three-unit multilayer structure. The residual noise 8 reflected from the folds of the noise reflector 9 repeatedly collides with the vibration-damping and sound-absorbing material 11 constituting the outer shell 12 of the closed space 13 surrounding the noise reflector 9, damping sound absorption, damping sound and vibration. In addition to the attenuation and silencing, the phase difference of the residual noise 8 is combined and the phase difference attenuation and silencing is performed. In addition, when changing the incident angle of the noise 2 with respect to the vibration damping sound absorbing material 11 in the closed space 13,
There is a method of replacing the noise reflector with a different angle.

【００３９】次に上記で得た本発明になる騒音と気流分
離型消音器を、排気ダクト口径が５０mm（φ）、排気流
速が５．５ｍ／秒、卓越周波数５００Hz及びオールパス
騒音７４ｄＢを発する小型ブロアに取り付けた結果、排
気の残存騒音８は６２ｄＢで、騒音の低減効果は１２ｄ
Ｂであった。Next, the noise and airflow separation type silencer according to the present invention obtained above was replaced with a small-sized exhaust duct having a diameter of 50 mm (φ), an exhaust velocity of 5.5 m / sec, a dominant frequency of 500 Hz and an all-pass noise of 74 dB. As a result of attaching to the blower, the residual noise 8 of the exhaust gas is 62 dB, and the noise reduction effect is 12 d.
B.

【００４０】実施例４ 図８の（ａ）は、本発明の他の一実施例になる騒音と気
流分離型消音器の断面図及び（ｂ）はそのＥ−Ｅ線断面
図であり、図７に示す実施例３で得た騒音と気流分離型
消音器の騒音反射体９をはずし、排気流入口１の取付け
位置を円盤状の閉塞空間１３の外周に変更したものであ
る。排気流入口１から流入した排気のうち、気流３は気
圧の低い排気放出口４へ向かって流れ消音器の系外に排
出される。一方騒音２は、円盤状の閉塞空間１３の内壁
に直進し、この内壁が騒音反射体９の役割をはたし衝突
と反射を繰り返しながらその内壁の外周を廻り、吸音減
衰消音、衝突減衰消音、振動減衰消音及び位相差減衰消
音が繰り返し行われる。第１ユニットから漏れた残存騒
音８は、第２ユニット以下に入り、以下同様に消音され
る。なお、閉塞空間１３の制振吸音材１１に対する騒音
２の入射角を変更する場合は、外殻１２に対する排気流
入口１の取付け角度を調節すればよい。ここで、閉塞空
間１３の各ユニットを螺旋状に連結構成しても本発明の
目的を達成することができる。Embodiment 4 FIG. 8 (a) is a cross-sectional view of a noise and airflow separation type silencer according to another embodiment of the present invention, and FIG. 8 (b) is a cross-sectional view taken along line EE. 7, the noise reflector 9 of the noise and airflow separation type silencer obtained in Example 3 was removed, and the mounting position of the exhaust inlet 1 was changed to the outer periphery of the disc-shaped closed space 13. Among the exhaust gas flowing from the exhaust gas inlet 1, the air current 3 flows toward the exhaust outlet 4 having a low pressure and is discharged out of the muffler. On the other hand, the noise 2 travels straight to the inner wall of the disc-shaped closed space 13, and this inner wall plays the role of the noise reflector 9 and turns around the outer wall of the inner wall while repeating collision and reflection. , The vibration damping silencing and the phase difference damping silencing are repeated. The residual noise 8 leaking from the first unit enters the second unit and below, and is similarly silenced. In addition, when changing the incident angle of the noise 2 with respect to the vibration damping / absorbing material 11 in the closed space 13, the mounting angle of the exhaust inlet 1 with respect to the outer shell 12 may be adjusted. Here, the object of the present invention can be achieved even if each unit of the closed space 13 is spirally connected.

【００４１】次に本発明になる上記で得た騒音と気流分
離型消音器を、排気ダクト口径が５０mm（φ）、排気流
速が３．１ｍ／秒、卓越周波数５００Hz及びオールパス
騒音７１ｄＢを発する小型ブロアに取り付けた結果、排
気の残存騒音８は６２ｄＢで、騒音低減効果は９ｄＢで
あった。Next, the noise and airflow separation type silencer obtained above according to the present invention is manufactured by using a small-sized muffler having an exhaust duct diameter of 50 mm (φ), an exhaust flow velocity of 3.1 m / sec, a dominant frequency of 500 Hz and an all-pass noise of 71 dB. As a result of being attached to the blower, the residual noise 8 of the exhaust gas was 62 dB, and the noise reduction effect was 9 dB.

