JPH0688515A - Muffler - Google Patents
MufflerInfo
- Publication number
- JPH0688515A JPH0688515A JP23817592A JP23817592A JPH0688515A JP H0688515 A JPH0688515 A JP H0688515A JP 23817592 A JP23817592 A JP 23817592A JP 23817592 A JP23817592 A JP 23817592A JP H0688515 A JPH0688515 A JP H0688515A
- Authority
- JP
- Japan
- Prior art keywords
- valve
- static pressure
- silencer
- pressure
- force
- 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
Landscapes
- Exhaust Silencers (AREA)
- Control Of Throttle Valves Provided In The Intake System Or In The Exhaust System (AREA)
Abstract
Description
【0001】[0001]
【産業上の利用分野】本発明は脈動圧を呈する流体の排
気音を低減する消音器に関する。本発明は、例えば、内
燃機関からの排気ガスを排出する排気系に適用できる。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a muffler for reducing exhaust noise of a fluid exhibiting pulsating pressure. The present invention can be applied to, for example, an exhaust system that exhausts exhaust gas from an internal combustion engine.
【0002】[0002]
【従来技術】従来より、消音器、例えば内燃機関の排気
系に用いられる消音器においては、排気ガスが流れる排
気通路内に揺動可能に設けられた揺動弁と、揺動弁を付
勢するバネとをもつものとして、以下述べる様なものが
知られている。即ち、図7に示す様に、排気通路100
に揺動弁102を軸104により揺動可能に枢支すると
共に、バネ106で揺動弁102を閉弁方向つまり矢印
A1方向に付勢した消音器が知られている(特開昭58
−217714号公報)。このものでは、排気ガスの圧
力の増加につれて揺動弁102の開弁度が増すものであ
る。このものでは、内燃機関の軽負荷運転域、つまり排
気ガスの圧力が低い場合には、排気通路100の通路面
積が揺動弁102で絞られ、排気音の消音効果が得られ
る。2. Description of the Related Art Conventionally, in a muffler, for example, a muffler used for an exhaust system of an internal combustion engine, a swing valve provided in an exhaust passage through which exhaust gas flows and a swing valve are energized. The following is known as a spring having a spring. That is, as shown in FIG.
In addition, there is known a silencer in which a swing valve 102 is pivotally supported by a shaft 104 so as to swing, and a spring 106 biases the swing valve 102 in a valve closing direction, that is, an arrow A1 direction (JP-A-58).
No. 217714). In this case, the degree of opening of the rocking valve 102 increases as the pressure of the exhaust gas increases. In this case, in the light load operation range of the internal combustion engine, that is, when the pressure of the exhaust gas is low, the passage area of the exhaust passage 100 is throttled by the oscillating valve 102, and the effect of silencing exhaust noise is obtained.
【0003】また図8に示す様に、排気通路200の側
方に対面する開口202、204を介して連通するタン
ク室206を設けると共に、タンク室206に軸208
により揺動弁210を揺動可能に枢支し、開口202を
開く様にバネ212で揺動弁210を付勢した消音器が
知られている(実開平3−114512号公報)。この
ものでは、排気通路200を流れる排気ガスの一部を開
口202からタンク室206に一時的に溜め、その後、
揺動弁210が矢印A3方向に揺動して開口204を開
くので、タンク室206内の排気ガスを開口204から
排出する。このものでは、排気ガスを分割して排出する
ので、消音効果が期待される。Further, as shown in FIG. 8, a tank chamber 206 communicating with openings 202 and 204 facing the side of the exhaust passage 200 is provided, and the tank chamber 206 is provided with a shaft 208.
There is known a silencer in which the rocking valve 210 is pivotally supported by the rocking mechanism and the rocking valve 210 is biased by a spring 212 so as to open the opening 202 (Japanese Utility Model Laid-Open No. 3-114512). In this structure, a part of the exhaust gas flowing through the exhaust passage 200 is temporarily stored in the tank chamber 206 through the opening 202, and then,
Since the swing valve 210 swings in the direction of arrow A3 to open the opening 204, the exhaust gas in the tank chamber 206 is discharged from the opening 204. In this case, the exhaust gas is divided and discharged, so that a sound deadening effect is expected.
【0004】また図9に示す様に、曲げ部300をもつ
薄板状の弁302を排気通路304の内壁面にほぼ平行
に沿わせた消音器が知られている(実開平3−8992
2号公報)。曲げ部300は排気通路304の出口側に
位置している。このものでは、排気バリ音の様な高周波
成分をもつ騒音が、負方向つまり矢印A5方向に流れる
脈動流に起因していることに着目し、弁302の曲げ部
300により、負方向の脈動流を阻止するものである。Further, as shown in FIG. 9, there is known a silencer in which a thin plate-shaped valve 302 having a bent portion 300 is arranged substantially parallel to an inner wall surface of an exhaust passage 304 (actually open 3-8992).
