JP4157490B2 - Valve unit for silencer - Google Patents

Valve unit for silencer Download PDF

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JP4157490B2
JP4157490B2 JP2004117205A JP2004117205A JP4157490B2 JP 4157490 B2 JP4157490 B2 JP 4157490B2 JP 2004117205 A JP2004117205 A JP 2004117205A JP 2004117205 A JP2004117205 A JP 2004117205A JP 4157490 B2 JP4157490 B2 JP 4157490B2
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valve
plate
stopper member
leaf spring
silencer
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JP2004204856A (en
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上兼　　正之
功 廣川
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Honda Motor Co Ltd
Yutaka Giken Co Ltd
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Honda Motor Co Ltd
Yutaka Giken Co Ltd
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    • 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

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Exhaust Silencers (AREA)

Description

本発明は、主として車両用エンジンの排気系に介設する消音器用のバルブ装置に関し、詳しくは、消音器内の排気ガスのバイパス経路を、排気圧が所定圧に上昇したときに開くバルブ装置に関する。   The present invention relates to a valve device for a silencer that is mainly provided in an exhaust system of a vehicle engine. More specifically, the present invention relates to a valve device that opens an exhaust gas bypass path in the silencer when the exhaust pressure rises to a predetermined pressure. .

一般に車両においては、加速走行時や高速走行時の性能を向上させるため、エンジンの高速回転域の出力を十分に確保することが要求される。また、アイドリング時や低速走行時の静粛性を確保するため、排気騒音を低減することが要求される。すなわち、エンジンの高速回転域の出力を十分に確保しつつ、少なくともエンジンの低速回転域では排気騒音を低減することが要求されている。   In general, in a vehicle, it is required to sufficiently secure an output in a high-speed rotation region of an engine in order to improve performance during acceleration traveling or high-speed traveling. In addition, it is required to reduce exhaust noise in order to ensure quietness during idling or low speed running. That is, it is required to reduce exhaust noise at least in the low-speed rotation region of the engine while ensuring a sufficient output in the high-speed rotation region of the engine.

ここで、エンジン出力および排気騒音は、車両用エンジンの排気系を構成する通路の断面積によって大きく影響されることが知られている。すなわち、通路の断面積を増大すれば、排気抵抗の減少によりエンジン出力を十分に確保することができる反面、排気抵抗の減少によって排気騒音が増大し、反対に通路の断面積を減少すれば、排気抵抗の増大により排気騒音を低減できる反面、排気抵抗の増大によってエンジン出力が低下することが知られている。   Here, it is known that the engine output and the exhaust noise are greatly influenced by the cross-sectional area of the passage constituting the exhaust system of the vehicle engine. That is, if the cross-sectional area of the passage is increased, the engine output can be sufficiently secured by reducing the exhaust resistance, while the exhaust noise is increased by reducing the exhaust resistance, and conversely if the cross-sectional area of the passage is decreased, It is known that exhaust noise can be reduced by increasing exhaust resistance, but engine output is reduced by increasing exhaust resistance.

そのため、エンジンの排気系に設けられる消音器においては、排気通路にバイパス経路が設けられているものがある。そして、このバイパス経路には、バルブ装置が設けられ、高速回転時にのみバイパス経路を開くように構成されている（例えば特許文献１参照）。
このバルブ装置は、弁孔を有するハウジング（基台）と、ハウジングの弁孔を塞ぐように設けられた板状弁とから主として構成されており、板状弁はその基端部がハウジングに固定されて、消音器内の排気通路の圧力に応じて撓み、弁孔を開くようになっている。
特開２００１−１２３８１７号公報（第３頁、図２等） For this reason, some silencers provided in the exhaust system of the engine have a bypass path in the exhaust passage. The bypass path is provided with a valve device, and is configured to open the bypass path only during high-speed rotation (see, for example, Patent Document 1).
This valve device is mainly composed of a housing (base) having a valve hole and a plate valve provided so as to close the valve hole of the housing, and the base end portion of the plate valve is fixed to the housing. Then, it bends according to the pressure of the exhaust passage in the silencer and opens the valve hole.
Japanese Patent Laid-Open No. 2001-123817 (page 3, FIG. 2, etc.)

しかしながら、エンジンの排気圧は脈動しており、前記した板状弁はこの脈動に応じて振動する。特に、この振動は板状弁の先端で大きく、この開閉振動数が板状弁の固有振動数と一致すると板状弁が共振することになる。板状弁に共振が発生すると、バルブの動作が不安定になったり、異音が発生したりすることがある。   However, the exhaust pressure of the engine pulsates, and the plate-like valve described above vibrates in response to this pulsation. In particular, this vibration is large at the tip of the plate valve, and the plate valve resonates when this open / close frequency matches the natural frequency of the plate valve. When resonance occurs in the plate valve, the operation of the valve may become unstable or abnormal noise may occur.

そこで、本発明は、以上の点に鑑み、板状弁の動作を安定させうるようにした消音器用バルブ装置を提供することを目的とする。   Accordingly, an object of the present invention is to provide a silencer valve device capable of stabilizing the operation of a plate valve in view of the above points.

