JP2521902B2 - Combustion chamber of internal combustion engine - Google Patents

Combustion chamber of internal combustion engine

Info

Publication number
JP2521902B2
JP2521902B2 JP60270287A JP27028785A JP2521902B2 JP 2521902 B2 JP2521902 B2 JP 2521902B2 JP 60270287 A JP60270287 A JP 60270287A JP 27028785 A JP27028785 A JP 27028785A JP 2521902 B2 JP2521902 B2 JP 2521902B2
Authority
JP
Japan
Prior art keywords
combustion chamber
fuel
injection port
corner
combustion
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 - Lifetime
Application number
JP60270287A
Other languages
Japanese (ja)
Other versions
JPS62129517A (en
Inventor
史郎 石田
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Isuzu Motors Ltd
Original Assignee
Isuzu Motors Ltd
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Isuzu Motors Ltd filed Critical Isuzu Motors Ltd
Priority to JP60270287A priority Critical patent/JP2521902B2/en
Priority to US06/935,450 priority patent/US4733643A/en
Priority to AU65690/86A priority patent/AU586595B2/en
Priority to DE8686116498T priority patent/DE3674160D1/en
Priority to EP86116498A priority patent/EP0225551B1/en
Priority to CN86108109A priority patent/CN1009473B/en
Publication of JPS62129517A publication Critical patent/JPS62129517A/en
Application granted granted Critical
Publication of JP2521902B2 publication Critical patent/JP2521902B2/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Classifications

    • 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
    • F02B23/00—Other engines characterised by special shape or construction of combustion chambers to improve operation
    • F02B23/08—Other engines characterised by special shape or construction of combustion chambers to improve operation with positive ignition
    • F02B23/10—Other engines characterised by special shape or construction of combustion chambers to improve operation with positive ignition with separate admission of air and fuel into cylinder
    • F02B2023/103—Other engines characterised by special shape or construction of combustion chambers to improve operation with positive ignition with separate admission of air and fuel into cylinder the injector having a multi-hole nozzle for generating multiple sprays
    • 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
    • F02B75/00—Other engines
    • F02B75/12—Other methods of operation
    • F02B2075/125—Direct injection in the combustion chamber for spark ignition engines, i.e. not in pre-combustion chamber

Landscapes

  • Combustion Methods Of Internal-Combustion Engines (AREA)
  • Fuel-Injection Apparatus (AREA)

Description

【発明の詳細な説明】 ［産業上の利用分野］ 本発明は内燃機関の燃焼室に係り、特に、アルコール
・ガソリン等の揮発性が高く、セタン価の低い燃料油を
使用できる内燃機関の燃焼室に関する。Description: TECHNICAL FIELD The present invention relates to a combustion chamber of an internal combustion engine, and more particularly to combustion of an internal combustion engine capable of using fuel oil having a high volatility such as alcohol and gasoline and a low cetane number. Regarding the room.

［従来の技術］ 一般に熱効率が高く、燃料消費率が良い燃焼室を有す
る内燃機関の提案としては、第９図、第10図に示す直噴
式ディーゼルエンジン（実開昭59−81775号公報）があ
る。[Prior Art] In general, as a proposal of an internal combustion engine having a combustion chamber having high thermal efficiency and good fuel consumption rate, a direct injection diesel engine (Japanese Utility Model Publication No. 59-81775) shown in FIGS. is there.

図示されるこの提案はシリンダヘッドａに配設される
燃料噴射ノズルｂに、燃焼噴射ノズルｂのニードル弁ｃ
が所定リフト以下で開口する副噴口ｄと所定リフト以上
で開口する主噴口ｅとを設け、副噴口ｄを燃焼室ｆ内に
突出するグロープラグ方向に指向させ、主噴口ｅをグロ
ープラグｇに燃料噴霧が衝突しない方向に指向させ、さ
らに燃焼室ｆ内に複数配設されるグロープラグｇにあっ
ては、主噴口ｅと副噴口ｄとが、グロープラグｇと同数
個形成して構成されるのである。This proposal shown in the drawing shows that a fuel injection nozzle b arranged in a cylinder head a is connected to a needle valve c of a combustion injection nozzle b.
Is provided with a sub injection port d opened below a predetermined lift and a main injection port e opened above a predetermined lift, and the sub injection port d is directed toward the glow plug projecting into the combustion chamber f, and the main injection port e is connected to the glow plug g. A plurality of glow plugs g that are oriented in a direction in which fuel spray does not collide and that are arranged in the combustion chamber f are formed by forming the same number of main injection ports e and sub injection ports d as the glow plugs g. It is.

