JPH0810655Y2 - Engine muffler - Google Patents
Engine mufflerInfo
- Publication number
- JPH0810655Y2 JPH0810655Y2 JP1990010092U JP1009290U JPH0810655Y2 JP H0810655 Y2 JPH0810655 Y2 JP H0810655Y2 JP 1990010092 U JP1990010092 U JP 1990010092U JP 1009290 U JP1009290 U JP 1009290U JP H0810655 Y2 JPH0810655 Y2 JP H0810655Y2
- Authority
- JP
- Japan
- Prior art keywords
- expansion chamber
- muffler
- exhaust
- flow direction
- sectional area
- 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 - Lifetime
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- Exhaust Silencers (AREA)
Description
【考案の詳細な説明】 〈産業上の利用分野〉 本考案は、エンジンのマフラに関する。DETAILED DESCRIPTION OF THE INVENTION <Industrial Application Field> The present invention relates to an engine muffler.
〈従来技術〉 本考案は、その基本構造として、例えば第１図及び第
６図に示すように、エンジンＥのマフラ１の排気入口管
５に少なくとも第１膨張室２・第１連通路７・第２膨張
室３・第２連通路８及び第３膨張室４を順に介して排気
出口管６を連通させて構成したマフラに関する。<Prior Art> As a basic structure of the present invention, as shown in FIGS. 1 and 6, for example, at least a first expansion chamber 2, a first communication passage 7, and an exhaust inlet pipe 5 of a muffler 1 of an engine E are provided. The present invention relates to a muffler configured by communicating an exhaust outlet pipe 6 through the second expansion chamber 3, the second communication passage 8 and the third expansion chamber 4 in order.
従来では、上記基本構造において、第６図に示すよう
に、第１膨張室２及び第３膨張室４の長さL1・L3を長
く、第２膨張室３の長さL2を短く形成し、第１膨張室
２、第２膨張室３及び第３膨張室４の横断面積A1・A2・
A3を同じに形成することで、第１膨張室２及び第３膨張
室４で排気騒音中の低周波音を消音し、第２膨張室３で
排気騒音中の高周波音を消音していた。Conventionally, in the above basic structure, as shown in FIG. 6, the lengths L 1 and L 3 of the first expansion chamber 2 and the third expansion chamber 4 are long, and the length L 2 of the second expansion chamber 3 is short. And the cross-sectional area of the first expansion chamber 2, the second expansion chamber 3 and the third expansion chamber 4 A 1 · A 2 ·
By forming A 3 to be the same, the first expansion chamber 2 and the third expansion chamber 4 silenced the low-frequency noise in the exhaust noise, and the second expansion chamber 3 silenced the high-frequency noise in the exhaust noise. .
〈考案が解決しようとする課題〉 しかし、上記従来例では、次の問題がある。<Problems to be Solved by the Invention> However, the above conventional example has the following problems.
排気騒音中の低周波音と高周波音とを比較すると、音
圧レベル（dB）が同じである場合には、高周波音の方が
人間の耳に感ずる大きさは大きい（即ち、騒音の単位で
あるホンの値が大きい）。Comparing low-frequency sound and high-frequency sound in exhaust noise, when the sound pressure level (dB) is the same, the high-frequency sound is more noticeable to the human ear (that is, in units of noise). The value of a certain phone is large).
上記従来例のように、第１膨張室で排気騒音中の低周
波音を消音し、第２膨張室で高周波音を消音するもので
は、第２膨張室で高周波音が消音される前に第１膨張室
から高周波音が透過してしまうので、マフラから漏洩す
る騒音（ホンの値）が大きくなる。In the case where the low frequency sound in the exhaust noise is silenced in the first expansion chamber and the high frequency sound is silenced in the second expansion chamber as in the above-mentioned conventional example, the first high frequency sound is silenced before being silenced in the second expansion chamber. (1) Since high-frequency sound is transmitted from the expansion chamber, noise (phone value) leaked from the muffler becomes large.
本考案は、簡単な構造により、漏洩騒音（ホンの値）
を低下させることを課題とする。The present invention has a simple structure to prevent leakage noise (phone value).
It is an issue to reduce.
〈課題を解決するための手段〉 本考案は、上記課題を解決するために、例えば第１図
に示すように、構成したものである。<Means for Solving the Problems> The present invention is configured to solve the above problems, for example, as shown in FIG.
