JP6004639B2 - Intake device for internal combustion engine - Google Patents

Intake device for internal combustion engine Download PDF

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JP6004639B2
JP6004639B2 JP2011273979A JP2011273979A JP6004639B2 JP 6004639 B2 JP6004639 B2 JP 6004639B2 JP 2011273979 A JP2011273979 A JP 2011273979A JP 2011273979 A JP2011273979 A JP 2011273979A JP 6004639 B2 JP6004639 B2 JP 6004639B2
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volume chamber
cover
combustion engine
internal combustion
intake device
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JP2013124599A (en
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福本　一朗
一朗 福本
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Mahle Filter Systems Japan Corp
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Mahle Filter Systems Japan Corp
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Priority to JP2011273979A priority Critical patent/JP6004639B2/en
Priority to PCT/JP2012/081602 priority patent/WO2013089010A1/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M35/00—Combustion-air cleaners, air intakes, intake silencers, or induction systems specially adapted for, or arranged on, internal-combustion engines
    • F02M35/12—Intake silencers ; Sound modulation, transmission or amplification
    • F02M35/1205—Flow throttling or guiding
    • F02M35/1238—Flow throttling or guiding by using secondary connections to the ambient, e.g. covered by a membrane or a porous member
    • 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
    • F01N13/00—Exhaust or silencing apparatus characterised by constructional features ; Exhaust or silencing apparatus, or parts thereof, having pertinent characteristics not provided for in, or of interest apart from, groups F01N1/00 - F01N5/00, F01N9/00, F01N11/00
    • F01N13/007—Apparatus used as intake or exhaust silencer
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M35/00—Combustion-air cleaners, air intakes, intake silencers, or induction systems specially adapted for, or arranged on, internal-combustion engines
    • F02M35/12—Intake silencers ; Sound modulation, transmission or amplification
    • F02M35/1255—Intake silencers ; Sound modulation, transmission or amplification using resonance
    • F02M35/1261—Helmholtz resonators
    • 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
    • F01N1/02—Silencing apparatus characterised by method of silencing by using resonance
    • F01N1/023—Helmholtz resonators
    • 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
    • F01N1/161—Silencing apparatus characterised by method of silencing by using movable parts for adjusting resonance or dead chambers or passages to resonance or dead chambers
    • 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
    • F01N1/22—Silencing apparatus characterised by method of silencing by using movable parts the parts being resilient walls

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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)
  • Characterised By The Charging Evacuation (AREA)

Description

本発明は、消音室（レゾネータ）としてヘルムホルツ型の共鳴室を備えた内燃機関の吸気装置に関する。   The present invention relates to an intake device for an internal combustion engine having a Helmholtz-type resonance chamber as a silencer (resonator).

従来、この種の内燃機関の吸気装置として、例えば特許文献１に記載されているように、吸気系の消音のためにヘルムホルツ型の共鳴室として機能する容積室の容積を積極的に可変にしたものが提案されている。   Conventionally, as an intake device of this type of internal combustion engine, for example, as described in Patent Document 1, the volume of a volume chamber functioning as a Helmholtz-type resonance chamber has been actively made variable in order to mute the intake system. Things have been proposed.

特開２００９−３６１８５号公報JP 2009-36185 A

しかしながら、特許文献１に記載された技術では、いわゆるハードタイプの容積室の内部に有底円筒状のベローズ状の弾性部材を配置するとともに、その弾性部材の内部に負圧を導入して、負圧の度合いに応じて当該弾性部材を伸縮変形させることで容積室の容積を変化させるようにしているため、容積室の弾性特性および容積室を形成している材料特性が本来の消音効果あるいは共鳴過給効果として何ら有効活用されておらず、なおも改善の余地を残している。また、上記のように容積室の容積を積極的に可変とするためには、負圧導入のための配管やモータ等のアクチュエータが必要となり、装置全体の大型化と複雑化が余儀なくされる。 However, in the technique described in Patent Document 1, a bottomed cylindrical bellows-like elastic member is disposed inside a so-called hard type volume chamber, and a negative pressure is introduced into the elastic member, thereby generating a negative pressure. Since the volume of the volume chamber is changed by expanding and contracting the elastic member according to the degree of pressure, the elastic characteristics of the volume chamber and the characteristics of the material forming the volume chamber are the original silencing effect or resonance. It is not effectively utilized as a supercharging effect, and there is still room for improvement. Further, in order to actively vary the volume of the volume chamber in the Hare yo above, actuator piping and motor or the like for the negative pressure introduction is required, it is forced upsizing and complication of the entire system .

