JPS58124057A - Suction air resonator - Google Patents
Suction air resonatorInfo
- Publication number
- JPS58124057A JPS58124057A JP646882A JP646882A JPS58124057A JP S58124057 A JPS58124057 A JP S58124057A JP 646882 A JP646882 A JP 646882A JP 646882 A JP646882 A JP 646882A JP S58124057 A JPS58124057 A JP S58124057A
- Authority
- JP
- Japan
- Prior art keywords
- intake
- diaphragm
- resonator
- chamber
- engine
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
- 238000005192 partition Methods 0.000 claims description 5
- 238000013016 damping Methods 0.000 abstract description 5
- 230000002093 peripheral effect Effects 0.000 abstract description 4
- 238000000034 method Methods 0.000 abstract 1
- 238000010586 diagram Methods 0.000 description 3
- 238000010521 absorption reaction Methods 0.000 description 2
- 102000006947 Histones Human genes 0.000 description 1
- 108010033040 Histones Proteins 0.000 description 1
- 230000002238 attenuated effect Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000005086 pumping Methods 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M35/00—Combustion-air cleaners, air intakes, intake silencers, or induction systems specially adapted for, or arranged on, internal-combustion engines
- F02M35/12—Intake silencers ; Sound modulation, transmission or amplification
- F02M35/1255—Intake silencers ; Sound modulation, transmission or amplification using resonance
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M35/00—Combustion-air cleaners, air intakes, intake silencers, or induction systems specially adapted for, or arranged on, internal-combustion engines
- F02M35/12—Intake silencers ; Sound modulation, transmission or amplification
- F02M35/1272—Intake silencers ; Sound modulation, transmission or amplification using absorbing, damping, insulating or reflecting materials, e.g. porous foams, fibres, rubbers, fabrics, coatings or membranes
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Characterised By The Charging Evacuation (AREA)
Abstract
Description
【発明の詳細な説明】
本発明はエンジンの吸気配管を通して放出される（Ｉ−
ぐ・−（ノイズを共鳴吸収する吸気レゾネータの改良Ｇ
こ関するものである。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to
(Improved intake resonator that absorbs noise by resonance)
This is related to this.
ヒストンのポンプ作用によってエンジンの気筒内には間
欠的に空気が吸い込まれ、これに起因して、ドとしてエ
ンジンの同転数に関連した周波数１＋Ｖ、うｔを（１す
る吸気ノイズがエンジンの吸気配管を１１ｔｉ して；
攻出される。このため、エンジンの吸気配管（こ接着さ
れた共鳴空室を６ｉＨえ、その共鳴空室の共鳴吸収作用
によってその吸気配管を通して放出される吸気ノイズを
減衰させる吸気レゾネータが提供されている。しかしな
がら、斯る従来の吸気レゾネータによれば、その減衰性
能を高めるためには共鳴空室の容積を大きくしなければ
ならない一方、エンジンおよびその吸気配管が収容され
るエンジンルーム内において吸気レゾネータのための容
積が充分に許容されないため、吸気ノイズを減衰させる
ための充分な共鳴吸収特性が必ずしも得られなかった。Due to the pumping action of histones, air is intermittently sucked into the cylinders of the engine, and as a result, intake noise with a frequency of 1+V, t(1), which is related to the engine's rotational speed, Connect the piping to 11ti;
be attacked. For this reason, an intake resonator is provided which has a resonant cavity bonded to the engine's intake pipe (6iH) and attenuates the intake noise emitted through the intake pipe by the resonance absorbing action of the resonant cavity.However, According to such a conventional intake resonator, in order to improve its damping performance, the volume of the resonant chamber must be increased, while the volume for the intake resonator in the engine room where the engine and its intake piping are housed is small. is not sufficiently tolerated, and therefore sufficient resonance absorption characteristics for attenuating intake noise cannot necessarily be obtained.