No. 2). The bent portion 300 is located on the outlet side of the exhaust passage 304. In this device, attention is paid to the fact that noise having a high-frequency component such as exhaust burr is caused by the pulsating flow that flows in the negative direction, that is, the arrow A5 direction, and the bending portion 300 of the valve 302 causes the pulsating flow in the negative direction. Is to prevent.
【0005】また図10に示す様に、排気通路400に
連設された副室402の壁に、外気に連通する通孔40
3を設け、揺動弁404を複数個のバネ406で支持
し、揺動弁404の第1弁408を排気通路400に配
置し、第2弁410を副室402に配置した消音器が知
られている(特表平2−501585号公報)。このも
のでは、揺動弁404の第1弁408及び第2弁410
が互いに逆方向に揺動する。これにより、排気通路40
0を流れる脈動流に対して逆位相の流れを副室402で
生成し、排気通路400の脈動流と副室402の逆位相
の流れとを互いに合体空間410で干渉させ、消音効果
を得る。Further, as shown in FIG. 10, a through hole 40 communicating with the outside air is formed in a wall of a sub chamber 402 which is continuously provided in the exhaust passage 400.
3 is provided, the swing valve 404 is supported by a plurality of springs 406, the first valve 408 of the swing valve 404 is arranged in the exhaust passage 400, and the second valve 410 is arranged in the auxiliary chamber 402. (Japanese Patent Publication No. 2-501585). In this case, the first valve 408 and the second valve 410 of the swing valve 404 are included.
Oscillate in opposite directions. As a result, the exhaust passage 40
A flow having an opposite phase to the pulsating flow that flows through 0 is generated in the sub chamber 402, and the pulsating flow in the exhaust passage 400 and the flow having the opposite phase in the sub chamber 402 interfere with each other in the united space 410 to obtain a silencing effect.
【0006】[0006]
【発明が解決しようとする課題】ところで、上記した図
7に示す様な消音器では、バネ106で揺動弁102を
閉弁方向つまり矢印A1方向に付勢する方式が採用され
ており、基本的には、揺動弁102を開く開弁力Fα
は、排気通路100を流れる流体の全圧で定まり、一
方、揺動弁102を閉じる閉弁力Fβはバネ106の付
勢力で定まる。By the way, in the silencer as shown in FIG. 7 described above, a method of urging the rocking valve 102 by the spring 106 in the valve closing direction, that is, the arrow A1 direction is adopted. Specifically, the valve opening force Fα for opening the oscillating valve 102
Is determined by the total pressure of the fluid flowing through the exhaust passage 100, while the valve closing force Fβ for closing the rocking valve 102 is determined by the biasing force of the spring 106.
【0007】そのため、開弁に伴い、揺動弁102の手
前上流側Hの圧力が抜けると、揺動弁102の手前上流
側Hの全圧が低下するので、開弁力Fαが急に低下し、
従って、開弁力Fαよりも閉弁力Fβがかなり大きくな
る。そのため、揺動弁102が急に閉弁して排気通路1
00のストッパ部100aに打撃するハンチング現象が
生じ易い。更に、内燃機関から排出される排気ガスは脈
動圧を呈するため、打撃音が連続するチャタリング現象
が生じ易い。Therefore, when the pressure on the upstream side H of the oscillating valve 102 is released with the opening of the valve, the total pressure on the upstream side H of the oscillating valve 102 decreases, so that the valve opening force Fα suddenly decreases. Then
Therefore, the valve closing force Fβ becomes considerably larger than the valve opening force Fα. Therefore, the rocking valve 102 suddenly closes and the exhaust passage 1
The hunting phenomenon of hitting the stopper portion 100a of No. 00 is likely to occur. Further, since the exhaust gas discharged from the internal combustion engine exhibits a pulsating pressure, a chattering phenomenon in which impact sounds are continuous is likely to occur.
【0008】特に車両では、排気ガスの脈動圧の影響
で、チャタリング現象が生じる運転領域が広く存在す
る。例えば、排気ガスの流れが基本的にはない車両の減
速時においても、動弁系の関係で排気通路100内で脈
動圧が生じる。このとき、閉弁に近い状態の揺動弁10
2に脈動圧が作用するため、チャタリング現象が生じ易
い。かかるチャタリング現象を回避するには、バネ10
6の付勢力を強くすればよいが、この場合には、バネ1
06の付勢力が強いため、車両の加速時に必要とする開
弁度が得られない不具合が生じる。Particularly in a vehicle, there is a wide operating range where a chattering phenomenon occurs due to the influence of the pulsating pressure of exhaust gas. For example, pulsating pressure is generated in the exhaust passage 100 due to the valve system even during deceleration of the vehicle in which the flow of exhaust gas is basically not present. At this time, the swing valve 10 in a state close to the closed valve
Since pulsating pressure acts on 2, chattering is likely to occur. In order to avoid such chattering phenomenon, the spring 10
6 may be strengthened, but in this case, the spring 1
Since the biasing force of 06 is strong, there is a problem in that the degree of valve opening required for accelerating the vehicle cannot be obtained.
