JP2009062922A - Resonance device and exhaust device of internal combustion engine - Google Patents

Resonance device and exhaust device of internal combustion engine Download PDF

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JP2009062922A
JP2009062922A JP2007232797A JP2007232797A JP2009062922A JP 2009062922 A JP2009062922 A JP 2009062922A JP 2007232797 A JP2007232797 A JP 2007232797A JP 2007232797 A JP2007232797 A JP 2007232797A JP 2009062922 A JP2009062922 A JP 2009062922A
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pipe
exhaust
inner pipe
exhaust pipe
resonance
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Koji Matsueda
幸治 松枝
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Toyota Motor Corp
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Toyota Motor Corp
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Priority to JP2007232797A priority Critical patent/JP2009062922A/en
Priority to PCT/IB2008/002293 priority patent/WO2009031012A2/en
Publication of JP2009062922A publication Critical patent/JP2009062922A/en
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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
    • F01N1/02—Silencing apparatus characterised by method of silencing by using resonance
    • 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
    • F01N1/026—Annular resonance chambers arranged concentrically to an exhaust passage and communicating with it, e.g. via at least one opening in the exhaust passage
    • 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
    • F01N13/02—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 having two or more separate silencers in series
    • 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
    • F01N13/18—Construction facilitating manufacture, assembly, or disassembly
    • F01N13/1805—Fixing exhaust manifolds, exhaust pipes or pipe sections to each other, to engine or to vehicle body
    • 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
    • F01N2340/00—Dimensional characteristics of the exhaust system, e.g. length, diameter or volume of the apparatus; Spatial arrangements of exhaust apparatuses
    • F01N2340/02—Dimensional characteristics of the exhaust system, e.g. length, diameter or volume of the apparatus; Spatial arrangements of exhaust apparatuses characterised by the distance of the apparatus to the engine, or the distance between two exhaust treating apparatuses

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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)

Abstract

<P>PROBLEM TO BE SOLVED: To provide a resonance device and an exhaust device of an internal combustion engine capable of reducing unpleasant noise while preventing the increase in manufacturing cost. <P>SOLUTION: The exhaust device of an internal combustion engine is equipped with a main muffler connected to an engine, an exhaust pipe whose one end is connected to the main muffler, a sub muffler connected to the other end of the exhaust pipe, an exhaust pipe whose one end is connected to the sub muffler, and a resonance device connected to the other end of the exhaust pipe. The resonance device is constituted of an inner pipe 35 connecting the other end 34b of the exhaust pipe thereto and including a through hole 35a and an outer pipe 36 mounted to the inner pipe 35 so as to surround the periphery of the inner pipe 35 and demarcating a space becoming a resonance chamber 37 by a space with the outer periphery part of the inner pipe 35. The outer peripheral part of the other end 34b of the exhaust pipe is inserted into the inner pipe 35. Thus, the step difference 39 is formed at the connection part of the other end 34b of the exhaust pipe and the inner pipe 35. The through hole 35a is formed in the exhaust pipe 35 so as to be adjacent to the connection part of the other end 34b of the exhaust pipe 34 and the inner pipe 35. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

本発明は、共鳴装置および内燃機関の排気装置に関し、特に、車両等に適用され、内燃機関から排出される排気ガスの特定の周波数音を消音する共鳴装置および内燃機関の排気装置に関する。   The present invention relates to a resonance device and an exhaust device for an internal combustion engine, and more particularly to a resonance device and an exhaust device for an internal combustion engine that are applied to a vehicle or the like and mute a specific frequency sound of exhaust gas discharged from the internal combustion engine.

一般に、自動車等の車両に設けられた内燃機関は、内燃機関の運転中に回転数に応じて様々な周波数の排気音を発生するが、そのうち、ある特定の周波数のものは特に大きな音となる。したがって、この特定の周波数の大きな音を消すには、その周波数に対して有効であることと、消音効果が大きいことが重要である。
特に、消音器の構造や消音器および排気管のレイアウトによって特定の周波数音が発生する場合には、特定の周波数音を消音するために共鳴装置を設けて対応する場合がある。 In general, an internal combustion engine provided in a vehicle such as an automobile generates exhaust noise of various frequencies according to the number of rotations during operation of the internal combustion engine. . Therefore, in order to mute a sound with a specific frequency, it is important to be effective for the frequency and to have a great muffing effect.
In particular, when a specific frequency sound is generated depending on the structure of the silencer or the layout of the silencer and the exhaust pipe, a resonance device may be provided to mute the specific frequency sound.

従来のこの種の特定の周波数音を消音する共鳴装置としては、図９に示すようなものがある（例えば、特許文献１参照）。図９において、内燃機関のシリンダの燃焼室から排気された排気ガスは、図示しない消音器から排気管を通して共鳴装置１に供給されるようになっており、この共鳴装置１は、排気管に接続されたインナーパイプ２と、インナーパイプ２の周囲を取り囲むようにしてインナーパイプ２に取付けられ、インナーパイプ２の外周部との間で共鳴室４となる空間が画成されるアウターパイプ３とを備えている。   As a conventional resonance apparatus for muting a specific frequency sound of this type, there is one as shown in FIG. 9 (see, for example, Patent Document 1). In FIG. 9, the exhaust gas exhausted from the combustion chamber of the cylinder of the internal combustion engine is supplied to the resonance device 1 from the silencer (not shown) through the exhaust pipe, and this resonance device 1 is connected to the exhaust pipe. An inner pipe 2 that is attached to the inner pipe 2 so as to surround the inner pipe 2, and an outer pipe 3 that defines a space serving as a resonance chamber 4 between the outer periphery of the inner pipe 2. I have.

インナーパイプ２には貫通孔２ａが形成されており、インナーパイプ２に供給される排気ガスは、貫通孔２ａを通してインナーパイプ２とアウターパイプ３との間に画成される共鳴室４に向けて放射されることにより、消音されてインナーパイプ２を通して排気される。また、この共鳴室４の容積を任意に設定することにより、消音する周波数音を調整することができる。具体的には、低周波数音を消音するためには、共鳴室４の容積を大きくし、高周波数音を消音するためには、共鳴室４の容積を小さくするようにしている。   A through hole 2a is formed in the inner pipe 2, and the exhaust gas supplied to the inner pipe 2 is directed to the resonance chamber 4 defined between the inner pipe 2 and the outer pipe 3 through the through hole 2a. By being radiated, the sound is silenced and exhausted through the inner pipe 2. Moreover, the frequency sound to be silenced can be adjusted by arbitrarily setting the volume of the resonance chamber 4. Specifically, the volume of the resonance chamber 4 is increased in order to mute the low frequency sound, and the volume of the resonance chamber 4 is decreased in order to mute the high frequency sound.

ところで、このような構成を有する共鳴装置１にあっては、内燃機関の高回転時等に高速の排気ガスがインナーパイプ２から貫通孔２ａを通して共鳴室４に放射される際に、笛吹き音となって不快な騒音が発生してしまう。   By the way, in the resonance apparatus 1 having such a configuration, when high-speed exhaust gas is radiated from the inner pipe 2 to the resonance chamber 4 through the through-hole 2a when the internal combustion engine rotates at high speed, the whistling sound is generated. And unpleasant noise is generated.