本発明者は以上の事情を背景として種々試作を重ねた結
果、共鳴空室内を振動可能な隔壁で分割すると、共鳴空
室の容積を大きくしなくても吸気ノイズの減衰特性が大
幅に向上する事実を見い出した。本発明は以上の知見に
基づいて為されたものである。With the above circumstances in mind, the inventors of the present invention have repeatedly produced various prototypes, and have found that by dividing the resonant chamber with vibrating partition walls, the damping characteristics of intake noise can be significantly improved without increasing the volume of the resonant chamber. I found out the truth. The present invention has been made based on the above findings.
すなわち、本発明の要旨とするところは、エンジンの吸
気配管に接続された共鳴空室を備え、その吸気配管系の
吸気ノイズを共鳴吸収する吸気レゾネータにおいて、そ
の共鳴空室を分割する隔壁を！１、鳴空室内に配設し、
且つその隔壁を弾性的に支持して振動可能としたことに
ある。That is, the gist of the present invention is to provide an intake resonator that includes a resonant chamber connected to the intake piping of an engine and that resonates and absorbs the intake noise of the intake piping system. 1. Placed inside the Naruko room,
In addition, the partition wall is elastically supported so as to be able to vibrate.
１す下、本発明の一実施例を示す図面に基づいてＡ’Ｎ
細に説明する。1 below, A'N based on the drawings showing one embodiment of the present invention.
Explain in detail.
第１図において、エンジンの吸気配管の先端部を成すエ
ヤクリーナの円筒状のノーズ部１０には１１１７ ’＜
ｊレゾネータ１２が接続されている。吸気レゾネータ１
２は上容器１１および下容器１３から成る短円筒状の本
体１４と本体１４の端面から突設された接続管部１６と
から成り、本体１４内の気密な共鳴空室が接続管部１６
を通してノーズ部１０に接続されている。共鳴空室にお
いては隔壁を成す円形のダイヤフラム１８が上容器１１
および上容器１３によって挾持され、それによってノー
ズ部１０に連通する上室２０と上室２０よりも容Ｉ、：
のかなり小さい密閉された下室２２とに分割さ才１てい
る。り゛イヤ７ラム１８は円板状の中央部２づ
・１と同心円波状の外周部２６とを備え、その中
央部か外周部によって振動可能に弾性的に支持されてい
る。そして、第２図にも示されるように、ダイヤフラム
１８の中央部にはダイヤフラム１８の振動質量を定める
調節片２８が固着されている。In FIG. 1, the cylindrical nose part 10 of the air cleaner, which forms the tip of the engine's intake pipe, has a 1117'<
j resonator 12 is connected. Intake resonator 1
2 consists of a short cylindrical main body 14 consisting of an upper container 11 and a lower container 13, and a connecting pipe section 16 protruding from the end surface of the main body 14.
It is connected to the nose part 10 through. In the resonant chamber, a circular diaphragm 18 forming a partition wall is connected to the upper container 11.
and an upper chamber 20 which is sandwiched by the upper container 13 and thereby communicates with the nose portion 10 and a volume I than the upper chamber 20:
It is divided into a fairly small sealed lower chamber 22 and a lower chamber 22. The rear 7 ram 18 has a disc-shaped central part 2.
1 and a concentric wave-like outer peripheral part 26, and is elastically supported by the central part or the outer peripheral part so as to be able to vibrate. As shown in FIG. 2, an adjustment piece 28 is fixed to the center of the diaphragm 18 to determine the vibrating mass of the diaphragm 18.
以上のように構成された吸気レゾネータ１２が取り付け
られた吸気配管を備えたエンジンが作動させられると、
そのエンジンの回転数に対応した周波数成分を有し、ノ
ーズ部１０を通して外部に放出される吸気配管系の吸気
ノイズが従来に比較してきわめて効果的に抑制されるの
である。このような効果が得られるのは以下の理由によ
るものと考えられる。When an engine equipped with an intake pipe to which the intake resonator 12 configured as described above is attached is operated,
It has a frequency component corresponding to the rotational speed of the engine, and the intake noise of the intake piping system that is released to the outside through the nose portion 10 is suppressed very effectively compared to the conventional case. The reason why such an effect is obtained is considered to be due to the following reasons.