即ち、第１膨張室２の排気流動方向の長さL1を短かく
形成するのに対し、第２膨張室３の排気流動方向の長さ
L2及び第３膨張室４の排気流動方向の長さL3を長く形成
し、 第１膨張室２の排気流動方向と直交する横断面積A1を
広く形成するのに対し、第２膨張室３の排気流動方向と
直交する横断面積A2及び第３膨張室４の排気流動方向と
直交する横断面積A3を狭く形成した事を特徴とする。That is, the length L 1 of the first expansion chamber 2 in the exhaust flow direction is made short, while the length of the second expansion chamber 3 in the exhaust flow direction is made short.
The length L 3 of L 2 and the third expansion chamber 4 in the exhaust flow direction is made long, and the cross-sectional area A 1 orthogonal to the exhaust flow direction of the first expansion chamber 2 is made wide, whereas the second expansion chamber 2 is made wide. It is characterized in that the cross-sectional area A 2 orthogonal to the exhaust gas flow direction 3 and the cross-sectional area A 3 orthogonal to the exhaust gas flow direction of the third expansion chamber 4 are narrowly formed.
〈作用〉 次に、作用を説明する。<Operation> Next, the operation will be described.
エンジンＥからマフラ１の第１膨張室２に流入した排
気騒音は、まずその中の高周波音が第１膨張室２で消音
される。しかも、第１膨張室２の横断面積A1が広く形成
されていることから、高周波音が大きく消音されて、第
１膨張室２での高周波音の減音量（dBの値）が大きくな
る。The exhaust noise flowing from the engine E into the first expansion chamber 2 of the muffler 1 is such that the high frequency sound therein is first silenced in the first expansion chamber 2. Moreover, since the cross-sectional area A 1 of the first expansion chamber 2 is formed to be wide, the high-frequency sound is largely damped, and the volume reduction (value of dB) of the high-frequency sound in the first expansion chamber 2 increases.
次に、第２膨張室３及び第３膨張室４で排気騒音の中
の低周波音が消音される。これら第２膨張室３及び第３
膨張室４では、その横断面積A2及び横断面積A3が狭く形
成されていることから、低周波音の減音量（dBの値）が
小さくなる。Next, the low-frequency sound in the exhaust noise is silenced in the second expansion chamber 3 and the third expansion chamber 4. These second expansion chamber 3 and third
In the expansion chamber 4, the cross-sectional area A 2 and the cross-sectional area A 3 are formed narrow, so that the volume reduction (value of dB) of the low frequency sound becomes small.
そして、第１膨張室２、第２膨張室３及び第３膨張室
４の各室内の容積の総和を一定にすることで、各室内で
の減音量（dBの値）の総和は一定に保持されるものであ
りながら、排気騒音中の高周波音の方を広い第１膨張室
２で大きく消音するようにしたことから、マフラ１の排
気出口管６からの騒音（ホンの値）は小さくなる。Then, by keeping the total volume of the first expansion chamber 2, the second expansion chamber 3 and the third expansion chamber 4 constant, the total volume reduction (dB value) in each room is kept constant. However, since the high frequency noise in the exhaust noise is largely suppressed in the wide first expansion chamber 2, the noise (value of the phon) from the exhaust outlet pipe 6 of the muffler 1 is reduced. .
しかも、第１膨張室２で高周波音を消音するので、第
２膨張室で初めて高周波音を消音するものと比べて、マ
フラ１からの高周波音の透過が少なく、マフラ１からの
漏洩騒音（ホンの値）は低くなる。Moreover, since the high-frequency sound is silenced in the first expansion chamber 2, the high-frequency sound is less transmitted from the muffler 1 as compared with the first expansion chamber in which the high-frequency sound is silenced for the first time. Value) becomes low.
〈考案の効果〉 本考案は、上述のように構成され、作用することか
ら、下記の効果を奏する。<Effects of the Invention> The present invention, which is configured and operates as described above, has the following effects.
（イ）．聴感特性の高い高周波音の大気中への漏洩量が
少ない まず、第１膨張室２の排気流動方向の長さL1を短かく
形成した構成から、エンジンＥの排気騒音のうち、聴感
特性の高い高周波音は、長さL1の短い第１膨張室２で消
音されて、第２膨張室３および第３膨張室４へはあまり
流れ込まないので、第２膨張室３および第３膨張室４の
周壁から大気中への漏洩量が非常に少なくなる。(I). The amount of leakage of high-frequency sound having a high audible characteristic to the atmosphere is small. First, since the length L 1 in the exhaust flow direction of the first expansion chamber 2 is formed to be short, the audible characteristic of the exhaust noise of the engine E The high-frequency sound is silenced in the first expansion chamber 2 having a short length L 1 and does not flow into the second expansion chamber 3 and the third expansion chamber 4 so much that the second expansion chamber 3 and the third expansion chamber 4 The amount of leakage from the peripheral wall of the to the atmosphere is very small.
