JPS6337244B2 - - Google Patents
Info
- Publication number
- JPS6337244B2 JPS6337244B2 JP17657380A JP17657380A JPS6337244B2 JP S6337244 B2 JPS6337244 B2 JP S6337244B2 JP 17657380 A JP17657380 A JP 17657380A JP 17657380 A JP17657380 A JP 17657380A JP S6337244 B2 JPS6337244 B2 JP S6337244B2
- Authority
- JP
- Japan
- Prior art keywords
- exhaust pipe
- cylinder
- muffler
- inner cylinder
- exhaust
- 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.)
- Expired
Links
- 239000011358 absorbing material Substances 0.000 claims description 11
- 230000003584 silencer Effects 0.000 claims description 6
- 230000000694 effects Effects 0.000 description 3
- 230000004048 modification Effects 0.000 description 3
- 238000012986 modification Methods 0.000 description 3
- 238000011144 upstream manufacturing Methods 0.000 description 3
- 230000002238 attenuated effect Effects 0.000 description 2
- 230000030279 gene silencing Effects 0.000 description 2
- 238000004519 manufacturing process Methods 0.000 description 2
- 239000002184 metal Substances 0.000 description 2
- 230000033228 biological regulation Effects 0.000 description 1
- 238000004891 communication Methods 0.000 description 1
- 230000008602 contraction Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 239000011491 glass wool Substances 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 230000001105 regulatory effect Effects 0.000 description 1
- 230000001743 silencing effect Effects 0.000 description 1
- 210000002268 wool Anatomy 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
- F01N3/00—Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust
- F01N3/08—Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust for rendering innocuous
- F01N3/10—Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust for rendering innocuous by thermal or catalytic conversion of noxious components of exhaust
- F01N3/24—Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust for rendering innocuous by thermal or catalytic conversion of noxious components of exhaust characterised by constructional aspects of converting apparatus
- F01N3/28—Construction of catalytic reactors
- F01N3/2882—Catalytic reactors combined or associated with other devices, e.g. exhaust silencers or other exhaust purification devices
- F01N3/2885—Catalytic reactors combined or associated with other devices, e.g. exhaust silencers or other exhaust purification devices with exhaust silencers in a single housing
Landscapes
- Chemical & Material Sciences (AREA)
- Chemical Kinetics & Catalysis (AREA)
- Engineering & Computer Science (AREA)
- Health & Medical Sciences (AREA)
- Toxicology (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Exhaust Silencers (AREA)
Description
【発明の詳細な説明】
本発明は、消音器に係り、特に、自動車の排気
管の終端部に設けられて排気音を消音する消音器
に関する。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a muffler, and more particularly to a muffler that is installed at the end of an automobile exhaust pipe and muffles exhaust noise.
一般に、自動車の排気音の消音対策としては、
大きく分けて、排気管系の音響特性（消音器の装
着位置、消音器の内部構造、排気管の形状等が関
係する。）と、噴流騒音特性（消音器の内部構造
排気管のテール口径、テール形状等が関係する。）
とについて考慮した対策があり、そして、通過騒
音規制を満足するために、両観点から種々の消音
対策手段が講じられている。 In general, measures to muffling automobile exhaust noise include:
Broadly speaking, the acoustic characteristics of the exhaust pipe system (related to the mounting position of the muffler, the internal structure of the muffler, the shape of the exhaust pipe, etc.) and the jet noise characteristics (internal structure of the muffler, tail diameter of the exhaust pipe, etc.) (Depends on the tail shape etc.)
There are measures taken into consideration, and in order to satisfy passing noise regulations, various noise reduction measures have been taken from both viewpoints.