前記した課題を解決するため、本発明の消音器用バルブ装置は、消音器内の排気ガスのバイパス経路を、排気圧が所定圧に上昇したときに開く消音器用バルブ装置であって、排気ガスが流通する弁孔を有する基台と、前記弁孔を開閉し、前記基台に基端部が固定された板状弁と、前記板状弁の表面に先端が当接して前記板状弁を閉弁方向に付勢する板バネ部材と、基端側において前記基台との間で前記板状弁を挟んで固定するとともに、先端側においてリテーナとの間で前記板バネ部材を挟んで固定するストッパ部材と、を備え、前記板バネ部材は、前記ストッパ部材及び前記リテーナよりも幅が小さく、前記板バネ部材と前記リテーナは、それぞれの先端側の縁部において前記ストッパ部材に溶接されているとともに、前記先端側の縁部から所定範囲の両側縁部において前記リテーナ部材が前記ストッパ部材にのみ溶接されていることを特徴とする。 In order to solve the above-described problem, the silencer valve device of the present invention is a silencer valve device that opens the exhaust gas bypass path in the silencer when the exhaust pressure rises to a predetermined pressure. A base having a valve hole that circulates; a plate-like valve that opens and closes the valve hole and has a base end fixed to the base; and a tip that abuts the surface of the plate-like valve to The leaf spring member energized in the valve closing direction is fixed with the plate valve sandwiched between the base on the base end side and the leaf spring member is fixed with the retainer on the distal end side. The leaf spring member is smaller in width than the stopper member and the retainer, and the leaf spring member and the retainer are welded to the stopper member at the respective edge portions on the front end side. And the edge on the tip side It said retainer member at both side edge portions of the predetermined range, characterized in that it is welded only to the stopper member.

このような構成の消音器用バルブ装置によれば、板バネをストッパ部材の先端部の縁のみで位置合わせ及び仮押えをし、ストッパ部材とリテーナに挟んで固定するので、板バネを溶接するときに板バネに穴を開けてしまったり、板バネが歪んだりする不具合を起こすことがない。
また、前記板バネ部材は、前記板状弁の撓み量の増加につれて板状弁との当接位置が板状弁の基端部側へ変位するように板状弁に対し傾斜して配置されるとともに、前記先端が曲面状に形成され、この曲面状に形成された部分で前記板状弁の表面に当接するのが好ましい。
このようにすれば、板状弁の撓み量の増加につれて板バネ部材と板状弁の当接位置が板状弁の基端部側へ変位するので、板バネ部材の付勢力による板状弁の閉じ側へのモーメントが板状弁の撓み量の増加につれて小さくなる。従って、エンジンがある回転数の時に板状弁が開閉を繰り返す過度状態を無くし、開くときは一気に開き、閉まるときも一気に閉まる動作をするので、板状弁の共振が起こりにくくなる。さらに、この板バネ部材は、先端が曲面状に形成され、この曲面に形成された部分で前記板状弁の表面に当接しているので、板状弁と板バネ部材との摺動が滑らかである。 According to the silencer valve device having such a configuration, the leaf spring is positioned and temporarily pressed only by the edge of the tip of the stopper member, and fixed between the stopper member and the retainer. There is no problem that the leaf spring is perforated or the leaf spring is distorted.
Further, the leaf spring member is disposed to be inclined with respect to the plate valve so that the contact position with the plate valve is displaced toward the base end side of the plate valve as the amount of deflection of the plate valve increases. At the same time, it is preferable that the tip is formed in a curved shape, and the portion formed in the curved shape is in contact with the surface of the plate valve.
In this way, the contact position of the plate spring member and the plate valve is displaced toward the base end side of the plate valve as the amount of deflection of the plate valve increases, so that the plate valve due to the urging force of the plate spring member The moment toward the closing side decreases as the amount of deflection of the plate valve increases. Accordingly, an excessive state in which the plate valve repeatedly opens and closes when the engine is at a certain rotational speed is eliminated, and when the engine is opened, the valve is opened at once, and when the engine is closed, the valve closes at once. Furthermore, since the tip of the leaf spring member is formed in a curved shape, and the portion formed in the curved surface is in contact with the surface of the plate valve, the sliding between the plate valve and the leaf spring member is smooth. It is.

本発明によれば、板状弁の開閉が一気になされ、また、板状弁と板バネ部材の摺動が滑らかなので板状弁の動作を安定させることができる。   According to the present invention, the opening and closing of the plate valve is performed at once, and since the sliding of the plate valve and the plate spring member is smooth, the operation of the plate valve can be stabilized.

次に、本発明の実施形態について適宜図面を参照しながら説明する。参照する図面において、図１は、本発明のバルブ装置が適用される消音器の一例を示す断面図である。
図１に示すように、内燃機関の排気系の途中に介設される消音器１は、筒状のシェル１１と、シェル１１の一端と他端とを閉塞する端壁１２、１３とで消音器本体１０が構成されている。消音器本体１０は、その内部空間を第１及び第２セパレータ１４、１５により３つに区画され、さらに、排気流入管２１、インナーパイプ２２、排気流出管２３の３つのパイプにより、排気ガスの通路が形成されている。 Next, embodiments of the present invention will be described with reference to the drawings as appropriate. In the drawings to be referred to, FIG. 1 is a cross-sectional view showing an example of a silencer to which the valve device of the present invention is applied.
As shown in FIG. 1, a silencer 1 interposed in the middle of an exhaust system of an internal combustion engine is silenced by a cylindrical shell 11 and end walls 12 and 13 closing one end and the other end of the shell 11. A container body 10 is configured. The silencer main body 10 is divided into three internal spaces by first and second separators 14 and 15, and further, exhaust gas is exhausted by three pipes of an exhaust inflow pipe 21, an inner pipe 22, and an exhaust outflow pipe 23. A passage is formed.

第１セパレータ１４及び第２セパレータ１５は、消音器本体１０内で端壁１２，１３と平行に配置されている。第１セパレータ１４は、端壁１２との間で第１消音室３１を形成し、第２セパレータ１５は、第１セパレータ１４との間で第２消音室３２を、また、端壁１３との間で第３消音室３３を形成している。   The first separator 14 and the second separator 15 are disposed in parallel to the end walls 12 and 13 in the silencer body 10. The first separator 14 forms a first silencing chamber 31 with the end wall 12, the second separator 15 forms a second silencing chamber 32 with the first separator 14, and the end wall 13. A third silencing chamber 33 is formed between them.