【0009】本発明は上記した実情に鑑みなされたもの
であり、その目的は、開弁力として作用する流体の全圧
と同位相の静圧を閉弁力として作用させることにより、
消音弁が閉弁する際の打撃に起因するハンチング現象、
チャタリング現象を低減または回避するのに有利な消音
器を提供することにある。The present invention has been made in view of the above situation, and an object thereof is to make a static pressure in the same phase as the total pressure of a fluid acting as a valve opening force act as a valve closing force.
Hunting phenomenon caused by impact when the silencer valve closes,
An object of the present invention is to provide a silencer that is advantageous in reducing or avoiding the chattering phenomenon.
【0010】[0010]
【課題を解決するための手段】本発明の消音器は、脈動
圧を呈する流体が上流から下流に向けて流れる主通路
と、弁支持部と、弁支持部よりも上流側で主通路に対面
して開口する静圧取入口と、静圧取入口に連通する副室
とを備えた管体と、管体の弁支持部に揺動可能に支持さ
れ、主通路に開閉可能に配置され主通路の流体の全圧を
受けて開弁方向に付勢される消音弁と、消音弁と一体的
にかつ副室内で揺動可能に配置され静圧取入口からの静
圧を受けて消音弁を閉弁方向に付勢するダンピング弁と
をもつ揺動弁と、消音弁を閉弁方向に付勢するバネとで
構成され、消音弁を開弁方向に付勢する主通路の流体の
全圧と同位相の静圧が静圧取入口を介してダンピング弁
に閉弁力として作用する様にしたことを特徴とするもの
である。DISCLOSURE OF THE INVENTION A muffler of the present invention comprises a main passage through which a fluid exhibiting a pulsating pressure flows from upstream to downstream, a valve support portion, and a main passage that is upstream of the valve support portion. A tubular body having a static pressure inlet opening and a sub-chamber communicating with the static pressure inlet, and a valve support part of the tubular body swingably supported and openably and closably arranged in the main passage. A muffler valve that is urged in the valve opening direction by receiving the total pressure of the fluid in the passage, and a muffler valve that is integrated with the muffler valve and is swingable in the auxiliary chamber and receives the static pressure from the static pressure intake port. Is composed of a swing valve having a damping valve for urging the silencer valve in the closing direction and a spring for urging the silencer valve in the closing direction. It is characterized in that the static pressure in the same phase as the pressure acts as a valve closing force on the damping valve via the static pressure inlet.
【0011】主通路は流体が通過するものであり、断面
円形状でも、角形状でも良い。静圧取入口は、消音弁で
生じるよどみ圧の領域を避けて形成する。揺動弁は、主
通路を開閉する消音弁と、副室に配置されたダンピング
弁とをもつ。揺動弁は、後述する実施例で例示する様に
断面Lの字形状であることが好ましい。弁支持部は揺動
弁を支持するものであり、軸、軸受、筒体等を利用して
形成できる。バネは消音弁を閉弁方向に付勢するもので
あり、公知のバネ、例えばネジリコイルバネ、引張コイ
ルバネ、板バネ等を適宜採用できる。The main passage is for passage of fluid and may have a circular cross section or a rectangular cross section. The static pressure inlet is formed so as to avoid the stagnation pressure region that occurs in the silencer valve. The rocking valve has a muffling valve that opens and closes the main passage, and a damping valve that is arranged in the sub chamber. The oscillating valve preferably has an L-shaped cross section, as illustrated in the examples described later. The valve support portion supports the swing valve, and can be formed by using a shaft, a bearing, a cylindrical body, or the like. The spring urges the muffler valve in the valve closing direction, and a known spring, for example, a torsion coil spring, a tension coil spring, a leaf spring, or the like can be appropriately adopted.
【0012】[0012]
【作用】主通路を流れる流体により消音弁は開弁方向に
揺動する。従って、消音弁を開弁する開弁力Fαは、基
本的には、主通路を流れる流体の全圧に起因する。一
方、消音弁を閉弁させる閉弁力Fβは、静圧取入口から
副室に取り入られた静圧がタンピング弁に作用する付勢
力Fβ1 と、バネの付勢力Fβ2 との和に起因する。[Function] The silencer valve swings in the valve opening direction by the fluid flowing through the main passage. Therefore, the valve opening force Fα for opening the silencer valve is basically caused by the total pressure of the fluid flowing through the main passage. On the other hand, the valve closing force Fβ for closing the silencer valve is due to the sum of the biasing force Fβ 1 of the static pressure taken from the static pressure intake port into the sub chamber acting on the tamping valve and the biasing force Fβ 2 of the spring. To do.