本発明はこのような課題に着目してなされたものであり、容積室の弾性特性や容積室を形成している材料そのものの特性の有効活用によって消音効果あるいは共鳴過給効果が得られるようにし、もって簡単な構造で所期の目的を達成できるようにした内燃機関の吸気装置を提供するものである。   The present invention has been made paying attention to such problems, and it is possible to obtain a silencing effect or a resonance supercharging effect by effectively utilizing the elastic characteristics of the volume chamber and the characteristics of the material itself forming the volume chamber. Thus, the present invention provides an intake device for an internal combustion engine that can achieve an intended purpose with a simple structure.

本発明は、消音のためのヘルムホルツ型の共鳴室を備えた内燃機関の吸気装置において、一端が吸気管に接続された導入管と、上記導入管の他端に接続されて当該導入管よりも大径の共鳴室として機能する弾性変形可能で且つ密閉された容積室と、この容積室を同心状に覆う密閉式のカバーと、上記カバーの一部に設けられ導入管径よりも小さな極小径の複数の穴部と、を備えていることを特徴とする。 The present invention relates to an intake device for an internal combustion engine having a Helmholtz-type resonance chamber for silencing, and an introduction pipe having one end connected to the intake pipe, and an other end of the introduction pipe connected to the other end of the introduction pipe. An elastically deformable and hermetically sealed volume chamber that functions as a large-diameter resonance chamber, a hermetically sealed cover that concentrically covers the volume chamber, and a minimum diameter that is provided in part of the cover and is smaller than the diameter of the introduction tube And a plurality of holes.

この場合において、容積室の弾性特性の制御や容積室からの放射音の制御を積極的に行うためには、請求項２に記載のように、カバーの穴部に相当する位置に、カバーの内圧が外部圧力よりも大きい場合のみ上記穴部を開放する逆止弁タイプの弁体を備えていることが望ましい。この弁体としては例えばグロメットタイプあるいはリード弁タイプ等の比較的簡単なものでも所期の目的を達成できる。   In this case, in order to positively control the elastic characteristics of the volume chamber and the radiated sound from the volume chamber, as described in claim 2, at a position corresponding to the hole of the cover, It is desirable to provide a check valve type valve element that opens the hole only when the internal pressure is greater than the external pressure. As the valve body, for example, a relatively simple one such as a grommet type or a reed valve type can achieve the intended purpose.

また、容積室の弾性変形を一段と容易に且つ安定化させるためには、請求項３に記載のように、容積室は少なくとも筒状胴部がカバーよりも軟質の可撓性材料にて形成されたベローズ状のものとなっているとともに、全体として有底円筒状のものであることが望ましい。   In order to make the elastic deformation of the volume chamber easier and more stable, as described in claim 3, the volume chamber is formed of a flexible material in which at least the cylindrical body portion is softer than the cover. It is desirable that it is a bellows-like one and has a bottomed cylindrical shape as a whole.

より具体的には、請求項４に記載のように、容積室およびカバーは共に導入管と同心状のものであるとともに、上記カバーは容積室と相似形をなす有底円筒状のものであり、その底壁部に相当する位置に穴部および弁体を設けてあることが望ましい。   More specifically, as described in claim 4, the volume chamber and the cover are both concentric with the introduction pipe, and the cover has a bottomed cylindrical shape similar to the volume chamber. It is desirable that a hole and a valve body are provided at a position corresponding to the bottom wall.

さらに、請求項５に記載のように、開閉弁を有しない穴部が、吸気管に対する導入管の接続位置とは異なる位置にて吸気管に接続されていても良い。   Further, as described in claim 5, the hole portion having no on-off valve may be connected to the intake pipe at a position different from the connection position of the introduction pipe to the intake pipe.