排気流入管２１は、端壁１２、第１セパレータ１４及び第２セパレータ１５を貫通して、エンジンからの排気経路と第３消音室３３を連通している。また、排気流入管２１の第２消音室３２を通過している部分の管壁には、多数の透孔２１ａが形成されている。   The exhaust inflow pipe 21 passes through the end wall 12, the first separator 14, and the second separator 15, and communicates the exhaust path from the engine and the third silencing chamber 33. In addition, a large number of through holes 21 a are formed in the tube wall of the portion of the exhaust inflow pipe 21 that passes through the second silencing chamber 32.

インナーパイプ２２は、第１セパレータ１４及び第２セパレータ１５を貫通して、第１消音室３１と第３消音室３３を連通している。また、インナーパイプ２２の第２消音室を通過している部分の管壁には、多数の透孔２２ａが形成されていることで、インナーパイプ２２は、排気流入管２１と第２消音室３２を介して連通している。   The inner pipe 22 passes through the first separator 14 and the second separator 15 and communicates the first silencing chamber 31 and the third silencing chamber 33. The inner pipe 22 is formed with a plurality of through holes 22a in a portion of the inner pipe 22 that passes through the second silencing chamber, so that the inner pipe 22 has the exhaust inflow pipe 21 and the second silencing chamber 32. It communicates through.

排気流出管２３は、第１セパレータ１４、第２セパレータ１５及び端壁１３を貫通して、第１消音室３１と外部を連通している。   The exhaust outlet pipe 23 passes through the first separator 14, the second separator 15, and the end wall 13, and communicates with the first silencing chamber 31 and the outside.

このような構造により、排気流入管２１に流入した排気ガスの流通経路は、第３消音室３３、インナーパイプ２２、第１消音室３１を通って排気流出管２３に至る経路と、透孔２１ａ、第２消音室３２、透孔２２ａ、インナーパイプ２２、第１消音室３１を通って排気流出管２３に至る経路との２系統になる。   With such a structure, the flow path of the exhaust gas that has flowed into the exhaust inflow pipe 21 is the passage through the third silencing chamber 33, the inner pipe 22, the first silencing chamber 31 to the exhaust outflow pipe 23, and the through hole 21a. , The second silencing chamber 32, the through hole 22 a, the inner pipe 22, and the path leading to the exhaust outlet pipe 23 through the first silencing chamber 31.

ところで、内燃機関の高速回転に伴って多量の排気ガスが排気流入管２１に流入すると、前記２系統だけの排気ガスの流通経路では第２及び第３消音室３２，３３内の排気圧が高くなり、ひいては、内燃機関の出力が低下する。   By the way, when a large amount of exhaust gas flows into the exhaust inflow pipe 21 as the internal combustion engine rotates at high speed, the exhaust pressure in the second and third silencing chambers 32 and 33 becomes high in the exhaust gas distribution path of only the two systems. As a result, the output of the internal combustion engine decreases.

このため、第１セパレータ１４に、第２消音室３２と第１消音室３１とを連通するバイパス経路用の開口部１４ａを設け、この開口部１４ａに、排気圧が所定圧に上昇したときに開くバルブ装置４を設けている。そして、内燃機関の高回転域では、前記した２系統にバイパス経路を追加した３系統の流通経路で多量の排気ガスが大気にスムーズに排出されるようになっている。   For this reason, the first separator 14 is provided with an opening 14a for a bypass path that communicates the second silencing chamber 32 and the first silencing chamber 31, and when the exhaust pressure rises to a predetermined pressure in the opening 14a. An opening valve device 4 is provided. In a high rotation range of the internal combustion engine, a large amount of exhaust gas is smoothly discharged to the atmosphere through the three distribution channels obtained by adding a bypass route to the two systems described above.

次に、バルブ装置４について詳細に説明する。図２は、バルブ装置の斜視図であり、図３は、バルブ装置の分解斜視図、図４は、図２における４−４断面図である。   Next, the valve device 4 will be described in detail. 2 is a perspective view of the valve device, FIG. 3 is an exploded perspective view of the valve device, and FIG. 4 is a sectional view taken along line 4-4 in FIG.

バルブ装置４は、図２〜図４に示すように、弁孔４１を有する弁座（基台）４２と、弁孔４１を開閉するバルブである板状弁４３と、板状弁４３の開度を規制するストッパ部材４６と、板状弁４３の撓み特性を調整する板バネ（板バネ部材）４７とを備えている。   As shown in FIGS. 2 to 4, the valve device 4 includes a valve seat (base) 42 having a valve hole 41, a plate valve 43 that is a valve for opening and closing the valve hole 41, and an opening of the plate valve 43. A stopper member 46 that regulates the degree and a leaf spring (plate spring member) 47 that adjusts the bending characteristics of the plate valve 43 are provided.

弁座４２は、矩形の板材に矩形の弁孔４１が形成されて構成されている。また、弁座４２の基端部４２ａには２つの貫通した位置決め孔４２ｂが形成されている。   The valve seat 42 is configured by forming a rectangular valve hole 41 in a rectangular plate material. Further, two penetrating positioning holes 42b are formed in the base end portion 42a of the valve seat 42.

