JPS5974325A - Exhaust device for internal-combustion engine - Google Patents
Exhaust device for internal-combustion engineInfo
- Publication number
- JPS5974325A JPS5974325A JP18425482A JP18425482A JPS5974325A JP S5974325 A JPS5974325 A JP S5974325A JP 18425482 A JP18425482 A JP 18425482A JP 18425482 A JP18425482 A JP 18425482A JP S5974325 A JPS5974325 A JP S5974325A
- Authority
- JP
- Japan
- Prior art keywords
- muffler
- engine
- internal combustion
- mufflers
- combustion engine
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
- 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
- F01N13/04—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 silencers in parallel, e.g. having interconnections for multi-cylinder engines
Abstract
Description
【発明の詳細な説明】 本発明は内燃機関の排気装置に関する。[Detailed description of the invention] The present invention relates to an exhaust system for an internal combustion engine.
一般に内燃機関においては、その排気系特に消音器が出
力特性に大きな影響を及ぼすことは言うまでもないが、
単一の消音器で低速性能から高速性能までをも充分に引
き出すことは極めて難かしく、低速もしくは高速性能の
いずれかが犠牲となる場合が多い。In general, it goes without saying that in internal combustion engines, the exhaust system, especially the muffler, has a large effect on the output characteristics.
It is extremely difficult to fully bring out both low-speed and high-speed performance with a single muffler, and either low-speed or high-speed performance is often sacrificed.
本発明はこのような事情にもとづいてなされたもので、
低速域から高速域までの全運転領域に亘って充分な出力
性能が得られる内燃機関の排気装置の提供を目的とする
。The present invention was made based on these circumstances, and
The object of the present invention is to provide an exhaust system for an internal combustion engine that can obtain sufficient output performance over the entire operating range from low speed range to high speed range.
すなわち、本発明は上記目的を達成するため、気筒から
導出された排気管を、出力特性が相異る複数の消音器に
接続するとともに、この排気管と上記少なくともいずれ
か1個の消音器との連通路を開閉する制御弁を設け、こ
の制御弁を内燃機関の運転負荷に応じて開閉制御するこ
とにより、排気を運転負荷に最適な消音器に導びくよう
にしたことを特徴とする。That is, in order to achieve the above object, the present invention connects an exhaust pipe led out from a cylinder to a plurality of mufflers having different output characteristics, and connects this exhaust pipe to at least one of the above mufflers. The present invention is characterized in that a control valve is provided to open and close the communication passage, and by controlling the opening and closing of this control valve according to the operating load of the internal combustion engine, exhaust gas is guided to a muffler that is optimal for the operating load.
以下本発明の一実施例を自動二輪車に適用した図面にも
とづいて説明する。An embodiment of the present invention will be described below based on drawings in which it is applied to a motorcycle.
図中1は4気筒内燃機関であり、夫々の気筒2 a +
2 b + 2 cおよび2dには排気管、:la。1 in the figure is a 4-cylinder internal combustion engine, and each cylinder 2 a +
2b + 2c and 2d have exhaust pipes, :la.
J b + 3cおよび3dが接続されている。排気管
3h、3b、3cおよび3dの後端は排気チャンバ4内
で互に1つに集合されており、この排気チャンバ4の下
流側端部は2本に分岐されている。そしてこれら各分岐
部5,6には後輪19の両側に位置して消音器7,8が
連結されている。これら消音器7,8は外形が互に同形
状をなしてお9、夫々膨張室9,10の下流側に複数の
隔壁11・・・と紋り管12・・・とで構成される消音
室13.14を有している。一方の消音器9の消音室1
3は隔壁11や紋り管12の数が少く、排気抵抗が極め
て少ない内部構造となっている。これに対して他方の消
音器10の消音室14は隔壁11や紋9管12の数が多
く、上記一方の消音器9よりも抵気抵抗が大きい内部構
造となっている。したがって、一方の消音器9は高回転
域での性能を重視した構造となっているとともに、他方
の消音器1θは低中回転域での性能を重視した構造とな
っており、互いに出力特性が異なっている。J b + 3c and 3d are connected. The rear ends of the exhaust pipes 3h, 3b, 3c, and 3d are gathered together in the exhaust chamber 4, and the downstream end of the exhaust chamber 4 is branched into two pipes. Mufflers 7 and 8 are connected to each of these branch portions 5 and 6 on both sides of the rear wheel 19. These mufflers 7 and 8 have the same external shape 9 and are composed of a plurality of partition walls 11 and a strut tube 12 on the downstream side of the expansion chambers 9 and 10, respectively. It has chambers 13 and 14. Sound deadening chamber 1 of one silencer 9
No. 3 has a small number of partition walls 11 and pierced pipes 12, and has an internal structure with extremely low exhaust resistance. On the other hand, the muffling chamber 14 of the other muffler 10 has a large number of partition walls 11 and pipes 12, and has an internal structure with greater resistance than the muffler 9. Therefore, one silencer 9 has a structure that emphasizes performance in the high rotation range, and the other silencer 1θ has a structure that emphasizes performance in the low and medium rotation range, so that the output characteristics of each are different. It's different.