【００４２】本発明の実施例では、騒音と気流分離型消
音器を排気ダクトの先端に取り付けた例で示したが、騒
音発生源の設備装置の内部に備えても消音効果を示すも
のである。In the embodiment of the present invention, the noise and air flow separation type silencer is mounted at the end of the exhaust duct. However, even if the silencer is provided inside the equipment of the noise source, the noise reduction effect is exhibited. .

【００４３】[0043]

【発明の効果】請求項１及び２記載の騒音と気流分離型
消音器は、４種類の消音原理に、降雨の排出構造を開発
したことによる残存騒音を任意の方向に排出した「距離
減衰消音」を加えた合計５種類の消音原理を複合重複活
用し、消音効果が大きく、圧力損失が少なく、用途共用
範囲が広く、消音器で消音できなかった残存騒音と排気
を垂直上空に排出することができるため地上騒音を大幅
に削減でき、かつ構造が簡易で、安価に作製することが
できる。請求項３記載の騒音と気流分離型消音器は、請
求項１及び２記載の騒音と気流分離型消音器の効果を奏
し、さらに対象周波数帯の選択と気流抵抗による新たな
騒音発生の抑制と圧力損失の抑制の最適化を図ることが
できる。According to the first and second aspects of the present invention, the noise and airflow separation type silencer has the following four types of silencing principles. And a total of five types of silencing principles are combined and utilized to produce a large silencing effect, low pressure loss, a wide range of common use, and exhaust of residual noise and exhaust that could not be silenced by the silencer to the vertical sky. Therefore, ground noise can be greatly reduced, the structure is simple, and the device can be manufactured at low cost. The noise and airflow separation type silencer according to claim 3 has the effects of the noise and airflow separation type silencer according to claims 1 and 2, and further suppresses generation of new noise due to selection of a target frequency band and airflow resistance. Optimization of suppression of pressure loss can be achieved.

【００４４】請求項４記載の騒音と気流分離型消音器
は、請求項１、２及び３記載の騒音と気流分離型消音器
の効果を奏し、さらに降雨を系外に排出することができ
る。請求項５記載の騒音と気流分離型消音器は、請求項
１、２、３及び４記載の騒音と気流分離型消音器の効果
を奏し、さらに少ない空間容積で、かつ小型で消音効果
に優れる。請求項６記載の騒音と気流分離型消音器は、
請求項１、２、３、４及び５記載の騒音と気流分離型消
音器の効果を奏し、さらに解体、運搬、組立て等の施工
性と掃除、騒音反射体、外殻等の交換作業性に優れる。
請求項７記載の騒音と気流分離型消音器は、請求項１、
２、３、４、５及び６記載の騒音と気流分離型消音器の
効果を奏し、さらに従来使用していた降雨浸入防止又は
浸入降雨の排出機能を有しない従来の騒音と気流分離型
消音器を併用して使用できる。請求項８記載の低騒音型
設備装置は、消音効果が大きく、圧力損失が少なく、用
途共用範囲が広く、構造が簡易で、安価な騒音と気流分
離型消音器を備えた低騒音型設備装置である。The noise and airflow separation type silencer according to the fourth aspect has the effects of the noise and airflow separation type silencer according to the first, second and third aspects, and can further discharge rainfall out of the system. The noise and airflow separation type silencer according to claim 5 has the effects of the noise and airflow separation type silencer according to claims 1, 2, 3, and 4, and has a smaller space volume, is smaller, and has an excellent noise reduction effect. . The noise and airflow separation type silencer according to claim 6,
The effect of the noise and airflow separation type silencer according to claims 1, 2, 3, 4, and 5 is exhibited, and further, the workability of disassembly, transportation, assembly, etc. and the cleaning work, the replacement work of the noise reflector, the outer shell, etc. are improved. Excellent.
The noise and airflow separation type silencer according to claim 7 is based on claim 1,
2. A conventional noise and airflow separation type silencer that has the effects of the noise and airflow separation type silencer described in 2, 3, 4, 5, and 6, and does not have the function of preventing rainfall intrusion or discharging intrusion and rainfall which has been conventionally used. Can be used in combination. The low-noise facility apparatus according to claim 8, which has a large noise reduction effect, has a small pressure loss, has a wide range of common use, has a simple structure, is inexpensive, and has a low-noise and airflow type silencer. It is.

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

【図１】本発明の騒音と気流分離型消音器の消音原理図
で、（ａ）は断面図及び（ｂ）はそのＡ−Ａ線断面図で
ある。BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a diagram illustrating the principle of silencing of a noise and airflow separation type silencer according to the present invention, wherein (a) is a cross-sectional view and (b) is a cross-sectional view taken along line AA.