すなわち、共鳴空室の壁面が剛性の高い材質形状で構成
される従来の吸気レゾネータにおいては、その共振周波
数ｆｏ は、次式；
ここで、Ｃは音速、■は共鳴空室の容積、ｅは接続管部
の長さ、Ｓは接続管路の断面積である；によって表わさ
れ、その共鳴吸収による減衰量へ 。In other words, in a conventional intake resonator in which the wall surface of the resonant chamber is made of a highly rigid material, the resonant frequency fo is calculated by the following formula; where C is the speed of sound, ■ is the volume of the resonant chamber, and e is The length of the connecting pipe section, S is the cross-sectional area of the connecting pipe; and is expressed by the amount of attenuation due to resonance absorption.
（単位：デシベル）は、第３図の実線にも示されるよう
に、次式；
ここで、ρ０は媒質の密度、Ｃｏは共鳴空室の音響伝導
率、ｏＩは音波（吸気ノイズ）の角速度である；によっ
て表わされる特性が備えられている。(Unit: decibel), as shown by the solid line in Figure 3, is expressed by the following formula; where ρ0 is the density of the medium, Co is the acoustic conductivity of the resonant chamber, and oI is the angular velocity of the sound wave (intake noise). It has the property represented by;
しかしながら、吸気配管を通して外部に放射さ１する吸
気ノイズはエンジンの回転数に関連した周波数成分によ
って主体的に構成され、エンジンの回転に伴って吸気ノ
イズの周波数が変化するため、第３図の実線に示される
ような鋭いピークを有する減衰ｑ１特性を有する従来の
吸気レゾネータによって幅広い周波数成分に変化し得る
吸気ノイズを減貞させることは共鳴空室の容量■を大き
くする以ダ１、に困難であったのである。However, the intake noise radiated to the outside through the intake pipe is mainly composed of frequency components related to the engine speed, and the frequency of the intake noise changes as the engine rotates, so the solid line in Figure 3 It is difficult to attenuate intake noise that can vary over a wide range of frequency components using a conventional intake resonator that has an attenuation q1 characteristic with a sharp peak as shown in Figure 1, except by increasing the capacity of the resonance chamber. There it was.
これに対し、吸気レゾネータ１２によれば、その！（鳴
空室がダイヤプラム１８によって分割されてｊｊＨ１ｇ
空室の過半を占め且つノーズ部１０に連通ずる１−室２
０が形成され、その、Ｉ〕室２０において実際の共鳴吸
収作用が為されるのであるが、その１−室２０の内壁面
の一部を為すダイヤフラム１８が弾性的に支持されて振
動可能であるので、そのダイヤフラム１８の振動特性と
相俟って、第３図の点線に示されるように、周波数に対
して幅広い減衰量特性が得られる。この結果、吸気レゾ
ネータ１２の容積を大きくすることなく、幅広い周波数
成分に変化し得る吸気ノイズが吸気レゾネータ１２によ
って全体として有効に吸収させられ得るのである。On the other hand, according to the intake resonator 12, that! (The Naraku chamber is divided by diaphragm 18 and jjH1g
1-chamber 2, which occupies the majority of the empty space and communicates with the nose portion 10;
The diaphragm 18, which forms part of the inner wall surface of the 1-chamber 20, is elastically supported and vibrates. Therefore, together with the vibration characteristics of the diaphragm 18, a wide range of attenuation characteristics with respect to frequency can be obtained, as shown by the dotted line in FIG. As a result, the intake noise that can vary over a wide range of frequency components can be effectively absorbed by the intake resonator 12 as a whole without increasing the volume of the intake resonator 12.
ここで、減衰量特性は調節片２８の重量、ダイヤフラム
１８の外周部の弾性力等を変化させることによって適宜
変更され得るので、同じ上容器ｌｌおよび下容器１３か
ら成る吸気レゾネータ１２が、ダイヤフラム１８のみを
変更することによって種々の型式のエンジンに適用され
る利点がある。Here, the attenuation characteristic can be changed as appropriate by changing the weight of the adjusting piece 28, the elastic force of the outer periphery of the diaphragm 18, etc. It has the advantage that it can be applied to various types of engines by only changing.