したがって、少なくとも請求項１に記載の発明では、導入管の断面積と長さおよび容積室の容積で決まるヘルムホルツ型の共鳴室効果として例えば特定の共鳴周波数（例えば、ｆ１とする。）が得られるほか、ベローズ部を含む弾性変形可能な容積室の形状と当該容積室の材質とで決まる別の共鳴周波数（例えば、ｆ２とする。）が得られることになる。その上、ベローズ部を含む弾性変形可能な容積室によるいわゆるダンパー効果が期待でき、特に弾性変形可能な容積室による構造的な吸気音減衰効果とともに、容積室を形成している材料そのものによる材質的な損失効果が得られ、それらの相乗効果として顕著な消音効果と共鳴過給効果が得られることになる。   Therefore, in at least the first aspect of the invention, for example, a specific resonance frequency (for example, f1) is obtained as the Helmholtz type resonance chamber effect determined by the cross-sectional area and length of the introduction tube and the volume of the volume chamber. In addition, another resonance frequency (for example, f2) determined by the shape of the elastically deformable volume chamber including the bellows portion and the material of the volume chamber is obtained. In addition, a so-called damper effect can be expected due to the elastically deformable volume chamber including the bellows part, and in particular, the material that forms the volume chamber itself as well as the structural intake sound attenuation effect due to the elastically deformable volume chamber. As a synergistic effect, a remarkable silencing effect and a resonance supercharging effect are obtained.

本発明によれば、容積室を積極的に弾性変形させるための手段を必要としないため、小型で且つ簡単な構造のもとで、互いに異なる複数の共鳴周波数による従来以上の消音効果と共鳴過給効果が得られる。   According to the present invention, since a means for positively elastically deforming the volume chamber is not required, it is possible to achieve a more effective silencing effect and resonance excess due to a plurality of different resonance frequencies in a small and simple structure. A pay effect is obtained.

また、請求項２に記載の発明によれば、導入管の断面積と長さおよび容積室の容積で決まる特定の共鳴周波数とは異なる任意の音圧モードでの減衰効果を持たせることが可能となる。   According to the second aspect of the present invention, it is possible to provide an attenuation effect in an arbitrary sound pressure mode different from a specific resonance frequency determined by the cross-sectional area and length of the introduction pipe and the volume of the volume chamber. It becomes.

請求項３に記載の発明によれば、容積室が実質的にベローズ状のものであるため、容積室の弾性変形が安定して行われる利点がある。   According to the invention described in claim 3, since the volume chamber is substantially bellows-shaped, there is an advantage that the elastic deformation of the volume chamber is stably performed.

請求項４に記載の発明によれば、吸気の圧力変動に応じ容積室が連動して伸縮する際の圧力差または吸気の所定の周波数に応じて弁体が開くことで、容積室の弾性特性や放射音特性を任意に設定することができる。   According to the fourth aspect of the present invention, the valve body opens according to the pressure difference when the volume chamber expands and contracts in response to the pressure fluctuation of the intake air or the predetermined frequency of the intake air, so that the elastic characteristics of the volume chamber And radiated sound characteristics can be set arbitrarily.

さらに、請求項５に記載の発明によれば、導入管の断面積と長さおよび容積室の容積で決まる特定の共鳴周波数とは異なる任意の音圧モードでの減衰効果を持たせることができる利点がある。   Further, according to the invention described in claim 5, it is possible to have an attenuation effect in an arbitrary sound pressure mode different from a specific resonance frequency determined by the cross-sectional area and length of the introduction pipe and the volume of the volume chamber. There are advantages.