板状弁４３は、弾性変形可能な薄い矩形の板材からなり、前記した弁孔４１を被うように配置されている。例えば、板状弁４３は、厚さ０．１５ｍｍ程度のバネ鋼からなる板で形成されている。板状弁４３の基端部４３ａには、弁座４２の位置決め孔４２ｂに対応する位置及び大きさで位置決め孔４３ｂ，４３ｂが形成されている。板状弁４３の基端部４３ａは、板状弁４３の末端に相当する基端４３ｅから所定範囲、すなわち、図３におけるエリアＡ１において、ストッパ部材４６と弁座４２に挟まれて固定されている。一方、板状弁４３の先端４３ｃから所定範囲、すなわち図３におけるエリアＡ３において、板状弁４３の両側縁部が弁座４２とは逆側へ折り曲げられて、折曲げ部４３ｄ，４３ｄを形成している。この折曲げ部４３ｄ，４３ｄにより、板状弁４３はエリアＡ３での曲げ剛性が高くなっており、板状弁４３の共振が抑制される。また、エリアＡ３の曲げ剛性が高い結果、板状弁４３は、エリアＡ１とエリアＡ３の間、すなわち、図３におけるエリアＡ２で撓み変形し、弁孔４１を開閉する。
なお、折曲げ部４３ｄ，４３ｄは、弁座４２とは逆側へ曲げてあるので、板状弁４３は弁孔４１と隙間を形成することなく、弁孔４１を密閉できる。 The plate-like valve 43 is made of a thin rectangular plate that can be elastically deformed, and is arranged so as to cover the valve hole 41 described above. For example, the plate valve 43 is formed of a plate made of spring steel having a thickness of about 0.15 mm. Positioning holes 43 b and 43 b are formed in the base end portion 43 a of the plate-like valve 43 at positions and sizes corresponding to the positioning holes 42 b of the valve seat 42. The base end portion 43a of the plate-like valve 43 is fixed by being sandwiched between the stopper member 46 and the valve seat 42 in a predetermined range from the base end 43e corresponding to the end of the plate-like valve 43, that is, in the area A1 in FIG. Yes. On the other hand, in a predetermined range from the tip 43c of the plate valve 43, that is, in the area A3 in FIG. 3, both side edges of the plate valve 43 are bent to the opposite side to the valve seat 42 to form bent portions 43d and 43d. is doing. Due to the bent portions 43d and 43d, the plate valve 43 has high bending rigidity in the area A3, and resonance of the plate valve 43 is suppressed. Further, as a result of the high bending rigidity of the area A3, the plate valve 43 is bent and deformed between the area A1 and the area A3, that is, in the area A2 in FIG.
Since the bent portions 43d and 43d are bent to the opposite side of the valve seat 42, the plate valve 43 can seal the valve hole 41 without forming a gap with the valve hole 41.

なお、折曲げ部４３ｄの折り曲げ角度は、弁座４２と逆側へ折り返されている限り適宜に設定することができる。例えば、弁座４２に対し垂直に折り曲げてもよいし、４５度程度に折り曲げるものでも構わない。なお、板状弁４３のストッパ部材４６及び弁座４２に挟持される部分での幅（図２におけるＸ方向の大きさ）は、弁座４２の幅及びストッパ部材４６の幅よりも小さい。   In addition, the bending angle of the bending part 43d can be appropriately set as long as it is folded back to the valve seat 42 side. For example, it may be bent perpendicular to the valve seat 42 or may be bent at about 45 degrees. The width of the plate-shaped valve 43 between the stopper member 46 and the valve seat 42 (size in the X direction in FIG. 2) is smaller than the width of the valve seat 42 and the width of the stopper member 46.

ストッパ部材４６は、板状弁４３の押さえ部分となる基端部４６ａと、基端部４６ａから延出し、基端部４６ａに対し傾斜したストッパ面４６ｅと、ストッパ面４６ｅからさらに延出し、ストッパ面４６ｅに対してさらに傾斜した先端部４６ｃとが一体になって形成されている。ストッパ部材４６は、板状弁４３に比較して厚い、例えば板厚２ｍｍ程度の板材をプレス成形したものである。そして、ストッパ部材４６は、板状弁４３を弁座４２に固定する機能を有するとともに、板状弁４３が大きく撓んだときに、ストッパ面４６ｅで板状弁４３を受け止めて、板状弁４３の過度な撓みを防止している。なお、ストッパ部材４６の両側縁部は、全長にわたって弁座４２と逆側に折り曲げられたリブ４６ｆ，４６ｆ（図３参照）が形成されることで、剛性が高められている。また、ストッパ部材４６の基端部４６ａには、弁座４２の位置決め孔４２ｂ，４２ｂに対応する位置及び大きさで位置決め孔４６ｂ，４６ｂが形成されている。   The stopper member 46 is a base end portion 46a that serves as a pressing portion of the plate valve 43, a stopper surface 46e that extends from the base end portion 46a and is inclined with respect to the base end portion 46a, and further extends from the stopper surface 46e. A tip 46c that is further inclined with respect to the surface 46e is integrally formed. The stopper member 46 is formed by press-molding a plate material that is thicker than the plate-like valve 43, for example, a plate thickness of about 2 mm. The stopper member 46 has a function of fixing the plate-like valve 43 to the valve seat 42. When the plate-like valve 43 is largely bent, the stopper member 46 receives the plate-like valve 43 at the stopper surface 46e, 43 is prevented from excessive bending. The side edges of the stopper member 46 are formed with ribs 46f and 46f (see FIG. 3) that are bent over the entire length to the opposite side of the valve seat 42, thereby increasing rigidity. Positioning holes 46b and 46b are formed in the base end portion 46a of the stopper member 46 at positions and sizes corresponding to the positioning holes 42b and 42b of the valve seat 42.

ストッパ部材４６の先端部４６ｃには、板バネ４７が固定されている。また、先端部４６ｃには、板バネ４７を固定するときに、板バネ４７との位置決めに使われる貫通した一対の位置決め孔４６ｄ，４６ｄが形成されている。   A leaf spring 47 is fixed to the distal end portion 46 c of the stopper member 46. The distal end portion 46c is formed with a pair of through-hole positioning holes 46d and 46d used for positioning with the leaf spring 47 when the leaf spring 47 is fixed.