【0013】FαがFβよりも大きいとき消音弁は開弁
方向に揺動する。このとき、(Fα−Fβ)の差が、消
音弁を開弁方向に駆動する力として働く。FβがFαよ
りも大きいとき、消音弁は閉弁する。FαとFβとが均
衡すると、消音弁はその揺動角度で停止する。ところで
本発明では、消音弁を開弁する主通路の流体の全圧と、
静圧取入口から副室に取り入れられた静圧とは基本的に
は同位相である。そのため、開弁力Fα及び閉弁力Fβ
は基本的には同位相で変動する。When Fα is larger than Fβ, the muffler valve swings in the valve opening direction. At this time, the difference of (Fα-Fβ) acts as a force for driving the silencer valve in the valve opening direction. When Fβ is larger than Fα, the silencer valve closes. When Fα and Fβ are in equilibrium, the silencer valve stops at its swing angle. By the way, in the present invention, the total pressure of the fluid in the main passage for opening the silencer valve,
The static pressure introduced from the static pressure inlet into the sub chamber is basically in phase. Therefore, the valve opening force Fα and the valve closing force Fβ
Basically fluctuate in phase.
【0014】[0014]
【実施例】以下、本発明を車両の消音器に適用した実施
例について、図1〜図6を参照して説明する。図1、図
2は消音器を水平方向に切断した断面図である。この消
音器は車両の排気系の一部をなす。消音器を構成する管
体1は、主管10と、主管10に固定された副部材11
とで構成されている。主管10の内壁面で、主通路とし
ての排気通路14が形成されている。排気通路14で
は、脈動圧を呈する排気ガスが上流から下流に向けてつ
まり矢印B1方向に流れる。副部材11の内壁面で副室
16が形成されている。なお、副部材11は主管10の
横側壁に設けられているので、管体1の高さの抑制、車
高の抑制に有利である。DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment in which the present invention is applied to a vehicle silencer will be described below with reference to FIGS. 1 and 2 are cross-sectional views of the muffler cut horizontally. This silencer is part of the exhaust system of the vehicle. The pipe body 1 constituting the silencer includes a main pipe 10 and a sub member 11 fixed to the main pipe 10.
It consists of and. An exhaust passage 14 as a main passage is formed on the inner wall surface of the main pipe 10. In the exhaust passage 14, the exhaust gas having a pulsating pressure flows from upstream to downstream, that is, in the direction of arrow B1. A sub chamber 16 is formed on the inner wall surface of the sub member 11. Since the sub member 11 is provided on the lateral side wall of the main pipe 10, it is advantageous for suppressing the height of the pipe body 1 and the vehicle height.
【0015】揺動弁2は、排気通路14に配置された消
音弁20と、消音弁20に連設され副室16に配置され
たダンピング弁22と、消音弁20及びダンピング弁2
2を止め具24aあるいは溶接で固定した弁軸24とで
構成されている。図3に示す様に弁軸24の一端部24
aには筒体26が回り止め状態で保持されている。弁軸
24は、管体1に形成された弁支持部としての支持筒1
a、1bに固体潤滑剤系のブッシュ28を介して揺動可
能に支持されている。なお29はキャップである。The rocking valve 2 includes a muffler valve 20 arranged in the exhaust passage 14, a damping valve 22 connected to the muffler valve 20 and arranged in the sub chamber 16, the muffler valve 20 and the damping valve 2.
2 is constituted by a stopper 24a or a valve shaft 24 fixed by welding. As shown in FIG. 3, one end portion 24 of the valve shaft 24
A cylindrical body 26 is held in a in a non-rotating state. The valve shaft 24 is a support cylinder 1 as a valve support portion formed in the tubular body 1.
A and b are swingably supported by a bush 28 of a solid lubricant system. Note that 29 is a cap.
【0016】バネ3は所定の付勢力を発揮するネジリコ
イルバネであり、図3に示す様にその一端部3aは筒体
26に係止し、その他端部3bは支持筒1aのピン状突
起1eに係止している。この結果、内燃機関の非作動時
には、図1に示す様に、消音弁20が閉弁方向つまり矢
印C1方向に向けて付勢され、ストッパ部1rに当接し
ており、これにより排気通路14を閉鎖している。The spring 3 is a torsion coil spring that exerts a predetermined urging force. As shown in FIG. 3, one end 3a of the spring 3 is locked to the cylindrical body 26, and the other end 3b thereof is a pin-shaped projection 1e of the support cylinder 1a. Is locked to. As a result, when the internal combustion engine is not in operation, as shown in FIG. 1, the silencer valve 20 is biased in the valve closing direction, that is, in the direction of arrow C1 and is in contact with the stopper portion 1r. It is closed.
【0017】図1に示す様に、主管10の側壁うち、揺
動弁2の弁軸24よりも上流側に静圧取入口40が形成
されている。静圧取入口40はL字通路41をもつ連結
管42により副室16に連通している。従って、静圧取
入口40から取り入れられた静圧は副室16内のダンピ
ング弁22に作用する。L字通路41は、排気通路14
と直交する向きでかつ長さがL2の第1通路41aと、
排気通路14とほぼ平行でかつ長さがL3の第2通路4
1bとからなる。L2とL3との和は適宜設定できる
が、本実施例では約3〜10cm程度とされている。As shown in FIG. 1, a static pressure inlet 40 is formed on the side wall of the main pipe 10 on the upstream side of the valve shaft 24 of the rocking valve 2. The static pressure intake 40 communicates with the sub chamber 16 through a connecting pipe 42 having an L-shaped passage 41. Therefore, the static pressure introduced from the static pressure inlet 40 acts on the damping valve 22 in the sub chamber 16. The L-shaped passage 41 is the exhaust passage 14
A first passage 41a having a length L2 in a direction orthogonal to
The second passage 4 which is substantially parallel to the exhaust passage 14 and has a length L3
1b and. Although the sum of L2 and L3 can be set as appropriate, it is set to about 3 to 10 cm in this embodiment.