各消音器9,10と排気チャンバ4との連通部分には、
この連通路を開閉する制御弁15゜20が設けられてい
る。そして制御弁15.20は内燃機関1の運転状況に
応じて開閉制御される。すなわち、一方の制御弁20は
内燃機関1の始動時から中負荷運転時にかけて開操作さ
れる常開形のもので、本実施例の場合、内燃機関1の回
転数(rpm )をイグニッションユニット16の点火
パルスから検出し、この検出信号が所定レベル、例えば
内燃機関1の回転数に対して5000 rpmに達した
時点でコントロールユニット17は制御弁20の駆動源
であるパルスモーク18に作動信号を与え、この作動信
号により制御弁20が閉操作されるようになっている。In the communication portion between each silencer 9, 10 and the exhaust chamber 4,
Control valves 15 and 20 are provided to open and close this communication passage. The control valves 15 and 20 are controlled to open and close depending on the operating status of the internal combustion engine 1. That is, one of the control valves 20 is of a normally open type that is opened from the start of the internal combustion engine 1 to the time of medium load operation. When this detection signal reaches a predetermined level, for example, 5000 rpm relative to the rotation speed of the internal combustion engine 1, the control unit 17 sends an activation signal to the pulse smoke 18, which is the drive source of the control valve 20. This activation signal causes the control valve 20 to be closed.
また他方の制御弁15は内燃機関1の低負荷および中負
荷運転時から高負荷運転への移行時に開操作される常閉
形のもので、内燃機関1の回転数が500Orpmを上
回るとコントロールユニット17からの作動信号を受け
たAルスモータ18により開操作されるようになってい
る。The other control valve 15 is a normally closed type that is opened when the internal combustion engine 1 shifts from low-load or medium-load operation to high-load operation. The opening operation is performed by the A-rus motor 18 which receives an activation signal from the A-rus motor 18.
次に上記構成の作用について説明する。Next, the operation of the above configuration will be explained.
内燃機関1の低・中負荷運転時には制御弁15が閉じ、
かつ制御弁20が開かれているため、各気筒2a、2b
、2cおよび2dから排気チャンバ4内に導びかれた
排気は、図中実線の矢印で示したように他方の消音器8
内に向つて流れる。この消音器8は低中速性能を重視し
た内部構造となっているから、排気脈動の効果によって
排気の膨張が充分になされ、低・中負荷運転時に高トル
クが得られる。During low/medium load operation of the internal combustion engine 1, the control valve 15 closes;
And since the control valve 20 is open, each cylinder 2a, 2b
, 2c and 2d into the exhaust chamber 4, the exhaust gas is directed into the other muffler 8 as shown by the solid arrow in the figure.
Flow inward. Since this muffler 8 has an internal structure emphasizing low and medium speed performance, the exhaust gas is sufficiently expanded by the effect of exhaust pulsation, and high torque can be obtained during low and medium load operation.