板バネ４７は、第１バネ４７１及び第２バネ４７２を重ねて組み合わせることで構成されている。
第１ばね４７１は、板状弁４３よりも薄いばね鋼の板、たとえば０．１ｍｍ程度の板からなる矩形の板バネである。第１ばね４７１の一端４７１ａ側にはストッパ部材４６の位置決め孔４６ｄ，４６ｄに対応する位置及び大きさの一対の位置決め孔４７１ｂ，４７１ｂが形成されている。一方、第１ばね４７１の他端部４７１ｃ（図３参照）は、板状弁４３の先端４３ｃから所定範囲、すなわちエリアＡ３に斜めに当接している。第１ばね４７１は、板状弁４３の先端４３ｃから基端部４３ａへ近付くにつれ徐々に板状弁に近付くように傾斜して配置されている。また、他端部４７１ｃは、曲面に形成されることで、その末端付近で板状弁４３とほぼ同じ向きになって当接している。このように、他端部４７１ｃを曲面状にすることで、板状弁４３と板バネ４７の摺動を滑らかにしている。 The leaf spring 47 is configured by overlapping and combining the first spring 471 and the second spring 472.
The first spring 471 is a rectangular plate spring made of a spring steel plate thinner than the plate valve 43, for example, a plate of about 0.1 mm. A pair of positioning holes 471b and 471b having positions and sizes corresponding to the positioning holes 46d and 46d of the stopper member 46 are formed on the one end 471a side of the first spring 471. On the other hand, the other end 471c (see FIG. 3) of the first spring 471 is in contact with the predetermined range, that is, the area A3 obliquely from the tip 43c of the plate valve 43. The first spring 471 is disposed so as to gradually approach the plate valve as it approaches the base end portion 43a from the distal end 43c of the plate valve 43. Further, the other end portion 471c is formed in a curved surface, so that the other end portion 471c abuts in the same direction as the plate valve 43 in the vicinity of the end thereof. As described above, the other end portion 471c is formed in a curved surface so that the sliding of the plate valve 43 and the leaf spring 47 is smooth.

第２ばね４７２は、板状弁４３よりも薄いばね鋼の板、例えば０．１ｍｍ程度の板からなる矩形の板バネである。第２ばね４７２の一端４７２ａ側には、ストッパ部材４６の位置決め孔４６ｄ，４６ｄに対応する位置及び大きさの一対の位置決め孔４７２ｂ，４７２ｂが形成されている。第２ばね４７２は、他端４７２ｃ（図３参照）までの長さ、すなわち撓み方向の長さが第１ばね４７１よりも短くなっており、これにより、第１ばね４７１と第２ばね４７２を重ねて撓ませたときの変形をスムーズにしている。   The second spring 472 is a rectangular plate spring made of a spring steel plate thinner than the plate valve 43, for example, a plate of about 0.1 mm. A pair of positioning holes 472b and 472b having positions and sizes corresponding to the positioning holes 46d and 46d of the stopper member 46 are formed on the one end 472a side of the second spring 472. The length of the second spring 472 to the other end 472c (see FIG. 3), that is, the length in the bending direction is shorter than that of the first spring 471, and thereby the first spring 471 and the second spring 472 are connected. Deformation is smooth when it is bent and overlapped.

このようにストッパ部材４６に固定された板バネ４７は、その他端部４７１ｃにおいて板状弁４３と当接するが、板状弁４３に対し、傾斜して当接することで、板状弁４３の開度が大きくなるに従い、その当接位置が板状弁４３の基端部４３ａ側へ変位するようになっている。また、その当接位置は、折曲げ部４３ｄ，４３ｄにより補強されたエリアＡ３であるため、ある程度強く当接しても板状弁４３が折れ曲がるように撓むことがない。また、エリアＡ３は、ほとんど撓まない、つまり振動しないので、板バネ４７が板状弁４３に与える付勢力が安定し、板状弁４３の動作が安定する。
なお、板バネ４７（４７１，４７２）のストッパ部材４６及び後記するリテーナ４８に挟持される部分での幅（図２におけるＸ方向の大きさ）は、ストッパ部材４６の幅及び後記するリテーナ４８の幅よりも小さい。 The leaf spring 47 fixed to the stopper member 46 in this manner abuts the plate valve 43 at the other end 471c. However, by inclining contact with the plate valve 43, the plate valve 43 is opened. As the degree increases, the contact position is displaced toward the base end portion 43a of the plate valve 43. Further, since the contact position is the area A3 reinforced by the bent portions 43d and 43d, the plate valve 43 will not be bent so as to be bent even if the contact is strong to some extent. Further, since the area A3 hardly bends, that is, does not vibrate, the urging force that the leaf spring 47 applies to the plate valve 43 is stabilized, and the operation of the plate valve 43 is stabilized.
The width (size in the X direction in FIG. 2) of the leaf spring 47 (471, 472) between the stopper member 46 and the retainer 48 described later is the width of the stopper member 46 and the retainer 48 described later. It is smaller than the width.

第１ばね４７１及び第２ばね４７２は、ストッパ部材４６の先端部４６ｃの弁座４２側の面に第１ばね４７１、第２ばね４７２の順に重ねられ、さらにリテーナ４８が重ねられた上でこれらが一体に固定されている。   The first spring 471 and the second spring 472 are stacked in the order of the first spring 471 and the second spring 472 on the surface of the distal end portion 46c of the stopper member 46 on the valve seat 42 side, and the retainer 48 is further stacked. Are fixed together.

