JPH02248612A - Exhaust device for internal combustion negine - Google Patents
Exhaust device for internal combustion negineInfo
- Publication number
- JPH02248612A JPH02248612A JP1287253A JP28725389A JPH02248612A JP H02248612 A JPH02248612 A JP H02248612A JP 1287253 A JP1287253 A JP 1287253A JP 28725389 A JP28725389 A JP 28725389A JP H02248612 A JPH02248612 A JP H02248612A
- Authority
- JP
- Japan
- Prior art keywords
- cylindrical part
- exhaust
- air diffuser
- inverted conical
- cylindrical
- 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
- 238000002485 combustion reaction Methods 0.000 title claims abstract description 10
- 238000000034 method Methods 0.000 claims description 5
- 238000004904 shortening Methods 0.000 abstract 1
- 239000007789 gas Substances 0.000 description 9
- 238000005273 aeration Methods 0.000 description 1
- 238000009792 diffusion process Methods 0.000 description 1
- 230000000763 evoking effect Effects 0.000 description 1
- 230000002000 scavenging effect Effects 0.000 description 1
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
- F01N13/08—Other arrangements or adaptations of exhaust conduits
-
- 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
- F01N1/06—Silencing apparatus characterised by method of silencing by using interference effect
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B27/00—Use of kinetic or wave energy of charge in induction systems, or of combustion residues in exhaust systems, for improving quantity of charge or for increasing removal of combustion residues
- F02B27/04—Use of kinetic or wave energy of charge in induction systems, or of combustion residues in exhaust systems, for improving quantity of charge or for increasing removal of combustion residues in exhaust systems only, e.g. for sucking-off combustion gases
-
- 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
- F01N2470/00—Structure or shape of gas passages, pipes or tubes
- F01N2470/20—Dimensional characteristics of tubes, e.g. length, diameter
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/10—Internal combustion engine [ICE] based vehicles
- Y02T10/12—Improving ICE efficiencies
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Exhaust Silencers (AREA)
Abstract
Description
【発明の詳細な説明】
この発明は排気ガスの流れ方向に順次配設された排気管
、散気装置、円筒状部及び逆円錐状部材の部品を有する
出力決定部品と、マフラーとから成っていて、予排気圧
力波の正の反射に作用する部品は生成された正圧波がシ
リンダの再給気に寄与するような距離を排出口との間に
置いて配置されており、排気工程により喚起される排気
装置内の圧力変動が給気交換を促進する構成の内燃エン
ジン用排気装置に関する。DETAILED DESCRIPTION OF THE INVENTION The present invention consists of an output determining part including an exhaust pipe, an air diffuser, a cylindrical part, and an inverted conical member arranged in sequence in the flow direction of exhaust gas, and a muffler. Therefore, the parts that act on the positive reflection of the pre-evacuation pressure wave are placed at a distance from the exhaust port such that the generated positive pressure wave contributes to the refilling of the cylinder, and is aroused by the evacuation process. The present invention relates to an exhaust system for an internal combustion engine in which pressure fluctuations within the exhaust system facilitate air exchange.
ドイツの文献、Ｈ，ペンシュ著、オートバイ技術（エン
ジン、ブック出版、１４６／１４７ページ）から基本構
造が出力決定部品とマフラーとから成っている排気装置
が公知である。出力決定部品は順次、排気口、排気管、
散気装置、円筒状部、反射ブラインド、及び端管の部品
から成っている。排気装置の出力部は排気ガス圧力変動
の活用のため決定的な役割を果たす、各構成部品はトル
クが大きい領域で排気の最適な圧力比を達成するため特
別な機能を有している。所望の圧力特性は構成部品を考
慮して次のようになる。即ち、高圧で排気口から排出さ
れるガスは排気管を貫流して散気装置に到達し、そこで
断面積が急激に拡大することにより、負の反射が喚起さ
れる。そこで生成される負圧波は排気口方向に逆流し、
それによってシリンダ内の給気交換を促進する。しかし
、排気圧力波は散気装置内では部分的にしか反射されな
い。From the German literature H. Pensch, Motorcycle Technology (Engine, Book Publishing, pages 146/147), an exhaust system is known whose basic structure consists of a power-determining part and a muffler. The output determining parts are the exhaust port, exhaust pipe,
It consists of the following parts: a diffuser, a cylindrical section, a reflective blind, and an end tube. The output part of the exhaust system plays a decisive role in exploiting the exhaust gas pressure fluctuations; each component has a special function to achieve the optimum pressure ratio of the exhaust in the high torque region. The desired pressure characteristics are as follows, taking into account the components. That is, the gas discharged from the exhaust port at high pressure flows through the exhaust pipe and reaches the diffuser, where the cross-sectional area rapidly expands, causing negative reflection. The negative pressure waves generated there flow back toward the exhaust port,
This facilitates air exchange within the cylinder. However, the exhaust pressure wave is only partially reflected within the diffuser.
