JPH10141041A - Noise eliminator for internal combustion engine - Google Patents
Noise eliminator for internal combustion engineInfo
- Publication number
- JPH10141041A JPH10141041A JP8302795A JP30279596A JPH10141041A JP H10141041 A JPH10141041 A JP H10141041A JP 8302795 A JP8302795 A JP 8302795A JP 30279596 A JP30279596 A JP 30279596A JP H10141041 A JPH10141041 A JP H10141041A
- Authority
- JP
- Japan
- Prior art keywords
- movable valve
- exhaust gas
- gas pressure
- moving valve
- 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.)
- Granted
Links
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
- F01N1/00—Silencing apparatus characterised by method of silencing
- F01N1/16—Silencing apparatus characterised by method of silencing by using movable parts
- F01N1/166—Silencing apparatus characterised by method of silencing by using movable parts for changing gas flow path through the silencer or for adjusting the dimensions of a chamber or a pipe
Abstract
Description
【０００１】[0001]
【発明の属する技術分野】本発明は、自動車等の内燃機
関に用いられる消音装置に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a muffler used for an internal combustion engine of an automobile or the like.
【０００２】[0002]
【従来の技術】一般に自動車等に使用される内燃機関で
あるガソリンエンジン（以下エンジンという）において
は、アイドル回転の７５０回転／分から２５００〜３０
００回転／分の常用使用回転域においては騒音が少ない
静粛さが求められ、３０００回転／分以上の高回転域に
おいては静粛さよりも高出力が求められている。このエ
ンジンの騒音のほとんどは、エンジンから排出される排
気音であり、この排気音を抑え、しかも高出力を発揮す
るため、消音装置に様々な工夫が加えられていた。2. Description of the Related Art In general, a gasoline engine (hereinafter, referred to as an engine), which is an internal combustion engine used in automobiles and the like, has an idling speed of 750 rpm / min to 2500-30 min.
In a normal use rotation range of 00 revolutions / minute, quietness with little noise is required, and in a high revolution range of 3000 revolutions / minute or more, higher output than quietness is required. Most of the noise of this engine is the exhaust sound exhausted from the engine, and in order to suppress the exhaust noise and exhibit a high output, various ideas have been added to the silencer.
【０００３】この要求を満たす消音装置として、従来
は、図８に示すように、消音器内に排気ガス圧を抑制す
る可動弁を備えている消音装置のものがあった。この消
音装置においては、消音器３０内の連通管３１の排気ガ
スの出口３１ａに、可動弁３２をコイルばね３３で付勢
するように取り付けてある。この、可動弁３２は、常用
使用回転域においては排気ガス圧が弱いので、コイルば
ね３３の付勢力が勝り、可動弁３２を連通管３１側に押
し付けて通路Ｒを閉じている状態となり、消音器３０か
ら外に排出される排気ガスは、排気抵抗の大きい通路Ｑ
を経由して排出されるので、排気音も静かになる。一
方、エンジンが３０００回転／分以上の高回転域になる
と、排気ガス圧が増すので、コイルばね３３の付勢力よ
り排気ガス圧が強くなり、徐々に可動弁３２が開く。こ
れにより排気通路が通路Ｑと通路Ｒに並列化され、排気
ガスの流速の低下に伴い気流音が低減される。また、排
気抵抗も小さくなるためエンジンの出力が最大限に発揮
されるようになる。Conventionally, as a silencer satisfying this requirement, there has been a silencer having a movable valve for suppressing exhaust gas pressure in a silencer as shown in FIG. In this silencer, the movable valve 32 is attached to the exhaust gas outlet 31 a of the communication pipe 31 in the silencer 30 so as to urge the movable valve 32 with a coil spring 33. Since the movable valve 32 has a low exhaust gas pressure in a normal use rotation range, the urging force of the coil spring 33 is superior, and the movable valve 32 is pressed against the communication pipe 31 to close the passage R, so that the sound is muted. Exhaust gas discharged outside from the vessel 30 passes through a passage Q having a large exhaust resistance.
As the air is exhausted through the exhaust port, the exhaust noise is also reduced. On the other hand, when the engine enters a high rotation region of 3000 rpm or more, the exhaust gas pressure increases, so the exhaust gas pressure becomes stronger due to the urging force of the coil spring 33, and the movable valve 32 gradually opens. As a result, the exhaust passage is arranged in parallel with the passage Q and the passage R, and the airflow noise is reduced as the flow velocity of the exhaust gas decreases. In addition, since the exhaust resistance is reduced, the output of the engine is maximized.