リテーナ４８は、ストッパ部材４６の先端部４６ｃに相当する大きさの矩形の板である。リテーナ４８は、ストッパ部材４６との間で板バネ４７を挟む形で固定することにより、板バネ４７の固定点に応力が集中することを防止して、板バネ４７の耐久性を向上させている。また、リテーナ４８には、ストッパ部材４６の位置決め孔４６ｄ，４６ｄに対応する位置及び大きさで位置決め孔４８ａ，４８ａが形成されている。また、リテーナ４８は、板バネ４７より剛性が高く、溶接に耐えうる部材、すなわち板厚が厚い２ｍｍ程度の厚さの部材で構成するのが望ましい。   The retainer 48 is a rectangular plate having a size corresponding to the distal end portion 46 c of the stopper member 46. The retainer 48 is fixed in such a manner as to sandwich the leaf spring 47 with the stopper member 46, thereby preventing stress from concentrating on the fixing point of the leaf spring 47 and improving the durability of the leaf spring 47. Yes. The retainer 48 is formed with positioning holes 48a, 48a at positions and sizes corresponding to the positioning holes 46d, 46d of the stopper member 46. The retainer 48 is preferably composed of a member that has higher rigidity than the leaf spring 47 and can withstand welding, that is, a member having a thickness of about 2 mm, which is thick.

次に、板状弁４３、ストッパ部材４６、及び板バネ４７の固定方法について詳細に説明する。なお、図２及び図３において、太い破線で示した部分は、溶接をする範囲である。   Next, a method for fixing the plate valve 43, the stopper member 46, and the plate spring 47 will be described in detail. In FIGS. 2 and 3, the portion indicated by a thick broken line is a range to be welded.

まず、ストッパ部材４６に板バネ４７を固定するときには、ストッパ部材４６の先端部４６ｃに第２ばね４７２、第１ばね４７１、リテーナ４８を順に重ね合わせ、位置決め孔４６ｄ、４７２ｂ、４７１ｂ、４８ａがそれぞれ重なるように位置を調整する。この際、各位置決め孔４６ｄ、４７２ｂ、４７１ｂ、４８ａに合う太さのピンを差し込むと、位置決めが確実である。   First, when the leaf spring 47 is fixed to the stopper member 46, the second spring 472, the first spring 471, and the retainer 48 are sequentially stacked on the tip end portion 46c of the stopper member 46, and the positioning holes 46d, 472b, 471b, 48a are respectively provided. Adjust the position so that they overlap. At this time, if a pin having a thickness suitable for each of the positioning holes 46d, 472b, 471b, 48a is inserted, positioning is assured.

位置合わせができたならば、まず、ストッパ部材４６、第１ばね４７１、第２ばね４７２、リテーナ４８をストッパ部材４６の先端側の縁部（つまり、第１ばね４７１、第２ばね４７２の一端側の縁）で一体に溶接する。この溶接により、ストッパ部材４６、板バネ４７及びリテーナ４８は一応一体となり、位置決めは不要となる。   If the positioning is completed, first, the stopper member 46, the first spring 471, the second spring 472, and the retainer 48 are attached to the edge of the stopper member 46 on the front end side (that is, one end of the first spring 471 and the second spring 472). Weld together at the edges. By this welding, the stopper member 46, the leaf spring 47, and the retainer 48 are once integrated, and positioning is unnecessary.

次に、ストッパ部材４６とリテーナ４８を、ストッパ部材４６の先端側の縁部から所定範囲の両側縁部で溶接する。このとき、板バネ４７は、ストッパ部材４６及びリテーナ４８よりも幅が小さいので、溶接はなされない。従って、板バネ４７は、リテーナ４８とストッパ部材４６の先端部４６ｃに挟まれた形で固定される。   Next, the stopper member 46 and the retainer 48 are welded at both side edge portions within a predetermined range from the edge portion on the distal end side of the stopper member 46. At this time, since the leaf spring 47 is smaller in width than the stopper member 46 and the retainer 48, welding is not performed. Therefore, the leaf spring 47 is fixed in a form sandwiched between the retainer 48 and the distal end portion 46 c of the stopper member 46.

このように、薄い板材からなる板バネ４７をストッパ部材４６の先端部４６ｃの縁のみで位置合わせ及び仮押えをし、ストッパ部材４６とリテーナ４８に挟んで固定するので、板バネ４７を溶接するときに板バネ４７に穴を開けてしまったり、板バネ４７が歪んだりする不具合を起こすことがない。なお、これらの溶接は例えばアーク溶接やレーザ溶接を利用することができる。   In this manner, the plate spring 47 made of a thin plate material is positioned and temporarily pressed only by the edge of the tip end portion 46c of the stopper member 46, and is fixed by being sandwiched between the stopper member 46 and the retainer 48. Therefore, the plate spring 47 is welded. There is no problem that the leaf spring 47 is sometimes perforated or the leaf spring 47 is distorted. In addition, arc welding and laser welding can be utilized for these welding, for example.

次に、弁座４２に板状弁４３及びストッパ部材４６を固定するときには、弁座４２の基端部４２ａに板状弁４３、ストッパ部材４６を順に重ね合わせ、位置決め孔４２ｂ、４３ｂ、４６ｂがそれぞれ重なるように位置を調整する。この際、各位置決め孔４２ｂ、４３ｂ、４６ｂに合う太さのピンを差し込むと、位置決めが確実である。   Next, when the plate-like valve 43 and the stopper member 46 are fixed to the valve seat 42, the plate-like valve 43 and the stopper member 46 are sequentially stacked on the base end portion 42a of the valve seat 42, and the positioning holes 42b, 43b, 46b are formed. Adjust the position so that they overlap each other. At this time, if a pin having a thickness suitable for each positioning hole 42b, 43b, 46b is inserted, positioning is assured.

位置合わせができたならば、まず、弁座４２、板状弁４３、ストッパ部材４６の基端側の縁部を一体に溶接する。この溶接により、弁座４２、板状弁４３、及びストッパ部材４６は一応一体となり、位置決めは不要となる。   When the alignment is completed, first, the base end side edge of the valve seat 42, the plate valve 43, and the stopper member 46 is integrally welded. By this welding, the valve seat 42, the plate-like valve 43, and the stopper member 46 are once integrated, and positioning is unnecessary.