一方、高負荷運転に移行し、内燃機関1の回転数が50
00 rpmを上回ると、コントロールユニット17か
らの作動信号により制御弁15が開かれる一方制御弁2
0は閉じられるから、この時点からは排気チャンバ4と
一方の消音器7とが連通され、排気は破線の矢印で示す
ように一方の消音器7に流れ込む。この消音器7は上記
他方の消音器8よりも抵気抵抗が少なく高速性能を重視
した内部構造となっているから、高負荷運転に至るとそ
れに応じて排気効率が高められ、高トルク、高出力が得
られる。したがってこの構成によれば、排気を運転負荷
に応じた最適な出力特性を持つ消音器7,8に導びける
ので、低速域から高速域までの全運転領域に亘って高ト
ルク、高出力な特性が得られる。On the other hand, the internal combustion engine 1 shifts to high-load operation, and the rotational speed of the internal combustion engine 1 increases to 50.
00 rpm, the control valve 15 is opened by an actuation signal from the control unit 17, while the control valve 2 is opened.
0 is closed, from this point on the exhaust chamber 4 and one of the mufflers 7 are communicated with each other, and the exhaust gas flows into one of the mufflers 7 as shown by the dashed arrow. This muffler 7 has an internal structure that has less resistance than the other muffler 8 and emphasizes high-speed performance, so when high-load operation is reached, the exhaust efficiency is increased accordingly, resulting in high torque and high-speed performance. I get the output. Therefore, according to this configuration, the exhaust gas can be guided to the silencers 7 and 8 that have optimal output characteristics according to the operating load, so high torque and high output can be achieved over the entire operating range from low speed range to high speed range. characteristics are obtained.
なお、上述した実施例では高負荷運転に移行5−
する状態を内燃機関の回転数から検出したが、例えば排
気圧力等から検出しても良く、また内燃機関の回転数を
検出する手段も電気式に限らず機械式であっても良い。In the above-described embodiment, the state of transition to high-load operation was detected from the rotational speed of the internal combustion engine, but it may also be detected from, for example, the exhaust pressure, and the means for detecting the rotational speed of the internal combustion engine may also be electrical. It is not limited to a type, but may be a mechanical type.
また制御弁は夫々の消音器と排気管との連通路に設ける
ものに特定されず、例えば一方の高速型の消音器と排気
管との連通路のみに設けても良く、要は排気管と少なく
ともいずれか1個の消音器との連通路を開閉できれば良
い。Furthermore, the control valve is not limited to being provided in the communication path between each muffler and the exhaust pipe, but may be provided only in the communication path between one high-speed muffler and the exhaust pipe, for example, and in short, the control valve may be provided only in the communication path between one of the high-speed mufflers and the exhaust pipe. It is sufficient if the communication path with at least one of the silencers can be opened and closed.
さらに上述した実施例では、消音器を低中速型と高速型
の2本としたが、例えば低速型、中速型および高速型の
3本としても良い。Further, in the above-described embodiment, there are two silencers, a low-medium speed type and a high-speed type, but it is also possible to use three silencers, for example, a low-speed type, a medium-speed type, and a high-speed type.
さらに本発明に係る内燃機関は、4気筒等の多気筒内燃
機関に特定されるものではなく、単気筒内燃機関であっ
ても同様に実施できる。Further, the internal combustion engine according to the present invention is not limited to a multi-cylinder internal combustion engine such as a four-cylinder engine, but can be similarly implemented even if it is a single-cylinder internal combustion engine.
以上詳述したように本発明によれば、排気管を出力特性
が相異る複数の消音器に接続するとともに、この排気管
と上記少なくともいずれか1個の消音器との連通路を開
閉する制御弁を設け、この制御弁を内燃機関の運転負荷
に応じて6−
開閉制御するようにしたから、排気を運転負荷に応じた
最適な出力特性を持つ消音器に導ひくことができ、低速
域から高速域までの全運転領域に亘って高トルク、高出
力な特性が得られる等の利点がある。As detailed above, according to the present invention, an exhaust pipe is connected to a plurality of mufflers having different output characteristics, and a communication path between the exhaust pipe and at least one of the mufflers is opened and closed. Since a control valve is provided and the control valve is controlled to open and close according to the operating load of the internal combustion engine, exhaust gas can be guided to a silencer with optimal output characteristics according to the operating load, and low-speed It has the advantage of being able to provide high torque and high output characteristics over the entire operating range from high speed to high speed.