具体的には、内燃機関の高回転時等に排気管からインナーパイプ２に導入される排気ガスの流速が速くなると、排気ガスの排気方向上流側の貫通孔２ａのエッジ部で渦が発生し、この渦が下流側に流れると、一定周期の圧力波となり、この圧力波が加振源となって共鳴室４内で高周波の気柱共鳴となって、所謂、笛吹き音が発生してしまう。   Specifically, when the flow rate of the exhaust gas introduced from the exhaust pipe to the inner pipe 2 becomes high at the time of high rotation of the internal combustion engine, a vortex is generated at the edge portion of the through hole 2a upstream of the exhaust gas in the exhaust direction. When this vortex flows downstream, it becomes a pressure wave with a fixed period, and this pressure wave becomes a vibration source and becomes a high-frequency air column resonance in the resonance chamber 4, so-called whistling sound is generated. End up.

このような笛吹き音が発生するのを防止するために、共鳴装置１の下流側に吸音材を有する消音器を設けるようにしたものがあるが、このようにすると、吸音材を有する消音器を設ける分だけ排気装置の製造コストが増大してしまう。   In order to prevent such whistling noises from being generated, there is one in which a silencer having a sound absorbing material is provided on the downstream side of the resonance device 1. In this way, a silencer having a sound absorbing material is provided. The manufacturing cost of the exhaust device will increase by the amount provided.

このように排気装置の製造コストが増大するのを抑制しつつ、笛吹き音が発生するのを防止するものとして、図１０に示すような共鳴装置を有する消音器がある（例えば、特許文献２参照）。
図１０において、消音器１０の消音器本体１１は、仕切板１２、１３、１４によって複数の共鳴室１５、拡張室１６ａ、１６ｂ、１６ｃに区画されており、消音器本体１１内には、複数の貫通孔１８ａが形成された入口管１８、複数の貫通孔１９ａが形成された連通管１９および１つの貫通孔２０ａが形成された共鳴装置としての出口管２０が設けられている。 In order to prevent the whistling sound from being generated while suppressing the increase in the manufacturing cost of the exhaust device in this way, there is a silencer having a resonance device as shown in FIG. 10 (for example, Patent Document 2). reference).
In FIG. 10, the silencer body 11 of the silencer 10 is partitioned into a plurality of resonance chambers 15 and expansion chambers 16 a, 16 b, and 16 c by partition plates 12, 13, and 14. Are provided with an inlet pipe 18 having a through hole 18a, a communication pipe 19 having a plurality of through holes 19a, and an outlet pipe 20 as a resonance device having one through hole 20a.

出口管２０は、低周波音を消音するためにＵ字状に折り曲げて形成されているとともに、貫通孔２０ａを通して共鳴室１５に連通しており、貫通孔２０ａに対して排気ガスの排気方向上流側の内壁に凸部２０ｂが形成されている。   The outlet pipe 20 is formed to be bent in a U shape in order to mute low-frequency sound, and communicates with the resonance chamber 15 through the through hole 20a, and is upstream of the exhaust gas in the exhaust direction with respect to the through hole 20a. A convex portion 20b is formed on the inner wall on the side.

このように構成された消音器にあっては、内燃機関の高回転時に排気ガスの流速が速くなった場合には、貫通孔２０ａの上流側に設けられた凸部２０ｂに排気ガスを衝突させて渦が発生するのを防止して、高周波の気柱共鳴、すなわち、笛吹き音の発生を防止することができ、不快な騒音を低減することができる。
特開２００６−２９２２４号公報 実公平３−３２７３５号公報 In the silencer configured as described above, when the flow rate of the exhaust gas becomes high at the time of high rotation of the internal combustion engine, the exhaust gas collides with the convex portion 20b provided on the upstream side of the through hole 20a. Thus, it is possible to prevent the generation of vortices, to prevent high-frequency column resonance, that is, the generation of whistling noise, and to reduce unpleasant noise.
JP 2006-29224 A Japanese Utility Model Publication No.3-33235

しかしながら、このような従来の出口管２０を有する消音器１０にあっては、貫通孔２０ａに対して排気ガスの排気方向上流側の出口管２０の内壁に凸部２０ｂを形成しているため、出口管２０に凸部２０ｂを加工する必要があり、その分だけ出口管２０の製造コストが増大してしまい、結果的に消音器１０の製造コストが増大してしまうという問題があった。   However, in the silencer 10 having such a conventional outlet pipe 20, the convex portion 20b is formed on the inner wall of the outlet pipe 20 on the upstream side in the exhaust direction of the exhaust gas with respect to the through hole 20a. There is a problem that the convex portion 20b needs to be processed in the outlet pipe 20, and the manufacturing cost of the outlet pipe 20 increases accordingly, and as a result, the manufacturing cost of the silencer 10 increases.

本発明は、上述のような従来の問題を解決するためになされたもので、製造コストが増大するのを防止しつつ不快な騒音を低減することができる共鳴装置および内燃機関の排気装置を提供することを目的とする。   The present invention has been made to solve the above-described conventional problems, and provides a resonance device and an exhaust device for an internal combustion engine that can reduce unpleasant noise while preventing an increase in manufacturing cost. The purpose is to do.

本発明に係る共鳴装置は、上記目的達成のため、（１）内燃機関から排出される排気ガスを消音する消音器を有する排気装置に設けられ、特定の周波数音を消音する共鳴装置において、前記消音器に対して排気ガスの排気方向下流側に設けられ、一端部が前記消音器に接続された排気管と、前記排気管の他端部が接続され、少なくとも１つ以上の貫通孔を有するインナーパイプと、前記インナーパイプの周囲を取り囲むようにして前記インナーパイプに取付けられ、前記インナーパイプの外周部との間で共鳴室となる空間が画成されるアウターパイプとを備え、前記排気管の他端部の外周部を前記インナーパイプに挿通することにより、前記排気管の他端部と前記インナーパイプの接続部に段差を形成し、前記貫通孔を、前記排気管の他端部と前記インナーパイプの接続部に近接するように前記インナーパイプに形成したものから構成されている。   In order to achieve the above object, the resonance device according to the present invention is (1) provided in an exhaust device having a silencer for silencing exhaust gas discharged from an internal combustion engine, wherein the resonance device silences a specific frequency sound. Provided downstream of the silencer in the exhaust gas exhaust direction, one end of the exhaust pipe is connected to the silencer, and the other end of the exhaust pipe is connected, and has at least one through hole An exhaust pipe comprising: an inner pipe; and an outer pipe which is attached to the inner pipe so as to surround the inner pipe and defines a space serving as a resonance chamber between the outer periphery of the inner pipe. The other end of the exhaust pipe is inserted into the inner pipe to form a step at the other end of the exhaust pipe and the connecting portion of the inner pipe, and the through hole is connected to the other end of the exhaust pipe. And a one formed on the inner pipe so as to be close to the connecting portion of the inner pipe.