【0018】図1に示す様に、前記した静圧取入口40
は弁軸24よりも距離L4離れた位置に形成されてい
る。距離L4ぶん離した理由は次の様である。即ち、図
4は本例装置を模式的に示したものであり、消音弁20
は流れに対して障害物として機能する関係上、消音弁2
0の前面側には、図4にハッチングで示す様に流れの流
線に沿うよどみ圧の領域Sが生じるので、よどみ圧の領
域Sを避けて静圧取入口40を形成し、副室16に静圧
のみを作用させるためである。従って副室16には排気
通路14の動圧は作用しない。As shown in FIG. 1, the static pressure inlet 40 described above.
Is formed at a position separated from the valve shaft 24 by a distance L4. The reason for the distance L4 is as follows. That is, FIG. 4 schematically shows the device of this example, and the silencer valve 20
Muffler valve 2 because it functions as an obstacle to the flow
On the front side of 0, a stagnation pressure region S along the flow line of the flow occurs as shown by hatching in FIG. 4, so that the static pressure inlet 40 is formed so as to avoid the stagnation pressure region S, and the sub chamber 16 This is because only static pressure is applied to. Therefore, the dynamic pressure of the exhaust passage 14 does not act on the sub chamber 16.
【0019】ここで、排気通路14を流れる排気ガスの
脈動圧の基本波長λは、内燃機関の種類、内燃機関の回
転域等によって多少異なるが、一般的には15m〜2m
程度である。従って、前記したL字通路41の長さ(L
2+L3)は、排気通路14を流れる排気ガスの脈動圧
の基本波長λよりもはるかに短い距離とされている。よ
って本実施例では、消音弁20を開弁方向に付勢する排
気通路14の流体の全圧と、副室16内の静圧とは、基
本的に同位相となる。Here, the fundamental wavelength λ of the pulsating pressure of the exhaust gas flowing through the exhaust passage 14 varies somewhat depending on the type of internal combustion engine, the rotation range of the internal combustion engine, etc., but is generally 15 m to 2 m.
It is a degree. Therefore, the length of the L-shaped passage 41 (L
2 + L3) is a distance much shorter than the fundamental wavelength λ of the pulsating pressure of the exhaust gas flowing through the exhaust passage 14. Therefore, in this embodiment, the total pressure of the fluid in the exhaust passage 14 that urges the silencer valve 20 in the valve opening direction and the static pressure in the sub chamber 16 are basically in the same phase.
【0020】さて本実施例では、内燃機関からの排気ガ
スは排気通路14を矢印B1方向に流れ、排気ガスによ
り消音弁20は押圧される。そして、図2に示す様に消
音弁20は開弁方向つまり矢印C2方向に揺動する。図
2は消音弁20の開弁角度が角度θとなった状態を示
す。ここで、消音弁20を開く開弁力Fαは、排気通路
14を流れる流体の全圧に起因する。また、消音弁20
を閉じる閉弁力Fβは、静圧取入口40から副室16に
取り入られた静圧がタンピング弁22に作用する付勢力
Fβ1 と、バネ3による付勢力Fβ2 との和に起因す
る。そして、(Fα−Fβ)の差が、消音弁20を開弁
方向に駆動する力として作用し、開弁角度θの進行につ
れてFαとFβとが均衡して消音弁20はその揺動位置
で停止する。In the present embodiment, the exhaust gas from the internal combustion engine flows through the exhaust passage 14 in the direction of arrow B1, and the muffler valve 20 is pressed by the exhaust gas. Then, as shown in FIG. 2, the silencer valve 20 swings in the valve opening direction, that is, the arrow C2 direction. FIG. 2 shows a state in which the valve opening angle of the muffler valve 20 is the angle θ. Here, the valve opening force Fα for opening the silencer valve 20 is due to the total pressure of the fluid flowing through the exhaust passage 14. In addition, the silencer valve 20
The valve closing force Fβ for closing is due to the sum of the urging force Fβ 1 acting on the tamping valve 22 by the static pressure taken into the sub chamber 16 from the static pressure inlet 40 and the urging force Fβ 2 by the spring 3. Then, the difference of (Fα−Fβ) acts as a force for driving the silencer valve 20 in the valve opening direction, and as the valve opening angle θ progresses, Fα and Fβ are balanced and the silencer valve 20 is in its swing position. Stop.