従来、噴流騒音特性についての消音対策として
は、テール口径を大きくとる手段が講じられてい
る。ところが、テール口径と消音特性との関係
は、第１図および第２図に示すような関係になつ
ているため、テール口径をこれ以上大きくする
と、自動車の車室内に所謂こもり音が発生する等
低周波音域における消音が劣悪化するという問題
を招来する。 Conventionally, measures to reduce jet noise characteristics include increasing the diameter of the tail. However, since the relationship between the tail diameter and the noise reduction characteristics is as shown in Figures 1 and 2, if the tail diameter is made larger than this, so-called muffled noise will occur inside the vehicle interior. This results in the problem of poor sound deadening in the low frequency range.
一方、実際の自動車走行時におけるエンジン回
転数に対する排気騒音レベルの消音に対する前記
両特性の寄与度について検討すると、エンジンの
排気量およびテール口径によつて異なるが、2000
c.c.以上の高排気量の車種においては、低〜中回転
数域では排気管系の音響特性の寄与度が高く、高
回転数域では噴流騒音特性の寄与度が高い。 On the other hand, when considering the contribution of both of the above characteristics to the muffling of the exhaust noise level with respect to the engine speed during actual driving, it is found that 2000
In vehicle models with a high displacement of cc or more, the acoustic characteristics of the exhaust pipe system have a high contribution in the low to medium rotation speed range, and the contribution of the jet noise characteristics has a high contribution in the high rotation speed range.
したがつて、従来のテール口径による噴流騒音
特性に関する消音対策にあつては、エンジンの高
回転数域において十分な消音が行なわれない場合
が発生する危惧がある。しかしながら、テール口
径は、前述したように、これ以上増加することが
できないという問題がある。 Therefore, with conventional noise reduction measures for jet noise characteristics using the tail diameter, there is a risk that sufficient noise reduction may not be achieved in the high rotational speed range of the engine. However, as mentioned above, there is a problem in that the tail diameter cannot be increased any further.
本発明は、このような従来技術の問題点に着目
してなされたものであり、排気管に消音材を排気
ガス流についての圧力損失を発生しないように介
設することにより、テール口径を増加することな
く、高回転数域における消音も完全に行なうこと
ができる消音器を提供することを目的とする。 The present invention has been made by focusing on the problems of the conventional technology, and increases the tail diameter by interposing a sound deadening material in the exhaust pipe so as to prevent pressure loss from occurring in the exhaust gas flow. To provide a muffler capable of completely muffling noise in a high rotational speed range without causing any noise.
以下図面に即して本発明の実施例を説明する。 Embodiments of the present invention will be described below with reference to the drawings.
第３図は本発明にかかる消音器を適用した排気
管系の一実施例を示すものであり、この排気管系
における排気管１の中間部にはコンバータ２と従
来の構造を有する主消音器３とが上流側から順次
介設されており、主消音器３は特に前述した音響
特性に関する対策手段が考慮されている。主消音
器３の出口側はその流路が絞られることにより、
低周波数音域の低減が行なわれるようになつてい
る。この排気管１の終端部には、補助消音器とし
て本発明にかかる消音器４が設けられており、こ
の消音器４は、エンジンの高回転数域における消
音を完全に行なうとともに、排気管端における噴
流騒音の低減化および主消音器３の内部で発生し
た排気ガス流による騒音の低減化を行なうことに
より補助消音器としての機能を果すものであり、
第４図に示すように構成されている。 FIG. 3 shows an embodiment of an exhaust pipe system to which the muffler according to the present invention is applied. In this exhaust pipe system, a converter 2 and a main muffler having a conventional structure are installed in the middle of the exhaust pipe 1. 3 are successively provided from the upstream side, and the main muffler 3 is particularly designed to take measures regarding the above-mentioned acoustic characteristics. By constricting the flow path on the outlet side of the main silencer 3,
The reduction of low frequency ranges is becoming more and more common. A muffler 4 according to the present invention is provided at the end of the exhaust pipe 1 as an auxiliary muffler. It functions as an auxiliary muffler by reducing the jet noise in the main muffler 3 and the noise caused by the exhaust gas flow generated inside the main muffler 3.