この構成により、消音器から排気管を通してインナーパイプに導入される排気ガスが、排気管の他端部とインナーパイプの接続部によって形成された段差を通過する際に、気流の乱れが生じるため、段差の近傍に位置するインナーパイプの貫通孔の縁に排気ガスが衝突したときに、一定周期の渦が発生するのを防止することができる。このため、笛吹き音を防止して不快な騒音を低減することができる。   With this configuration, when the exhaust gas introduced from the silencer through the exhaust pipe to the inner pipe passes through the step formed by the other end of the exhaust pipe and the connection portion of the inner pipe, the air current is disturbed. When exhaust gas collides with the edge of the through hole of the inner pipe located in the vicinity of the step, it is possible to prevent the vortex having a constant period from being generated. For this reason, a whistling sound can be prevented and unpleasant noise can be reduced.

そして、排気管の他端部とインナーパイプの接続部によって形成された段差を利用して排気ガスの気流を乱すことができるため、排気管やインナーパイプに加工を施すのを不要にすることができ、共鳴装置の製造コストが増大するのを防止することができる。   And since the flow of the exhaust gas can be disturbed by utilizing the step formed by the other end of the exhaust pipe and the connection part of the inner pipe, it is not necessary to process the exhaust pipe and the inner pipe. It is possible to prevent the manufacturing cost of the resonance device from increasing.

上記（１）に記載の共鳴装置において、（２）前記インナーパイプに前記貫通孔が１つ形成されているものから構成されている。
この構成により、インナーパイプに形成される貫通孔が１つのときには、貫通孔の縁に排気ガスが衝突して一定周期の渦が発生して笛吹き音が発生し易いが、共鳴装置のインナーパイプに導入される排気ガスが、排気管の他端部とインナーパイプの接続部によって形成された段差を通過する際に、気流の乱れを生じさせることができるため、インナーパイプの貫通孔の縁に排気ガスが衝突したときに、段差の近傍に位置する一定周期の渦が発生するのを防止することができる。このため、笛吹き音を防止して不快な騒音を確実に低減することができる。 The resonance device according to (1) above is configured by (2) one in which one through hole is formed in the inner pipe.
With this configuration, when there is one through-hole formed in the inner pipe, exhaust gas collides with the edge of the through-hole and a vortex with a fixed period is generated, so that whistling noise is likely to occur. When the exhaust gas introduced into the gas passes through the step formed by the other end of the exhaust pipe and the connection part of the inner pipe, air currents can be disturbed, so that the edge of the through hole of the inner pipe When exhaust gas collides, it is possible to prevent the generation of a vortex with a constant period located in the vicinity of the step. For this reason, a whistling sound can be prevented and unpleasant noise can be reduced reliably.

上記（１）または（２）に記載の共鳴装置において、（３）前記貫通孔が、排気ガスが前記段差を通過したときに気流の乱れが生じる位置に形成されるものから構成されている。
この構成により、排気ガスが段差を通過したときに気流の乱れが生じる位置に貫通孔を形成したので、インナーパイプに導入された排気ガスが貫通孔に到達する前に整流されてしまうのを防止して、貫通孔の縁に排気ガスが衝突したときに、段差の近傍に位置する一定周期の渦が発生するのを確実に防止することができる。 In the resonance apparatus according to the above (1) or (2), (3) the through hole is formed at a position where an air current is disturbed when exhaust gas passes through the step.
With this configuration, the through-hole is formed at a position where the turbulence of the exhaust gas occurs when the exhaust gas passes through the step, so that the exhaust gas introduced into the inner pipe is prevented from being rectified before reaching the through-hole. Thus, when exhaust gas collides with the edge of the through hole, it is possible to reliably prevent the occurrence of a vortex with a constant period located near the step.

上記（１）ないし（３）の何れかに記載の共鳴装置を備えた内燃機関の排気装置において、（４）内燃機関に接続された第１の消音器と、前記第１の消音器に一端部が接続された第１の排気管と、前記第１の排気管の他端部に接続された第２の消音器と、前記第２の消音器に一端部が接続された第２の排気管とを備え、前記第１の排気管の延在方向長さと前記第２の排気管および前記インナーパイプの延在方向長さとを略同一長さに形成し、前記第２の排気管の他端部の外周部を前記共鳴装置のインナーパイプに挿通したものから構成されている。   In the exhaust device for an internal combustion engine provided with the resonance device according to any one of (1) to (3), (4) a first silencer connected to the internal combustion engine, and one end of the first silencer. A first exhaust pipe connected to the first exhaust pipe, a second silencer connected to the other end of the first exhaust pipe, and a second exhaust connected to one end of the second silencer An extension direction length of the first exhaust pipe and an extension direction length of the second exhaust pipe and the inner pipe are formed to be substantially the same length, and other than the second exhaust pipe The outer peripheral portion of the end portion is constituted by inserting the inner pipe of the resonance device.

このようにしたのは、以下の理由による。
第１の消音器と第２の消音器を車両の前後方向に離隔して配置した場合には、第１の消音器と第２の消音器とを接続する排気管が長くなり、第１の消音器と第２の消音器の間で発生する気柱共鳴による低周波数音が発生してしまう。そして、第１の消音器と第２の消音器とを離隔して設置した場合には、音圧が低い気柱共鳴の節に第２の消音器が設置されることになり、低周波数音を抑制し難くなる。 The reason for this is as follows.
When the first silencer and the second silencer are spaced apart from each other in the vehicle front-rear direction, the exhaust pipe connecting the first silencer and the second silencer becomes longer, and the first silencer Low frequency sound due to air column resonance generated between the silencer and the second silencer is generated. When the first silencer and the second silencer are separated from each other, the second silencer is installed at the air column resonance node where the sound pressure is low. It becomes difficult to suppress.

これに対して、第１の消音器と第２の消音器を第１の排気管で接続し、第１の排気管の延在方向長さと第２の排気管および共鳴装置のインナーパイプの延在方向長さとを略同一長さに形成すれば、第２の消音器を低周波音の音圧のピーク位置に設置することができ、低周波数音を効率良く消音することができる。   On the other hand, the first silencer and the second silencer are connected by the first exhaust pipe, and the length of the first exhaust pipe in the extending direction and the extension of the second exhaust pipe and the inner pipe of the resonance device are connected. If the present length is formed to be substantially the same length, the second silencer can be installed at the peak position of the sound pressure of the low frequency sound, and the low frequency sound can be efficiently silenced.

ところが、第１の排気管の延在方向長さと第２の排気管および共鳴装置のインナーパイプの延在方向長さとを略同一長さに形成すると、第１の排気管と第２の排気管およびインナーパイプとの共鳴周波数が一致し、特定の高周波数で大きな高周波数音が発生してしまう。   However, if the extending direction length of the first exhaust pipe and the extending direction length of the second exhaust pipe and the inner pipe of the resonance device are formed to be substantially the same length, the first exhaust pipe and the second exhaust pipe are formed. And the resonance frequency of the inner pipe matches with that of the inner pipe, and a large high frequency sound is generated at a specific high frequency.