圧力波の別の部分は更に反射ブラインドまで進行し、そ
こで圧力波の正の反射が行われ、それによって、正圧波
が排気口へと戻る。この圧力波は、消滅したシリンダ内
への外気給気を再促進し、もって動的な後続給気を実現
する役割を果たす。Another part of the pressure wave travels further to the reflective blind where a positive reflection of the pressure wave takes place, thereby returning the positive pressure wave to the exhaust port. This pressure wave serves to reinvigorate the extinguished external air supply into the cylinder and thereby realize a dynamic subsequent air supply.
生成された排気装置内の圧力波は音速で伝播する。出力
決定部品の総長さはＤＥ−ＰＳ９４６９３０及びＤＥ−
ＰＳ９６４００５号に依れば、構造部で反射する正の圧
力波が“排気口閉鎖”の直前に再度シリンダに届くよう
に定められている。The generated pressure waves within the exhaust system propagate at the speed of sound. The total length of the output determining parts is DE-PS946930 and DE-
According to PS964005, it is provided that the positive pressure wave reflected from the structure reaches the cylinder again just before "exhaust port closure".
公知の技術的解決方法では排気装置の部品は排気ガスの
流九方向に順次配設されており、そのため特に同調トル
クが小さい場合は排気装置の長さが長くなる。そのため
オートバイの場合、収納スペースの点で又、オートバイ
のデザインの観点から問題が生じ、更に排気装置の表面
から大きな騒音が生じる原因となる。In known technical solutions, the parts of the exhaust system are arranged one after the other in the direction of exhaust gas flow, which results in a long length of the exhaust system, especially when the tuning torque is small. In the case of motorcycles, this creates problems in terms of storage space and in terms of the design of the motorcycle, and also causes a lot of noise to be generated from the surface of the exhaust system.
この発明の目的は、出力決定部品の構造的配置及び構成
によって、排気装置の長さを縮小し、且つ内燃エンジン
の排気口で給気交換を最適に促進するような圧力特性を
達成することである。この発明に本質は、出力決定部品
が排気ガスの流れ方向に順次配設されているだけではな
く、互いに集塊化されて重なり合って配設されており、
それにより、進行する排気圧力波は偶数２ｎの負の反射
及びｎの正の反射によって（２ｎ＋１）回だけその進行
方向の符号を転換し、且つ排気ガスの流れ方向の出口室
内の機能を保証するために特別の反射ブラインドは設け
られないことにある。進行する排気ガス圧力波の複数回
に及ぶ進行方向転換を達成するため、円筒状部の前部の
逆円錐部材はマフラーと対向して配置され、かつ散気装
置もしくは排気管と連結され、且つ散気装置は逆円錐部
材を貫き１円筒状部の一部まで突出し、その際、断面内
の散気装置の直径は円筒状部の直径よりも小さく、その
結果環状スリットが形成される。さらに別の実施態様で
は、内部に散気装置が突出し、散気装置の出口で円筒状
部と共に環状スリットを形成する円筒状部は前端部では
開放されており、直径がより大きい第二円筒状部によっ
て部分的に包囲されているので１両方の円筒状部の間に
は第二の環状スリットが形成され、且つ円筒状部はマフ
ラーの方向では逆円錐状部を介して円筒状部と、又、前
端部では部品、好適には逆円錐状部を介して散気装置も
しくは排気管と連結される０円筒状部もしくは散気装置
の領域内にも逆円錐状部として、直径が段階付けされた
ブラインドすなわち反射壁が設けられている。散気装置
と円筒状部との断面での直径比は０．８５乃至０．６５
の範囲にある。散気装置は出口部に流れをスムーズにす
るための湾曲部を設けることができる。The object of the invention is to reduce the length of the exhaust system and to achieve, by the structural arrangement and configuration of the power-determining components, pressure characteristics that optimally promote charge air exchange at the exhaust outlet of an internal combustion engine. be. The essence of this invention is that the output determining parts are not only arranged sequentially in the flow direction of exhaust gas, but also arranged in clusters and overlapping each other.