It is constructed as shown in FIG.
第４図は本発明の一実施例を示すものであり、
この消音器４は、排気管１よりも若干大口径を有
する外筒５と、この外筒５よりも若干小口径を有
する内筒６と、この内筒６および外筒５の両端部
にそれぞれ配設されて内筒６を外筒５内に支持
し、互に対となる第１および第２テーパ筒７，８
と、内筒６内に介挿された多孔質容器９と、この
多孔質容器９内に充填されたガラスウール等から
なる吸音材１０とを備えている。前記外筒５は排
気管１の終端部に膨径された大径部１Ａに一端を
外嵌して固着されることにより、排気管１内の排
気ガスを連通し得るように連結されている。前記
第１および第２テーパ筒７，８は一面に開口部ａ
を、他面に閉鎖部ｂを有する互に同一形のほぼさ
い頭円錐筒形状に金属薄板等からそれぞれ一体成
形されており、第１テーパ筒７は外筒５の上流側
に開口部ａを上流に向けて、第２テーパ筒８は外
筒５の下流側に開口部ａを下流に向けてそれぞれ
内嵌して固着されている。前記内筒６は両端部内
周を第１および第２テーパ筒７，８の閉鎖部ｂの
外周にそれぞれ嵌合することにより外筒５内に筒
芯をほぼ合致して支持されており、外筒５と内筒
６との間に形成された空間部分は流通部１１を構
成している。内筒６と第１、第２テーパ筒７，８
との筒壁には小孔１２が多数穿設されている。前
記多孔質容器９は発泡質の金属またはステンレス
ウール等によりほぼ円筒形状に成形されており、
この内部に充填された吸音材１０が飛散すること
を防止するとともに、この多孔質容器９自体が吸
音作用を発揮するようになつている。 FIG. 4 shows an embodiment of the present invention,
This muffler 4 has an outer cylinder 5 having a diameter slightly larger than that of the exhaust pipe 1, an inner cylinder 6 having a slightly smaller diameter than the outer cylinder 5, and an inner cylinder 6 and an outer cylinder 5, respectively. First and second tapered cylinders 7 and 8 are disposed to support the inner cylinder 6 within the outer cylinder 5 and are paired with each other.
A porous container 9 is inserted into an inner cylinder 6, and a sound absorbing material 10 made of glass wool or the like is filled in the porous container 9. The outer cylinder 5 is connected to the exhaust pipe 1 so that the exhaust gas in the exhaust pipe 1 can be communicated with the outer cylinder 5 by fitting and fixing one end to the large diameter part 1A expanded at the terminal end of the exhaust pipe 1. . The first and second tapered cylinders 7 and 8 have an opening a on one side.
are integrally molded from a thin metal plate or the like into substantially truncated conical cylinders having the same shape and having a closed part b on the other side, and the first tapered cylinder 7 has an opening a on the upstream side of the outer cylinder 5. Upstream, the second tapered cylinder 8 is fitted and fixed to the downstream side of the outer cylinder 5 with the opening a facing downstream. The inner cylinder 6 is supported within the outer cylinder 5 by fitting the inner peripheries of both ends into the outer peripheries of the closed portions b of the first and second tapered cylinders 7 and 8, respectively, so that the cylinder cores almost coincide with each other. A space formed between the cylinder 5 and the inner cylinder 6 constitutes a flow section 11. Inner cylinder 6 and first and second tapered cylinders 7 and 8
A large number of small holes 12 are bored in the cylinder wall. The porous container 9 is formed into a substantially cylindrical shape from foamed metal, stainless wool, or the like,
The sound absorbing material 10 filled inside is prevented from scattering, and the porous container 9 itself exhibits a sound absorbing effect.
前記構成にかかる消音器におけるエンジンの高
回転数域における消音作用について説明する。 The silencing effect in the high rotational speed range of the engine in the silencer according to the above configuration will be explained.
