JPS5951646B2 - Combustion chamber of internal combustion engine - Google Patents
Combustion chamber of internal combustion engineInfo
- Publication number
- JPS5951646B2 JPS5951646B2 JP13624378A JP13624378A JPS5951646B2 JP S5951646 B2 JPS5951646 B2 JP S5951646B2 JP 13624378 A JP13624378 A JP 13624378A JP 13624378 A JP13624378 A JP 13624378A JP S5951646 B2 JPS5951646 B2 JP S5951646B2
- Authority
- JP
- Japan
- Prior art keywords
- combustion chamber
- combustion
- cylinder head
- swirling flow
- generated
- 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.)
- Expired
Links
Landscapes
- Combustion Methods Of Internal-Combustion Engines (AREA)
Description
【発明の詳細な説明】 本発明は内燃機関の燃焼室に関する。[Detailed description of the invention] The present invention relates to a combustion chamber of an internal combustion engine.
従来より燃焼速度を速めるために吸気ポー１へをヘリカ
ル状に形成して吸気行程時に燃焼室内に旋回流を発生せ
しめるようにしたり、或いはビス１〜ン頂面とシリンダ
ヘッド内壁面間にスキッシュエリアを形成してスキッシ
ュエリアから噴出するスキッシュ流により圧縮行程末期
に燃焼室内に旋回流を発生せしめるようにした内燃機関
が知られている。In order to increase the combustion speed, the intake port 1 is formed in a helical shape to generate a swirling flow inside the combustion chamber during the intake stroke, or a squish area is formed between the top surface of the screw 1 and the inner wall surface of the cylinder head. An internal combustion engine is known in which a swirling flow is generated in a combustion chamber at the end of a compression stroke by a squish flow that forms a squish flow and jets out from a squish area.
しかしながらこのように燃焼室内に旋回流を発生せしめ
ても火炎の伝播速が未だ十分に速くなく、特に残留ガス
が多く燃焼の終了期の火炎伝播が冗漫になりやすい軽負
荷時においては大きなトルク変動をひき起こし、車両サ
ージを生ずるという問題がある。However, even if swirling flow is generated in the combustion chamber in this way, the flame propagation speed is still not fast enough, and large torque fluctuations occur especially under light loads where there is a lot of residual gas and flame propagation tends to become redundant at the end of combustion. There is a problem that this causes a surge in the vehicle.
このような問題を解決すべく燃焼室内の火炎伝播の様子
を写真撮影により観察したところ燃焼室内壁面付近にお
ける火炎の伝播速度が遅くなり、その結果特に後半での
燃焼期間が長くなるためにトルク変動ひいては車両サー
ジなどをひき起こすことが判明したのである。In order to solve this problem, we observed the state of flame propagation inside the combustion chamber by taking photographs and found that the flame propagation speed near the wall surface of the combustion chamber becomes slower, and as a result, the combustion period becomes longer especially in the latter half, causing torque fluctuations. It was also found that this caused vehicle surges.
本発明は燃焼室内壁面付近の混合気にマイクロタービュ
レンスを発生せしめて燃焼室内壁面付近における火炎の
伝播速度を速め、それによってすみやかでかつ安定した
燃焼を行なう内燃機関を提供することにある。An object of the present invention is to provide an internal combustion engine that generates microturbulence in the air-fuel mixture near the wall surface of the combustion chamber to increase the propagation speed of flame near the wall surface of the combustion chamber, thereby achieving rapid and stable combustion.
以下、添附図面を参照して本発明の詳細な説明する。Hereinafter, the present invention will be described in detail with reference to the accompanying drawings.
第１図並びに第２図を参照すると、１はシリンダブロッ
ク、２は平坦な頂面を有しかつシリンダブロック１内で
往復動するピストン、３はシリンダブロック１上に固定
されたシリンダヘッド、４はピストン２とシリンダヘッ
ド３間に形成された燃焼室、５はヘリカル状に形成され
た吸気ポート、６は吸気弁、７は排気ポート、８は排気
弁、９は点火栓を夫々示す。Referring to FIGS. 1 and 2, 1 is a cylinder block, 2 is a piston having a flat top surface and reciprocating within the cylinder block 1, 3 is a cylinder head fixed on the cylinder block 1, and 4 is a cylinder block. 1 is a combustion chamber formed between a piston 2 and a cylinder head 3, 5 is a helical intake port, 6 is an intake valve, 7 is an exhaust port, 8 is an exhaust valve, and 9 is a spark plug.