【0021】上記した様に排気ガスが排気通路14を流
れる際に、排気通路14は消音弁20により覆われる
と、排気通路14の通路面積は絞られ、排気ガスの脈動
圧による変動圧力が軽減され、消音効果が得られる。よ
って、排気系の吐出端から吐出される音圧は低下する。
特に、車両の低速時には、車室内でのこもり音の要因と
なる低周波成分をもつ排気音が生じ易いが、この点本実
施例では低速時には開弁力Fαが小さく、消音弁20の
開弁角度θは小さいので、消音弁20で排気通路20は
効果的に絞られ、これにより低周波成分をもつ排気音は
効果的に消音される。なお、低速時には排気ガスの排気
圧がもともと小さいため、絞りによる内燃機関の能力低
下は実用上ない。車両の高速時には、排気通路14の全
圧が増して消音弁20の開弁角度θが大きくなるので、
排気ガスの排出性も確保される。As described above, when the exhaust passage 14 is covered with the muffler valve 20 when the exhaust gas flows through the exhaust passage 14, the passage area of the exhaust passage 14 is narrowed and the fluctuation pressure due to the pulsating pressure of the exhaust gas is reduced. And a muffling effect is obtained. Therefore, the sound pressure discharged from the discharge end of the exhaust system decreases.
In particular, when the vehicle speed is low, exhaust noise having a low frequency component that causes a muffled noise in the passenger compartment is likely to occur. In this respect, however, the valve opening force Fα is small at low speed and the muffling valve 20 is opened. Since the angle θ is small, the muffler valve 20 effectively throttles the exhaust passage 20, whereby the exhaust sound having a low frequency component is effectively silenced. Since the exhaust pressure of the exhaust gas is originally low at low speeds, there is practically no reduction in the performance of the internal combustion engine due to the throttle. At high speed of the vehicle, the total pressure of the exhaust passage 14 increases and the valve opening angle θ of the silencer valve 20 increases,
Exhaust gas emission is also secured.
【0022】ところで、内燃機関から排出される排気ガ
スは脈動圧を呈するものである。この様に脈動圧が作用
する場合には、前述した様に消音弁20が閉弁の際にス
トッパ部1rに急にあたる打撃音であるハンチング現
象、チャタリング現象を誘発するおそれがある。この点
本実施例では、消音弁20に開弁力Fαとして作用する
排気通路14の全圧と、閉弁力Fβとしてダンピング弁
22に作用する副室16の静圧とは基本に同位相であ
り、開弁力Fαが減少したときには閉弁力Fβも減少す
る。よって、消音弁20が閉弁する際に消音弁20がス
トッパ部1rに急に当たることは抑制される。よって、
ハンチング現象、チャタリング現象の低減、回避に有利
である。Exhaust gas discharged from the internal combustion engine has a pulsating pressure. When the pulsating pressure acts in this way, there is a possibility that the hunting phenomenon or the chattering phenomenon, which is a striking sound that suddenly hits the stopper portion 1r when the muffling valve 20 is closed as described above, may be induced. In this regard, in this embodiment, the total pressure of the exhaust passage 14 acting as the valve opening force Fα on the muffling valve 20 and the static pressure of the sub chamber 16 acting on the damping valve 22 as the valve closing force Fβ are basically in the same phase. Yes, when the valve opening force Fα decreases, the valve closing force Fβ also decreases. Therefore, it is possible to prevent the silencer valve 20 from suddenly hitting the stopper portion 1r when the silencer valve 20 is closed. Therefore,
This is advantageous for reducing and avoiding the hunting phenomenon and chattering phenomenon.
【0023】なお、揺動弁2を設置する位置は排気系で
あれば、特に限定されないが、一般的にはメインマフラ
ーの前に設置することができる。 (適用例)上記装置を所定の内燃機関の排気系に適用し
た。この内燃機関からの排気ガスは図5、図6に示す圧
力特性をもつ。ここで、図5は排気通路14を流れる排
気ガスの脈動圧の状況を模式的に示す。測定は、内燃機
関(4気筒、4サイクル)を6000rpmで駆動さ
せ、メインマフラーの前で測定して行った。図5の破線
で示す特性線D1は全圧の脈動状況を示し、特性線D2
は静圧の脈動状況を示し、P1は全圧の平均値を示し、
P2は静圧の平均値を示す。排気ガスの脈動圧の基本波
長λは前述した様に15m〜2m程度である。内燃機関
の回転数が変動しても、排気ガスは基本的にはこれに対
応した脈動圧を呈する。この様な脈動圧を呈する排気ガ
スが排気通路14を流れる。The position at which the oscillating valve 2 is installed is not particularly limited as long as it is an exhaust system, but it can be generally installed in front of the main muffler. (Application example) The above device is applied to an exhaust system of a predetermined internal combustion engine. The exhaust gas from this internal combustion engine has the pressure characteristics shown in FIGS. Here, FIG. 5 schematically shows the state of the pulsating pressure of the exhaust gas flowing through the exhaust passage 14. The measurement was performed by driving an internal combustion engine (4 cylinders, 4 cycles) at 6000 rpm and measuring in front of the main muffler. A characteristic line D1 indicated by a broken line in FIG. 5 indicates the pulsation situation of the total pressure, and a characteristic line D2
Indicates the pulsation situation of static pressure, P1 indicates the average value of total pressure,
P2 shows the average value of static pressure. The fundamental wavelength λ of the pulsating pressure of exhaust gas is approximately 15 m to 2 m as described above. Even if the rotational speed of the internal combustion engine fluctuates, the exhaust gas basically exhibits a pulsating pressure corresponding to this. Exhaust gas exhibiting such a pulsating pressure flows through the exhaust passage 14.