【０００４】このエンジンの回転数と排気音との関係を
示したものが図９である。図９において、横軸はエンジ
ンの回転数（単位：ｒｐｍ）示し、縦軸は排気音の大き
さ（単位：ｄＢ）を示している。また、直線ｑは排気ガ
スが前記通路Ｑを通過した場合の排気音の特性を示し、
直線ｒは排気ガスが前記通路Ｒと前記通路Ｑを通過した
場合の排気音の特性を示したものである。この２つの直
線ｑと直線ｒは、エンジンの回転数が常用使用回転域か
ら高回転域へ移り変わる点Ｐで交差している。つまり直
線ｑは、エンジンの回転数が常用使用回転域において
は、直線ｒより排気音が小さく静粛性を示すが、エンジ
ンの回転数が高回転域では、直線ｒより排気音が大きく
なり、耳障りになってしまうものである。従って、消音
装置においては、エンジンの回転数が常用使用回転域で
は直線ｑの特性となり、エンジンの回転数が高回転域で
は直線ｒの特性となるように、可動弁を備えて排気ガス
をコントロールする必要があった。FIG. 9 shows the relationship between the engine speed and the exhaust noise. In FIG. 9, the horizontal axis indicates the engine speed (unit: rpm), and the vertical axis indicates the loudness of exhaust sound (unit: dB). Further, a straight line q indicates the characteristic of the exhaust noise when the exhaust gas passes through the passage Q,
The straight line r shows the characteristics of the exhaust noise when the exhaust gas passes through the passage R and the passage Q. The two straight lines q and r intersect at a point P at which the number of revolutions of the engine changes from the normal use rotation range to the high rotation range. In other words, the straight line q has a smaller exhaust sound than the straight line r in the normal rotational speed region of the engine and shows quietness, but has a higher exhaust sound than the straight line r in the high rotational speed region of the engine. It becomes something. Accordingly, the muffler is equipped with a movable valve to control the exhaust gas so that the engine speed has a characteristic of a straight line q in a normal operating speed range, and has a characteristic of a straight line r in a high engine speed range. I needed to.
【０００５】[0005]
【発明が解決しようとする課題】しかしながら、上記し
た従来の消音装置においては、可動弁３２が開く時は、
コイルばね３３に反発して開いて行くが、高回転域にお
ける可動弁３２の開度が十分でなく、可動弁３２が開け
ば開くほど、図７の点線で示すように、バネの特性上、
ばね３３の反発力が強まるので、高回転域になればなる
ほど、可動弁３２にかかる荷重が大きくなって、可動弁
３２を開くのが困難となり、特に可動弁３２を完全に開
いた状態（図８において水平方向）にすることは、非常
に困難であった。そのため、消音装置の排気抵抗が大き
くなり、高回転域においては、エンジンの出力を最大限
に発揮させることができないという問題があった。However, in the above-described conventional silencer, when the movable valve 32 is opened,
The coil spring 33 is repelled and opens. However, the opening degree of the movable valve 32 in the high rotation range is not sufficient, and the more the movable valve 32 is opened, the more the movable valve 32 opens, as shown by the dotted line in FIG.
Since the repulsive force of the spring 33 increases, the load applied to the movable valve 32 increases as the rotational speed increases, and it becomes difficult to open the movable valve 32. In particular, the state where the movable valve 32 is completely opened (see FIG. 8 in the horizontal direction) was very difficult. Therefore, there is a problem that the exhaust resistance of the silencer becomes large, and the output of the engine cannot be maximized in a high rotation range.
【０００６】本発明は、上記した従来の問題点に鑑みな
されたもので、エンジンの常用使用回転域においては騒
音が小さく静粛になり、エンジンの高回転域においては
可動弁を完全に開いて排気抵抗が小さく高出力を発揮す
る、内燃機関用消音装置を提供するものである。SUMMARY OF THE INVENTION The present invention has been made in view of the above-mentioned conventional problems, and has low noise and quietness in a normal operating speed range of an engine. An object of the present invention is to provide a silencer for an internal combustion engine that has a small resistance and exhibits a high output.