第３図に示す排気管系における主消音器３で所
期の消音を行なわれ、若干の排気音と主消音器３
の内部で発生した気流音を随伴した排気ガス流
は、排気管１の終端部に設けられた補助消音器４
に至る。補助消音器４において、排気ガスは第１
テーパ筒７の小孔１２群から流通部１１に流入
し、そこを流通して第２テーパ筒８の小孔１２群
を通過して大気に排出していく。このとき、排気
ガスはテーパ筒７，８の小孔１２群を通過するた
め、それにより受ける抵抗は小さく、また、エン
ジンから発生する脈動流を整圧し圧力損失および
噴流騒音は殆ど発生しない。排気ガスが流通部１
１を流通するとき、この排気ガスに随伴する排気
音の平面波は、内筒６の小孔１２群から内筒６内
を通り、多孔質容器９およびこれに充填された吸
音材１０により減衰されて殆ど消音される。 The main muffler 3 in the exhaust pipe system shown in Fig. 3 performs the desired muffling, and some exhaust noise and main muffler
The exhaust gas flow accompanied by airflow noise generated inside the exhaust pipe 1 is passed through an auxiliary silencer 4 provided at the terminal end of the exhaust pipe 1.
leading to. In the auxiliary silencer 4, the exhaust gas is
It flows into the flow section 11 through the 12 groups of small holes in the tapered tube 7, circulates there, passes through the 12 groups of small holes in the second tapered tube 8, and is discharged into the atmosphere. At this time, the exhaust gas passes through the group of small holes 12 in the tapered tubes 7 and 8, so the resistance it receives is small, and the pulsating flow generated from the engine is regulated, so that almost no pressure loss or jet noise occurs. Exhaust gas flows through the distribution section 1
1, the plane wave of the exhaust sound accompanying this exhaust gas passes through the inner cylinder 6 from the 12 groups of small holes in the inner cylinder 6, and is attenuated by the porous container 9 and the sound absorbing material 10 filled therein. Most of the sound is muted.
このようにして、この消音器４によれば、エン
ジンの高回転数域における排気音も、テール口径
を増加しないで、完全に消音することができる。
したがつて、低回転数域から高回転数域の全域に
おいて消音性能の高い排気管系を設計することが
可能になる。また、吸音材によつて排気音を減衰
消音させるため、特に中〜高周波数音域について
の減衰消音が可能である。他方、テーパ筒に小孔
を形成して排気ガスを流通させ、吸音材と接触さ
せるように構成されているので、流通抵抗が小さ
く、しかも、噴流騒音の発生を抑制することがで
きる。また、吸音材はそれ自体が吸音効果を有す
る多孔質容器の内部を充填したので、吸音材が排
気ガス流に随伴して飛散することを防止でき、長
期間一定の消音効果を維持することができる。さ
らに、消音器は排気管の終端部に簡単に装着する
ことができる。 In this way, according to this muffler 4, exhaust noise in the high rotational speed range of the engine can be completely muffled without increasing the tail diameter.
Therefore, it is possible to design an exhaust pipe system with high noise reduction performance over the entire range from low rotational speed to high rotational speed. Further, since the exhaust sound is attenuated and muffled by the sound absorbing material, it is possible to attenuate and muffle the sound particularly in the middle to high frequency range. On the other hand, since a small hole is formed in the tapered tube to allow exhaust gas to flow through and come into contact with the sound absorbing material, the flow resistance is small and the generation of jet noise can be suppressed. In addition, since the sound-absorbing material itself is filled inside the porous container, which has a sound-absorbing effect, it is possible to prevent the sound-absorbing material from scattering along with the exhaust gas flow, and to maintain a constant sound-absorbing effect for a long period of time. can. Furthermore, the muffler can be easily installed at the end of the exhaust pipe.