［発明が解決しようとする問題点］ 上記した提案は、副噴口からの微粒化された軽油をグ
ロープラグにて着火燃焼させ、その火炎を主噴口からの
燃料に伝播させるもので、燃費、出力、着火遅れ短縮の
上で優れた燃焼特性を示すものである。[Problems to be Solved by the Invention] The above-mentioned proposal is to ignite and combust finely divided light oil from the sub-injection with a glow plug and propagate the flame to the fuel from the main injection port. , Shows excellent combustion characteristics in shortening the ignition delay.

ところが、これは使用燃料が軽油等の燃料油に限られ
るもので、アルコール、ガソリン等の低セタン価・揮発
性燃料油を使用できるものではなかった。However, the fuel used is limited to fuel oil such as light oil, and low cetane number and volatile fuel oil such as alcohol and gasoline cannot be used.

これは、機関の軽負荷時に副噴口ｄから噴射される燃
料油が着火燃料できないためである。つまり、軽負荷時
に開放される噴口は副噴口ｄのみであり、その副噴口ｄ
の噴口あたりの噴射油量は少なくまた噴射燃料油ｈは、
グロープラグｇ及び燃焼室ｆの高温雰囲気によって瞬時
に蒸発されて、燃焼室ｆに対して均一分散されるからで
ある。即ち、この提案における燃焼室ｆ内の混合気は稀
薄になってグロープラグｇ周辺に着火させるための濃混
合気を生成できるものではなかった。This is because the fuel oil injected from the auxiliary injection port d cannot ignite fuel when the engine is lightly loaded. That is, the sub-jet port d is the only one that is opened when the load is light.
The amount of injected oil per nozzle is small and the injected fuel oil h is
This is because the glow plug g and the combustion chamber f instantly evaporate by the high-temperature atmosphere and are uniformly dispersed in the combustion chamber f. That is, in this proposal, the air-fuel mixture in the combustion chamber f becomes so lean that a rich air-fuel mixture for igniting around the glow plug g cannot be generated.

［発明の目的］ 本発明は上記問題点を解消すべく創案されたものであ
る。[Object of the Invention] The present invention was devised to solve the above problems.

本発明の目的は機関始動時を含むあらゆる使用負荷領
域で軽油をはじめアルコール・ガソリン等の低セタン価
・揮発性燃料油を失火なく燃焼させ得る内燃機関の燃焼
室を提供するにある。An object of the present invention is to provide a combustion chamber of an internal combustion engine capable of burning light oil, low cetane number and volatile fuel oil such as alcohol and gasoline without misfire in all usage load regions including engine startup.

［課題を解決するための手段］ 本発明は上記目的を達成するために、ピストン頂部に
窪ませられて設けられた燃焼室と、この燃焼室の内周部
に半径方向外方へ窪ませて設けられたコーナー部と、こ
のコーナー部を含むその近傍のスワール下流側にその点
火部を位置させて配設された点火プラグと、上記燃焼室
の中心よりコーナー部側の偏芯位置に配設されあらゆる
使用負荷時に上記コーナー部へ微粒化燃料噴霧を供給す
る副噴口及び所定負荷を越えてから上記燃焼室を円周方
向に等分割する方向の内周部へ向けてそれぞれ上記副噴
口から供給される微粒化燃料噴霧より粒径の大きい燃料
噴霧を供給する主噴口を有して構成された噴射ノズルと
を備えたものである。[Means for Solving the Problems] In order to achieve the above-mentioned object, the present invention is configured such that a combustion chamber is provided at the top of a piston by being recessed, and an inner peripheral portion of the combustion chamber is recessed radially outward. A corner portion provided, a spark plug having its ignition portion positioned downstream of the swirl including the corner portion, and an eccentric position closer to the corner portion than the center of the combustion chamber. The auxiliary injection port that supplies atomized fuel spray to the above corners at all usage loads, and the auxiliary injection port that supplies the combustion chamber to the inner peripheral portion in the direction where the combustion chamber is equally divided in the circumferential direction after the predetermined load is exceeded. And an injection nozzle configured to have a main injection port for supplying a fuel spray having a larger particle size than the atomized fuel spray.