本発明に係る内燃機関の吸気装置を実施するためのより具体的な第１の形態を示す図で、要部の拡大説明図。It is a figure which shows the more concrete 1st form for implementing the intake device of the internal combustion engine which concerns on this invention, and is expanded explanatory drawing of the principal part. 図１をモデル化した説明図。Explanatory drawing which modeled FIG. 消音効果を評価するためのｎ次の吸気騒音の内燃機関回転数−音圧レベル特性を示す図。The figure which shows the internal combustion engine rotation speed-sound pressure level characteristic of the nth order intake noise for evaluating a silencing effect. 消音効果を評価するための２ｎ次の吸気騒音の内燃機関回転数−音圧レベル特性を示す図。The figure which shows the internal-combustion-engine speed-sound-pressure level characteristic of the 2n-order intake noise for evaluating a silencing effect. 共鳴過給効果を評価するための内燃機関回転数−トルク特性を示す図。The figure which shows the internal combustion engine speed-torque characteristic for evaluating the resonance supercharging effect. 弾性変形可能な容積室の形状と材質に基づく周波数−損失係数（％）特性を示す図。The figure which shows the frequency-loss-factor (%) characteristic based on the shape and material of a volume chamber which can be elastically deformed. 弾性変形可能な容積室の形状と材質に基づく周波数−減衰比（％）特性を示す図。The figure which shows the frequency-damping ratio (%) characteristic based on the shape and material of a volume chamber which can be elastically deformed. 本発明に係る内燃機関の吸気装置を実施するためのより具体的な第２の形態を示す図で、（Ａ）は要部の拡大説明図、（Ｂ）は同図（Ａ）のＣ部拡大図。It is a figure which shows the more concrete 2nd form for implementing the intake device of the internal combustion engine which concerns on this invention, (A) is expanded explanatory drawing of the principal part, (B) is C section of the same figure (A). Enlarged view. 本発明に係る内燃機関の吸気装置を実施するためのより具体的な第３の形態を示す図で、（Ａ）は要部の拡大説明図、（Ｂ）は同図（Ａ）のＤ部拡大図。It is a figure which shows the more concrete 3rd form for implementing the intake device of the internal combustion engine which concerns on this invention, (A) is expanded explanatory drawing of the principal part, (B) is D section of the same figure (A). Enlarged view. 本発明に係る内燃機関の吸気装置を実施するためのより具体的な第４の形態を示す図で、（Ａ）は要部の拡大説明図、（Ｂ）は同図（Ａ）のＥ部拡大図。It is a figure which shows the more concrete 4th form for implementing the intake device of the internal combustion engine which concerns on this invention, (A) is expanded explanatory drawing of the principal part, (B) is E part of the same figure (A). Enlarged view. 本発明に係る内燃機関の吸気装置を実施するためのより具体的な第５の形態を示す図で、要部の拡大説明図。It is a figure which shows the more concrete 5th form for implementing the intake device of the internal combustion engine which concerns on this invention, and is expanded explanatory drawing of the principal part.

図１は本発明に係る内燃機関の吸気装置を実施するためのより具体的な第１の形態を示す図である。   FIG. 1 is a diagram showing a more specific first embodiment for implementing an intake device for an internal combustion engine according to the present invention.

図１に示すように、所定の断面積を有する樹脂製の吸気管１の途中には当該吸気管１よりも断面積の小さな同じく樹脂製の導入管２の一端が接続されていて、吸気管１の内部空間と連通している。また、導入管２の他端には当該導入管２と同心状に樹脂製のエンドピース３が挿入・接続されている。このエンドピース３は、それぞれに別ピースとして形成されたフランジ部４ａ付きのソケット部４とカバー５とを突き合わせるとともに、それら両者の間にベローズ状の容積室６における根元部のフランジ部６ａを挟み込んで、容積室６をカバー５と同心状に固定支持させたものである。そして、容積室６およびカバー５は共にその断面積は導入管２の断面積よりも大きく設定されているとともに、密閉式の容積室６は導入管２に連通してはいても、カバー５の内部空間と容積室６の内部空間とは隔離されている。
As shown in FIG. 1, one end of a resin introduction pipe 2 having a smaller cross-sectional area than that of the intake pipe 1 is connected to the midway of the resin intake pipe 1 having a predetermined cross-sectional area. 1 communicates with the interior space. A resin end piece 3 is inserted and connected to the other end of the introduction tube 2 concentrically with the introduction tube 2. The end piece 3 abuts the cover portion 5 and the socket portion 4 with the flange portion 4a formed as separate pieces, and the flange portion 6a at the root portion of the bellows-shaped volume chamber 6 is interposed therebetween. The volume chamber 6 is fixed and supported concentrically with the cover 5 by being sandwiched. The volume chamber 6 and the cover 5 are both set to have a cross-sectional area larger than the cross-sectional area of the introduction pipe 2, and the sealed volume chamber 6 communicates with the introduction pipe 2. The internal space and the internal space of the volume chamber 6 are isolated.