次に、第１膨張室２の排気流動方向と直交する横断面
積A1を広く形成した構成から、エンジンＥの排気騒音の
うちの高周波音は、第１膨張室２の横断面積A1が広い分
だけ消音量が多くなるので、第１膨張室２の周壁から大
気中への漏洩量も少なくなる。Next, since the cross-sectional area A 1 orthogonal to the exhaust flow direction of the first expansion chamber 2 is formed to be wide, the high-frequency sound of the exhaust noise of the engine E has a wide cross-sectional area A 1 of the first expansion chamber 2. Since the sound deadening amount increases by that amount, the amount of leakage from the peripheral wall of the first expansion chamber 2 into the atmosphere also decreases.
これにより、音圧レベル（dB）の割りに大きく聞こえ
る聴感特性（ホン）の高い高周波音は、マフラ１の全体
にわたり、大気中への漏洩量が少なくなるので、消音効
果が高く、排気騒音が静かになる。As a result, a high-frequency sound with a high audibility characteristic (phone), which sounds loud compared to the sound pressure level (dB), has a small amount of leakage into the atmosphere throughout the muffler 1, resulting in a high muffling effect and exhaust noise. Be quiet.
（ロ）．排気騒音低減のための構造が簡単 その上、上記騒音低減機能の割には、追加構造を必要
とせず、マフラの寸法関係を設定し直すだけで済み、構
造・形状が簡単で済む。(B). Simple structure for exhaust noise reduction In addition to the above noise reduction function, no additional structure is required, only the muffler dimensional relationship needs to be set again, and the structure and shape are simple.
〈実施例〉 次に、本考案の実施例を第１図乃至第５図に基づき説
明する。<Embodiment> Next, an embodiment of the present invention will be described with reference to FIGS.
エンジンＥのマフラ１は第１マフラ1aと第２マフラ1b
と両マフラ1a・1bを接続する中間連通管10とで構成され
る。The muffler 1 of the engine E is the first muffler 1a and the second muffler 1b.
And an intermediate communication pipe 10 connecting both mufflers 1a and 1b.
第１マフラ1aは排気入口管５と第１膨張室２と上側連
通管11とを有し、排気入口管５の一端開口がエンジンＥ
の排気出口９に接続し、他端に開口した多数の連通孔13
が第１膨張室２に連通している。The first muffler 1a has an exhaust inlet pipe 5, a first expansion chamber 2 and an upper communication pipe 11, and one end opening of the exhaust inlet pipe 5 is an engine E.
A large number of communicating holes 13 connected to the exhaust outlet 9 of
Communicate with the first expansion chamber 2.
第１膨張室２は、その排気流動方向の長さL1が短く、
その排気流動方向と直交する横断面積A1が広くなるよに
形成されており、第１膨張室２で排気騒音中の高周波音
が大きく消音される。The first expansion chamber 2 has a short length L 1 in the exhaust flow direction,
The cross-sectional area A 1 orthogonal to the exhaust flow direction is formed to be large, and the high-frequency sound in the exhaust noise is largely suppressed in the first expansion chamber 2.
第１マフラ1aの下部に水抜き用管16が付設され、上側
連通管11が第２マフラ1bの下側連通管12に接続してい
る。A water draining pipe 16 is attached to a lower portion of the first muffler 1a, and an upper communication pipe 11 is connected to a lower communication pipe 12 of the second muffler 1b.
第２マフラ1bは第２膨張室３と第３膨張室４と下側連
通管12と第２連通路８と排気出口管６とを有し、上側連
通管11と中間連通管10と下側連通管12とで第１連通路７
が構成される。The second muffler 1b has a second expansion chamber 3, a third expansion chamber 4, a lower communication pipe 12, a second communication passage 8 and an exhaust outlet pipe 6, and an upper communication pipe 11, an intermediate communication pipe 10 and a lower side. First communication passage 7 with communication pipe 12
Is configured.
第２膨張室３及び第３膨張室４はともに、その排気流
動方向の長さL2・L3が長く、その排気流動方向と直交す
る横断面積A2・A3が狭く形成されており、第２膨張室３
及び第３膨張室４で排気騒音中の低周波音が消音され
る。Both the second expansion chamber 3 and the third expansion chamber 4 have a long length L 2 · L 3 in the exhaust flow direction and a narrow cross-sectional area A 2 · A 3 orthogonal to the exhaust flow direction, Second expansion chamber 3
Also, the low frequency sound in the exhaust noise is silenced in the third expansion chamber 4.
図中、14・15は水抜き孔である。 In the figure, 14 and 15 are drain holes.