Thereby, the advancing exhaust pressure wave changes the sign of its traveling direction only (2n+1) times by an even number of 2n negative reflections and n positive reflections, and guarantees the function of the exhaust gas flow direction in the outlet chamber. Therefore, no special reflective blinds are provided. In order to achieve multiple changes in direction of the traveling exhaust gas pressure wave, the inverted conical member at the front of the cylindrical part is arranged opposite to the muffler and is connected to the air diffuser or the exhaust pipe, and The diffuser protrudes through the inverted conical part to a part of the cylindrical part, the diameter of the diffuser in the cross section being smaller than the diameter of the cylindrical part, so that an annular slit is formed. In a further embodiment, the cylindrical part in which the air diffuser protrudes and which together with the cylindrical part form an annular slit at the outlet of the air diffuser is open at the front end and is shaped like a second cylindrical part having a larger diameter. 1 so that a second annular slit is formed between both cylindrical parts, and in the direction of the muffler the cylindrical part connects to the cylindrical part via the inverted conical part; In addition, at the front end there is also a cylindrical part or an inverted conical part in the area of the diffuser which is connected to the part, preferably an inverted conical part, to the diffuser or exhaust pipe, with a graduated diameter. A reflective blind or reflective wall is provided. The diameter ratio in the cross section of the air diffuser and the cylindrical part is 0.85 to 0.65
within the range of The air diffuser can be provided with a curved part at the outlet part to smooth the flow.
控えとして散気装置と円筒用状部との間に流通口を有す
る支持板を設けることができる０円筒状部内の断面とマ
フラーの始端部との間隔は円筒状部の直径の少なくとも
半分である。A support plate having a flow port may be provided between the air diffuser and the cylindrical part as a backup.The distance between the cross section inside the cylindrical part and the starting end of the muffler is at least half the diameter of the cylindrical part. .
この発明に基づく排気装置の出力決定部品の実施態様に
よって、該出力決定部品内の流入する排気圧力波は反射
された排気圧力波が再度排気口機構に到達するまで奇数
（２ｎ＋１）回、その進行方向の符号を変え、給気交換
の改善に寄与する。The embodiment of the power-determining component of the exhaust system according to the invention allows the incoming exhaust pressure wave in the power-determining component to travel an odd number of (2n+1) times until the reflected exhaust pressure wave reaches the exhaust port mechanism again. Changes the sign of the direction and contributes to improving supply air exchange.
進行方向転換のため、偶数２ｎの負の反射及びｎの正の
反射が実現される。それによって、断面積が狭い部位で
の正の反射は必ずしも排気ガスの流れ方向になくてもよ
くなる。圧力波が複数回方向転換することは、出力決定
部品の長さを大幅に縮小し、同時に光出力を達成するた
めの前提条件である。Due to the direction change, an even number of 2n negative reflections and n positive reflections are realized. As a result, positive reflection at a portion with a narrow cross-sectional area does not necessarily have to be in the flow direction of the exhaust gas. Multiple redirection of the pressure wave is a prerequisite for significantly reducing the length of the power-determining component and at the same time achieving a light output.
つぎにこの発明の実施例を添付図面を参照しつつ詳細に
説明する。添付図面は排気装置を概略的に図示したもの
である。Next, embodiments of the present invention will be described in detail with reference to the accompanying drawings. The accompanying drawings schematically depict an exhaust system.
排気装置の出力決定部品は排気管３と、散気装置４と、
円筒状部５と、逆円錐部６とから構成されている。逆円
錐状部６は円筒状部５の前端部１０でマフラー１２と対
向して配設され、且つ逆円錐状部６は散気装置４もしく
は排気管３と連結されているので、逆円錐状部６は閉鎖
構造になっている。散気装置４は逆円錐状部６を貫いて
、円筒状部５ので出口室１１の断面８まで突起している
。散気装置４の直径ｄＤＨ円筒状部５の直径ｄＺよりも
小さい、双方の直径ｄＤとｄＺとの比率は０．８５乃至
０．６５である。散気装置４の直径のほうが小さいこと
によって、断面８の散気装置４と円筒状部５との間には
環状スリット７が形成されている。The output determining parts of the exhaust system are an exhaust pipe 3, a diffuser 4,
It is composed of a cylindrical portion 5 and an inverted conical portion 6. The inverted conical part 6 is disposed at the front end 10 of the cylindrical part 5 to face the muffler 12, and since the inverted conical part 6 is connected to the air diffuser 4 or the exhaust pipe 3, the inverted conical part 6 has an inverted conical shape. Section 6 has a closed structure. The air diffuser 4 passes through the inverted conical portion 6 and projects from the cylindrical portion 5 to the cross section 8 of the outlet chamber 11 . The diameter dDH of the aeration device 4 is smaller than the diameter dZ of the cylindrical portion 5, and the ratio of both diameters dD and dZ is 0.85 to 0.65. Since the diameter of the air diffuser 4 is smaller, an annular slit 7 is formed between the air diffuser 4 and the cylindrical portion 5 having a cross section 8 .