次に、弁座４２とストッパ部材４６を、ストッパ部材４６の基端側の縁部から所定範囲の両側縁部で溶接する。このとき、板状弁４３は、弁座４２及びストッパ部材４６よりも幅が小さいので、溶接はなされない。従って、板状弁４３は、弁座４２とストッパ部材４６の基端部４６ａに挟まれた形で固定される。   Next, the valve seat 42 and the stopper member 46 are welded at both side edge portions within a predetermined range from the edge portion on the proximal end side of the stopper member 46. At this time, since the plate-like valve 43 has a smaller width than the valve seat 42 and the stopper member 46, welding is not performed. Therefore, the plate valve 43 is fixed in a form sandwiched between the valve seat 42 and the base end portion 46 a of the stopper member 46.

このように、薄い板材からなる板状弁４３を基端４３ｅの縁のみで位置合わせ及び仮押えをし、弁座４２とストッパ部材４６に挟んで固定するので、板状弁４３を溶接するときに板状弁３４に穴を開けてしまったり、板状弁４３が歪んだりする不具合を起こすことがない。なお、これらの溶接は例えばアーク溶接やレーザ溶接を利用することができる。   In this way, the plate-like valve 43 made of a thin plate material is positioned and temporarily pressed only by the edge of the base end 43e, and is fixed by being sandwiched between the valve seat 42 and the stopper member 46. Therefore, when the plate-like valve 43 is welded Therefore, there is no problem that the plate valve 34 is perforated or the plate valve 43 is distorted. In addition, arc welding and laser welding can be utilized for these welding, for example.

以上のように、板状弁４３、ストッパ部材４６、及び板バネ４７の固定の際に溶接を用いることにより、ボルトを使う必要が無く、またタッピングをする必要も無く、さらに、細かいボルトを複数締め付ける工数も省略できることから、バルブ装置の生産コストを下げることができる。また、バルブ装置を消音器１の第１セパレータ１４へ固定する際にも弁座４２の縁で溶接するようにすれば、ボルトを使用せずに済み、さらに生産コストを下げることができる。   As described above, by using welding when fixing the plate valve 43, the stopper member 46, and the leaf spring 47, there is no need to use a bolt, and there is no need for tapping, and a plurality of fine bolts are provided. Since the number of steps for tightening can be omitted, the production cost of the valve device can be reduced. Further, when the valve device is fixed to the first separator 14 of the silencer 1, if welding is performed at the edge of the valve seat 42, it is not necessary to use a bolt, and the production cost can be further reduced.

次に、以上のようなバルブ装置４の動作について説明する。エンジンの回転数が低いうちは、第２消音室３２内の排気圧は低いので、板状弁４３は撓むことなく弁座４２と接することにより、バルブ装置４は閉じている。   Next, the operation of the valve device 4 as described above will be described. Since the exhaust pressure in the second silencing chamber 32 is low while the engine speed is low, the valve device 4 is closed by contacting the valve seat 42 without the plate valve 43 being bent.

エンジンの回転数が上昇して、第２消音室３２内の排気圧が所定圧に上昇すると、板状弁４３に掛かる圧力（力）が高くなって、板状弁４３が撓み始める。このとき、エンジンの排気圧には脈動があるので、板状弁４３は振動しようとするが、本実施形態の板状弁４３は、折曲げ部４３ｄ，４３ｄが形成されているので、剛性が十分に高く、共振が起こりにくい。そして、板状弁４３がある量だけ撓むと、板バネ４７も撓んで、板バネ４７と板状弁４３の当接位置が板状弁４３の基端側へ変位する。このとき、板バネ４７の付勢力の増加はさほどではないが、当接位置の変位によって、板バネ４７が板状弁４３を回転させるモーメントの減少は比較的大きいので、図４の２点鎖線で示したように、板状弁４３は一気に大きく開く。   When the engine speed increases and the exhaust pressure in the second silencing chamber 32 rises to a predetermined pressure, the pressure (force) applied to the plate valve 43 increases and the plate valve 43 begins to bend. At this time, since the exhaust pressure of the engine has a pulsation, the plate-like valve 43 tries to vibrate, but the plate-like valve 43 of the present embodiment has the bent portions 43d and 43d, so that the rigidity is high. High enough to prevent resonance. When the plate-like valve 43 is bent by a certain amount, the plate spring 47 is also bent, and the contact position between the plate spring 47 and the plate-like valve 43 is displaced to the proximal end side of the plate-like valve 43. At this time, although the increase in the urging force of the leaf spring 47 is not so large, the decrease in the moment that the leaf spring 47 rotates the leaf valve 43 due to the displacement of the contact position is relatively large. As shown by, the plate-like valve 43 opens greatly at a stretch.

そして、再びエンジンの回転数が低くなると、板状弁４３の撓み量が小さくなって、ある撓み量以下になると、板バネ４７の板状弁４３との当接位置が板状弁４３の先端側へ変位してくるので、板バネ４７が板状弁４３を回転させるモーメントが大きくなり、板状弁４３を一気に閉じる。この際にも、開くときと同様に、折曲げ部４３ｄ，４３ｄのため共振が起こりにくく、板バネ４７が２枚重ねで構成されているので、共振が起こりにくい。   When the engine speed decreases again, the amount of deflection of the plate valve 43 decreases, and when the amount of deflection is less than a certain amount of deflection, the contact position of the plate spring 47 with the plate valve 43 is the tip of the plate valve 43. Since the plate spring 47 is displaced to the side, the moment that the plate spring 47 rotates the plate valve 43 increases, and the plate valve 43 is closed at once. Also at this time, as in the case of opening, resonance is unlikely to occur due to the bent portions 43d and 43d, and since the leaf springs 47 are constituted by two layers, resonance is unlikely to occur.