本実施例では、排気入口管５の直径（30mm）は、排気
入口管５の通路断面積A4が排気出口９の通路断面積A0の
75％となるように、また連通孔13の直径及び個数は、連
通孔13の合計の通路断面積が排気出口９の通路断面積A0
の75％となるように、それぞれ設計されている。In the present embodiment, the diameter (30 mm) of the exhaust inlet pipe 5 is such that the passage sectional area A 4 of the exhaust inlet pipe 5 is the passage sectional area A 0 of the exhaust outlet 9.
75%, and the diameter and number of the communicating holes 13 are such that the total passage sectional area of the communicating holes 13 is the passage sectional area A 0 of the exhaust outlet 9.
Each is designed to be 75% of.
上記75％以上では減音効果が少なく、反対に75％以下
では背圧が高くなる。Above 75%, the sound reduction effect is small, and conversely, below 75%, the back pressure is high.
次に、第１膨張室２の長さL1は195mmに、直径は152mm
に、第２膨張室３及び第３膨張室４の長さL2・L3はそれ
ぞれ250mmに、直径はそれぞれ135mmに設計されている。Next, the length L 1 of the first expansion chamber 2 is 195 mm and the diameter is 152 mm.
In addition, the lengths L 2 and L 3 of the second expansion chamber 3 and the third expansion chamber 4 are each designed to be 250 mm, and the diameter is designed to be 135 mm.
そして、上側連通管11、中間連通管10、下側連通管1
2、第２連通路８及び排気出口管６の直径はそれぞれ30m
mに設計されている。Then, the upper communication pipe 11, the intermediate communication pipe 10, the lower communication pipe 1
2, the diameter of the second communication passage 8 and the exhaust outlet pipe 6 are each 30m
Designed to m.
第５図には、減音（dB）と周波数（Hz）との関係図が
示されており、実線が本実施例を示し、点線が従来例を
示す。FIG. 5 shows a relationship diagram between the sound reduction (dB) and the frequency (Hz), the solid line shows the present embodiment, and the dotted line shows the conventional example.
上記関係図は、第４図に示す計測方法により、計測し
た結果をグラフに表したものであり、第４図では、本実
施例のマフラ１の第１マフラ1aと第２マフラ1bとを別置
きにし、エンジンＥに第１マフラ1a、第２マフラ1bの順
に接続し、これらを発泡スチロール19の下側空間に配置
し、発泡スチロール19の上側空間に排気出口17を開口
し、この排気出口17から0.3m離れた位置に騒音計18を配
置している。The above relational diagram is a graph showing the results of measurement by the measuring method shown in FIG. 4. In FIG. 4, the first muffler 1a and the second muffler 1b of the muffler 1 of this embodiment are separated. In the other side, the first muffler 1a and the second muffler 1b are connected to the engine E in this order, they are arranged in the lower space of the styrofoam 19, and the exhaust outlet 17 is opened in the upper space of the styrofoam 19. From this exhaust outlet 17 A sound level meter 18 is placed at a position 0.3 m away.
計測結果からわかる通り、減音（dBの値）のピーク値
を低周波側にスライドさせて、１〜2KHz、４〜5KHz、７
〜8KHzに減音のピーク値がくるようにできる。従って、
本実施例のマフラ１によると、排気騒音中の高周波音か
ら低周波音までを効果的に減音できることがわかる。As you can see from the measurement results, slide the peak value of the sound reduction (dB value) to the low frequency side, 1-2KHz, 4-5KHz, 7
The peak value of sound reduction can be set to ~ 8KHz. Therefore,
According to the muffler 1 of the present embodiment, it can be understood that the high frequency sound to the low frequency sound in the exhaust noise can be effectively reduced.
なお、本実施例ではマフラ１を第１マフラ1aと第２マ
フラ1bとに別体に形成し、別置きとすることでスペース
の制約をあまり受けないようにしているが、第１マフラ
1aと第２マフラ1bとを一体形成することも考えられる。In the present embodiment, the muffler 1 is formed separately from the first muffler 1a and the second muffler 1b, and the muffler 1 is placed separately so that the space is not restricted so much.
It is also conceivable to integrally form 1a and the second muffler 1b.
第１図乃至第４図は本考案の実施例を示し、第１図はマ
フラの縦断側面図、第２図は第１図のII−II線断面図、
第３図は第１マフラの上面図、第４図はマフラ騒音の計
測方法を示す概略図であり、第５図は本考案の実施例と
従来例とにおける減音（dB）と周波数（Hz）との関係図
であり、第６図は従来例を示す第１図相当図である。 １……マフラ、２……第１膨張室、３……第２膨張室、
４……第３膨張室、５……排気入口管、６……排気出口
管、７……第１連通路、８……第２連通路。1 to 4 show an embodiment of the present invention, FIG. 1 is a longitudinal side view of a muffler, FIG. 2 is a sectional view taken along line II-II of FIG.