第一図に示す反射長さは次の通りである。The reflection lengths shown in Figure 1 are as follows.
ＬＲ＝ＬＡ＋ＬＫ＋ＬＺ＋ＬＧ／２．第二図では円筒状
部５内の逆円錐状部６の代わりに散気装置４の領域に直
径に段階付けされたブラインド１３が設けてあり、これ
は散気装置４又は円筒状部５と固定的に連結されている
。LR=LA+LK+LZ+LG/2. In FIG. 2, instead of the inverted cone 6 in the cylindrical part 5, a diameter-graded blind 13 is provided in the area of the diffuser 4, which is connected to the diffuser 4 or to the cylindrical part 5. Fixedly connected.
第３図は出力決定部品の複数回の集塊化が行われた排気
装置を示している。この実施態様では内部に散気装置４
が突出し、断面８内の散気装置の出口で円筒状部５と共
に環状スリット７を形成する円筒状部５は前端部１０で
は開放されており。FIG. 3 shows an exhaust system in which output-determining components have been agglomerated multiple times. In this embodiment, there is an air diffuser 4 inside.
The cylindrical part 5, which projects and forms an annular slit 7 with the cylindrical part 5 at the outlet of the air diffuser in the cross section 8, is open at the front end 10.
直径がより大きい第二円筒状部１４によって部分的に包
囲されている。それによって、双方の円筒状部５，１４
の間の断面１６ないに第二の環状スリット１７が形成さ
れる１円筒状部１４はマフラー１２の方向では逆円錐状
部６を介して円筒状部５と、又、前端部１８では部品、
好適には逆円錐状部１５を介して散気装置４もしくは排
気管３と連結されている。逆円錐状部として真っ直ぐの
壁を設けることも可能である。第三図に示す反射長さは
次のとおりである。It is partially surrounded by a second cylindrical part 14 of larger diameter. Thereby, both cylindrical parts 5, 14
A second annular slit 17 is formed in the cross section 16 between the cylindrical part 14 and the cylindrical part 5 via the inverted conical part 6 in the direction of the muffler 12, and also in the front end 18 of the part,
It is preferably connected to the air diffuser 4 or the exhaust pipe 3 via the inverted conical portion 15. It is also possible to provide a straight wall as an inverted cone. The reflection lengths shown in Figure 3 are as follows.
ｉ＝１ ｉ＝に
更に第三図には主反射の推移曲線が示され、この場合も
圧力波の進行方向の５回の転換が示されている。第四図
では散気装置４は出口部に湾曲部１９を設けている。第
五図では散気装置ｉ！４と円筒状部５との間に流通口２
１を有する支持板２０を設けている。それによって、一
方では散気装置４が円筒状部５に支持され、他方では流
通口２１の面積を定めることにより、排気構造が同一で
ある場合のトルク、乃至出口曲線に影響を及ぼすことが
できる。その際、支持板２０と断面８との間隔は所望の
特性曲線に応じて定めることができる。i=1 i= In addition, FIG. 3 shows the course curve of the main reflection, again showing five changes in the direction of travel of the pressure wave. In FIG. 4, the air diffuser 4 is provided with a curved portion 19 at the outlet portion. In Figure 5, the air diffuser i! 4 and the cylindrical part 5 has a flow port 2
A support plate 20 having 1 is provided. Thereby, on the one hand, the diffuser 4 is supported in the cylindrical part 5, and on the other hand, by determining the area of the flow opening 21, it is possible to influence the torque or exit curve for the same exhaust structure. . In this case, the distance between the support plate 20 and the cross section 8 can be determined depending on the desired characteristic curve.
第一乃至第五図に示したバリエーションでは、主反射を
引き起こす前記構成部品の下で、さらに別の反射部位が
生じる。従って、全ての実施態様において、出力決定部
品とマフラーとの連結部位での付加的な反射を計算に入
れる必要がある。第、天国では、逆円錐状部６でもさら
に付加的な反射が生じる。従って、断面８とマフラー始
端部との間隔及び、第三図の断面１６と逆円錐状部材１
５の固定点との間隔は、これらの反射現象が排気口で実
現される圧力特性に好影響を及ぼすように定められる。In the variations shown in Figures 1 to 5, further reflection sites occur below the component that causes the main reflection. Therefore, in all embodiments it is necessary to take into account the additional reflections at the connection between the power-determining component and the muffler. In the second heaven, an additional reflection also occurs in the inverted conical portion 6. Therefore, the distance between the cross section 8 and the starting end of the muffler, and the distance between the cross section 16 and the inverted conical member 1 in FIG.