【図２】本発明の騒音と気流分離型消音器の消音原理図
で、（ａ）は断面図、（ｂ）はその側面図及び（ｃ）は
騒音反射体の拡大図である。FIGS. 2A and 2B are diagrams showing the principle of silencing of the noise and airflow separation type silencer of the present invention, wherein FIG. 2A is a sectional view, FIG. 2B is a side view thereof, and FIG. 2C is an enlarged view of a noise reflector.

【図３】本発明の騒音と気流分離型消音器の消音原理図
で、（ａ）は断面図及び（ｂ）はそのＢ−Ｂ線断面図で
ある。FIGS. 3A and 3B are diagrams illustrating the principle of silencing of the noise and airflow separation type silencer of the present invention, wherein FIG. 3A is a cross-sectional view and FIG.

【図４】（ａ）は本発明の一実施例になる騒音と気流分
離型消音器の断面図及び（ｂ）はそのＣ−Ｃ線断面図で
ある。FIG. 4A is a sectional view of a noise and airflow separation type silencer according to an embodiment of the present invention, and FIG. 4B is a sectional view taken along line CC of FIG.

【図５】本発明の実施例になる騒音と気流分離型消音器
を集塵機上に設置した状態を示す斜視図である。FIG. 5 is a perspective view showing a state in which the noise and airflow separation type silencer according to the embodiment of the present invention is installed on a dust collector.

【図６】（ａ）は本発明の他の一実施例になる騒音と気
流分離型消音器の断面図及び（ｂ）はそのＤ−Ｄ線断面
図である。6A is a cross-sectional view of a noise and airflow separation type silencer according to another embodiment of the present invention, and FIG. 6B is a cross-sectional view taken along line DD of FIG.

【図７】（ａ）は本発明の他の一実施例になる騒音と気
流分離型消音器の断面図、（ｂ）はその側面図及び
（ｃ）は騒音反射体の拡大図である。7A is a sectional view of a noise and airflow separation type silencer according to another embodiment of the present invention, FIG. 7B is a side view thereof, and FIG. 7C is an enlarged view of a noise reflector.

【図８】（ａ）は本発明の他の一実施例になる騒音と気
流分離型消音器の断面図及び（ｂ）はそのＥ−Ｅ線断面
図である。8A is a cross-sectional view of a noise and airflow separation type silencer according to another embodiment of the present invention, and FIG. 8B is a cross-sectional view taken along line EE.

【図９】従来の雨傘付き吸音型ダクト用消音器である。FIG. 9 is a conventional sound absorber for a sound absorbing duct with an umbrella.

【図１０】従来のダクトの先端を下方に折り曲げた吸音
型消音器である。FIG. 10 shows a conventional sound-absorbing silencer in which a distal end of a duct is bent downward.

【符号の説明】[Explanation of symbols]

１ 排気流入口 ２ 騒音 ３ 気流 ４ 排気放出口 ５ 雨傘 ６ 降雨 ７ 消音器 ８ 残存騒音 ９ 騒音反射体 １０、１０′、１０″ 吸音材層 １１ 制振吸音材 １２ 外殻 １３ 閉塞空間 １４ 降雨排出口 １５ 気流の通路 １６ 残存騒音の反射距離調節体 １７ 角度、距離の調節固定部 １８ 集塵機 １９ 本発明になる騒音と気流分離型消音器 ２０ ちょうつがい DESCRIPTION OF SYMBOLS 1 Exhaust inlet 2 Noise 3 Air flow 4 Exhaust outlet 5 Rain umbrella 6 Rainfall 7 Silencer 8 Residual noise 9 Noise reflector 10, 10 ', 10 "Sound-absorbing material layer 11 Vibration-absorbing sound-absorbing material 12 Outer shell 13 Closed space 14 Rainfall exhaust Exit 15 Airflow passage 16 Reflection distance adjustment body for residual noise 17 Angle and distance adjustment fixed part 18 Dust collector 19 Noise and airflow separation type silencer according to the present invention 20 Hinge

Claims (8)