FIG. 3 is a top view of the first muffler, FIG. 4 is a schematic diagram showing a method of measuring muffler noise, and FIG. 5 is a sound reduction (dB) and frequency (Hz) in the embodiment of the present invention and the conventional example. ), And FIG. 6 is a view corresponding to FIG. 1 showing a conventional example. 1 ... muffler, 2 ... first expansion chamber, 3 ... second expansion chamber,
4 ... Third expansion chamber, 5 ... Exhaust inlet pipe, 6 ... Exhaust outlet pipe, 7 ... First communication passage, 8 ... Second communication passage.
───────────────────────────────────────────────────── フロントページの続き (72)考案者 小磯 慶高 大阪府堺市石津北町64 久保田鉄工株式会 社堺製造所内 (56)参考文献 実開 昭59−52023（ＪＰ，Ｕ) 実開 昭53−41540（ＪＰ，Ｕ) ─────────────────────────────────────────────────── ─── Continuation of the front page (72) Inventor Keitaka Koiso 64 Ishizukitamachi, Sakai City, Osaka Prefecture Kubota Iron Works Co., Ltd. Sakai Works (56) References: 59-52023 (JP, U) -41540 (JP, U)
Claims (1)
管（５）に少なくとも第１膨張室（２）・第１連通路
（７）・第２膨張室（３）・第２連通路（８）及び第３
膨張室（４）を順に介して排気出口管（６）を連通させ て構成したエンジンのマフラにおいて、 第１膨張室（２）の排気流動方向の長さ（L1）を短かく
形成するのに対し、第２膨張室（３）の排気流動方向の
長さ（L2）及び第３膨張室（４）の排気流動方向の長さ
（L3）を長く形成し、 第１膨張室（２）の排気流動方向と直交する横断面積
（A1）を広く形成するのに対し、第２膨張室（３）の排
気流動方向と直交する横断面積（A2）及び第３膨張室
（４）の排気流動方向と直交する横断面積（A3）を狭く
形成した 事を特徴とするエンジンのマフラ。1. An exhaust inlet pipe (5) of a muffler (1) of an engine (E) having at least a first expansion chamber (2), a first communication passage (7), a second expansion chamber (3) and a second communication chamber. Passage (8) and third
In the muffler of the engine configured by connecting the exhaust outlet pipe (6) through the expansion chamber (4) in order, the length (L 1 ) in the exhaust flow direction of the first expansion chamber (2) is formed to be short. On the other hand, the length of the second expansion chamber (3) in the exhaust flow direction (L 2 ) and the length of the third expansion chamber (4) in the exhaust flow direction (L 3 ) are formed to be long, and the first expansion chamber ( While the cross-sectional area (A 1 ) orthogonal to the exhaust flow direction of 2) is formed wide, the cross-sectional area (A 2 ) orthogonal to the exhaust flow direction of the second expansion chamber (3) and the third expansion chamber (4) are formed. ) The engine muffler is characterized by a narrow cross-sectional area (A 3 ) that is orthogonal to the exhaust flow direction.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1990010092U JPH0810655Y2 (en) | 1990-02-02 | 1990-02-02 | Engine muffler |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1990010092U JPH0810655Y2 (en) | 1990-02-02 | 1990-02-02 | Engine muffler |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH03102020U JPH03102020U (en) | 1991-10-24 |
| JPH0810655Y2 true JPH0810655Y2 (en) | 1996-03-29 |
Family
ID=31513687
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP1990010092U Expired - Lifetime JPH0810655Y2 (en) | 1990-02-02 | 1990-02-02 | Engine muffler |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH0810655Y2 (en) |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6929619B2 (en) | 2002-08-02 | 2005-08-16 | Liebel-Flarshiem Company | Injector |
| JP2011102521A (en) * | 2009-11-10 | 2011-05-26 | Akira Tamai | Crime preventive door with door room |
Family Cites Families (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5553699Y2 (en) * | 1976-09-16 | 1980-12-12 | ||
| JPS5952023U (en) * | 1982-09-29 | 1984-04-05 | マツダ株式会社 | Engine exhaust silencer structure |
-
1990
- 1990-02-02 JP JP1990010092U patent/JPH0810655Y2/en not_active Expired - Lifetime
Also Published As
| Publication number | Publication date |
|---|---|
| JPH03102020U (en) | 1991-10-24 |
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