【０００７】[0007]
【課題を解決するための手段】上記課題を解決するた
め、本発明は、消音器の連通管の出口に取付けられ、排
気ガス圧の増大に伴って開度を増大することにより排気
ガス圧の制御をする制御装置を備えている内燃機関用消
音装置において、前記制御装置は第１の可動弁と第２の
可動弁と取付ブラケットとを備え、前記第２の可動弁は
前記第１の可動弁により押し開かれることを特徴とする
ものである。また、前記第１の可動弁は、一端を取付ブ
ラケットに回動自在に取り付けられ、他端にはコロが取
付けられ、前記コロは第２の可動弁の内面に当接してい
ることを特徴とするものである。また、前記第２の可動
弁は、凹面を持つ板で形成され、一端を前記取付ブラケ
ットに回動自在に取付けられていることを特徴とするも
のである。また、前記第２の可動弁と前記取付ブラケッ
トには複数の孔が設けられていることを特徴とするもの
である。SUMMARY OF THE INVENTION In order to solve the above-mentioned problems, the present invention is provided at an outlet of a communication pipe of a silencer, and the exhaust gas pressure is increased by increasing an opening with an increase in the exhaust gas pressure. In a silencer for an internal combustion engine including a control device for performing control, the control device includes a first movable valve, a second movable valve, and a mounting bracket, and the second movable valve includes the first movable valve. It is characterized by being pushed open by a valve. Further, the first movable valve has one end rotatably attached to a mounting bracket, the other end attached with a roller, and the roller is in contact with an inner surface of the second movable valve. Is what you do. Further, the second movable valve is formed of a plate having a concave surface, and has one end rotatably attached to the mounting bracket. Further, the second movable valve and the mounting bracket are provided with a plurality of holes.
【０００８】[0008]
【発明の実施の形態】以下、本発明の実施の形態を図に
基づいて説明する。図１は、本発明の内燃機関用消音装
置を示す断面図、図２は、図１の内燃機関用消音装置の
制御装置を示す斜視図、図３は、図２の制御装置の閉じ
た状態を示す一部破断の側面図、図４は、図２の制御装
置の一部破断の正面図、図５は、図２の制御装置の第２
の可動弁を示す正面図、図６は、図２の制御装置の開い
た状態を示す断面図、図７は、図２の制御装置の可動弁
の開き角度と可動弁にかかる排気ガス圧の関係を示す相
関図である。DESCRIPTION OF THE PREFERRED EMBODIMENTS Embodiments of the present invention will be described below with reference to the drawings. 1 is a cross-sectional view showing a silencer for an internal combustion engine of the present invention, FIG. 2 is a perspective view showing a control device of the silencer for an internal combustion engine of FIG. 1, and FIG. 3 is a closed state of the control device of FIG. 4 is a partially cutaway front view of the control device of FIG. 2, and FIG. 5 is a second view of the control device of FIG.
FIG. 6 is a cross-sectional view showing the opened state of the control device of FIG. 2, and FIG. 7 is a view showing the opening angle of the movable valve and the exhaust gas pressure applied to the movable valve of the control device of FIG. FIG. 7 is a correlation diagram showing the relationship.
【０００９】まず、図１において、本発明の内燃機関用
消音装置は、筒状の消音器１の一方の端面に接続されて
いる入口管２、他方の端面に接続されている２つの出口
管３，４、および隔壁５，６により区画されている膨張
室７，８，９を有している。また、入口管２が開口する
膨張室７と出口管３が開口する膨張室８を連通する連通
管１０、そして出口管４が開口する膨張室９と膨張室７
を連通する連通管１１を有している。この連通管１０は
エンジンの低回転域側の排気ガスの通路Ｓとされ、他方
の連通管１１はエンジンの高回転域側の排気ガスの通路
Ｔとされて、このときには連通管１０と並列に排気ガス
が流れるようになっている。この連通管１１の出口１１
ａには制御装置１２が取り付けられている。First, referring to FIG. 1, a silencer for an internal combustion engine according to the present invention includes an inlet pipe 2 connected to one end face of a cylindrical silencer 1 and two outlet pipes connected to the other end face. 3 and 4, and expansion chambers 7, 8, 9 defined by partition walls 5, 6. A communication pipe 10 that communicates between the expansion chamber 7 where the inlet pipe 2 opens and the expansion chamber 8 where the outlet pipe 3 opens, and an expansion chamber 9 and an expansion chamber 7 where the outlet pipe 4 opens.
And a communication pipe 11 for communicating the The communication pipe 10 serves as a passage S for exhaust gas on the low rotation speed side of the engine, and the other communication pipe 11 serves as a passage T for exhaust gas on the high rotation speed side of the engine. Exhaust gas flows. Outlet 11 of this communication pipe 11
The control device 12 is attached to a.
【００１０】連通管１１に取り付けられている制御装置
１２は、図２に示すように、連通管１１を開閉する第１
の可動弁１３と、この第１の可動弁１３が内面に当接し
ている第２の可動弁１４と、この第１の可動弁１３と第
２の可動弁１４を前記連通管１１に取り付けるための取
付ブラケット２０から構成されている。第１の可動弁１
３は、図３、図４に示すように、中央部が皿状に形成さ
れた底部１３ａの径が、ほぼ連通管１１の内径と同一に
形成され、第１の可動弁１３を閉じた状態では、連通管
１１を通る排気ガスをシャットするように構成されてい
る。As shown in FIG. 2, a control device 12 attached to the communication pipe 11 is used to open and close the first communication pipe 11.