ここで、ソケット部４およびカバー５が樹脂製のものであるのに対して、容積室６はカバー５等の材質よりも軟質の可撓性材料、例えば熱可塑性エラストマーあるいは熱可塑性エラストマーと熱可塑性樹脂との複合材にて形成されていて、軸心方向に弾性変形可能、より具体的には軸心方向に伸縮変形可能となっている。すなわち、図１から明らかなように、容積室６は筒状胴部６ｂがベローズ状に形成された有底円筒状のもので、導入管２を介して吸気管１に連通していることで図２のようなヘルムホルツ型の共鳴室として機能するとともに、容積室６はそれと相似形をなす一回り大きな密閉式のカバー５にて包囲または覆われていることになる。   Here, while the socket part 4 and the cover 5 are made of resin, the volume chamber 6 is a flexible material softer than the material of the cover 5 or the like, for example, a thermoplastic elastomer or a thermoplastic elastomer and a thermoplastic. It is formed of a composite material with resin and can be elastically deformed in the axial direction, more specifically, can be expanded and contracted in the axial direction. That is, as apparent from FIG. 1, the volume chamber 6 is a bottomed cylindrical shape in which the cylindrical body portion 6 b is formed in a bellows shape, and communicates with the intake pipe 1 through the introduction pipe 2. While functioning as a Helmholtz-type resonance chamber as shown in FIG. 2, the volume chamber 6 is surrounded or covered by a slightly larger sealed cover 5 having a similar shape.

そして、カバー５のうち導入管２とは反対側の部位、より具体的にはカバー５における底壁部５ａの中央部には容積室６やカバー５の直径に比べて極小径の穴部として単一の円形状の***７が形成されている。この***７はカバー５の内部空間を大気開放して、容積室６の弾性変形を安定化させるとともに、放射音制御のために設けられる。それ故に、所期の目的さえ達成できれば、***７は必ずしもカバー５の底壁部５ａに設ける必要はない。また、***７はスリット状のものであっても良く、さらに二つ以上設けても良い。   A portion of the cover 5 opposite to the introduction pipe 2, more specifically, a hole portion having a minimum diameter compared with the diameter of the volume chamber 6 or the cover 5 in the center portion of the bottom wall portion 5 a of the cover 5. A single circular small hole 7 is formed. The small holes 7 are provided for opening the internal space of the cover 5 to the atmosphere to stabilize the elastic deformation of the volume chamber 6 and for controlling radiated sound. Therefore, the small hole 7 is not necessarily provided in the bottom wall portion 5a of the cover 5 as long as the intended purpose can be achieved. Further, the small holes 7 may be slit-shaped, or two or more.

したがって、このような吸気装置によれば、導入管２の断面積Ｓと長さＬおよび容積室６の容積Ｖで決まるヘルムホルツ型の共鳴室効果として例えば特定の共鳴周波数ｆ１が得られるほか、筒状胴部６ｂを含む弾性変形可能な容積室６の形状と当該容積室６の材質とで決まる別の共鳴周波数ｆ２が得られることになる。しかも、筒状胴部６ｂを含む弾性変形可能な容積室６によるいわゆるダンパー効果が期待でき、特に弾性変形可能な容積室６による構造的な吸気音減衰効果とともに、容積室６を形成している材料そのものによる材質的な損失効果が得られ、それらの相乗効果として顕著な消音効果と共鳴過給効果が得られることになる。   Therefore, according to such an intake device, for example, a specific resonance frequency f1 can be obtained as a Helmholtz type resonance chamber effect determined by the cross-sectional area S and length L of the introduction pipe 2 and the volume V of the volume chamber 6, and Another resonance frequency f2 determined by the shape of the elastically deformable volume chamber 6 including the cylindrical body 6b and the material of the volume chamber 6 is obtained. In addition, a so-called damper effect can be expected by the elastically deformable volume chamber 6 including the cylindrical body 6b, and the volume chamber 6 is formed together with a structural intake sound attenuation effect by the elastically deformable volume chamber 6. A material-like loss effect by the material itself is obtained, and a remarkable silencing effect and a resonance supercharging effect are obtained as a synergistic effect thereof.