この実施例では第１図並びに第２図に示すように互いに
等間隔をおいて配置された断面矩形の多数個の突起１０
がピストン２の頂面周縁に沿うシリンダヘッド内壁面周
縁部の全周に亘ってシリンダヘッド内壁面周部縁上に一
体形成される。In this embodiment, as shown in FIGS. 1 and 2, a large number of protrusions 10 each having a rectangular cross section are arranged at regular intervals.
is integrally formed on the peripheral edge of the inner wall surface of the cylinder head over the entire circumference of the peripheral edge of the inner wall surface of the cylinder head along the peripheral edge of the top surface of the piston 2.
吸気行程時、可燃混合気が吸気弁６を介して吸気ポート
５から燃焼室４内に導入される。During the intake stroke, combustible air-fuel mixture is introduced into the combustion chamber 4 from the intake port 5 via the intake valve 6 .
このとき前述したように吸気ポート５はヘリカル状に形
成されているので可燃混合気は旋回しつつ燃焼室４内に
流入し、次いでこの可燃混合気は滑らかなシリンダ内壁
面に沿って旋回して強力な旋回流を燃焼室４内に発生す
る。At this time, as mentioned above, since the intake port 5 is formed in a helical shape, the combustible mixture flows into the combustion chamber 4 while swirling, and then this combustible mixture swirls along the smooth inner wall surface of the cylinder. A strong swirling flow is generated within the combustion chamber 4.
ピストン２の頂面が平坦に形成されているのでこの旋回
流はピストン２が下死点に達し、次いで圧縮作用が行な
われている間さほど減衰することなく維持される。Since the top surface of the piston 2 is formed flat, this swirling flow is maintained without being significantly attenuated until the piston 2 reaches the bottom dead center and then the compression action is performed.
次いでビス１〜ン２が上死点に近づくと旋回混合気流の
周辺部は突起１０によって乱れを与えられ、その結果シ
リンダーベッド３の内壁面周縁部上にはマイクロタービ
ュレンスが発生する。Next, when the screws 1 to 2 approach the top dead center, the periphery of the swirling air mixture is disturbed by the protrusion 10, and as a result, microturbulence is generated on the periphery of the inner wall surface of the cylinder bed 3.
次いで点火栓９により燃焼室４内の可燃混合気が着火さ
れると旋回流が発生しているために火炎は急速に燃焼室
４内に伝播し、更にシリンダヘッド３の内壁面周縁部上
にはマイクロタービュレンスが発生しているので火炎は
シリンダヘッド３の内壁面周縁部上においても減速され
ることなく高速度で伝播して燃焼室４内の隅々まで達す
るので燃焼室４内の可燃混合気は完全に燃焼せしめられ
ることになる。Next, when the flammable mixture in the combustion chamber 4 is ignited by the ignition plug 9, the flame rapidly propagates into the combustion chamber 4 due to the swirling flow, and further spreads onto the periphery of the inner wall surface of the cylinder head 3. Since microturbulence is generated, the flame propagates at high speed without being decelerated even on the periphery of the inner wall surface of the cylinder head 3 and reaches every corner of the combustion chamber 4. The mixture will be completely combusted.
このようにシリンダヘッド内壁面周縁部上に突起１０を
形成することによって火炎の伝播速度を燃焼の初期およ
び中期のみならず終了期においても速めることができる
のですみやかで安定した燃焼を行なわせしめることがで
き、トルク変動並びに車両日カージを大巾に軽減するこ
とができる。By forming the protrusions 10 on the peripheral edge of the inner wall surface of the cylinder head in this manner, the flame propagation speed can be increased not only in the initial and middle stages of combustion but also in the final stage, so that prompt and stable combustion can be achieved. This makes it possible to greatly reduce torque fluctuations and vehicle damage.
第３図並びに第４図は別の実施例を示す。3 and 4 show another embodiment.
なおこの実施例でも第１図と同様に吸気ポーＩ〜５はヘ
リカル状に形成される。Note that in this embodiment as well, the intake ports I to 5 are formed in a helical shape as in FIG.