【0024】図6は内燃機関の回転数と排気ガスの圧力
との関係を示す。特性線E1は平均全圧を示し、特性線
E2は平均静圧を示す。図6に示す様に内燃機関の回転
数が増すにつれて(全圧−静圧)の差圧が大きくなる。
この差圧がバネ3の付勢力と共に消音弁20を実際に開
弁する力として作用することから、内燃機関の回転数が
増すにつれて消音弁20の開弁角度θが増加する。よっ
て、内燃機関の高速回転領域における排気ガスの排出性
が確保され、消音弁20による内燃機関の能力低下は実
用上生じない。FIG. 6 shows the relationship between the rotational speed of the internal combustion engine and the pressure of exhaust gas. The characteristic line E1 shows the average total pressure, and the characteristic line E2 shows the average static pressure. As shown in FIG. 6, the differential pressure (total pressure-static pressure) increases as the rotational speed of the internal combustion engine increases.
Since this pressure difference acts as a force for actually opening the muffling valve 20 together with the biasing force of the spring 3, the valve opening angle θ of the muffling valve 20 increases as the rotational speed of the internal combustion engine increases. Therefore, exhaust gas discharge performance in the high-speed rotation region of the internal combustion engine is ensured, and the ability of the internal combustion engine due to the muffler valve 20 does not actually decrease.
【0025】(他の例)その他、本発明は、上記したか
つ図面に示した実施例のみに限定されるものではなく、
例えば、排気通路14は断面円形状でもよく、バネは引
張コイルバネでも良いなど必要に応じて適宜変更して実
施できるものである。(Other Examples) In addition, the present invention is not limited to the embodiments described above and shown in the drawings,
For example, the exhaust passage 14 may have a circular cross-section, and the spring may be a tension coil spring.
【0026】[0026]
【発明の効果】本発明の消音器によれば、開弁力Fαと
して作用する流体の全圧と同位相の静圧を閉弁力Fβと
して作用させるため、開弁力Fα及び閉弁力Fβは基本
的には同位相で変動する。したがって、開弁状態の消音
弁に作用する開弁力Fαが急に減少して消音弁が閉弁し
ようとする際、閉弁力Fβも減少する。よって、閉弁時
に生じる消音弁の打撃は低減または回避される。よっ
て、消音弁のハンチング現象、チャタリング現象の低減
または回避に有利である。According to the silencer of the present invention, since the static pressure in the same phase as the total pressure of the fluid acting as the valve opening force Fα acts as the valve closing force Fβ, the valve opening force Fα and the valve closing force Fβ. Basically fluctuate in phase. Therefore, when the valve opening force Fα acting on the muffler valve in the valve open state suddenly decreases and the muffler valve tries to close, the valve closing force Fβ also decreases. Therefore, the impact of the muffler valve that occurs when the valve is closed is reduced or avoided. Therefore, it is advantageous for reducing or avoiding the hunting phenomenon and chattering phenomenon of the silencer valve.
【図1】消音弁が閉弁した状態を示す水平方向にそう消
音器の断面図である。FIG. 1 is a cross-sectional view of a silencer in the horizontal direction showing a state in which the silencer valve is closed.
【図2】消音弁が一部開弁した状態を示す水平方向にそ
う消音器の断面図である。FIG. 2 is a cross-sectional view of the silencer in the horizontal direction showing a state in which the silencer valve is partially opened.
【図3】図1のW−W線に沿う揺動弁の枢支部分付近を
示す断面図である。3 is a cross-sectional view showing the vicinity of a pivotal support portion of the rocking valve taken along the line WW in FIG.
【図4】消音弁により生じるよどみ圧の領域を示す消音
器の模式的断面図である。FIG. 4 is a schematic cross-sectional view of a silencer showing a region of stagnation pressure generated by a silencer valve.
【図5】排気通路を流れる排気ガスの脈動圧の状況を示
すグラフである。FIG. 5 is a graph showing a situation of pulsating pressure of exhaust gas flowing through an exhaust passage.
【図6】内燃機関の回転数と排気ガスの圧力との関係を
示すグラフである。FIG. 6 is a graph showing the relationship between the rotation speed of the internal combustion engine and the pressure of exhaust gas.
【図7】従来例に係る消音器の模式的断面図である。FIG. 7 is a schematic cross-sectional view of a silencer according to a conventional example.