なお、前記実施例では、外筒５を排気管１の大
径部１Ａに外嵌して装着する場合について説明し
たが、第５図に示すように、外筒５は、その一端
部を排気管１の外径とほぼ等しい口径を有する小
径部５Ａに形成し、この小径部５Ａを排気管１に
外嵌して固着することにより、排気管１に連通状
態で装着することもできる。また、前記実施例で
は、内筒６とテーパ筒７，８とを別体に形成して
これらを連結する場合について説明したが、第６
図に示すように、内筒６とテーパ筒７，８とを連
結した状態で、かつ、筒芯方向に２つ割にそれぞ
れ一体成形し、この分割体を最中合せにして連結
して成る構造にしてもよく、この構造によれば、
製造が一層簡単になる。この場合、吸音材１０を
充填した多孔質容器９の両筒端面に閉鎖部ｂをそ
れぞれ形成するとよい。さらに、内筒６とテーパ
筒７，８との一体連結構造としては、第７図に示
すような構造を採用することもできる。第７図に
おいて、テーパ筒７，８はほぼ円錐筒形状をなし
た形態となり、内筒６の両端は閉鎖された形態と
なり、テーパ筒７，８と内筒６の両端との連結部
分は空間的には仕切られた状態となり、板形状部
Ｃでテーパ筒７，８と内筒６とが連結されること
になる。この構造によれば、製造の簡単化ととも
に、テーパ筒７，８における小孔１２群が増加
し、排気ガスの拡張および縮流面積が増加し、圧
力損失を一層低減化できるという効果を得ること
ができる。 In the above embodiment, the case where the outer cylinder 5 is fitted onto the large diameter portion 1A of the exhaust pipe 1 has been described, but as shown in FIG. By forming a small diameter portion 5A having a diameter approximately equal to the outer diameter of the pipe 1, and fitting and fixing the small diameter portion 5A onto the exhaust pipe 1, it can also be mounted in communication with the exhaust pipe 1. Further, in the above embodiment, the case where the inner cylinder 6 and the tapered cylinders 7 and 8 are formed separately and connected to each other has been explained, but the sixth embodiment
As shown in the figure, the inner cylinder 6 and the tapered cylinders 7 and 8 are connected and integrally molded into two halves in the direction of the cylinder core, and these divided bodies are joined in the middle and connected. According to this structure,
Manufacturing becomes easier. In this case, it is preferable to form closing portions b on the end faces of both cylinders of the porous container 9 filled with the sound absorbing material 10, respectively. Further, as the integral connection structure between the inner cylinder 6 and the tapered cylinders 7 and 8, a structure as shown in FIG. 7 may be adopted. In FIG. 7, the tapered cylinders 7 and 8 have a substantially conical cylinder shape, both ends of the inner cylinder 6 are closed, and the connection portion between the tapered cylinders 7 and 8 and both ends of the inner cylinder 6 is a space. In other words, they are in a partitioned state, and the tapered cylinders 7, 8 and the inner cylinder 6 are connected at the plate-shaped portion C. This structure not only simplifies manufacturing, but also increases the number of 12 groups of small holes in the tapered tubes 7 and 8, increases the expansion and contraction area of exhaust gas, and further reduces pressure loss. Can be done.
ちなみに、前記実施例では、エンジンの高回転
数域における排気音の減衰消音の場合について説
明したが、本発明にかかる消音器はこれに限らず
べての回転数域およびすべての周波数音域につい
ての消音が可能であり、かつ、単独使用も可能で
ある。 Incidentally, in the above embodiment, the case of attenuating and silencing the exhaust sound in the high rotation speed range of the engine was explained, but the muffler according to the present invention is not limited to this, and can suppress noise in all rotation speed ranges and all frequency ranges. It is also possible to use it alone.