この実施例では点火栓９と反対側に位置するシリンダヘ
ッド３の内壁周縁部上に一対の鋸歯状突起１１が形され
る。In this embodiment, a pair of sawtooth protrusions 11 are formed on the peripheral edge of the inner wall of the cylinder head 3 located on the opposite side from the ignition plug 9.
この実施例では燃焼の終了期において燃焼変動しやすい
領域内に特にマイクロタービュレンスを発生させること
により火炎の伝播速度を速めて安定した状態で燃焼を完
了せしめるようにしている。In this embodiment, microturbulence is generated particularly in a region where combustion is likely to fluctuate at the end of combustion, thereby increasing the flame propagation speed and completing combustion in a stable state.
また、第４図に示す実施例においては矢印Ｗの方向に旋
回流が発生するがこの旋回流Ｗの流れ方向に対して点火
栓９の上流近傍に更に別の鋸歯状突起１２がシリンダヘ
ッド内壁周縁部上に形成される。In the embodiment shown in FIG. 4, a swirling flow is generated in the direction of the arrow W, and another serrated projection 12 is formed on the inner wall of the cylinder head near the upstream side of the spark plug 9 with respect to the flow direction of the swirling flow W. formed on the periphery.
この突起１２を設けることによって突起１２により発生
したマイクロタービュレンスが点火栓９の電極筒りに案
内され、それによって点火栓９の電極に形成された火炎
核の成長を１逆進することができるので安定した着火を
確保することができる。By providing this protrusion 12, the microturbulence generated by the protrusion 12 is guided to the electrode barrel of the spark plug 9, thereby reversing the growth of the flame kernel formed on the electrode of the spark plug 9. Therefore, stable ignition can be ensured.
以上述べたように本発明によればピストン頂面を平坦に
形成することによって吸気行程および圧縮行程時に旋回
流が弱められることがなく、従って点火が行なわれる圧
縮行程末期においても燃焼室内には強力な旋回流が発生
維持せしめられる。As described above, according to the present invention, by forming the top surface of the piston flat, the swirling flow is not weakened during the intake stroke and compression stroke, and therefore, even at the end of the compression stroke when ignition occurs, there is a strong A swirling flow is generated and maintained.
そして、このように圧縮行程末期においても燃焼室内に
は強力な旋回流が発生維持せしめられるので旋回流の周
辺部はシリンダヘッド内壁面周縁部に形成された突起に
よって強力な乱れを与えられ、斯くしてシリンダヘッド
内壁面周縁部上には強力なマイクロタービュレンスが発
生する。In this way, even at the end of the compression stroke, a strong swirling flow is generated and maintained in the combustion chamber, so the periphery of the swirling flow is strongly disturbed by the protrusions formed on the periphery of the inner wall of the cylinder head. As a result, strong microturbulence is generated on the peripheral edge of the inner wall surface of the cylinder head.
このように本発明では圧縮行程末期に燃焼室内に強力な
旋回流が発生せしめられるので燃焼の初期および中期に
おける火炎の伝播速度を速めることができ、更に圧縮行
程末期にシリンダヘッド内壁面周縁部上には強力なマイ
クロタービュレンスが発生しているので燃焼の終了期に
おける火炎の伝播速度を速めることができる。In this way, in the present invention, a strong swirling flow is generated in the combustion chamber at the end of the compression stroke, so that the flame propagation speed can be increased in the early and middle stages of combustion. Since strong microturbulence occurs in the combustion process, the flame propagation speed can be increased at the end of combustion.
従って特に軽負荷時において燃焼後半における燃焼時間
を短かくすることができるので訃ルク変動を大巾に低減
することができる。Therefore, especially when the load is light, the combustion time in the latter half of combustion can be shortened, so that the variation in motor torque can be greatly reduced.
第１図は第２図のＩ−Ｉ線に沿ってみた本発明に係る内
燃機関の側面断面図、第２図は第１図のシリンダヘッド
の底面図、第３図は第４図のＩＩＩ−ＩＩＩ線に沿って
みた別の実施例の側面断面図、第４図は第３図のシリン
ダヘッドの底面図である。
２・・・ビス１〜ン、３・・・シリンダヘッド、４・・
・燃焼室、６・・・吸気弁、８・・・排気弁、９・・・
点火栓、１０．１１，１２・・・突起。1 is a side sectional view of an internal combustion engine according to the present invention taken along the line II in FIG. 2, FIG. 2 is a bottom view of the cylinder head in FIG. 1, and FIG. FIG. 4 is a side sectional view of another embodiment taken along line -III, and FIG. 4 is a bottom view of the cylinder head of FIG. 3. 2... Screws 1~, 3... Cylinder head, 4...