より詳しくは、ヘルムホルツ型の共鳴室効果として導入管２の断面積Ｓと長さＬおよび容積室６の容積Ｖで決まる特定の共鳴周波数ｆ１が得られることは先に述べたとおりであって、これとは別の特定の共鳴周波数ｆ２が筒状胴部６ｂを含む弾性変形可能な容積室６の形状と当該容積室６の材質とで決まる固有振動数から得られることになる。そして、容積室６は先に述べたようにヘルムホルツ型の共鳴室とみなし得ることから、導入管２がマス、弾性変形可能な容積室６がバネとなるマス−バネモデルと理解することができる。これにより、容積室６を構成する材料とその容積室６の形状とから決まる損失係数と減衰比が上記マス−バネモデルにおけるバネに作用することで、異なる共鳴周波数ｆ１およびｆ２によるそれぞれの消音効果と共鳴過給効果に加えて、筒状胴部６ｂを含む弾性変形可能な容積室６の形状と当該容積室６の材質とで決まるいわゆるダンパー効果によってさらなる消音効果と共鳴過給効果が期待できるようになる。   More specifically, as described above, the Helmholtz-type resonance chamber effect is that a specific resonance frequency f1 determined by the cross-sectional area S and length L of the introduction tube 2 and the volume V of the volume chamber 6 is obtained. Another specific resonance frequency f2 is obtained from the natural frequency determined by the shape of the elastically deformable volume chamber 6 including the cylindrical body 6b and the material of the volume chamber 6. Since the volume chamber 6 can be regarded as a Helmholtz type resonance chamber as described above, it can be understood as a mass-spring model in which the introduction tube 2 is a mass and the elastically deformable volume chamber 6 is a spring. As a result, the loss coefficient and the damping ratio determined from the material constituting the volume chamber 6 and the shape of the volume chamber 6 act on the spring in the mass-spring model, thereby reducing the respective silencing effects due to the different resonance frequencies f1 and f2. In addition to the resonance supercharging effect, a further silencing effect and a resonance supercharging effect can be expected by a so-called damper effect determined by the shape of the elastically deformable volume chamber 6 including the cylindrical body 6b and the material of the volume chamber 6. become.

図３はｎ次の吸気騒音の消音効果について、図４は２ｎ次の吸気騒音の消音効果について、それぞれ回転数（ｒｐｍ）−音圧レベル（ｄＢ）特性をもって上記第１の形態と従来構造とを比較したものである。なお、従来構造は上記弾性変形可能な容積室６と同じ容積のヘルムホルツ型の共鳴室とした。   FIG. 3 shows the silencing effect of the n-th order intake noise, and FIG. 4 shows the silencing effect of the 2n-order intake noise, with the above-mentioned first embodiment and the conventional structure having the rotational speed (rpm) -sound pressure level (dB) characteristics. Is a comparison. The conventional structure is a Helmholtz resonance chamber having the same volume as the elastically deformable volume chamber 6.

また、図５は上記吸気騒音の共鳴過給効果について、回転数（ｒｐｍ）−トルク特性をもって上記第１の形態と従来構造とを比較したものである。   FIG. 5 shows a comparison between the first embodiment and the conventional structure with respect to the resonance supercharging effect of the intake noise with a rotational speed (rpm) -torque characteristic.

さらに、図６は上記弾性変形可能な容積室６の構造的特徴および材質に基づく周波数−損失係数（％）特性を、図７は同じく周波数−減衰比（％）特性をそれぞれ示している。   Further, FIG. 6 shows a frequency-loss coefficient (%) characteristic based on the structural characteristics and materials of the elastically deformable volume chamber 6, and FIG. 7 shows a frequency-damping ratio (%) characteristic.

図３，４から明らかなように、図６，７の周波数−損失係数（％）特性および周波数−減衰比（％）との相乗効果によって、内燃機関の特定の回転数域において上記第１の形態による吸気騒音の消音効果が顕著に表れている。   As apparent from FIGS. 3 and 4, the first and second frequencies in the specific engine speed range of the internal combustion engine are obtained by the synergistic effect of the frequency-loss factor (%) characteristics and the frequency-damping ratio (%) in FIGS. The silencing effect of the intake noise depending on the form is prominent.

同様に、図５から明らかなように、内燃機関の特定の回転数域において上記第１の形態による吸気騒音の共鳴過給効果が顕著に表れている。   Similarly, as apparent from FIG. 5, the resonance supercharging effect of the intake noise according to the first embodiment is prominent in a specific rotational speed range of the internal combustion engine.

図８は本発明に係る内燃機関の吸気装置を実施するためのより具体的な第２の形態を示す図であり、図１と共通する部分には同一符号を付してある。   FIG. 8 is a view showing a more specific second embodiment for implementing the intake device for an internal combustion engine according to the present invention, and the same reference numerals are given to the portions common to FIG.