そこで、本発明は、第２の排気管に共鳴装置を接続して第２の消音器の上流側と下流側の共鳴周波数を一致しないようにすることにより、共鳴装置によって高周波数音を消音する。そして、内燃機関の高回転時に第２の消音器から第２の排気管を介してインナーパイプに導入される排気ガスが、第２の排気管の他端部とインナーパイプの接続部によって形成された段差を通過する際に、気流の乱れを生じさせることができるため、インナーパイプの貫通孔の縁に排気ガスが衝突したときに、段差の近傍に位置する一定周期の渦が発生するのを防止することができる。このため、笛吹き音を防止して不快な騒音を低減することができる。   Therefore, the present invention silences high-frequency sound by the resonance device by connecting a resonance device to the second exhaust pipe so that the upstream and downstream resonance frequencies of the second silencer do not coincide. . Then, exhaust gas introduced from the second silencer through the second exhaust pipe to the inner pipe when the internal combustion engine rotates at a high speed is formed by the other end of the second exhaust pipe and the connection portion of the inner pipe. As the air flow can be disturbed when passing through the step, when the exhaust gas collides with the edge of the through hole of the inner pipe, a vortex with a fixed period located near the step is generated. Can be prevented. For this reason, a whistling sound can be prevented and unpleasant noise can be reduced.

そして、第２の排気管の他端部とインナーパイプの接続部によって形成された段差を利用して排気ガスの気流を乱すことができるため、排気管やインナーパイプに加工を施すのを不要にすることができ、共鳴装置の製造コストが増大するのを防止することができる。   And since the flow of the exhaust gas can be disturbed by using the step formed by the other end of the second exhaust pipe and the connection part of the inner pipe, it is unnecessary to process the exhaust pipe and the inner pipe. It is possible to prevent the manufacturing cost of the resonance device from increasing.

上記（４）に記載の内燃機関の排気装置において、（５）前記第２の消音器が、前記第１の排気管の他端部および前記第２の排気管の一端部が接続され、複数の貫通孔を有するインナーパイプと、前記インナーパイプの周囲を取り囲むようにして前記インナーパイプに取付けられ、前記インナーパイプの外周部との間で共鳴室となる空間が画成されるアウターパイプとを備え、前記共鳴室に吸音材が設けられるものから構成されている。   In the exhaust system for an internal combustion engine according to the above (4), (5) the second silencer is connected to the other end of the first exhaust pipe and one end of the second exhaust pipe. An inner pipe having a through hole and an outer pipe attached to the inner pipe so as to surround the inner pipe and defining a space serving as a resonance chamber between the outer periphery of the inner pipe. And the resonance chamber is provided with a sound absorbing material.

この構成により、第２の消音器の共鳴室に吸音材を設けたので、吸音材によって低周波音を効率良く消音することができる。   With this configuration, since the sound absorbing material is provided in the resonance chamber of the second silencer, the low frequency sound can be efficiently silenced by the sound absorbing material.

本発明によれば、製造コストが増大するのを防止しつつ不快な騒音を低減することができる共鳴装置および内燃機関の排気装置を提供することができる。   ADVANTAGE OF THE INVENTION According to this invention, the resonance apparatus and the exhaust apparatus of an internal combustion engine which can reduce an unpleasant noise can be provided, preventing a manufacturing cost increasing.

以下、本発明に係る共鳴装置および共鳴装置を備えた内燃機関の排気装置の一実施の形態について、図面を用いて説明する。
図１〜図８は本発明に係る共鳴装置および共鳴装置を備えた内燃機関の排気装置の一実施の形態を示す図である。なお、図１は、排気装置の上面図、図２は、排気装置の正面図を示している。 DESCRIPTION OF EXEMPLARY EMBODIMENTS An embodiment of an exhaust device for an internal combustion engine including the resonance device and the resonance device according to the invention will be described below with reference to the drawings.
FIGS. 1-8 is a figure which shows one Embodiment of the exhaust apparatus of the internal combustion engine provided with the resonance apparatus which concerns on this invention, and a resonance apparatus. 1 is a top view of the exhaust device, and FIG. 2 is a front view of the exhaust device.

まず、構成を説明する。
図１、図２において、４気筒の内燃機関としてのエンジン２１は、各気筒の燃焼室が排気ポートを介して排気マニホールド２２に連通しており、この排気マニホールド２２には排気装置２３が接続されている。排気装置２３は、触媒コンバータ２４、第１の消音器としてのメインマフラ２６、第２の消音器としてのサブマフラ２７および共鳴装置としての共鳴器２８を備えている。なお、触媒コンバータ２４とは別体の触媒コンバータをメインマフラ２６内に設けてもよい。 First, the configuration will be described.
1 and 2, an engine 21 as a four-cylinder internal combustion engine has a combustion chamber of each cylinder communicating with an exhaust manifold 22 via an exhaust port, and an exhaust device 23 is connected to the exhaust manifold 22. ing. The exhaust device 23 includes a catalytic converter 24, a main muffler 26 as a first silencer, a sub muffler 27 as a second silencer, and a resonator 28 as a resonance device. A catalytic converter separate from the catalytic converter 24 may be provided in the main muffler 26.

触媒コンバータ２４は、ハニカム基材または粒状の活性アルミナ製担体に白金、パラジウム等の触媒を付着させたものが本体ケースに収納されたものから構成されており、ＮＯｘの還元やＣＯ、ＨＣの酸化を行うようになっている。   The catalytic converter 24 is composed of a honeycomb base or a granular activated alumina support to which a catalyst such as platinum or palladium is attached and housed in a main body case. The reduction of NOx and the oxidation of CO and HC Is supposed to do.

メインマフラ２６は、排気管２５を介して触媒コンバータ２４に接続されており、排気ガスの一次消音を行うようになっている。メインマフラ２６には第１の排気管としての排気管２９の一端部２９ａが接続されており、この排気管２９の他端部２９ｂはサブマフラ２７に接続されている。   The main muffler 26 is connected to the catalytic converter 24 via the exhaust pipe 25, and performs primary noise reduction of the exhaust gas. One end 29 a of an exhaust pipe 29 as a first exhaust pipe is connected to the main muffler 26, and the other end 29 b of the exhaust pipe 29 is connected to the sub muffler 27.

図３に示すように、サブマフラ２７は、排気管２９の他端部２９ｂが嵌合され、複数の貫通孔３０ａが形成されたインナーパイプ３０と、インナーパイプ３０の周囲を取り囲むようにしてインナーパイプ３０に取付けられ、インナーパイプ３０の外周部との間で共鳴室３２となる空間が画成されるアウターパイプ３１と、共鳴室３２に充填された吸音材３３とを備えている。   As shown in FIG. 3, the sub muffler 27 includes an inner pipe 30 in which the other end portion 29 b of the exhaust pipe 29 is fitted and a plurality of through holes 30 a are formed, and an inner pipe that surrounds the inner pipe 30. 30, an outer pipe 31 that defines a space serving as a resonance chamber 32 between the outer periphery of the inner pipe 30 and a sound absorbing material 33 filled in the resonance chamber 32.

また、サブマフラ２７に第２の排気管としての排気管３４の一端部３４ａが接続されており、この排気管３４の一端部３４ａはインナーパイプ３０に嵌合されている。   Further, one end 34 a of an exhaust pipe 34 as a second exhaust pipe is connected to the sub muffler 27, and one end 34 a of the exhaust pipe 34 is fitted to the inner pipe 30.