［作用］ 燃焼室の内周部にこれを半径方向外方へ窪ませてコー
ナー部を設け、そして噴射ノズルを燃焼室の中心よりコ
ーナー部側の偏芯位置に配置させてその副噴口をコーナ
ー部へ臨ませると、スワールの影響が生じないコーナー
部内には、噴射ノズルの副噴口から噴射された微粒化燃
料噴霧が、主燃焼室内に流出することなく分布する。し
たがってガソリン，アルコール等のセタン価が低く揮発
性の強い燃料であっても、これをコーナー部内に分布さ
せておくことができ、ここで蒸気化させ混合気化させる
ことができる。よって点火プラグの点火を行えばあらゆ
る使用負荷において、コーナー部で確実な着火と燃焼と
を生じさせることができる。[Operation] The inner peripheral portion of the combustion chamber is dented outward in the radial direction to provide a corner portion, and the injection nozzle is arranged at an eccentric position on the corner portion side from the center of the combustion chamber, and the auxiliary injection port is cornered. When exposed to the portion, the atomized fuel spray injected from the auxiliary injection port of the injection nozzle is distributed without flowing out into the main combustion chamber in the corner portion where the influence of swirl does not occur. Therefore, even a fuel having a low cetane number and strong volatility such as gasoline and alcohol can be distributed in the corner portion, and can be vaporized and mixed and vaporized there. Therefore, if the ignition plug is ignited, reliable ignition and combustion can be generated at the corners under any load.

所定負荷を越えたとき、噴射ノズルは、各主噴口から
それぞれ燃焼室にその円周方向に等分割する方向の内周
部へ向けて燃料噴霧を噴射する。これら燃料噴霧は、コ
ーナー部で生じた火炎を伝播されて燃焼する。When a predetermined load is exceeded, the injection nozzle injects fuel spray from each main injection port into the combustion chamber toward the inner peripheral portion in the direction in which it is equally divided in the circumferential direction. These fuel sprays propagate the flame generated at the corner and burn.

［実施例］ 以下に本発明の内燃機関の燃焼室の好適−実施例を添
付図面に基づいて説明する。[Examples] Preferred examples of a combustion chamber of an internal combustion engine of the present invention will be described below with reference to the accompanying drawings.

第１図、第２図に示す１はピストンであり、２はピス
トン頂部、３はピストン頂部２を深く窪ませて形成した
燃焼室、４はシリンダヘッドである。In FIGS. 1 and 2, 1 is a piston, 2 is a piston top, 3 is a combustion chamber formed by deeply recessing the piston top 2, and 4 is a cylinder head.

燃焼室３内には、図示されないスワールポートからの
スワール化された吸気が供給されて、その燃焼室３の内
周部3aに沿ってスワールＳが生成されている。Swirlized intake air is supplied into the combustion chamber 3 from a swirl port (not shown), and a swirl S is generated along the inner peripheral portion 3a of the combustion chamber 3.

さて、本発明の内燃機関の燃焼室の特長とするところ
は、低セタン価・揮発性燃料油を機関始動時を含むあら
ゆる使用負荷領域で失火なく燃焼させることにある。Now, the feature of the combustion chamber of the internal combustion engine of the present invention is to burn the low cetane number and volatile fuel oil without misfire in any load range including engine start.

そこで、燃焼室の形状及びこれに配設される噴射ノズ
ル及びスパークプラグを以下のごとく関係づけて構成す
る。Therefore, the shape of the combustion chamber and the injection nozzles and spark plugs arranged therein are related in the following manner.