この第２の形態では、カバー５の底壁部５ａに形成された***７に、通気性および通水性を有するフィルター８を装着したもので、先の第１の形態と同様の効果に加えて、例えばカバー５内への異物の侵入を未然に防止できる利点がある。   In the second embodiment, a small hole 7 formed in the bottom wall portion 5a of the cover 5 is provided with a filter 8 having air permeability and water permeability. In addition to the same effect as the first embodiment, For example, there is an advantage that foreign matter can be prevented from entering the cover 5 beforehand.

図９の（Ａ），（Ｂ）は本発明に係る内燃機関の吸気装置を実施するためのより具体的な第３の形態を、図１０の（Ａ），（Ｂ）は本発明に係る内燃機関の吸気装置を実施するためのより具体的な第４の形態をそれぞれ示していて、図１と共通する部分には同一符号を付してある。   FIGS. 9A and 9B show a more specific third embodiment for implementing the intake device for an internal combustion engine according to the present invention, and FIGS. 10A and 10B show the present invention. A more specific fourth embodiment for implementing an intake device for an internal combustion engine is shown, and the same reference numerals are given to portions common to FIG.

図９の（Ａ），（Ｂ）に示す第３の形態では、カバー５の底壁部５ａに形成される***１７を二つとし、これらの二つの***１７が共有するかたちで例えばゴムあるいは軟質樹脂製のプラグあるいはグロメットタイプの弁体９を装着し、カバー５の内圧が外部圧力よりも大きい場合のみ上記***１７を開放するいわゆる常閉タイプで且つ逆止弁タイプの開閉弁機能を具備させたものである。   In the third embodiment shown in FIGS. 9A and 9B, there are two small holes 17 formed in the bottom wall portion 5a of the cover 5, and the two small holes 17 share, for example, rubber or A soft resin plug or grommet type valve element 9 is mounted, and a so-called normally closed type and check valve type opening / closing valve function that opens the small hole 17 only when the internal pressure of the cover 5 is larger than the external pressure is provided. It has been made.

また、図１０の（Ａ），（Ｂ）に示す第４の形態では、カバー５の底壁部５ａに形成された単一の***２７にリード弁タイプの弁体１０をリベット１１にて装着し、カバー５の内圧が外部圧力よりも大きい場合、または弁体１０の共振周波数により上記***２７を開放するいわゆる常閉タイプで且つ逆止弁タイプの開閉弁機能を具備させたものである。   Further, in the fourth embodiment shown in FIGS. 10A and 10B, the reed valve type valve element 10 is attached to the single small hole 27 formed in the bottom wall portion 5a of the cover 5 with the rivet 11. When the internal pressure of the cover 5 is larger than the external pressure, or a so-called normally closed type check valve type opening / closing valve function that opens the small hole 27 by the resonance frequency of the valve body 10 is provided.

これらの第３，第４の形態によれば、先の第１の形態と同様の効果が得られることはもちろんのこと、吸気管１より導かれる吸気の圧力変動に応じ容積室６が連動して伸縮する際の圧力差または吸気の所定の周波数に応じて弁体９または１０が開くことで、容積室６の弾性特性や放射音特性を任意に設定することが可能となる。   According to these third and fourth embodiments, the same effect as the first embodiment can be obtained, and the volume chamber 6 is interlocked according to the pressure fluctuation of the intake air introduced from the intake pipe 1. By opening the valve body 9 or 10 according to the pressure difference when expanding and contracting or the predetermined frequency of the intake air, it becomes possible to arbitrarily set the elastic characteristics and radiated sound characteristics of the volume chamber 6.

図１１は本発明に係る内燃機関の吸気装置を実施するためのより具体的な第５の形態を示す図であり、図１と共通する部分には同一符号を付してある。   FIG. 11 is a view showing a more specific fifth embodiment for implementing the intake device for an internal combustion engine according to the present invention, and the same reference numerals are given to the portions common to FIG.

この第５の形態では、***３７に対して、エンドピース３の当該***３７側から吸気管１側に向かって漸次断面積が大きくなるダクト１２を接続し、吸気管１に対する導入管２の接続位置とは異なる任意の位置にて***３７をダクト１２にて吸気管１に接続したものである。   In the fifth embodiment, the duct 12 having a gradually increasing cross-sectional area from the small hole 37 side of the end piece 3 toward the intake pipe 1 side is connected to the small hole 37, and the connection of the introduction pipe 2 to the intake pipe 1 is performed. A small hole 37 is connected to the intake pipe 1 by a duct 12 at an arbitrary position different from the position.