また、ダイヤフラム１８は振動可能に設けられているの
で、下容器１３はダイヤフラム１８を通して吸気ノイズ
が外部に伝達されることを防ぐ機能を有している。Further, since the diaphragm 18 is provided to be able to vibrate, the lower container 13 has a function of preventing intake noise from being transmitted to the outside through the diaphragm 18.
次に、本発明の他の実施例を説明する。尚、以下の説明
において前述の説明と共通する部分にはは？Ｗ数の小さ
な貫通孔３２が形成されている。Next, another embodiment of the present invention will be described. In addition, what parts of the following explanation have in common with the previous explanation? A through hole 32 with a small W number is formed.
したがって、下室２２は上室２０と貫通孔３２全通して
連通させられ、下室２２自体も上室２０内に到達した吸
気ノイズを共鳴吸収するので、吸％ ノイズか吸気レゾ
ネータ１２によって一層有効に１１−に収さｔすること
かできる。Therefore, the lower chamber 22 is communicated with the upper chamber 20 through the through hole 32, and the lower chamber 22 itself resonates and absorbs the intake noise that reaches the upper chamber 20. It is possible to fit it into 11-.
Ｉ１１本発明の一実施例を示す図面に基づいて説明した
が、本発明はその他の態様においても適用される。I11 Although the embodiment of the present invention has been described based on the drawings, the present invention can also be applied to other aspects.
たとえば、同一型式のエンジンに適用するため１ｆこ１
及気レゾネータ１２の周波数に対する減衰特性が一定で
よい場合には、ダイヤフラム１８の中央部２４の質１斜
：を調節片２８の質量を含んだものとし、調節片２８を
除去しても良いのである。For example, 1f is applied to the same model of engine.
If the damping characteristic of the air resonator 12 with respect to the frequency is sufficient to be constant, the quality of the central portion 24 of the diaphragm 18 may include the mass of the adjustment piece 28, and the adjustment piece 28 may be removed. be.
土だ、ｒｉ通孔３２の数、径、および位置は、吸気レゾ
ネータ１２が適用されるエンジンの型式に応じて適宜変
更され得るのである。The number, diameter, and position of the intake resonator 12 can be changed as appropriate depending on the type of engine to which the intake resonator 12 is applied.
以り詳記したように、本発明の吸気レゾネータ的に支持
された隔壁が設けられているので、吸気レゾネータの周
波数に対する減衰特性の幅が広くなり、エンジンの吸気
配管を通して外部に放射される吸気ノイズが、吸気レゾ
ネータの容積を増やすことなく有効に減衰させられるの
である。As described in detail above, since the intake resonator of the present invention is provided with a supported bulkhead, the frequency range of the damping characteristic of the intake resonator is widened, and the intake air radiated to the outside through the intake pipe of the engine is increased. Noise is effectively attenuated without increasing the volume of the intake resonator.