The distance from the fixed point 5 is such that these reflection phenomena have a positive influence on the pressure characteristics achieved at the outlet.
第六図は４サイクル内燃エンジン用の実施例を示してい
る。基本構造は第一図に示したものと同じである。しか
し、この場合興味深いのは、排気段階中、据え付けられ
たマフラー１２によって予測される反射への負の影響が
圧力特性に及ぼされないことである。マフラーから１２
から反射される圧力波は従って、“排気口閉鎖”の後で
初めて排気弁に届くことが必要である。それに基づいて
、断面８とマフラー１２との間隔が定められるべきもの
である。排気工程中、第一図に示すように次の経過をた
どる。即ち、予排気圧力波が排気管口と排気管３を通過
する０次にこの圧力波は散気装置４を通過する。散気装
置４の断面積が次第に拡大していることにより、シリン
ダの掃気工程を持続的に促進する負の圧力波（帰還波部
分）が排気口ｌに送り返される。断面８内には、前進す
る圧力波に対して、急激な断面積の拡大部があり、その
結果、際立った負の反射が喚起され、この負の反射は、
一方では排気口１へと逆流する負の圧力波を生じ、他方
では前進する負圧波として逆円錐状部６の他方に進行す
る。それによって圧力波の走行方向が転換する。逆円錐
状部６では断面積が狭くなることによって、到達する負
圧波は単極で反射し、そのため再度圧力波の走行方向が
転換する。断面８には到達する負の圧力波によって急激
な断面積の拡大部があるので、圧力波の極性が変化する
。そのため、正圧波は排気口１の方向に進行する。FIG. 6 shows an embodiment for a four-stroke internal combustion engine. The basic structure is the same as shown in Figure 1. However, what is interesting in this case is that during the evacuation phase, the negative influence on the reflections expected by the installed muffler 12 is not exerted on the pressure characteristics. 12 from the muffler
It is therefore necessary for the pressure waves reflected from the exhaust valve to reach the exhaust valve only after "exhaust port closure". Based on this, the distance between the cross section 8 and the muffler 12 should be determined. During the evacuation process, the following progress is followed as shown in Figure 1. That is, the pre-exhaust pressure wave passes through the exhaust pipe port and the exhaust pipe 3, and then this pressure wave passes through the air diffuser 4. Due to the gradually increasing cross-sectional area of the air diffuser 4, a negative pressure wave (return wave part) that continuously promotes the scavenging process of the cylinder is sent back to the exhaust port l. Within the cross-section 8 there is a sharp widening of the cross-sectional area for the advancing pressure wave, as a result of which a pronounced negative reflection is evoked, which negative reflection is
On the one hand, it produces a negative pressure wave that flows back into the outlet 1 and on the other hand, it travels as a forward negative pressure wave to the other side of the inverted cone 6. This changes the direction of travel of the pressure waves. Since the cross-sectional area of the inverted conical portion 6 is narrowed, the arriving negative pressure wave is reflected by a single pole, so that the traveling direction of the pressure wave is changed again. Since the cross section 8 has a sharply enlarged cross-sectional area due to the arriving negative pressure wave, the polarity of the pressure wave changes. Therefore, the positive pressure wave travels in the direction of the exhaust port 1.
即ち、圧力波の進行方向は新たに転換したことになる。In other words, the direction of travel of the pressure wave has been newly changed.
適性に同調すると、この圧力波によって排気工程の終了
前にシリンダの再給気が可能になる。出力決定部品内の
図示した推移曲線は簡略化したメカニズムを示したもの
に過ぎない、説明した工程の他、多くの別の反射が生じ
る０例えば。When properly tuned, this pressure wave allows the cylinder to be re-aired before the end of the evacuation stroke. The illustrated curves in the output-determining component only represent a simplified mechanism; in addition to the steps described, many other reflections occur, for example.
圧力波が散気装置４内に還流する際に反射が生じる。何
故ならば、そのとき断面積の継続的な狭窄が存在し、又
は円筒状部５の出口室１１内に流入する圧力波部分の反
射も計算にいれる必要があるからである。優れた効果を
伴って圧力波反射の前述の工程を実現するためには、断
面８内の散気装置４と円筒状部５との直径の比率を最適
にすることが必要である。逆円錐状部６から反射された
排気圧力波が“排気口閉鎖″の直前に排気口に確実に到
達するように保証するため、所望の同調トルク領域に必
要な反射長ＬＲを定めなければならない。Reflection occurs when the pressure waves flow back into the diffuser 4. This is because there is then a continuous narrowing of the cross-sectional area, or reflections of the pressure wave portion flowing into the outlet chamber 11 of the cylindrical part 5 also have to be taken into account. In order to realize the aforementioned process of pressure wave reflection with good effectiveness, it is necessary to optimize the ratio of the diameters of the diffuser 4 and the cylindrical part 5 in the cross section 8. In order to ensure that the exhaust pressure wave reflected from the inverted cone 6 reaches the exhaust port just before "exhaust port closure", the reflection length LR required for the desired tuning torque region must be determined. .