Movable valve 13, a second movable valve 14 in which the first movable valve 13 is in contact with an inner surface, and a first movable valve 13 and a second movable valve 14 for attaching to the communication pipe 11. Of the mounting bracket 20. First movable valve 1
3 shows a state in which the diameter of the bottom portion 13a whose central portion is formed in a dish shape is substantially the same as the inner diameter of the communication pipe 11, and the first movable valve 13 is closed, as shown in FIGS. Is configured to shut off the exhaust gas passing through the communication pipe 11.
【００１１】また、第１の可動弁１３の下側の端部１３
ｂには、ピン１５が貫通され、取付ブラケット２０の両
側のガイド壁２１，２２に回動自在に軸支されている。
また、ピン１５には、バネ１６が巻回され、このバネ１
６の一端１６ａが延長されて第１の可動弁１３を付勢し
ており、バネ１６の他端は取付ブラケット２０に形成さ
れた切欠２３に嵌入されてバネ１６を固定する。このバ
ネ１６の強さは、エンジンが高回転になった時に第１の
可動弁１３が完全に開くように従来の半分程度の荷重に
バネを選定してある。さらに、第１の可動弁１３の上側
の端部１３ｃにはコロ１７が取り付けられ、このコロ１
７が第２の可動弁１４の内面１４ｂに当接している。The lower end 13 of the first movable valve 13
The pin 15 is penetrated by b, and is rotatably supported by the guide walls 21 and 22 on both sides of the mounting bracket 20.
A spring 16 is wound around the pin 15, and the spring 1
6, one end 16a is extended to urge the first movable valve 13, and the other end of the spring 16 is fitted into a notch 23 formed in the mounting bracket 20 to fix the spring 16. The strength of the spring 16 is selected so that the first movable valve 13 is completely opened when the engine rotates at a high speed. Further, a roller 17 is attached to the upper end 13 c of the first movable valve 13.
7 is in contact with the inner surface 14b of the second movable valve 14.
【００１２】第２の可動弁１４は、図２、図３、および
図５に示すように、全体が凹面状の板に形成され、全面
に排気ガスを整流するため複数の小孔が開けられてい
る。この第２の可動弁１４の上部１４ａは、ピン１８で
取付ブラケット２０の両側の壁２１，２２に回動自在に
取り付けられている。また、このピン１８にはバネ１９
が巻回されており、このバネ１９の一端１９ａが延長さ
れて第２の可動弁１４を付勢しており、バネ１９の他端
１９ｂが延長されて、取付ブラケット２０に形成された
切欠２４に嵌入されバネ１９を固定している。このバネ
１９の強さはエンジンが常用回転域においては、第１の
可動弁１３と第２の可動弁１４が閉じるように、前記バ
ネ１６より強いバネを選定している。さらに、第２の可
動弁１４の内面１４ｂには、前記第１の可動弁１３のコ
ロ１７が当接しており、図６に示すように、このコロ１
７が内面１４ｂを滑動することにより第２の可動弁１４
は第１の可動弁１３により押し開かれる。As shown in FIGS. 2, 3, and 5, the second movable valve 14 is formed entirely in a concave plate, and has a plurality of small holes formed on the entire surface thereof to rectify exhaust gas. ing. The upper portion 14a of the second movable valve 14 is rotatably attached to the walls 21 and 22 on both sides of the mounting bracket 20 by pins 18. The pin 18 has a spring 19
Is wound, one end 19a of the spring 19 is extended to urge the second movable valve 14, and the other end 19b of the spring 19 is extended, so that the notch 24 formed in the mounting bracket 20 is formed. And the spring 19 is fixed. The strength of the spring 19 is selected to be stronger than the spring 16 so that the first movable valve 13 and the second movable valve 14 close when the engine is in a normal rotation range. Further, a roller 17 of the first movable valve 13 is in contact with an inner surface 14b of the second movable valve 14, and as shown in FIG.
7 slides on the inner surface 14b so that the second movable valve 14
Is pushed open by the first movable valve 13.