噴射ノズル５は第３図にも示すように、針弁６を昇降
自在に収納するノズルボディ７の先端に、その針弁６の
スロットル部6aが着座する弁座８を形成すると共に、そ
の弁座８より軸方向に隆起されてスロットル部6aにより
開閉される燃料噴射室９を形成し、上記弁座８に副噴口
10を、上記燃料噴射室９にその周方向に所定間隔を有し
て開口される複数の主噴口11を設けて構成される。As shown in FIG. 3, the injection nozzle 5 is formed with a valve seat 8 on which a throttle portion 6a of the needle valve 6 is seated at the tip of a nozzle body 7 which accommodates the needle valve 6 in a vertically movable manner. A fuel injection chamber 9 that is axially raised from the seat 8 and is opened and closed by the throttle portion 6a is formed.
The fuel injection chamber 9 is provided with a plurality of main injection ports 11 opened at predetermined intervals in the circumferential direction.

この噴射ノズル５の副噴口10は主噴口11に対して噴口
径が小さく設定されており、噴射ノズル５は上記針弁６
が所定リフト値以下で、副噴口10が開放され、そのリフ
ト値を越えたときに主噴口11が開放されるような、ピン
トークスタイプのものとして構成される。The auxiliary nozzle 10 of the injection nozzle 5 is set to have a smaller diameter than the main nozzle 11, and the injection nozzle 5 has the needle valve 6
Is a predetermined lift value or less, the auxiliary injection port 10 is opened, and when the lift value is exceeded, the main injection port 11 is opened, and it is configured as a pintoks type.

一方、第１図、第２図に示す如く、燃焼室３は、本実
施例ではその燃焼室３の水平断面が矩形状に形成されて
いる。矩形状に形成される燃焼室３は、これに生成され
るスワールＳに対して、そのコーナー部12がスワールＳ
の侵入しない空間を形成する。なお、燃焼室３の内周部
3aを径方向に窪ませて第４図に示すようにコーナー部12
aを形成してもよく、また第５図に示すように、スワー
ルＳに対して花びら状のものでも良い。その際にコーナ
ー部12aは燃焼室３の内周部3aに対して燃焼室３に連通
するように形成される。On the other hand, as shown in FIGS. 1 and 2, the combustion chamber 3 is formed in a rectangular horizontal cross section in this embodiment. The corner portion 12 of the combustion chamber 3 formed in a rectangular shape is swirl S with respect to the swirl S generated therein.
Form a space that does not enter. The inner peripheral portion of the combustion chamber 3
3a is recessed in the radial direction and the corner portion 12 is formed as shown in FIG.
a may be formed, and as shown in FIG. 5, it may be petal-shaped with respect to the swirl S. At that time, the corner portion 12a is formed so as to communicate with the inner peripheral portion 3a of the combustion chamber 3 in the combustion chamber 3.

本実施例にあって矩形状の燃焼室３には、その上記燃
焼室３の中心よりコーナー部12側の偏芯位置に垂下状に
噴射ノズル５が配設されており、その噴射ノズル５の副
噴口10は、上記コーナー部12の一つを臨ませられ、主噴
口11は燃焼室３を周方向に等分割する内周部3aを臨ませ
られ上記コーナー部12またはそのコーナー部12の近傍の
スワールＳ方向下流側にはスパークプラグ14が配設され
ている。In the rectangular combustion chamber 3 in the present embodiment, the injection nozzle 5 is disposed so as to hang down at an eccentric position on the corner 12 side from the center of the combustion chamber 3. The sub injection port 10 faces one of the corner portions 12, and the main injection port 11 faces the inner peripheral portion 3a that equally divides the combustion chamber 3 in the circumferential direction, and the corner portion 12 or the vicinity of the corner portion 12 thereof. A spark plug 14 is disposed on the downstream side of the swirl S direction.

以下に、本発明の内燃機関の燃焼室の作用を添付図面
に基づいて説明する。The operation of the combustion chamber of the internal combustion engine of the present invention will be described below with reference to the accompanying drawings.