図面は本発明の一笑施例を示す概略構成図である。
1・・・内燃機関、2a〜2d・・・気筒、3a〜3d
・・・排気管、7.8・・・消音器、15,2θ・・・
制御弁O
出願人代理人 弁理士 鈴 江 武 彦7−The drawings are schematic configuration diagrams showing one embodiment of the present invention. 1... Internal combustion engine, 2a-2d... Cylinder, 3a-3d
...exhaust pipe, 7.8...silencer, 15,2θ...
Control valve O Applicant's agent Patent attorney Takehiko Suzue 7-
Claims (1)
消音器に接続するとともに、この排気管と上記少なくと
もいずれか1個の消音器との連通路を開閉する制御弁を
設け、この制御弁は内燃機関の運転負荷に応じて開閉制
御するようにしたことを特徴とする内燃機関の排気装置
。The exhaust pipe led out from the cylinder is connected to a plurality of mufflers having different output characteristics, and a control valve is provided for opening and closing a communication path between the exhaust pipe and at least one of the above-mentioned mufflers. An exhaust system for an internal combustion engine, characterized in that the control valve is controlled to open and close according to the operating load of the internal combustion engine.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP18425482A JPS5974325A (en) | 1982-10-20 | 1982-10-20 | Exhaust device for internal-combustion engine |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP18425482A JPS5974325A (en) | 1982-10-20 | 1982-10-20 | Exhaust device for internal-combustion engine |
Publications (1)
Publication Number | Publication Date |
---|---|
JPS5974325A true JPS5974325A (en) | 1984-04-26 |
Family
ID=16150087
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP18425482A Pending JPS5974325A (en) | 1982-10-20 | 1982-10-20 | Exhaust device for internal-combustion engine |
Country Status (1)
Country | Link |
---|---|
JP (1) | JPS5974325A (en) |
Cited By (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS61138814A (en) * | 1984-12-10 | 1986-06-26 | Yamaha Motor Co Ltd | Exhaust pipe for motorcycle |
US4809800A (en) * | 1984-12-10 | 1989-03-07 | Yamaha Hatsudoki Kabushiki Kaisha | Exhaust system for vehicle |
JPH01195908A (en) * | 1988-01-30 | 1989-08-07 | Mazda Motor Corp | Engine exhauster |
EP0329165A2 (en) * | 1988-02-18 | 1989-08-23 | Mazda Motor Corporation | Engine-control apparatus |
US4901528A (en) * | 1988-01-16 | 1990-02-20 | Nissan Motor Co., Ltd. | System for suppressing noise due to exhaust gas from motor vehicle |
US5003781A (en) * | 1988-05-23 | 1991-04-02 | Mazda Motor Corporation | Air supply and exhaust control systems for turbocharged internal combustion engines |
US5301503A (en) * | 1991-07-26 | 1994-04-12 | Ferrari S.P.A. | Vehicle internal combustion engine exhaust system |
JP2010012447A (en) * | 2008-07-07 | 2010-01-21 | Ckd Corp | Device for feeding dried air |
-
1982
- 1982-10-20 JP JP18425482A patent/JPS5974325A/en active Pending
Cited By (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS61138814A (en) * | 1984-12-10 | 1986-06-26 | Yamaha Motor Co Ltd | Exhaust pipe for motorcycle |
US4809800A (en) * | 1984-12-10 | 1989-03-07 | Yamaha Hatsudoki Kabushiki Kaisha | Exhaust system for vehicle |
US4901528A (en) * | 1988-01-16 | 1990-02-20 | Nissan Motor Co., Ltd. | System for suppressing noise due to exhaust gas from motor vehicle |
JPH01195908A (en) * | 1988-01-30 | 1989-08-07 | Mazda Motor Corp | Engine exhauster |
EP0329165A2 (en) * | 1988-02-18 | 1989-08-23 | Mazda Motor Corporation | Engine-control apparatus |
US5003781A (en) * | 1988-05-23 | 1991-04-02 | Mazda Motor Corporation | Air supply and exhaust control systems for turbocharged internal combustion engines |
US5301503A (en) * | 1991-07-26 | 1994-04-12 | Ferrari S.P.A. | Vehicle internal combustion engine exhaust system |
JP2010012447A (en) * | 2008-07-07 | 2010-01-21 | Ckd Corp | Device for feeding dried air |
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