・Combustion chamber, 6... Intake valve, 8... Exhaust valve, 9...
Spark plug, 10.11,12...Protrusion.
Claims (1)
うにした内燃機関において、ピストン頂面を平坦に形成
し、ピストン頂面周縁に沿うシリンダヘッド内壁面周縁
部上に複数個のマイクロタービュレンス発生用突起を形
成した内燃機関の燃焼室。1. In an internal combustion engine that generates a swirling flow in the combustion chamber during the engine intake stroke, the top surface of the piston is formed flat, and multiple microturbulences are generated on the periphery of the inner wall surface of the cylinder head along the periphery of the top surface of the piston. Combustion chamber of an internal combustion engine with a projection.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP13624378A JPS5951646B2 (en) | 1978-11-07 | 1978-11-07 | Combustion chamber of internal combustion engine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP13624378A JPS5951646B2 (en) | 1978-11-07 | 1978-11-07 | Combustion chamber of internal combustion engine |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS5564122A JPS5564122A (en) | 1980-05-14 |
| JPS5951646B2 true JPS5951646B2 (en) | 1984-12-15 |
Family
ID=15170623
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP13624378A Expired JPS5951646B2 (en) | 1978-11-07 | 1978-11-07 | Combustion chamber of internal combustion engine |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS5951646B2 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0319484Y2 (en) * | 1985-12-16 | 1991-04-24 |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5898624A (en) * | 1981-12-07 | 1983-06-11 | Mitsubishi Heavy Ind Ltd | Combustion chamber of diesel engine |
| US4541376A (en) * | 1982-12-20 | 1985-09-17 | Alun Thomas | Internal combustion engine |
-
1978
- 1978-11-07 JP JP13624378A patent/JPS5951646B2/en not_active Expired
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0319484Y2 (en) * | 1985-12-16 | 1991-04-24 |
Also Published As
| Publication number | Publication date |
|---|---|
| JPS5564122A (en) | 1980-05-14 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| JPS5949407B2 (en) | Combustion chamber of internal combustion engine | |
| US3923015A (en) | Combustion chamber of spark ignition internal combustion engine | |
| US4367707A (en) | Combustion chamber of an internal combustion engine | |
| US4178903A (en) | Internal combustion engine with an auxiliary combustion chamber | |
| US4041923A (en) | Internal combustion engine of lean air-fuel mixture combustion type | |
| JPS5951646B2 (en) | Combustion chamber of internal combustion engine | |
| JPS6011626A (en) | Combustion chamber for split combustion type engine | |
| US4489686A (en) | Torch ignition type internal combustion engine | |
| JP2003049650A (en) | Compressed self-ignition internal combustion engine | |
| GB1261176A (en) | Internal combustion spark ignition engines | |
| JPS5845572B2 (en) | Combustion chamber of internal combustion engine | |
| US4182286A (en) | Tapered torch passage construction for internal combustion | |
| JPH0830414B2 (en) | Combustion chamber structure of internal combustion engine | |
| JPH04287826A (en) | Spark ignition internal combustion engine of auxiliary chamber | |
| JPS58206821A (en) | Reciprocating internal-combustion engine | |
| JP2007085220A (en) | Combustion chamber structure for spark ignition engine | |
| US4176646A (en) | Method of igniting in an internal combustion engine | |
| JPH07119469A (en) | Side valve internal combustion engine | |
| JPS5924817Y2 (en) | Combustion device of internal combustion engine | |
| KR200155754Y1 (en) | Apparatus for improving combustion efficiency | |
| JPS5943464Y2 (en) | side valve engine | |
| JPH0635829B2 (en) | Internal combustion engine | |
| JPH0828344A (en) | Overhead valve kerosene engine | |
| JPS6221712Y2 (en) | ||
| US4182285A (en) | Cylindrical torch passage construction for internal combustion engine |