(57)【特許請求の範囲】(57) [Claims] 【請求項１】騒音と気流が混在する排気の流入口と放出
口を有する角型状又は筒状の外殻の中に、騒音を一定方
向に反射して気流から分離し、かつ騒音を吸音減衰消
音、衝突減衰消音、振動減衰消音及び位相差減衰消音す
る機能を有する騒音反射体並びに閉塞空間を設けてなる
騒音と気流分離型消音器において、該騒音反射体は排気
流入口の端部から角度２０〜３５度で斜めに立ち上が
り、騒音反射面に吸音材層を形成し、長手方向の端部を
湾曲させ、該騒音反射体から気流が通過する分の空白を
開けて湾曲した吸音材層を設けてなる騒音と気流分離型
消音器。 1. A rectangular or cylindrical outer shell having an inlet and an outlet for exhaust gas in which noise and air flow are mixed, reflects noise in a certain direction, separates the noise from the air flow, and absorbs the noise. In a noise reflector having a function of damping muffling, collision damping muffling, vibration damping muffling, and phase difference damping muffling, and a noise and airflow separation type muffler having a closed space, the noise reflector is exhausted.
It rises obliquely at an angle of 20 to 35 degrees from the end of the inlet
A sound absorbing material layer on the noise reflecting surface,
Curve the air gap from the noise reflector to allow airflow to pass through.
Noise and airflow separation type with open and curved sound absorbing material layer
Silencer. 【請求項２】円盤状の外殻の中に中空の閉塞空間を形成
し、該円盤状の外殻の片側に排気流入口と反対側に排気
放出口を設け、該閉塞空間に風車状に襞を有する多角錐
の騒音反射体を下端を排気放出口を覆うように密着さ
せ、先端を排気放出口の中央になる位置に取付け、該騒
音反射体の円盤状の中心に向かう襞をくり抜いて気流の
通路とし、この襞の内側端部から次の襞の外側端部につ
ながる襞は残存騒音を閉塞空間の外殻に反射する役割を
持たせ、該騒音反射体、該閉塞空間、該外殻により、吸
音減衰消音、衝突減衰消音、振動減衰消音及び位相差減
衰消音を繰り返し行う騒音と気流分離型消音器。2. A hollow closed space is formed in a disk-shaped outer shell.
And one side of the disk-shaped outer shell is evacuated to the side opposite to the exhaust inlet.
A polygonal pyramid having a discharge port and having a windmill-like fold in the closed space
The noise reflector so that the lower end covers the exhaust outlet
And attach the tip to the center of the exhaust outlet,
Cut out the fold toward the disc-shaped center of the sound reflector
A passage from the inner end of this fold to the outer end of the next fold
The folds play a role in reflecting the residual noise to the outer shell of the enclosed space.
The noise reflector, the closed space, and the outer shell.
Sound damping silencing, collision damping silencing, vibration damping silencing, and phase difference reduction
A noise and airflow separation type silencer that repeats the attenuation sound . 【請求項３】 騒音反射体と閉塞空間の角度及び距離を
調節可能とした請求項１又は２記載の騒音と気流分離型
消音器。3. The noise and airflow separation type silencer according to claim 1, wherein an angle and a distance between the noise reflector and the closed space are adjustable. 【請求項４】 騒音反射体の下端又はこれに相対する外
殻の下端に、降雨の排出口を設けてなる請求項１、２又
は３記載の騒音と気流分離型消音器。4. The noise and airflow separation type silencer according to claim 1, wherein a rainfall discharge port is provided at a lower end of the noise reflector or a lower end of an outer shell opposed thereto. 【請求項５】 閉塞空間の外周部分が騒音反射体を兼
ね、かつこれらが連続一体化されたものである請求項
１、２、３又は４記載の騒音と気流分離型消音器。5. The noise and airflow separation type silencer according to claim 1, wherein an outer peripheral portion of the closed space also serves as a noise reflector, and these are continuously integrated. 【請求項６】 外殻、騒音反射体及び閉塞空間が分割構
造である請求項１、２、３、４又は５記載の騒音と気流
分離型消音器。6. The noise and airflow separation type silencer according to claim 1, wherein the outer shell, the noise reflector and the closed space have a divided structure. 【請求項７】 請求項１、２、３、４、５又は６記載の
騒音と気流分離型消音器の下部に降雨浸入防止又は浸入
した降雨の排出機能を有しない騒音と気流分離型消音器
を接続するか又は両者を連結一体化してなる騒音と気流
分離型消音器。7. The noise and airflow separation type silencer according to claim 1, 2, 3, 4, 5, or 6, which does not have a function of preventing rainfall from infiltrating or discharging the infiltrated rainfall under the noise and airflow separation type silencer. Or an airflow separation type silencer that is connected or integrated. 【請求項８】 請求項１、２、３、４、５、６又は７記
載の騒音と気流分離型消音器を騒音発生源の設備装置の
内部に備えてなる低騒音型設備装置。8. A low-noise facility apparatus comprising the noise and airflow separation type silencer according to claim 1, 2, 3, 4, 5, 6, or 7.