機関が始動時の極低速域及び軽負荷時にあっては第３
図に示す噴射ノズル５の針弁６が供給燃料油圧に応じて
リフト方向に作動される。このリフトと同時に針弁６の
スロットル部6aが弁座８より離れ副噴口10を開放する。
このときスロットル部6aの先端に形成されるステム部13
は、針弁６が所定リフト値に達するまで燃料噴射室９を
閉成する。したがって、第６図、第７図に示すように副
噴口10からの微粒化燃料噴霧F1の一部は燃焼室３内のス
ワールＳを横切ってスワールＳの影響のないコーナー部
12へ噴出され、そのコーナー部12の壁面に衝突して更に
微粒化されてコーナー部12が形成する空間に分布され
る。これと同時に残部はコーナー部12の壁面に燃料膜Ｇ
として付着生成される。この燃料膜Ｇの外面では壁熱に
よって燃料膜Ｇの一部が蒸発され蒸気層を形成する。微
粒化された燃料噴霧F1の一部は高温の圧縮空気に触れて
瞬時に蒸気化し、この蒸気と上記燃料膜Ｇの蒸気とは、
コーナー部12の空気と混合し、着火燃料性に優れた濃い
燃料蒸気層Ｈを生成する。ここでスパークプラグ14が点
火されると上記燃料蒸気層Ｈが瞬時に着火燃焼し、着火
遅れのない急速燃焼が達成される。Third if the engine is in the extremely low speed range at start-up and at light load
The needle valve 6 of the injection nozzle 5 shown in the figure is operated in the lift direction according to the supplied fuel oil pressure. Simultaneously with this lift, the throttle portion 6a of the needle valve 6 separates from the valve seat 8 and opens the auxiliary injection port 10.
At this time, the stem portion 13 formed at the tip of the throttle portion 6a
Closes the fuel injection chamber 9 until the needle valve 6 reaches a predetermined lift value. Therefore, as shown in FIGS. 6 and 7, a part of the atomized fuel spray F 1 from the auxiliary injection port 10 crosses the swirl S in the combustion chamber 3 and a corner portion where the swirl S has no influence.
The particles are ejected to 12, collide with the wall surface of the corner 12 and are further atomized, and are distributed in the space formed by the corner 12. At the same time, the remaining portion is the fuel film G on the wall surface of the corner portion 12.
Is generated as attached. On the outer surface of the fuel film G, part of the fuel film G is evaporated by the wall heat to form a vapor layer. A part of the atomized fuel spray F 1 is instantly vaporized upon contact with the hot compressed air, and this vapor and the vapor of the fuel film G are:
By mixing with the air in the corner portion 12, a rich fuel vapor layer H excellent in ignition fuel property is generated. Here, when the spark plug 14 is ignited, the fuel vapor layer H instantly ignites and burns, and rapid combustion without ignition delay is achieved.

中・高負荷運転領域に於いては、第８図に示すように
上記副噴口10のみを開放させるリフト値を越えて針弁６
がリフトされて（スロットル期間を終了）、主噴口11も
開放される。このとき、主噴口10からは、貫徹力の大き
な燃料噴霧F2…４が内周部3aに向けて噴射され、その一
部が衝突飛散されて高温空気により蒸気化され、残部が
壁熱によって蒸気化される。即ち、燃焼室３全体にはス
ワールＳ方向に流れ、着火燃焼性の良い燃料蒸気層H1が
均一に分散されることになる。このとき、主噴口11から
噴射される燃料油量は軽負荷に対して増量されているた
めに燃焼室３内の混合気の空燃比は所望の濃度に設定さ
れるため、上記コーナー部12にて生成される火炎と火炎
エネルギーにて瞬時に火炎伝播され、燃焼が完結され
る。In the medium / high load operation region, as shown in FIG. 8, the needle valve 6 is exceeded beyond the lift value for opening only the auxiliary injection port 10.
Is lifted (throttle period ended), and the main injection port 11 is also opened. At this time, from the main injection port 10, the fuel spray F 2 ... 4 having a large penetration force is injected toward the inner peripheral portion 3a, a part of which is collided and scattered and vaporized by the high temperature air, and the rest is caused by wall heat. Is vaporized. That is, the fuel vapor layer H 1 having a good ignition and combustibility flows uniformly in the entire combustion chamber 3 in the swirl S direction. At this time, since the amount of fuel oil injected from the main injection port 11 is increased with respect to the light load, the air-fuel ratio of the air-fuel mixture in the combustion chamber 3 is set to a desired concentration, so that the corner portion 12 is The generated flame and flame energy instantly propagate the flame to complete combustion.