また、排気管３４の他端部３４ｂはサブマフラ２７の排気ガスの排気方向下流側に設けられた共鳴器２８に接続されている。図４、図５に示すように、共鳴器２８は、排気管３４の他端部３４ｂが接続され、１つの貫通孔３５ａを有するインナーパイプ３５と、インナーパイプ３５の周囲を取り囲むようにしてインナーパイプ３５に取付けられ、インナーパイプ３５の外周部との間で共鳴室３７となる空間が画成されるアウターパイプ３６とを備えている。   The other end 34 b of the exhaust pipe 34 is connected to a resonator 28 provided downstream of the sub muffler 27 in the exhaust direction of the exhaust gas. As shown in FIGS. 4 and 5, the resonator 28 includes an inner pipe 35 having one through hole 35 a connected to the other end 34 b of the exhaust pipe 34, and an inner pipe 35 surrounding the inner pipe 35. An outer pipe 36 is provided which is attached to the pipe 35 and defines a space serving as a resonance chamber 37 between the outer periphery of the inner pipe 35.

また、排気管３４の他端部３４ｂの外周部はインナーパイプ３５に挿通されており、排気管３４の他端部３４ｂとインナーパイプ３５の接続部には段差３９が形成されている。また、貫通孔３５ａは、排気管３４の他端部３４ｂとインナーパイプ３５の接続部である段差３９に近接するようにインナーパイプ３５に形成されている。   Further, the outer peripheral portion of the other end portion 34 b of the exhaust pipe 34 is inserted into the inner pipe 35, and a step 39 is formed at the connection portion between the other end portion 34 b of the exhaust pipe 34 and the inner pipe 35. Further, the through hole 35 a is formed in the inner pipe 35 so as to be close to a step 39 that is a connection portion between the other end 34 b of the exhaust pipe 34 and the inner pipe 35.

また、排気管２９の延在方向長さと排気管３４および共鳴器２８のインナーパイプ３５の延在方向長さとは略同一長さに形成されており、貫通孔３５ａは、サブマフラ２７から排出される排気ガスの排気経路の途中に形成されていることになる。   Further, the length in the extending direction of the exhaust pipe 29 and the length in the extending direction of the inner pipe 35 of the exhaust pipe 34 and the resonator 28 are formed to be substantially the same length, and the through hole 35 a is discharged from the sub muffler 27. It is formed in the middle of the exhaust gas exhaust path.

また、インナーパイプ３５と排気管３４の他端部３４ｂとはフランジ部材３８によって締結されており、このフランジ部材３８は、排気管３４の他端部３４ｂとアウターパイプ３６の外周部を取り囲むようにして設けられている。   Further, the inner pipe 35 and the other end 34b of the exhaust pipe 34 are fastened by a flange member 38. The flange member 38 surrounds the other end 34b of the exhaust pipe 34 and the outer peripheral portion of the outer pipe 36. Is provided.

次に、図６、図７を用いて排気ガスの消音方法について説明する。
まず、図６（ａ）に示すように、従来のようにメインマフラ２６とサブマフラ２７を車両の前後方向に離隔して配置した場合には、メインマフラ２６とサブマフラ２７とを接続する排気管が長くなり、メインマフラ２６とサブマフラ２７の間で発生する気柱共鳴による周波数が４０Ｈｚ〜５０Ｈｚ程度の低周波数域で音圧が最大となってしまう。そして、このようにメインマフラ２６とサブマフラ２７とを離隔して設置した場合には、音圧が低い気柱共鳴の節にサブマフラ２７が設置されることになり、低周波数音を抑制し難くなる。 Next, a method for silencing exhaust gas will be described with reference to FIGS.
First, as shown in FIG. 6 (a), when the main muffler 26 and the sub muffler 27 are spaced apart from each other in the longitudinal direction of the vehicle as in the prior art, an exhaust pipe for connecting the main muffler 26 and the sub muffler 27 is provided. The sound pressure becomes maximum in a low frequency range where the frequency due to air column resonance generated between the main muffler 26 and the sub muffler 27 is about 40 Hz to 50 Hz. When the main muffler 26 and the sub muffler 27 are installed separately as described above, the sub muffler 27 is installed at the node of the air column resonance where the sound pressure is low, and it is difficult to suppress the low frequency sound. .

これに対して、本実施の形態では、図６（ｂ）に示すように、メインマフラ２６とサブマフラ２７を排気管２９で接続し、排気管２９の延在方向長さと排気管３４および共鳴器２８のインナーパイプ３５の延在方向長さとを略同一長さに形成したので、サブマフラ２７を低周波音の音圧のピーク位置（図６（ａ）のＡで示す位置）に設置することができ、低周波数音を効率良く消音することができる。また、サブマフラ２７に吸音材３３を設けたので、低周波数音をより一層効率良く消音することができる。   On the other hand, in the present embodiment, as shown in FIG. 6B, the main muffler 26 and the sub muffler 27 are connected by the exhaust pipe 29, the length of the exhaust pipe 29 in the extending direction, the exhaust pipe 34, and the resonator. Since the extension direction length of the 28 inner pipes 35 is formed to be substantially the same length, the sub muffler 27 can be installed at the peak position of the sound pressure of the low frequency sound (position indicated by A in FIG. 6A). It is possible to mute low frequency sound efficiently. Further, since the sound absorbing material 33 is provided in the sub muffler 27, it is possible to mute the low frequency sound more efficiently.

ところが、排気管２９の延在方向長さと排気管３４および共鳴器２８のインナーパイプ３５の延在方向長さとを略同一長さに形成すると、排気管２９と排気管３４およびインナーパイプ３５との共鳴周波数が一致し、２００Ｈｚ程度で高周波数音が最大となってしまう。   However, if the extending direction length of the exhaust pipe 29 and the extending direction length of the exhaust pipe 34 and the inner pipe 35 of the resonator 28 are formed to be substantially the same length, the exhaust pipe 29, the exhaust pipe 34, and the inner pipe 35 The resonance frequencies coincide with each other, and the high frequency sound becomes maximum at about 200 Hz.

そこで、本実施の形態では、排気管３４に共鳴器２８を接続してサブマフラ２７の上流側と下流側の共鳴周波数を一致しないようにすることにより、共鳴器２８によって高周波数音を消音する。   Therefore, in the present embodiment, the resonator 28 is connected to the exhaust pipe 34 so that the resonance frequencies on the upstream side and the downstream side of the sub muffler 27 do not coincide with each other, so that the high frequency sound is silenced by the resonator 28.

ここで、エンジン２１の高回転時等に排気管３４からインナーパイプ３５に導入される排気ガスの流速が速くなると、排気ガスの排気方向上流側の貫通孔３５ａのエッジ部で渦が発生し、この渦が下流側に流れると、一定周期の圧力波となり、この圧力波が加振源となり、共鳴室３７内で高周波の気柱共鳴となって、所謂、笛吹き音が発生してしまうことがある。   Here, when the flow rate of the exhaust gas introduced from the exhaust pipe 34 to the inner pipe 35 becomes high at the time of high rotation of the engine 21, a vortex is generated at the edge portion of the through hole 35a upstream of the exhaust gas in the exhaust direction, When this vortex flows downstream, it becomes a pressure wave with a constant period, and this pressure wave becomes a vibration source, which causes high-frequency air column resonance in the resonance chamber 37, and so-called whistling noise is generated. There is.