【００１３】第１の可動弁１３と第２の可動弁１４を連
通管１１に取り付けている取付ブラケット２０は、図
２、図３に示すように、第１の可動弁１３と第２の可動
弁１４の動作をガイドするガイド壁２１，２２と、連通
管１１との取付け部２５が一体に形成されている。ガイ
ド壁２１，２２は、扇形板状に形成され、全面に排気ガ
スを整流するための複数の小孔が開けられている。この
ガイド壁２１，２２の下部にはピン１５を挿入するため
の孔２１ａ，２２ａが形成され、第１の可動弁１３を軸
支するピン１５が挿入されている。また、ガイド壁２
１，２２の上部にはピン１８を挿入するための孔２１
ｂ，２２ｂが形成され、第２の可動弁１４を軸支するピ
ン１８が挿入されている。As shown in FIGS. 2 and 3, a mounting bracket 20 for mounting the first movable valve 13 and the second movable valve 14 to the communication pipe 11 is provided with a first movable valve 13 and a second movable valve. Guide walls 21 and 22 for guiding the operation of the valve 14 and a mounting portion 25 for connecting to the communication pipe 11 are formed integrally. The guide walls 21 and 22 are formed in a fan-shaped plate shape, and are provided with a plurality of small holes on the entire surface for rectifying exhaust gas. Holes 21a and 22a for inserting the pins 15 are formed in the lower portions of the guide walls 21 and 22, and the pins 15 that support the first movable valve 13 are inserted. Guide wall 2
A hole 21 for inserting the pin 18 is provided at the upper part of
b and 22b are formed, and a pin 18 that supports the second movable valve 14 is inserted.
【００１４】取付ブラケット２０の取付け部２５は、連
通管１１に取り付けるために、円筒形に形成され、連通
管１１に溶接等で取り付けられる。この取付け部２５
は、前記ガイド壁２１，２２の方向にじょうご形に開い
た傾斜部２５ａが形成されており、この傾斜部２５ａに
前記第１の可動弁１３の底部１３ａが収まるようになっ
ている。これにより、第１の可動弁１３を閉じたときに
連通管からの排気ガスの漏れを防いでいる。The mounting portion 25 of the mounting bracket 20 is formed in a cylindrical shape so as to be mounted on the communication pipe 11, and is mounted on the communication pipe 11 by welding or the like. This mounting part 25
Is formed with a funnel-shaped inclined portion 25a in the direction of the guide walls 21 and 22, and the bottom portion 13a of the first movable valve 13 fits in the inclined portion 25a. This prevents the exhaust gas from leaking from the communication pipe when the first movable valve 13 is closed.
【００１５】このように構成された制御装置１２は、エ
ンジンが低速回転の場合は、バネ１６の付勢力と、バネ
１９の付勢力により第２の可動弁１４が第１の可動弁１
３を取付け部２５に押しつけている荷重が排気ガス圧よ
り強いので、図３に示すように、第１の可動弁１３は閉
じた状態となっている。一方、エンジンが高回転域にな
ると、排気ガス圧が強くなるので、第１の可動弁１３の
バネ１６の付勢力と、第２の可動弁１４を介して第１の
可動弁１３を押さえつけているバネ１９の付勢力より大
きくなり、第１の可動弁１３が開く。そして、排気ガス
圧が最大になると、図６に示すように、第１の可動弁１
３が水平状態になるまで開き、エンジンの出力が最大限
に発揮されるようになる。また、このときの排気音は、
排気ガスが第２の可動弁１４の整流用の小孔と取付ブラ
ケットの整流用の小孔を通過するので、排気ガスが整流
されて耳障りな騒音の成分が低減することができる。When the engine is rotating at a low speed, the control device 12 having the above-described configuration allows the second movable valve 14 to move the first movable valve 1 by the urging force of the spring 16 and the urging force of the spring 19.
Since the load pressing the 3 against the mounting portion 25 is stronger than the exhaust gas pressure, the first movable valve 13 is in a closed state as shown in FIG. On the other hand, when the engine is in a high rotation range, the exhaust gas pressure increases, so that the urging force of the spring 16 of the first movable valve 13 and the first movable valve 13 are pressed down via the second movable valve 14. The first movable valve 13 is opened. Then, when the exhaust gas pressure becomes maximum, as shown in FIG.
3 is opened until it is horizontal, so that the output of the engine is maximized. Also, the exhaust sound at this time is
Since the exhaust gas passes through the rectifying small hole of the second movable valve 14 and the rectifying small hole of the mounting bracket, the exhaust gas is rectified, and annoying noise components can be reduced.