また、このように高い振動の中で使われていても、バルブ装置４を構成する各部品は溶接により固定されているので、振動によりボルトが外れるという心配もない。さらに、この溶接の際には、前記したように板状弁４３や板バネ４７を歪ませることなく固定しているのでバルブ装置４の安定した動作を実現できる。   Even when used in such high vibrations, the components constituting the valve device 4 are fixed by welding, so there is no concern that the bolts will come off due to vibrations. Further, during the welding, the plate valve 43 and the leaf spring 47 are fixed without distortion as described above, so that stable operation of the valve device 4 can be realized.

以上、本発明の実施形態について説明したが、本発明は前記した実施形態に限定されることなく適宜変更して実施することが可能である。
例えば、実施形態においては、板状弁４３が弁座４２の表面に接触してバルブを閉じるタイプのバルブ装置４について説明したが、板状弁４３及び板バネ４７の自然状態で板状弁４３の先端及び両側縁部を基台の弁孔内にまで入り込ませ、弁孔の内壁と板状弁４３の先端及び両側縁部とで弁孔を閉じるタイプ、いわば基台を板状弁のハウジングにしたタイプでも同様に本発明を適用することができる。また、この場合においては、板状弁４３の折曲げ部４３ｄは、ストッパ部材４６とは逆側、すなわち図３等において下向きに折り曲げても構わない。
また、バルブ装置４の各部品を溶接で固定することなく、従来から一般的に行われているようにボルトにより固定するのでも構わない。 Although the embodiments of the present invention have been described above, the present invention is not limited to the above-described embodiments, and can be appropriately modified and implemented.
For example, in the embodiment, the valve device 4 of the type in which the plate valve 43 contacts the surface of the valve seat 42 and closes the valve has been described, but the plate valve 43 and the plate spring 47 are in a natural state. The tip and both side edges of the valve are inserted into the valve hole of the base, and the valve hole is closed by the inner wall of the valve hole and the tip and both side edges of the plate valve 43, so to speak, the base is the plate valve housing. The present invention can be similarly applied to the types of the above. In this case, the bent portion 43d of the plate valve 43 may be bent on the side opposite to the stopper member 46, that is, downward in FIG.
In addition, the parts of the valve device 4 may be fixed by bolts as is generally done conventionally without being fixed by welding.

本発明のバルブ装置が適用される消音器の一例である。It is an example of the silencer to which the valve device of the present invention is applied. 実施形態に係るバルブ装置の斜視図である。It is a perspective view of the valve device concerning an embodiment. 実施形態に係るバルブ装置の分解斜視図である。It is a disassembled perspective view of the valve apparatus which concerns on embodiment. 図２の４−４線断面図である。FIG. 4 is a cross-sectional view taken along line 4-4 of FIG.

符号の説明Explanation of symbols

１ 消音器
４ バルブ装置
１４ａ 開口部
４１ 弁孔
４２ 弁座（基台）
４３ 板状弁
４３ａ 基端部
４３ｄ 折曲げ部
４７ 板バネ DESCRIPTION OF SYMBOLS 1 Silencer 4 Valve apparatus 14a Opening part 41 Valve hole 42 Valve seat (base)
43 Plate Valve 43a Base End 43d Bend 47 Leaf Spring

Claims (2)

消音器内の排気ガスのバイパス経路を、排気圧が所定圧に上昇したときに開く消音器用バルブ装置であって、
排気ガスが流通する弁孔を有する基台と、
前記弁孔を開閉し、前記基台に基端部が固定された板状弁と、
前記板状弁の表面に先端が当接して前記板状弁を閉弁方向に付勢する板バネ部材と、
基端側において前記基台との間で前記板状弁を挟んで固定するとともに、先端側においてリテーナとの間で前記板バネ部材を挟んで固定するストッパ部材と、を備え、
前記板バネ部材は、前記ストッパ部材及び前記リテーナよりも幅が小さく、
前記板バネ部材と前記リテーナは、それぞれの先端側の縁部において前記ストッパ部材に溶接されているとともに、前記先端側の縁部から所定範囲の両側縁部において前記リテーナが前記ストッパ部材にのみ溶接されていることを特徴とする消音器用バルブ装置。 A silencer valve device that opens the exhaust gas bypass path in the silencer when the exhaust pressure rises to a predetermined pressure,
A base having a valve hole through which exhaust gas flows;
A plate-shaped valve that opens and closes the valve hole and has a base end fixed to the base;
A leaf spring member whose tip is in contact with the surface of the plate valve and biases the plate valve in the valve closing direction;
A stopper member that fixes the plate-shaped valve between the base and the base on the base end side, and fixes the plate spring member between the retainer on the tip side, and
The leaf spring member is smaller in width than the stopper member and the retainer,
The leaf spring member and the retainer are welded to the stopper member at the respective leading edge portions, and the retainer is welded only to the stopper member at both side edge portions within a predetermined range from the leading edge portion. A valve device for a silencer, characterized in that 前記板バネ部材は、前記板状弁の撓み量の増加につれて板状弁との当接位置が板状弁の基端部側へ変位するように板状弁に対し傾斜して配置されるとともに、前記先端が曲面状に形成され、この曲面状に形成された部分で前記板状弁の表面に当接することを特徴とする請求項１に記載の消音器用バルブ装置。   The leaf spring member is disposed to be inclined with respect to the plate valve so that the contact position with the plate valve is displaced toward the proximal end side of the plate valve as the amount of deflection of the plate valve increases. 2. The silencer valve device according to claim 1, wherein the tip is formed in a curved surface shape, and a portion formed in the curved surface contacts the surface of the plate valve.
JP2004117205A 2004-04-12 2004-04-12 Valve unit for silencer Expired - Fee Related JP4157490B2 (en)

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KR101290212B1 (en) * 2007-01-26 2013-07-31 포레시아 씨스뗌 데샤쁘망 Valve for a motor vehicle exhaust silencer and silencer comprising a valve of this type

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