本実施の形態では、排気管３４の他端部３４ｂの外周部をインナーパイプ３５に挿通することにより、排気管３４の他端部３４ｂとインナーパイプ３５の接続部に段差３９を形成し、排気管３４の他端部３４ｂとインナーパイプ３５の接続部である段差３９に近接するように貫通孔３５ａをインナーパイプ３５に形成したので、図７に示すように、エンジン２１の高回転時にサブマフラ２７から排気管３４を介してインナーパイプ３５に導入される排気ガスＧが、段差３９を通過する際に、気流の乱れを生じさせることができる。   In the present embodiment, by inserting the outer peripheral portion of the other end 34b of the exhaust pipe 34 into the inner pipe 35, a step 39 is formed at the connection portion between the other end 34b of the exhaust pipe 34 and the inner pipe 35, and the exhaust pipe 34 is exhausted. Since the through-hole 35a is formed in the inner pipe 35 so as to be close to the step 39 which is the connecting portion between the other end 34b of the pipe 34 and the inner pipe 35, as shown in FIG. When the exhaust gas G introduced into the inner pipe 35 through the exhaust pipe 34 passes through the step 39, the turbulence of the airflow can be generated.

このため、段差３９の近傍に位置するインナーパイプ３５の貫通孔３５ａのエッジ部に排気ガスが衝突したときに、一定周期の渦が発生するのを防止することができる。このため、笛吹き音を防止して不快な騒音を低減することができる。   For this reason, when exhaust gas collides with the edge part of the through-hole 35a of the inner pipe 35 located in the vicinity of the level | step difference 39, it can prevent that a vortex of a fixed period generate | occur | produces. For this reason, a whistling sound can be prevented and unpleasant noise can be reduced.

したがって、貫通孔３５ａは、排気ガスが段差３９を通過したときに気流の乱れが生じる位置に形成されることが望ましく、この位置よりも貫通孔３５ａがさらに下流側に設けられると、排気ガスが整流されてしまい、一定周期の渦が発生してしまう可能性が大きい。   Therefore, it is desirable that the through hole 35a is formed at a position where the turbulence of the airflow occurs when the exhaust gas passes through the step 39. If the through hole 35a is provided further downstream than this position, the exhaust gas There is a high possibility that rectification will occur and vortices with a certain period will be generated.

図８は、エンジン２１の回転数と排気装置２３で発生する音圧レベルの関係を示す図であり、図８中、破線が本実施の形態の音圧レベル、実線が笛吹き音の抑制を考慮していない排気装置の音圧レベルである。   FIG. 8 is a diagram showing the relationship between the rotational speed of the engine 21 and the sound pressure level generated in the exhaust device 23. In FIG. 8, the broken line indicates the sound pressure level of the present embodiment, and the solid line indicates the suppression of the whistling sound. This is the sound pressure level of the exhaust system not considered.

図８から明らかなように、エンジン２１の回転数が５０００ｒｐｍ、５９５０ｒｐｍのの何れの高回転時にあっても、音圧レベルのピーク時の周波数帯域における音圧レベルを１０ｄＢ近く低減することができた。   As is apparent from FIG. 8, the sound pressure level in the frequency band at the peak of the sound pressure level could be reduced by nearly 10 dB at any high speed of the engine 21 at 5000 rpm or 5950 rpm. .

このように本実施の形態では、エンジン２１に接続されたメインマフラ２６と、メインマフラ２６に一端部２９ａが接続された排気管２９と、排気管２９の他端部２９ｂに接続されたサブマフラ２７と、サブマフラ２７に一端部３４ａが接続された排気管３４と、排気管３４の他端部３４ｂに接続された共鳴器２８とを備え、共鳴器２８を、排気管３４の他端部３４ｂが接続され、貫通孔３５ａを有するインナーパイプ３５と、インナーパイプ３５の周囲を取り囲むようにしてインナーパイプ３５に取付けられ、インナーパイプ３５の外周部との間で共鳴室３７となる空間が画成されるアウターパイプ３６とから構成し、排気管３４の他端部３４ｂの外周部をインナーパイプ３５に挿通することにより、排気管３４の他端部３４ｂとインナーパイプ３５の接続部に段差３９を形成し、排気管３４の他端部３４ｂとインナーパイプ３５の接続部に近接するように貫通孔３５ａをインナーパイプ３５に形成し、さらに、排気管２９の延在方向長さと排気管３４および共鳴器２８のインナーパイプ３５の延在方向長さとを略同一長さに形成した。   As described above, in the present embodiment, the main muffler 26 connected to the engine 21, the exhaust pipe 29 having one end 29 a connected to the main muffler 26, and the sub muffler 27 connected to the other end 29 b of the exhaust pipe 29. And an exhaust pipe 34 having one end 34a connected to the sub-muffler 27, and a resonator 28 connected to the other end 34b of the exhaust pipe 34. The resonator 28 is connected to the other end 34b of the exhaust pipe 34. A space that is connected to the inner pipe 35 having the through-hole 35a and is attached to the inner pipe 35 so as to surround the inner pipe 35 and that serves as a resonance chamber 37 is defined between the outer periphery of the inner pipe 35 and the inner pipe 35. The outer pipe 36 and the other end 34b of the exhaust pipe 34 are inserted into the inner pipe 35 so that the other end 34b of the exhaust pipe 34 and the inner pipe 35 A step 39 is formed in the connection portion of the pipe 35, a through hole 35 a is formed in the inner pipe 35 so as to be close to the connection portion of the other end 34 b of the exhaust pipe 34 and the inner pipe 35, and the exhaust pipe 29 is further extended. The length in the extending direction and the length in the extending direction of the inner pipe 35 of the exhaust pipe 34 and the resonator 28 are formed to be substantially the same length.

このため、サブマフラ２７によって低周波数音を効率良く消音することができるとともに、サブマフラ２７の上流側と下流側の共鳴周波数が一致しないようにして高周波数音を効率良く消音することができる。   Therefore, the low-frequency sound can be efficiently silenced by the sub muffler 27, and the high-frequency sound can be efficiently silenced so that the upstream and downstream resonance frequencies of the sub-muffler 27 do not match.

また、エンジン２１の高回転時にサブマフラ２７から排気管３４を介して共鳴器２８のインナーパイプ３５に導入される排気ガスが、排気管３４の他端部３４ｂとインナーパイプ３５の接続部によって形成された段差３９を通過する際に、気流の乱れを生じさせることができるため、段差３９の近傍に位置するインナーパイプ３５の貫通孔３５ａの縁に排気ガスが衝突したときに、一定周期の渦が発生するのを防止することができる。このため、笛吹き音を防止して不快な騒音を低減することができる。   Further, the exhaust gas introduced from the sub muffler 27 through the exhaust pipe 34 into the inner pipe 35 of the resonator 28 when the engine 21 rotates at a high speed is formed by the connection portion between the other end 34 b of the exhaust pipe 34 and the inner pipe 35. Since the air flow can be disturbed when passing through the step 39, when the exhaust gas collides with the edge of the through hole 35a of the inner pipe 35 located in the vicinity of the step 39, a vortex having a fixed period is generated. It can be prevented from occurring. For this reason, a whistling sound can be prevented and unpleasant noise can be reduced.