【００１６】また、第１の可動弁１３と第２の可動弁１
４が排気ガス圧により開く場合に、第１の可動弁１３の
開き角度と、２つの可動弁にかかる排気ガス圧の関係を
示すと図７のようになる。図７において、グラフの横軸
は可動弁の開き角度（°）とエンジンの回転数（ｒｐ
ｍ）を示し、縦軸は可動弁にかかる排気ガス圧の荷重
（Ｋｇｆ）を示してい。また、実線は本発明の可動弁の
特性を示し、点線は従来の可動弁の特性を示している。
図７によれば、第１の可動弁１３の開き始めは、図３に
示すように、第１の可動弁１３はコロ１７を介して第２
の可動弁１４の付け根の部分により押さえつけられてい
るため、従来の可動弁よりは開きにくくなっている。と
ころが、第１の可動弁１３は、一旦開き始めると、第１
の可動弁１３のコロ１７が第２の可動弁１４の付け根の
部分より遠ざかるため、図６に示すように、第２の可動
弁１４が開けば開く程、てこの作用で、第２の可動弁１
４を開くための荷重はそれほど必要とせず、荷重の大部
分は第１の可動弁１３のバネ１６に抗して開くためにだ
け必要となるもので、しかもバネ１６は柔らかいバネを
使用しているため、従来に比べはるかに小さい荷重で全
開するようになっている。従って、上述した消音装置
は、排気ガス圧が低い常用回転域の２５００回転／分以
下においては、可動弁の開かずに閉じたままなので排気
音が静粛となり、排気ガス圧が高い高回転域では可動弁
が完全に開いてエンジンの出力が最大限に発揮されるよ
うになっている。Further, the first movable valve 13 and the second movable valve 1
FIG. 7 shows the relationship between the opening angle of the first movable valve 13 and the exhaust gas pressure applied to the two movable valves when the valve 4 is opened by the exhaust gas pressure. In FIG. 7, the horizontal axis of the graph represents the opening angle (°) of the movable valve and the engine speed (rpm).
m), and the vertical axis indicates the load (Kgf) of the exhaust gas pressure applied to the movable valve. The solid line shows the characteristics of the movable valve of the present invention, and the dotted line shows the characteristics of the conventional movable valve.
According to FIG. 7, when the first movable valve 13 starts to open, as shown in FIG.
Of the movable valve 14 is harder to open than the conventional movable valve. However, once the first movable valve 13 starts to open,
Since the roller 17 of the movable valve 13 of FIG. 1 is farther from the base of the second movable valve 14, as shown in FIG. 6, the more the second movable valve 14 is opened, the more leverage the second movable valve Valve 1
4 does not require much load, most of the load is only required to open against the spring 16 of the first movable valve 13, and the spring 16 uses a soft spring. As a result, it opens fully with a much smaller load than before. Therefore, in the above-described muffler, the exhaust sound is quiet because the movable valve remains closed without being opened in the normal rotation range of 2500 rpm or lower where the exhaust gas pressure is low, and in the high rotation range where the exhaust gas pressure is high. The movable valve is fully open to maximize the engine output.
【００１７】[0017]
【発明の効果】以上に述べたように本発明は、消音器の
連通管に取り付けられ、排気ガス圧の増大に伴って開度
を増大することにより排気ガス圧の抑制をする可動弁を
備えている内燃機関用消音装置において、前記制御弁は
第１の可動弁と第２の可動弁を備え、前記第２の可動弁
は前記第１の可動弁により押し開かれることにより、、
エンジンの常用使用回転域においては騒音が小さく静粛
になり、エンジンの高回転域においては可動弁を完全に
開いて排気抵抗が小さくエンジンの出力が最大限に発揮
することができるという効果を奏するものである。ま
た、前記第２の可動弁と前記取付ブラケットには複数の
孔が設けられていることにより、エンジンの高回転域に
おいて排気ガスが整流され、排気音の騒音を低減するこ
とができる。As described above, the present invention is provided with a movable valve attached to a communication pipe of a muffler and suppressing an exhaust gas pressure by increasing an opening degree with an increase in the exhaust gas pressure. In the silencer for an internal combustion engine, the control valve includes a first movable valve and a second movable valve, and the second movable valve is pushed open by the first movable valve,
In the normal operating speed range of the engine, the noise is small and quiet, and in the high engine speed range, the movable valve is completely opened, the exhaust resistance is small and the engine output can be maximized. It is. Further, since the second movable valve and the mounting bracket are provided with a plurality of holes, exhaust gas is rectified in a high engine speed range, so that noise of exhaust noise can be reduced.
【図１】本発明の内燃機関用消音装置を示す断面図であ
る。FIG. 1 is a sectional view showing a silencer for an internal combustion engine according to the present invention.
【図２】図１の内燃機関用消音装置の制御装置を示す斜
視図である。FIG. 2 is a perspective view showing a control device of the silencing device for an internal combustion engine of FIG.