ここで、本実施例にあって副噴口10を１つとしたの
は、スワールＳに対する貫徹力を確保するためと、コー
ナー部12が形成する空間にスパークプラグ14の点火によ
って着火し、火炎伝播性の良い濃混合気の生成、即ち燃
料蒸気層Ｈを生成するためであり、主噴口11を４つとし
たのは、スワールＳに対して適度な貫徹力を確保し、噴
射燃料噴霧を燃焼室３に対して均一に分散させて、燃焼
蒸気層H1の形成と失火のない燃焼を成すためで、いずれ
も燃費、出力の観点で良好な燃焼を達成できるからであ
る。Here, in the present embodiment, the number of the sub-injection ports 10 is one, in order to secure the penetrating force against the swirl S and to ignite the space formed by the corner portion 12 by the ignition of the spark plug 14 so that the flame spread The reason for this is to produce a rich air-fuel mixture having a good quality, that is, to produce the fuel vapor layer H. The reason why the four main injection ports 11 are provided is to ensure a proper penetration force against the swirl S and to inject the injected fuel spray into the combustion chamber 3 This is because the combustion vapor layer H 1 is formed and combustion without misfire is achieved by uniformly dispersing the above, and both can achieve good combustion in terms of fuel consumption and output.

［発明の効果］ 以上説明したことから明らかなように本発明の内燃機
関の燃焼室によれば次のごとき優れた効果を発揮する。[Effects of the Invention] As is clear from the above description, the combustion chamber of the internal combustion engine of the present invention exhibits the following excellent effects.

（１） コーナー部に微粒化燃料噴霧を供給しこのコー
ナー部に着火性・燃焼性のよい混合気を分布させておく
ことができるようにしたので、あらゆる使用負荷で安定
した燃焼を生じさせることができる。(1) Since atomized fuel spray is supplied to the corners and a mixture with good ignitability and combustibility can be distributed in this corner, stable combustion can be generated under any load. You can

（２） 高負荷時にあっては燃焼室の空燃比を均一にで
きるので燃費、出力を大幅に向上できる。(2) At high load, the air-fuel ratio in the combustion chamber can be made uniform, so fuel consumption and output can be greatly improved.

（３） Hc、アルデヒドなどの未燃排出物を低減でき
る。(3) Unburned emissions such as Hc and aldehyde can be reduced.

【図面の簡単な説明】[Brief description of drawings]

第１図は本発明の内燃機関の燃焼室の好適一実施例を示
す概略断面図、第２図は第１図の上面図、第３図は噴射
ノズルの概略断面図、第４図、第５図は燃焼室に形成す
るコーナー部の一例を示す概略図、第６図及び第７図は
本発明の内燃機関の燃焼室の軽負荷時に於ける噴射・燃
焼状態を示す概略図、第８図は本発明の内燃機関の燃焼
室の中・高負荷時に於ける噴射燃焼状態を示す概略図、
第９図は及び第10図は従来の直噴式ディーゼルエンジン
を示す概略断面図である。 図中、１はピストン、３は燃焼室、４はシリンダヘッ
ド、５は噴射ノズル。10は副噴口、11は主噴口、12はコ
ーナー部である。FIG. 1 is a schematic sectional view showing a preferred embodiment of a combustion chamber of an internal combustion engine of the present invention, FIG. 2 is a top view of FIG. 1, FIG. 3 is a schematic sectional view of an injection nozzle, FIG. FIG. 5 is a schematic diagram showing an example of a corner portion formed in the combustion chamber, and FIGS. 6 and 7 are schematic diagrams showing the injection / combustion state of the combustion chamber of the internal combustion engine of the present invention when the load is light, FIG. 1 is a schematic diagram showing an injection combustion state at a medium and high load of a combustion chamber of an internal combustion engine of the present invention,
9 and 10 are schematic sectional views showing a conventional direct injection diesel engine. In the figure, 1 is a piston, 3 is a combustion chamber, 4 is a cylinder head, and 5 is an injection nozzle. 10 is a sub nozzle, 11 is a main nozzle, and 12 is a corner.