そして、排気管３４の他端部３４ｂとインナーパイプ３５の接続部によって形成された段差３９を利用して排気ガスの気流を乱すことができるため、排気管３４やインナーパイプ３５に加工を施すのを不要にすることができ、共鳴器２８の製造コストが増大するのを防止することができる。   And since the air flow of exhaust gas can be disturbed using the level | step difference 39 formed by the connection part of the other end part 34b of the exhaust pipe 34 and the inner pipe 35, the exhaust pipe 34 and the inner pipe 35 are processed. Can be eliminated, and an increase in the manufacturing cost of the resonator 28 can be prevented.

特に、本実施の形態では、排気ガスが段差３９を通過したときに気流の乱れが生じる位置に貫通孔３５ａを形成したので、インナーパイプ３５に導入された排気ガスが貫通孔３５ａに到達する前に整流されてしまうのを防止して、貫通孔３５ａの縁に排気ガスが衝突したときに一定周期の渦が発生するのを確実に防止することができる。   In particular, in the present embodiment, since the through hole 35a is formed at a position where the turbulence of the air flow occurs when the exhaust gas passes through the step 39, before the exhaust gas introduced into the inner pipe 35 reaches the through hole 35a. It is possible to prevent the vortex having a constant period from being generated when the exhaust gas collides with the edge of the through hole 35a.

また、本実施の形態のサブマフラ２７を、排気管２９の他端部２９ｂおよび排気管３４の一端部３４ａが接続され、複数の貫通孔３０ａを有するインナーパイプ３０と、インナーパイプ３０の周囲を取り囲むようにしてインナーパイプ３０に取付けられ、インナーパイプ３０の外周部との間で共鳴室３２となる空間が画成されるアウターパイプ３１とを備え、共鳴室３２に吸音材３３が設けられるものから構成したので、低周波数音を吸音材３３によって効率良く消音することができる。   Further, the sub-muffler 27 of the present embodiment is connected to the other end 29b of the exhaust pipe 29 and the one end 34a of the exhaust pipe 34, and surrounds the inner pipe 30 having a plurality of through holes 30a and the inner pipe 30. In this way, the outer pipe 31 is attached to the inner pipe 30 and defines a space serving as a resonance chamber 32 between the outer periphery of the inner pipe 30 and the sound absorbing material 33 is provided in the resonance chamber 32. Since it comprised, the low frequency sound can be efficiently muffled by the sound-absorbing material 33.

なお、本実施の形態の共鳴器２８では、貫通孔３５ａがインナーパイプ３５に１つだけ設けられているが、貫通孔３５ａは２つ以上であってもよい。特に、インナーパイプ３５に形成される貫通孔３５ａが１つのときには、渦が発生する個所が１個所だけとなるため、貫通孔３５ａの縁に排気ガスが衝突して一定周期の渦が発生して笛吹き音が発生し易いが、本実施の形態では、段差３９を利用することにより、上述したように気流の乱れを生じさせて一定周期の渦が発生するのを確実に防止することができる。   In the resonator 28 of the present embodiment, only one through hole 35a is provided in the inner pipe 35, but two or more through holes 35a may be provided. In particular, when there is only one through hole 35a formed in the inner pipe 35, there is only one place where vortices are generated. Therefore, exhaust gas collides with the edge of the through hole 35a and vortices with a fixed period are generated. Whistling sounds are likely to occur, but in the present embodiment, by using the step 39, it is possible to reliably prevent the occurrence of vortices with a fixed period by causing the turbulence of the air current as described above. .

また、本実施の形態では、排気管２９の延在方向長さと排気管３４および共鳴器２８のインナーパイプ３５の延在方向長さとを略同一長さに形成し、共鳴器２８によって特定の周波数音として高周波数音を消音しているが、本実施の形態の共鳴器２８は、マフラや排気管のレウアウトによって共鳴器２８の上流側で特定の周波数音が発生する場合に、この特定の周波数音を消音することができるものであり、共鳴器２８の上流側のマフラや排気管の構成はこれに限るものではない。   In the present embodiment, the length in the extending direction of the exhaust pipe 29 and the length in the extending direction of the inner pipe 35 of the exhaust pipe 34 and the resonator 28 are formed to be substantially the same length. Although the high frequency sound is muted as the sound, the resonator 28 according to the present embodiment has a specific frequency when a specific frequency sound is generated on the upstream side of the resonator 28 due to the muffler or exhaust pipe layout. The sound can be silenced, and the configuration of the muffler and exhaust pipe on the upstream side of the resonator 28 is not limited to this.

また、今回開示された実施の形態はすべての点で例示であってこの実施の形態に制限されるものではない。本発明の範囲は上記した実施の形態のみの説明ではなくて特許請求の範囲によって示され、特許請求の範囲と均等の意味および範囲内での全ての変更が含まれることが意図される。   In addition, the embodiment disclosed this time is illustrative in all respects and is not limited to this embodiment. The scope of the present invention is shown not by the above description of the embodiments but by the scope of the claims, and is intended to include all modifications within the meaning and scope equivalent to the scope of the claims.

以上のように、本発明に係る共鳴装置および内燃機関の排気装置は、製造コストが増大するのを防止しつつ不快な騒音を低減することができるという効果を有し、内燃機関から排出される排気ガスの特定の周波数音を消音する共鳴装置および内燃機関の排気装置等として有用である。   As described above, the resonance device and the exhaust device of the internal combustion engine according to the present invention have an effect of reducing unpleasant noise while preventing an increase in manufacturing cost, and are discharged from the internal combustion engine. It is useful as a resonance device that silences a specific frequency sound of exhaust gas, an exhaust device of an internal combustion engine, and the like.