【図8】他の従来例に係る消音器の模式的断面図であ
る。FIG. 8 is a schematic cross-sectional view of a silencer according to another conventional example.
【図9】他の従来例に係る消音器の模式的断面図であ
る。FIG. 9 is a schematic cross-sectional view of a silencer according to another conventional example.
【図10】他の従来例に係る消音器の模式的断面図であ
る。FIG. 10 is a schematic cross-sectional view of a silencer according to another conventional example.
【符号の説明】 図中、1は管体、10は主管、11は副部材、14は排
気通路(主通路)、16は副室、2は揺動弁、20は消
音弁、22はダンピング弁、24は弁軸、3はバネ、4
0は静圧取入口、41はL字通路を示す。DESCRIPTION OF SYMBOLS In the figure, 1 is a tubular body, 10 is a main pipe, 11 is an auxiliary member, 14 is an exhaust passage (main passage), 16 is an auxiliary chamber, 2 is a swing valve, 20 is a silencer valve, and 22 is damping. Valve, 24 is a valve shaft, 3 is a spring, 4
Reference numeral 0 indicates a static pressure inlet, and 41 indicates an L-shaped passage.
Claims (1)
て流れる主通路と、弁支持部と、該弁支持部よりも上流
側で該主通路に対面して開口する静圧取入口と、該静圧
取入口に連通する副室とを備えた管体と、 該管体の弁支持部に揺動可能に支持され、該主通路に開
閉可能に配置され該主通路の流体の全圧を受けて開弁方
向に付勢される消音弁と、該消音弁と一体的にかつ該副
室内で揺動可能に配置され該静圧取入口からの静圧を受
けて該消音弁を閉弁方向に付勢するダンピング弁とをも
つ揺動弁と、 該消音弁を閉弁方向に付勢するバネとで構成され、 該消音弁を開弁方向に付勢する該主通路の流体の全圧と
同位相の静圧が該静圧取入口を介して該ダンピング弁に
閉弁力として作用する様にしたことを特徴とする消音
器。1. A main passage through which a fluid exhibiting a pulsating pressure flows from upstream to downstream, a valve support portion, and a static pressure inlet opening facing the main passage upstream of the valve support portion. , A sub-chamber having a sub-chamber communicating with the static pressure inlet, and a valve support portion of the pipe, which is swingably supported, and is openably and closably arranged in the main passage so that all fluid in the main passage is opened. A silencer valve which is urged in the valve opening direction by receiving pressure, and arranged integrally with the silencer valve and swingable in the sub chamber to receive the static pressure from the static pressure intake port to activate the silencer valve. A fluid in the main passage configured by a rocking valve having a damping valve for urging the silencer valve and a spring for urging the silencer valve in the closing direction, and urging the silencer valve in the opening direction. A silencer characterized in that a static pressure in the same phase as the total pressure of (3) acts on the damping valve as a valve closing force via the static pressure inlet.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP23817592A JP2842074B2 (en) | 1992-09-07 | 1992-09-07 | Silencer |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP23817592A JP2842074B2 (en) | 1992-09-07 | 1992-09-07 | Silencer |
Publications (2)
Publication Number | Publication Date |
---|---|
JPH0688515A true JPH0688515A (en) | 1994-03-29 |
JP2842074B2 JP2842074B2 (en) | 1998-12-24 |
Family
ID=17026292
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP23817592A Expired - Fee Related JP2842074B2 (en) | 1992-09-07 | 1992-09-07 | Silencer |
Country Status (1)
Country | Link |
---|---|
JP (1) | JP2842074B2 (en) |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US6298878B1 (en) * | 1997-03-31 | 2001-10-09 | Westinghouse Air Brake Company | Ball cock for railway vehicle |
US6499562B1 (en) * | 1999-07-29 | 2002-12-31 | Zeuna-Staerker Gmbh & Co. Kg | Muffler with variable sound-absorbing characteristics |
CN104364480A (en) * | 2012-06-07 | 2015-02-18 | 双叶产业株式会社 | Muffler |
-
1992
- 1992-09-07 JP JP23817592A patent/JP2842074B2/en not_active Expired - Fee Related
Cited By (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US6298878B1 (en) * | 1997-03-31 | 2001-10-09 | Westinghouse Air Brake Company | Ball cock for railway vehicle |
US6499562B1 (en) * | 1999-07-29 | 2002-12-31 | Zeuna-Staerker Gmbh & Co. Kg | Muffler with variable sound-absorbing characteristics |
CN104364480A (en) * | 2012-06-07 | 2015-02-18 | 双叶产业株式会社 | Muffler |
US20150152760A1 (en) * | 2012-06-07 | 2015-06-04 | Futaba Industrial Co., Ltd. | Muffler |
US9388719B2 (en) * | 2012-06-07 | 2016-07-12 | Futaba Industrial Co., Ltd. | Muffler |
Also Published As
Publication number | Publication date |
---|---|
JP2842074B2 (en) | 1998-12-24 |
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