第１図は本発明の一実施例の構成を説明する図である。
第２図は第１図のＩ−１視断面図である。
第３図は第１図の特性を説明する図である。第４図は本
発明の他の実施例を説明する第２図に相当する図である
。
１０：ノーズ部（吸気配管）
１２：吸気レゾネータ
１８：ダイヤフラム（隔壁）
出願人 トヨタ自動車工業株式会社
パ′３図
゛４し１FIG. 1 is a diagram illustrating the configuration of an embodiment of the present invention. FIG. 2 is a sectional view taken along line I-1 in FIG. 1. FIG. 3 is a diagram explaining the characteristics of FIG. 1. FIG. 4 is a diagram corresponding to FIG. 2 explaining another embodiment of the present invention. 10: Nose part (intake piping) 12: Intake resonator 18: Diaphragm (partition wall) Applicant Toyota Motor Corporation Part'3 Figure 4-1
Claims (1)
気配管系の吸気ノイズを共鳴吸収する吸気レゾネータに
おいて、 朋記工を鳴空室を分割する隔壁を該共鳴空室内に配設し
、汁つ該隔壁を弾性的に支持して振動可能としたことを
特徴とする吸気レゾネータ。[Claims] In an intake resonator that includes a resonant chamber connected to the intake piping of an engine and that resonates and absorbs intake noise in the intake piping system, 1. An intake resonator, which is disposed indoors and is capable of vibrating by elastically supporting a partition wall.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP646882A JPS58124057A (en) | 1982-01-19 | 1982-01-19 | Suction air resonator |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP646882A JPS58124057A (en) | 1982-01-19 | 1982-01-19 | Suction air resonator |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPS58124057A true JPS58124057A (en) | 1983-07-23 |
Family
ID=11639280
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP646882A Pending JPS58124057A (en) | 1982-01-19 | 1982-01-19 | Suction air resonator |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS58124057A (en) |
Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP0704617A1 (en) * | 1994-09-02 | 1996-04-03 | General Motors Corporation | Acoustic absorber |
| FR2840652A1 (en) * | 2002-06-07 | 2003-12-12 | Trelleborg Automotive France | Attenuation device for noises coming form i.c. engine operation and vehicle air conditioning system comprises membrane responding to predetermined vibration frequency and is positioned on hole in air inlet pipe |
| US6792907B1 (en) | 2003-03-04 | 2004-09-21 | Visteon Global Technologies, Inc. | Helmholtz resonator |
| US7055484B2 (en) * | 2002-01-18 | 2006-06-06 | Carrier Corporation | Multiple frequency Helmholtz resonator |
| US7540353B2 (en) | 2004-09-29 | 2009-06-02 | Toyoda Gosei Co., Ltd. | Resonator |
| US7845466B2 (en) * | 2007-08-28 | 2010-12-07 | Visteon Global Technologies, Inc. | Sound generator with structurally and acoustically coupled sound radiation panel and method for manufacturing the same |
| US8381871B1 (en) | 2011-09-28 | 2013-02-26 | Visteon Global Technologies, Inc. | Compact low frequency resonator |
| FR2995028A1 (en) * | 2012-08-30 | 2014-03-07 | Coutier Moulage Gen Ind | Filtering device for filtering airflow in line of air inlet of internal combustion engine in car, has deflector arranged in inlet compartment, where deflector faces inlet orifice, so as to deflect dirty airflow penetrating inlet compartment |
-
1982
- 1982-01-19 JP JP646882A patent/JPS58124057A/en active Pending
Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP0704617A1 (en) * | 1994-09-02 | 1996-04-03 | General Motors Corporation | Acoustic absorber |
| US7055484B2 (en) * | 2002-01-18 | 2006-06-06 | Carrier Corporation | Multiple frequency Helmholtz resonator |
| FR2840652A1 (en) * | 2002-06-07 | 2003-12-12 | Trelleborg Automotive France | Attenuation device for noises coming form i.c. engine operation and vehicle air conditioning system comprises membrane responding to predetermined vibration frequency and is positioned on hole in air inlet pipe |
| US6792907B1 (en) | 2003-03-04 | 2004-09-21 | Visteon Global Technologies, Inc. | Helmholtz resonator |
| US7540353B2 (en) | 2004-09-29 | 2009-06-02 | Toyoda Gosei Co., Ltd. | Resonator |
| US7845466B2 (en) * | 2007-08-28 | 2010-12-07 | Visteon Global Technologies, Inc. | Sound generator with structurally and acoustically coupled sound radiation panel and method for manufacturing the same |
| US8381871B1 (en) | 2011-09-28 | 2013-02-26 | Visteon Global Technologies, Inc. | Compact low frequency resonator |
| FR2995028A1 (en) * | 2012-08-30 | 2014-03-07 | Coutier Moulage Gen Ind | Filtering device for filtering airflow in line of air inlet of internal combustion engine in car, has deflector arranged in inlet compartment, where deflector faces inlet orifice, so as to deflect dirty airflow penetrating inlet compartment |
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