Claims (1)

(57)【特許請求の範囲】(57) [Claims] 【請求項１】ピストン頂部に窪ませられて設けられた燃
焼室と、該燃焼室の内周部に半径方向外方へ窪ませて設
けられたコーナー部と、該コーナー部を含むその近傍の
スワール下流側にその点火部を位置させて配設された点
火プラグと、上記燃焼室の中心よりコーナー部側の偏芯
位置に配置されあらゆる使用負荷時に上記コーナー部へ
微粒化燃料噴霧を供給する副噴口及び所定負荷を越えて
から上記燃焼室を円周方向に等分割する方向の内周部へ
向けてそれぞれ上記副噴口から供給される微粒化燃料噴
霧より粒径の大きい燃料噴霧を供給する主噴口を有して
構成された噴射ノズルとを備えたことを特徴とする内燃
機関の燃焼室。1. A combustion chamber which is recessed in the top of the piston, a corner portion which is recessed radially outward in the inner peripheral portion of the combustion chamber, and the vicinity thereof including the corner portion. A spark plug with its ignition part located downstream of the swirl and an eccentric position on the corner side from the center of the combustion chamber, which supplies atomized fuel spray to the corner part under any load. A fuel spray having a particle size larger than that of the atomized fuel spray supplied from the sub-injection port is supplied toward the inner peripheral portion in the direction in which the combustion chamber is circumferentially equally divided after exceeding the sub-injection port and a predetermined load. A combustion chamber of an internal combustion engine, comprising: an injection nozzle having a main injection port.
JP60270287A 1985-11-30 1985-11-30 Combustion chamber of internal combustion engine Expired - Lifetime JP2521902B2 (en)

Priority Applications (6)

Application Number Priority Date Filing Date Title
JP60270287A JP2521902B2 (en) 1985-11-30 1985-11-30 Combustion chamber of internal combustion engine
US06/935,450 US4733643A (en) 1985-11-30 1986-11-26 Combustion chamber arrangement for an internal combustion engine
AU65690/86A AU586595B2 (en) 1985-11-30 1986-11-26 Combustion chamber arrangement for an internal combustion engine
DE8686116498T DE3674160D1 (en) 1985-11-30 1986-11-27 COMBUSTION CHAMBER ARRANGEMENT FOR AN INTERNAL COMBUSTION ENGINE.
EP86116498A EP0225551B1 (en) 1985-11-30 1986-11-27 Combustion chamber arrangement for an internal combustion engine
CN86108109A CN1009473B (en) 1985-11-30 1986-11-29 Combustion chamber arrangement for internal combustion engine

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP60270287A JP2521902B2 (en) 1985-11-30 1985-11-30 Combustion chamber of internal combustion engine

Publications (2)

Publication Number Publication Date
JPS62129517A JPS62129517A (en) 1987-06-11
JP2521902B2 true JP2521902B2 (en) 1996-08-07

Family

ID=17484156

Family Applications (1)

Application Number Title Priority Date Filing Date
JP60270287A Expired - Lifetime JP2521902B2 (en) 1985-11-30 1985-11-30 Combustion chamber of internal combustion engine

Country Status (1)

Country Link
JP (1) JP2521902B2 (en)

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5552516U (en) * 1978-10-05 1980-04-08
JPS58178419U (en) * 1982-05-26 1983-11-29 株式会社小松製作所 Diesel engine spark assist device

Also Published As

Publication number Publication date
JPS62129517A (en) 1987-06-11

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