【図３】図２の制御装置の可動弁の閉じた状態を示す側
面図である。FIG. 3 is a side view showing a closed state of a movable valve of the control device of FIG. 2;
【図４】図２の制御装置の可動弁の閉じた状態を示す一
部破断の正面図である。4 is a partially broken front view showing a closed state of a movable valve of the control device of FIG. 2;
【図５】図２の制御装置の第２の可動弁を示す正面図で
ある。FIG. 5 is a front view showing a second movable valve of the control device of FIG. 2;
【図６】図２の制御装置の開いた状態を示す断面図であ
る。FIG. 6 is a sectional view showing an open state of the control device of FIG. 2;
【図７】図２の制御装置の可動弁の開き角度と可動弁に
かかる排気ガス圧の関係を示す相関図である。7 is a correlation diagram showing a relationship between an opening angle of a movable valve of the control device of FIG. 2 and an exhaust gas pressure applied to the movable valve.
【図８】従来の内燃機関用消音装置を示す断面図であ
る。FIG. 8 is a sectional view showing a conventional silencer for an internal combustion engine.
【図９】従来の内燃機関用消音装置のエンジンの回転数
と排気音の関係を示す相関図である。FIG. 9 is a correlation diagram showing the relationship between the engine speed and exhaust sound of the conventional silencer for an internal combustion engine.
１ 消音器 ２ 入口管 ３ 出口管 ４ 出口管 ５ 隔壁 ６ 隔壁 ７ 膨張室 ８ 膨張室 ９ 膨張室 １０ 連通管 １１ 連通管 １２ 制御装置 １３ 第１の可動弁 １４ 第２の可動弁 １５ ピン １６ バネ １７ コロ １８ ピン １９ バネ ２０ 取付ブラケット ２１ ガイド壁 ２２ ガイド壁 ２３ 切欠 ２４ 切欠 ２５ 取付け部 REFERENCE SIGNS LIST 1 muffler 2 inlet pipe 3 outlet pipe 4 outlet pipe 5 partition 6 partition 7 expansion chamber 8 expansion chamber 9 expansion chamber 10 communication pipe 11 communication pipe 12 controller 13 first movable valve 14 second movable valve 15 pin 16 spring 17 Roller 18 Pin 19 Spring 20 Mounting bracket 21 Guide wall 22 Guide wall 23 Notch 24 Notch 25 Mounting part
───────────────────────────────────────────────────── フロントページの続き (72)発明者 富永 和也 広島県広島市安佐北区安佐町久地2029−５ 株式会社ユーメックス内 ──────────────────────────────────────────────────続 き Continued on the front page (72) Inventor Kazuya Tominaga 2029-5 Kuji, Asa-cho, Asa-Kita-ku, Hiroshima-shi, Hiroshima
Claims (4)
気ガス圧の増大に伴って開度を増大することにより排気
ガス圧の制御をする制御装置を備えている内燃機関用消
音装置において、 前記制御装置は第１の可動弁と第２の可動弁と取付ブラ
ケットとを備え、前記第２の可動弁は前記第１の可動弁
により押し開かれることを特徴とする内燃機関用消音装
置。1. A silencer for an internal combustion engine, comprising: a control device attached to an outlet of a communication pipe of a muffler and controlling an exhaust gas pressure by increasing an opening degree with an increase in the exhaust gas pressure. The control device includes a first movable valve, a second movable valve, and a mounting bracket, and the second movable valve is pushed and opened by the first movable valve. .
ットに回動自在に取り付けられ、他端にはコロが取付け
られ、前記コロは第２の可動弁の内面に当接しているこ
とを特徴とする請求項１記載の内燃機関用消音装置。2. The first movable valve has one end rotatably mounted on a mounting bracket and the other end mounted with a roller, and the roller is in contact with an inner surface of the second movable valve. The muffler for an internal combustion engine according to claim 1, wherein:
成され、一端を前記取付ブラケットに回動自在に取付け
られていることを特徴とする請求項１記載の内燃機関用
消音装置。3. The muffler for an internal combustion engine according to claim 1, wherein the second movable valve is formed of a plate having a concave surface, and one end of the second movable valve is rotatably mounted on the mounting bracket. .