開示された構造は特に４サイクル内燃エンジンの場合、
排気ガスの自由な排出が、排出方向への据え付けによっ
て妨害されずに、排気弁における所望の圧力分布が達成
できると言う利点を備えている。The disclosed structure is particularly suitable for four-stroke internal combustion engines.
The free evacuation of the exhaust gases has the advantage that the desired pressure distribution at the exhaust valve can be achieved without being hindered by mounting in the evacuation direction.
第一図は２サイクル内燃エンジン用排気装置と排気口に
おける最適な圧力特性曲線のグラフである。
第二図は直径に段階付けされたブラインドを備えた排気
装置である。
第三図は圧力波の進行方向が５回転換する内燃エンジン
用排気装置の別の実施態様と排気口での最適な圧力特性
のグラフである。
第四図は散気装置の出口が流れをよくする構造になって
いる排気装置である。
第五図は支持リングを備えた排気装置である。
第六図は４サイクル内燃エンジン用排気装置と排気口に
おける最適な圧力特性曲線のグラフである。
図中符号
１・・・排気口
２・・・排気口
３・・・排気間
４・・・散気装置
５・・・円筒状部
６・・・逆円錐状部
７・・・環状スリット
８・・・断面
９・・・固定点
１０・・・前端部
１１・・・出口室
１２・・・マフラー
１３・・・ブラインド
１４・・・円筒状部
１５−・・逆円錐状部
１６・・・断面
１７・・・環状スリット
１８・・・前端部
１９・・・湾曲部
２０・・・支持板
２１・・・貫通口
ｄＤ・・・散気装置直径
ｄＺ・・・円筒状部の直径
ｎ＝・・・（１，２，３，４゜
ＬＡ・・・排気口の長さ
ＬＫ・・・排気間の長さ
ＬＤ・・・散気装置の長さ
ＬＺ・・・円筒状部の長さ
ＬＧ・・・逆円錐状部の長さFIG. 1 is a graph of an exhaust system for a two-stroke internal combustion engine and an optimum pressure characteristic curve at the exhaust port. FIG. 2 shows an exhaust system with diameter-graded blinds. FIG. 3 is a graph of another embodiment of an exhaust system for an internal combustion engine in which the direction of the pressure wave changes five times and the optimum pressure characteristics at the exhaust port. Figure 4 shows an exhaust system in which the outlet of the air diffuser has a structure that improves the flow. FIG. 5 shows an exhaust device with a support ring. FIG. 6 is a graph of an exhaust system for a four-stroke internal combustion engine and an optimum pressure characteristic curve at the exhaust port. Reference numeral 1 in the figure... Exhaust port 2... Exhaust port 3... Exhaust gap 4... Air diffuser 5... Cylindrical portion 6... Inverted conical portion 7... Annular slit 8 ...Cross section 9...Fixing point 10...Front end portion 11...Outlet chamber 12...Muffler 13...Blind 14...Cylindrical portion 15-...Inverted conical portion 16...・Cross section 17...Annular slit 18...Front end 19...Curved portion 20...Support plate 21...Through hole dD...Diffusion device diameter dZ...Cylindrical part diameter n =...(1,2,3,4゜LA...Length of exhaust port LK...Length between exhausts LD...Length of air diffuser LZ...Length of cylindrical part SLG...Length of the inverted conical part
Claims (1)
装置、円筒状部及び逆円錐状部材の部品を有する出力決
定部品と、マフラーとから成っていて、予排気圧力波の
正の反射に作用する部品は生成された正圧波がシリンダ
への再給気に寄与するような距離を排出口との間に置い
て配置されており、排気工程により喚起される排気装置
内の圧力変動が給気交換を助長する構成の内燃エンジン
用排気装置において、出力決定部品は排気ガスの流れ方
向に順次配設されているだけではなく、互いに集塊化さ
れて重なり合って配設されており、それにより、進行す
る排気圧力波は偶数２ｎの負の反射及びｎの正の反射に
よって（２ｎ＋１）回だけその進行方向の符号を変化し
、且つ排気ガスの流れ方向の出口室内の機能を保証する
ために特別の反射ブラインドは設けられないことを特徴
とする排気装置。 ２、進行する排気ガス圧力波の複数回に及ぶ進行方向転
換を達成するため、円筒状部５の前部の逆円錐部材６は
マフラー１２と対向して配置され、かつ散気装置４もし
くは排気管３と連結され、且つ散気装置４は逆円錐部材
６を貫き、円筒状部５の一部まで突出し、その際、断面
８内の散気装置４の直径は円筒状部５の直径よりも小さ
く、その結果環状スリット７が形成されたことを特徴と
する請求項１記載の排気装置。 ３、内部に散気装置４が突出し、散気装置の出口で円筒
状部５と共に環状スリット７を形成する円筒状部５は前
端部１０では開放されており、直径がより大きい第二円
筒状部１４によって部分的に包囲されているので、両方
の円筒状部５、１４の間には第二の環状スリット１７が
形成され、且つ円筒状部１４はマフラー１２の方向では
逆円錐状部６を介して円筒状部５と又、前端部１８では
部品、好適には逆円錐状部１５を介して散気装置４もし
くは排気管３と連結されたことを特徴とする請求項１及
び２記載の排気装置。 ４、円筒状部５もしくは散気装置４の領域内の逆円錐状
部６として、直径が段階付けされたブラインド１３すな
わち反射壁を設けたことを特徴とする請求項１乃至３記
載の排気装置。 ５、散気装置４と円筒状部５との断面８での直径比（ｄ
Ｄ／ｄＺ）は０．８５乃至０．６５の範囲にあることを
特徴とする請求項１乃至４記載の排気装置。 ６、散気装置４が出口部に流れをスムーズにするための
湾曲部を設けたことを特徴とする請求項１乃至５記載の
排気装置。 ７、散気装置４と円筒状部５との間に流通口２１を有す