以上説明するように、本発明によれば、排気管
に吸音材を圧力損失を発生することのないように
設けたので、排気管系における排気ガス流の障害
等の二次障害を発生することなくして、排気音を
完全に消音することができる。 As explained above, according to the present invention, the sound absorbing material is provided in the exhaust pipe in such a way as to prevent pressure loss from occurring, thereby preventing the occurrence of secondary disturbances such as disturbances in the flow of exhaust gas in the exhaust pipe system. Exhaust noise can be completely silenced.
第１図および第２図はテール口径と消音特性と
の関係を示す各特性線図、第３図は本発明にかか
る消音器を使用した排気管系の一実施例を示す正
面図、第４図は本発明の一実施例を示す縦断面
図、第５図は外筒の変形例を示す斜視図、第６図
は内筒とテーパ筒との変形例を示す分解斜視図、
第７図は同じく他の変形例を示す分解斜視図であ
る。
１……排気管、３……主消音器、４……補助消
音器（本発明消音器）、５……外筒、６……内筒、
７，８……テーパ筒、９……多孔質容器、１０…
…吸音材。
1 and 2 are characteristic diagrams showing the relationship between the tail diameter and silencing characteristics, FIG. 3 is a front view showing an example of an exhaust pipe system using the muffler according to the present invention, and FIG. 5 is a perspective view showing a modification of the outer cylinder, FIG. 6 is an exploded perspective view showing a modification of the inner cylinder and the tapered cylinder,
FIG. 7 is an exploded perspective view showing another modification. DESCRIPTION OF SYMBOLS 1... Exhaust pipe, 3... Main muffler, 4... Auxiliary muffler (silencer of the present invention), 5... Outer cylinder, 6... Inner cylinder,
7, 8... Tapered tube, 9... Porous container, 10...
...Sound absorbing material.
Claims (1)
排気音を消音する消音器において、前記排気管よ
りも若干大口径であり、この排気管に排気ガスを
流通自在に連結される外筒内にこの外筒よりも若
干小口径の内筒を、この内筒の両端部にテーパ筒
を配設して支持するとともに、前記内筒およびテ
ーパ筒の筒壁に多数個の小孔を形成し、さらに、
内筒内に吸音材を充填したことを特徴とする消音
器。1. In a muffler that is installed in a part of the exhaust pipe of an automobile to muffle the exhaust noise of the automobile, an outer cylinder that has a slightly larger diameter than the exhaust pipe and is connected to the exhaust pipe so that exhaust gas can freely flow therethrough. An inner cylinder having a diameter slightly smaller than that of the outer cylinder is supported by a tapered cylinder arranged at both ends of the inner cylinder, and a large number of small holes are formed in the cylinder walls of the inner cylinder and the tapered cylinder. And furthermore,
A silencer characterized by filling an inner cylinder with a sound absorbing material.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP17657380A JPS57102507A (en) | 1980-12-16 | 1980-12-16 | Muffler |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP17657380A JPS57102507A (en) | 1980-12-16 | 1980-12-16 | Muffler |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS57102507A JPS57102507A (en) | 1982-06-25 |
| JPS6337244B2 true JPS6337244B2 (en) | 1988-07-25 |
Family
ID=16015918
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP17657380A Granted JPS57102507A (en) | 1980-12-16 | 1980-12-16 | Muffler |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS57102507A (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0286754U (en) * | 1988-12-22 | 1990-07-10 |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US9488079B2 (en) * | 2012-02-07 | 2016-11-08 | Black Widow Performance, Inc. | Muffler for automobile |
| CN103742242B (en) * | 2013-12-25 | 2016-05-11 | 潍柴动力股份有限公司 | A kind of SCR catalytic muffler and escape pipe thereof |
-
1980
- 1980-12-16 JP JP17657380A patent/JPS57102507A/en active Granted
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0286754U (en) * | 1988-12-22 | 1990-07-10 |
Also Published As
| Publication number | Publication date |
|---|---|
| JPS57102507A (en) | 1982-06-25 |
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