には複数の孔が設けられていることを特徴とする請求項
１記載の内燃機関用消音装置。4. The muffler for an internal combustion engine according to claim 1, wherein a plurality of holes are provided in the second movable valve and the mounting bracket.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP30279596A JP3739871B2 (en) | 1996-11-14 | 1996-11-14 | Silencer for internal combustion engine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP30279596A JP3739871B2 (en) | 1996-11-14 | 1996-11-14 | Silencer for internal combustion engine |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH10141041A true JPH10141041A (en) | 1998-05-26 |
| JP3739871B2 JP3739871B2 (en) | 2006-01-25 |
Family
ID=17913214
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP30279596A Expired - Fee Related JP3739871B2 (en) | 1996-11-14 | 1996-11-14 | Silencer for internal combustion engine |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP3739871B2 (en) |
Cited By (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US7066296B2 (en) | 2002-10-07 | 2006-06-27 | Honda Giken Kogyo Kabushiki Kaisha | Valve device for silencer |
| US7240768B2 (en) | 2002-10-24 | 2007-07-10 | Barnes Group Inc. | Flapper finger valve |
| WO2009111096A1 (en) * | 2008-03-03 | 2009-09-11 | Tenneco Automotive Operating Company Inc. | Snap-action valve for exhaust system |
| US8056673B2 (en) * | 2009-07-14 | 2011-11-15 | Compx International Inc. | Sound dampening and wear protecting flapper configuration for marine exhaust system |
| US8191572B2 (en) | 2009-04-16 | 2012-06-05 | Tenneco Automotive Operating Company Inc. | Snap action valve with bumper pad |
| US8215103B2 (en) | 2007-03-16 | 2012-07-10 | Tenneco Automotive Operating Company Inc. | Snap-action valve for exhaust system |
| JP2012241543A (en) * | 2011-05-16 | 2012-12-10 | Honda Motor Co Ltd | Pressure control valve |
| US8353153B2 (en) | 2010-02-25 | 2013-01-15 | Tenneco Automotive Operating Company Inc. | Snapper valve for hot end systems with burners |
| US8381401B2 (en) | 2009-04-16 | 2013-02-26 | Tenneco Automotive Operating Company Inc. | Method of installing rotatable flapper valve to an interior of a conduit |
| US8468813B2 (en) | 2007-03-16 | 2013-06-25 | Tenneco Automotive Operating Company Inc. | Snap-action valve for exhaust system |
| US8657065B1 (en) | 2012-12-14 | 2014-02-25 | Tenneco Automotive Operating Company Inc. | Exhaust valve with resilient spring pad |
| US11421690B2 (en) * | 2017-08-18 | 2022-08-23 | Gree Electric Appliances (Wuhan) Co., Ltd | Silencer and compressor |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR102228233B1 (en) * | 2015-03-04 | 2021-03-16 | 현대자동차주식회사 | Suppression apparatus of flow noise for exhaust gas |
-
1996
- 1996-11-14 JP JP30279596A patent/JP3739871B2/en not_active Expired - Fee Related
Cited By (13)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US7066296B2 (en) | 2002-10-07 | 2006-06-27 | Honda Giken Kogyo Kabushiki Kaisha | Valve device for silencer |
| US7240768B2 (en) | 2002-10-24 | 2007-07-10 | Barnes Group Inc. | Flapper finger valve |
| US8215103B2 (en) | 2007-03-16 | 2012-07-10 | Tenneco Automotive Operating Company Inc. | Snap-action valve for exhaust system |
| US7775322B2 (en) | 2007-03-16 | 2010-08-17 | Tenneco Automotive Operating Company Inc. | Snap-action valve for exhaust system |
| US8468813B2 (en) | 2007-03-16 | 2013-06-25 | Tenneco Automotive Operating Company Inc. | Snap-action valve for exhaust system |
| WO2009111096A1 (en) * | 2008-03-03 | 2009-09-11 | Tenneco Automotive Operating Company Inc. | Snap-action valve for exhaust system |
| US8191572B2 (en) | 2009-04-16 | 2012-06-05 | Tenneco Automotive Operating Company Inc. | Snap action valve with bumper pad |
| US8381401B2 (en) | 2009-04-16 | 2013-02-26 | Tenneco Automotive Operating Company Inc. | Method of installing rotatable flapper valve to an interior of a conduit |
| US8056673B2 (en) * | 2009-07-14 | 2011-11-15 | Compx International Inc. | Sound dampening and wear protecting flapper configuration for marine exhaust system |
| US8353153B2 (en) | 2010-02-25 | 2013-01-15 | Tenneco Automotive Operating Company Inc. | Snapper valve for hot end systems with burners |
| JP2012241543A (en) * | 2011-05-16 | 2012-12-10 | Honda Motor Co Ltd | Pressure control valve |
| US8657065B1 (en) | 2012-12-14 | 2014-02-25 | Tenneco Automotive Operating Company Inc. | Exhaust valve with resilient spring pad |
| US11421690B2 (en) * | 2017-08-18 | 2022-08-23 | Gree Electric Appliances (Wuhan) Co., Ltd | Silencer and compressor |
Also Published As
| Publication number | Publication date |
|---|---|
| JP3739871B2 (en) | 2006-01-25 |
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