る支持板２０を設けたことを特徴とする請求項１乃至６
記載の排気装置。 ８、円筒状部５内の断面８とマフラー１２の始端部との
間隔は円筒状部５の直径の少なくとも半分であることを
特徴とする請求項１乃至７記載の排気装置。[Scope of Claims] 1. Consists of an output determining part including an exhaust pipe, an air diffuser, a cylindrical part, and an inverted conical member arranged in sequence in the flow direction of exhaust gas, and a muffler, The components acting on the positive reflection of the pre-evacuation pressure wave are placed at such a distance from the exhaust port that the generated positive pressure wave contributes to the refilling of the cylinder, and is aroused by the evacuation process. In an exhaust system for an internal combustion engine that has a configuration in which pressure fluctuations within the exhaust system facilitate air exchange, the output determining parts are not only arranged sequentially in the flow direction of exhaust gas, but also agglomerated and overlapped with each other. As a result, the advancing exhaust pressure wave changes the sign of its traveling direction by (2n+1) times due to an even number of 2n negative reflections and n positive reflections, and also changes the sign of the exhaust gas flow direction by (2n+1) times. An exhaust system characterized in that no special reflective blinds are provided to ensure the functionality of the exit chamber. 2. In order to achieve multiple changes in the traveling direction of the advancing exhaust gas pressure wave, the inverted conical member 6 at the front of the cylindrical part 5 is disposed facing the muffler 12, and is connected to the air diffuser 4 or the exhaust gas. The air diffuser 4 is connected to the pipe 3 and extends through the inverted conical member 6 and protrudes to a part of the cylindrical part 5, in which case the diameter of the air diffuser 4 in the cross section 8 is smaller than the diameter of the cylindrical part 5. 2. Exhaust device according to claim 1, characterized in that the annular slit (7) is also small, so that an annular slit (7) is formed. 3. The air diffuser 4 protrudes inside, and the cylindrical part 5, which together with the cylindrical part 5 forms an annular slit 7 at the outlet of the air diffuser, is open at the front end 10 and is connected to a second cylindrical part with a larger diameter. 14 , so that a second annular slit 17 is formed between the two cylindrical parts 5 , 14 , and in the direction of the muffler 12 the cylindrical part 14 is surrounded by an inverted conical part 6 3. According to claims 1 and 2, it is connected to the cylindrical part 5 via the cylindrical part 5 and also to the air diffuser 4 or the exhaust pipe 3 via a component, preferably an inverted conical part 15, at the front end part 18. exhaust system. 4. The exhaust system according to claims 1 to 3, characterized in that the cylindrical part 5 or the inverted conical part 6 in the area of the air diffuser 4 is provided with a blind 13, that is, a reflecting wall, with a stepped diameter. . 5. Diameter ratio (d
5. The exhaust system according to claim 1, wherein D/dZ) is in the range of 0.85 to 0.65. 6. The exhaust device according to any one of claims 1 to 5, wherein the air diffuser 4 is provided with a curved portion at the outlet portion to smooth the flow. 7. Claims 1 to 6 characterized in that a support plate 20 having a flow port 21 is provided between the air diffuser 4 and the cylindrical portion 5.