この第５の形態によれば、先の第１の形態と同様の効果が得られることはもちろんのこと、先に述べた導入管２の断面積と長さおよび容積室６の容積で決まる特定の共鳴周波数ｆ１とは異なる任意の音圧モードでの減衰効果を持たせることが可能となる利点がある。   According to the fifth embodiment, the same effect as that of the first embodiment can be obtained, and the specificity determined by the cross-sectional area and length of the introduction pipe 2 and the volume of the volume chamber 6 described above can be obtained. There is an advantage that it is possible to provide an attenuation effect in an arbitrary sound pressure mode different from the resonance frequency f1.

１…吸気管
２…導入管
３…エンドピース
５…カバー
５ａ…底壁部
６…容積室
６ｂ…筒状胴部
７…***
９…弁体
１０…弁体
１２…ダクト
１７…***
２７…***
３７…*** DESCRIPTION OF SYMBOLS 1 ... Intake pipe 2 ... Introducing pipe 3 ... End piece 5 ... Cover 5a ... Bottom wall part 6 ... Volume chamber 6b ... Cylindrical body part 7 ... Small hole 9 ... Valve body 10 ... Valve body 12 ... Duct 17 ... Small hole 27 ... Small hole 37 ... Small hole

Claims (5)

消音のためのヘルムホルツ型の共鳴室を備えた内燃機関の吸気装置において、
一端が吸気管に接続された導入管と、
上記導入管の他端に接続されて当該導入管よりも大径の共鳴室として機能する弾性変形可能で且つ密閉された容積室と、
この容積室を同心状に覆う密閉式のカバーと、
上記カバーの一部に設けられ導入管径よりも小さな極小径の複数の穴部と、
を備えていることを特徴とする内燃機関の吸気装置。 In an internal combustion engine intake device having a Helmholtz-type resonance chamber for silencing,
An introduction pipe with one end connected to the intake pipe;
An elastically deformable and sealed volume chamber connected to the other end of the introduction tube and functioning as a resonance chamber having a larger diameter than the introduction tube;
A hermetic cover that concentrically covers this volume chamber;
A plurality of holes having a minimum diameter smaller than the introduction pipe diameter provided in a part of the cover;
An intake device for an internal combustion engine, comprising: 上記カバーの穴部に相当する位置に、カバーの内圧が外部圧力よりも大きい場合のみ上記穴部を開放する逆止弁タイプの弁体を備えていることを特徴とする請求項１に記載の内燃機関の吸気装置。   The check valve type valve body that opens the hole only when the internal pressure of the cover is larger than the external pressure is provided at a position corresponding to the hole of the cover. An intake device for an internal combustion engine. 上記容積室は少なくとも筒状胴部がカバーよりも軟質の可撓性材料にて形成されたベローズ状のものとなっているとともに、全体として有底円筒状のものであることを特徴とする請求項２に記載の内燃機関の吸気装置。   The volume chamber has a bellows shape in which at least a cylindrical body portion is formed of a flexible material softer than a cover, and has a bottomed cylindrical shape as a whole. Item 3. An intake device for an internal combustion engine according to Item 2. 上記容積室およびカバーは共に導入管と同心状のものであるとともに、上記カバーは容積室と相似形をなす有底円筒状のものであり、その底壁部に相当する位置に穴部および弁体を設けてあることを特徴とする請求項３に記載の内燃機関の吸気装置。   The volume chamber and the cover are both concentric with the introduction pipe, and the cover has a bottomed cylindrical shape similar to the volume chamber, and the hole and valve are located at a position corresponding to the bottom wall. 4. An intake device for an internal combustion engine according to claim 3, wherein a body is provided. 上記吸気管に対する導入管の接続位置とは異なる位置にて上記穴部が吸気管に接続されていることを特徴とする請求項１に記載に内燃機関の吸気装置。   The intake device for an internal combustion engine according to claim 1, wherein the hole is connected to the intake pipe at a position different from a connection position of the introduction pipe to the intake pipe.
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