本発明に係る共鳴装置および内燃機関の排気装置の一実施の形態を示す図であり、排気装置の上面図である。It is a figure which shows one Embodiment of the resonance apparatus which concerns on this invention, and the exhaust apparatus of an internal combustion engine, and is a top view of an exhaust apparatus. 本発明に係る共鳴装置および内燃機関の排気装置の一実施の形態を示す図であり、排気装置の正面図である。It is a figure which shows one Embodiment of the resonance apparatus which concerns on this invention, and the exhaust apparatus of an internal combustion engine, and is a front view of an exhaust apparatus. 本発明に係る共鳴装置および内燃機関の排気装置の一実施の形態を示す図であり、サブマフラの断面図である。It is a figure which shows one Embodiment of the resonance apparatus which concerns on this invention, and the exhaust apparatus of an internal combustion engine, and is sectional drawing of a sub muffler. 本発明に係る共鳴装置および内燃機関の排気装置の一実施の形態を示す図であり、共鳴装置の外観図である。BRIEF DESCRIPTION OF THE DRAWINGS It is a figure which shows one Embodiment of the resonance apparatus which concerns on this invention, and the exhaust apparatus of an internal combustion engine, and is an external view of a resonance apparatus. 図４のＢ−Ｂ方向矢視断面図である。It is a BB direction arrow sectional view of Drawing 4. 本発明に係る共鳴装置および内燃機関の排気装置の一実施の形態を示す図であり、（ａ）はサブマフラとメインマフラを離して設置した場合の気柱共鳴による音圧モードを示す図、（ｂ）は本発明の排気装置の気柱共鳴による音圧モードを示す図である。It is a figure which shows one Embodiment of the resonance apparatus which concerns on this invention, and the exhaust apparatus of an internal combustion engine, (a) is a figure which shows the sound pressure mode by air column resonance at the time of installing apart a sub muffler and a main muffler, b) is a diagram showing a sound pressure mode by air column resonance of the exhaust device of the present invention. 本発明に係る共鳴装置および内燃機関の排気装置の一実施の形態を示す図であり、共鳴装置の段差部分に流入する排気ガスの流れを示す図である。It is a figure which shows one Embodiment of the resonance apparatus which concerns on this invention, and the exhaust apparatus of an internal combustion engine, and is a figure which shows the flow of the exhaust gas which flows in into the level | step-difference part of a resonance apparatus. 本発明に係る共鳴装置および内燃機関の排気装置の一実施の形態を示す図であり、エンジンの回転数と排気装置で発生する音圧レベルの関係を示す図である。It is a figure which shows one Embodiment of the resonance apparatus which concerns on this invention, and the exhaust apparatus of an internal combustion engine, and is a figure which shows the relationship between the engine speed and the sound pressure level which generate | occur | produces in an exhaust apparatus. （ａ）は従来の共鳴装置の断面図、（ｂ）は同図（ａ）のＣ−Ｃ方向矢視断面図である。(A) is sectional drawing of the conventional resonance apparatus, (b) is CC sectional view taken on the line of the CC direction of the figure (a). （ａ）は従来の共鳴装置を備えた消音器の断面図、（ｂ）は同図（ａ）のＤ−Ｄ方向矢視断面図である。(A) is sectional drawing of the silencer provided with the conventional resonance apparatus, (b) is a DD direction arrow sectional drawing of the figure (a).

符号の説明Explanation of symbols

２１ エンジン（内燃機関）
２３ 排気装置
２６ メインマフラ（第１の消音器）
２７ サブマフラ（第２の消音器）
２８ 共鳴器（共鳴装置）
２９ 排気管
２９ａ 一端部
２９ｂ 他端部
３０ インナーパイプ
３０ａ 貫通孔
３１ アウターパイプ
３２ 共鳴室
３３ 吸音材
３４ 排気管
３４ａ 一端部
３４ｂ 他端部
３５ インナーパイプ
３５ａ 貫通孔
３６ アウターパイプ
３７ 共鳴室
３９ 段差 21 Engine (Internal combustion engine)
23 Exhaust device 26 Main muffler (first silencer)
27 Sub-muffler (second silencer)
28 Resonator (resonance device)
29 exhaust pipe 29a one end 29b other end 30 inner pipe 30a through hole 31 outer pipe 32 resonance chamber 33 sound absorbing material 34 exhaust pipe 34a one end 34b other end 35 inner pipe 35a through hole 36 outer pipe 37 resonance chamber 39 step

Claims (5)

内燃機関から排出される排気ガスを消音する消音器を有する排気装置に設けられ、特定の周波数音を消音する共鳴装置において、
前記消音器に対して排気ガスの排気方向下流側に設けられ、一端部が前記消音器に接続された排気管と、
前記排気管の他端部が接続され、少なくとも１つ以上の貫通孔を有するインナーパイプと、前記インナーパイプの周囲を取り囲むようにして前記インナーパイプに取付けられ、前記インナーパイプの外周部との間で共鳴室となる空間が画成されるアウターパイプとを備え、
前記排気管の他端部の外周部を前記インナーパイプに挿通することにより、前記排気管の他端部と前記インナーパイプの接続部に段差を形成し、前記貫通孔を、前記排気管の他端部と前記インナーパイプの接続部に近接するように前記インナーパイプに形成したことを特徴とする共鳴装置。 In a resonance apparatus that is provided in an exhaust device having a silencer that silences exhaust gas discharged from an internal combustion engine and silences a specific frequency sound,
An exhaust pipe provided on the downstream side in the exhaust direction of the exhaust gas with respect to the silencer, one end of which is connected to the silencer;
The other end of the exhaust pipe is connected to the inner pipe having at least one through hole, and the inner pipe is attached to the inner pipe so as to surround the inner pipe, and between the outer pipe and the outer peripheral portion of the inner pipe. And an outer pipe in which a space to be a resonance chamber is defined,
By inserting the outer peripheral portion of the other end portion of the exhaust pipe into the inner pipe, a step is formed in the connection portion between the other end portion of the exhaust pipe and the inner pipe, and the through hole is connected to the other end of the exhaust pipe. A resonance device, wherein the resonance device is formed in the inner pipe so as to be close to a connection portion between an end portion and the inner pipe. 前記インナーパイプに前記貫通孔が１つ形成されていることを特徴とする請求項１に記載の共鳴装置。 The resonance device according to claim 1, wherein one through hole is formed in the inner pipe. 前記貫通孔が、排気ガスが前記段差を通過したときに気流の乱れが生じる位置に形成されることを特徴とする請求項１または請求項２に記載の共鳴装置。 3. The resonance device according to claim 1, wherein the through hole is formed at a position where turbulence of an air flow occurs when exhaust gas passes through the step. 4. 請求項１ないし請求項３のいずれか１の請求項に記載の共鳴装置を備えた内燃機関の排気装置において、
内燃機関に接続された第１の消音器と、前記第１の消音器に一端部が接続された第１の排気管と、前記第１の排気管の他端部に接続された第２の消音器と、前記第２の消音器に一端部が接続された第２の排気管とを備え、
前記第１の排気管の延在方向長さと前記第２の排気管および前記インナーパイプの延在方向長さとを略同一長さに形成し、前記第２の排気管の他端部の外周部を前記共鳴装置のインナーパイプに挿通したことを特徴とする内燃機関の排気装置。 An exhaust system for an internal combustion engine comprising the resonance device according to any one of claims 1 to 3,
A first silencer connected to the internal combustion engine, a first exhaust pipe having one end connected to the first silencer, and a second exhaust connected to the other end of the first exhaust pipe. A silencer, and a second exhaust pipe having one end connected to the second silencer,
The length in the extending direction of the first exhaust pipe and the length in the extending direction of the second exhaust pipe and the inner pipe are formed to be substantially the same length, and the outer peripheral portion of the other end of the second exhaust pipe Is inserted through the inner pipe of the resonance device. 前記第２の消音器が、前記第１の排気管の他端部および前記第２の排気管の一端部が接続され、複数の貫通孔を有するインナーパイプと、前記インナーパイプの周囲を取り囲むようにして前記インナーパイプに取付けられ、前記インナーパイプの外周部との間で共鳴室となる空間が画成されるアウターパイプとを備え、前記共鳴室に吸音材が設けられることを特徴とする請求項４に記載の内燃機関の排気装置。 The second silencer is connected to the other end of the first exhaust pipe and one end of the second exhaust pipe, and surrounds the inner pipe having a plurality of through holes and the inner pipe. An outer pipe that is attached to the inner pipe and that defines a space serving as a resonance chamber between the outer periphery of the inner pipe and a sound absorbing material is provided in the resonance chamber. Item 5. An exhaust system for an internal combustion engine according to Item 4.
JP2007232797A 2007-09-07 2007-09-07 Resonance device and exhaust device of internal combustion engine Pending JP2009062922A (en)

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