Exhaust system as described. 8. The exhaust system according to claim 1, wherein the distance between the cross section 8 in the cylindrical part 5 and the starting end of the muffler 12 is at least half the diameter of the cylindrical part 5.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DD89326597A DD286727A7 (en) | 1989-03-15 | 1989-03-15 | EXHAUST SYSTEM FOR AN INTERNAL COMBUSTION ENGINE |
| DD02B/326597-3 | 1989-03-15 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH02248612A true JPH02248612A (en) | 1990-10-04 |
Family
ID=5607737
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP1287253A Pending JPH02248612A (en) | 1989-03-15 | 1989-11-02 | Exhaust device for internal combustion negine |
Country Status (5)
| Country | Link |
|---|---|
| JP (1) | JPH02248612A (en) |
| DD (1) | DD286727A7 (en) |
| DE (1) | DE3926921A1 (en) |
| FR (1) | FR2644510A1 (en) |
| GB (1) | GB2229224A (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US8356690B2 (en) | 2009-08-28 | 2013-01-22 | Toyota Jidosha Kabushiki Kaisha | Exhaust apparatus for an internal combustion engine |
Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| AT3206U1 (en) * | 1998-10-07 | 1999-11-25 | Avl List Gmbh | EXHAUST SYSTEM FOR A TWO-STROKE COMBUSTION ENGINE |
| WO2011161042A1 (en) * | 2010-06-22 | 2011-12-29 | Bekaert Combustion Technology B.V. | Fluegas slit cavity muffler |
| JP5870488B2 (en) * | 2011-01-20 | 2016-03-01 | マツダ株式会社 | Intake and exhaust system for multi-cylinder engine |
| GB202111213D0 (en) * | 2021-08-03 | 2021-09-15 | Mclaren Automotive Ltd | Improved sound bypass |
Family Cites Families (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB790330A (en) * | 1954-09-27 | 1958-02-05 | Schweizerische Lokomotiv | Improvements in or relating to a supercharged four-stroke-cycle internal combustion engine |
| US3665712A (en) * | 1970-02-09 | 1972-05-30 | William L Tenney | Two-cycle engine resonance exhaust system |
| DK128427B (en) * | 1971-11-24 | 1974-04-29 | Silentor As | Muffler. |
| GB1513473A (en) * | 1974-08-28 | 1978-06-07 | Yamaha Motor Co Ltd | Method and apparatus for silencing the exhaust noise of internal combustion engines |
| JPS5813738B2 (en) * | 1977-07-15 | 1983-03-15 | 川崎重工業株式会社 | Exhaust pipe for 2-stroke engine |
| JPS5813739B2 (en) * | 1977-07-15 | 1983-03-15 | 川崎重工業株式会社 | Exhaust pipe for 2-stroke engine |
| JPS63968Y2 (en) * | 1981-04-08 | 1988-01-12 | ||
| JPH0689668B2 (en) * | 1986-06-19 | 1994-11-09 | ヤマハ発動機株式会社 | Exhaust system for 2-cycle engine |
| JPH0681901B2 (en) * | 1986-06-19 | 1994-10-19 | ヤマハ発動機株式会社 | Exhaust system for 2-cycle engine |
| SE464097B (en) * | 1987-06-18 | 1991-03-04 | Claes Linden | EXHAUST RANGE EXPLAINED AS A RESONATOR ON A COMBUSTION ENGINE |
| DD271734A1 (en) * | 1988-05-04 | 1989-09-13 | Fortschritt Veb K | EXHAUST SYSTEM FOR SECONDARY MOTOR MOTORS |
-
1989
- 1989-03-15 DD DD89326597A patent/DD286727A7/en unknown
- 1989-08-16 DE DE3926921A patent/DE3926921A1/en not_active Withdrawn
- 1989-10-02 GB GB8922139A patent/GB2229224A/en not_active Withdrawn
- 1989-10-31 FR FR8914268A patent/FR2644510A1/en not_active Withdrawn
- 1989-11-02 JP JP1287253A patent/JPH02248612A/en active Pending
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US8356690B2 (en) | 2009-08-28 | 2013-01-22 | Toyota Jidosha Kabushiki Kaisha | Exhaust apparatus for an internal combustion engine |
Also Published As
| Publication number | Publication date |
|---|---|
| FR2644510A1 (en) | 1990-09-21 |
| GB2229224A (en) | 1990-09-19 |
| GB8922139D0 (en) | 1989-11-15 |
| DE3926921A1 (en) | 1990-09-27 |
| DD286727A7 (en) | 1991-02-07 |
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