JPS62129515A - Combustion chamber for internal combustion engine - Google Patents
Combustion chamber for internal combustion engineInfo
- Publication number
- JPS62129515A JPS62129515A JP26740185A JP26740185A JPS62129515A JP S62129515 A JPS62129515 A JP S62129515A JP 26740185 A JP26740185 A JP 26740185A JP 26740185 A JP26740185 A JP 26740185A JP S62129515 A JPS62129515 A JP S62129515A
- Authority
- JP
- Japan
- Prior art keywords
- combustion chamber
- sub
- main
- fuel
- plug
- 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.)
- Granted
Links
Landscapes
- Combustion Methods Of Internal-Combustion Engines (AREA)
- Fuel-Injection Apparatus (AREA)
- Ignition Installations For Internal Combustion Engines (AREA)
Abstract
Description
【発明の詳細な説明】
［産業上の利用分野］
本発明は燃焼室内に燃料油を直接噴射する内燃機関の燃
焼室に係り、特に燃料油としてガソリン、アルコール等
の低セタン価・揮発性燃料を使用できる内燃ｎＰＡの燃
焼室に関する。[Detailed Description of the Invention] [Industrial Application Field] The present invention relates to a combustion chamber of an internal combustion engine in which fuel oil is directly injected into the combustion chamber, and in particular, the fuel oil is a low cetane number/volatile fuel such as gasoline or alcohol. The present invention relates to a combustion chamber of an internal combustion nPA that can be used.
［従来の技ｖＦ１］
一般に、メタノール（メヂルアルコール）等の粗悪燃料
油を燃料油に使用できるものとしては、実開昭５７−１
０７８２０号公報記載のメタノール層状給気エンジンの
提案が知られており、第４図に示ずこの提案は、シリン
ダａの頂端側方に予燃焼室すを設け、その予燃焼室すの
底壁部Ｃに予熱栓ｄを横置配置し、その予熱栓ｄと対向
して燃料噴射弁ｅを配設すると共に、その燃料噴射弁０
と前記予熱栓ｄとの間に点火栓ｆを配置して構成される
ものである。[Conventional Technique vF1] In general, as a fuel oil that can be used with inferior fuel oil such as methanol (medyl alcohol), Utility Model Application No. 57-1
A proposal for a methanol stratified charge engine described in Japanese Patent No. 07820 is known, and this proposal, not shown in FIG. A preheating plug d is arranged horizontally in section C, and a fuel injection valve e is arranged opposite to the preheating plug d.
The ignition plug f is arranged between the preheating plug d and the preheating plug d.
［発明が解決しようとする問題点］
上記した提案は、機関の始動時、軽負荷運転性を高める
ために、グロープラグにて予燃焼室内を高温雰囲気にし
て燃料を着火燃焼させようとするものである。[Problems to be Solved by the Invention] The above proposal attempts to create a high-temperature atmosphere in the pre-combustion chamber using a glow plug to ignite and burn fuel in order to improve light-load operability when starting the engine. It is.
ところが、予燃焼室すと主燃焼室ｑとはス１：１−りｈ
によって連通される構成上、予燃焼室すに圧縮空気を押
し込む際の絞り損失、予燃焼室すからの燃焼ガスが主燃
焼室ｑに押し込まれる際の絞り損失が大きく、これらの
損失による熱効率の低下が生じていた。この熱効率の低
下は主燃焼室内の燃焼温度を低十ざぜるため、出力の低
下、 ＨＣ等の燃焼未燃物を増加させる恐れを有してい
る。また、大気温度が一２０℃を越えるような低温始動
時にあっては、その始動のために噴射燃料油が増量され
ることと、その燃料油がメタノール等の蒸発潜熱の小さ
なものであることから蒸気化しにくく、点火栓のアシス
トが可能となる混合気を生成するためには、加熱時間を
多く必要としたり、グロープラグの発熱能力を高める等
の対策を必要としたりし、バッテリーの容量や始動時間
等の観点から好ましいものではなかった。However, the pre-combustion chamber and the main combustion chamber q are 1:1-1
Due to the structure in which the compressed air is forced into the pre-combustion chamber, there is a large throttling loss when compressed air is forced into the pre-combustion chamber, and when combustion gas from the pre-combustion chamber is forced into the main combustion chamber q, the thermal efficiency is reduced due to these losses. There was a decline. This decrease in thermal efficiency lowers the combustion temperature in the main combustion chamber, which may lead to a decrease in output and an increase in unburned substances such as HC. In addition, when starting at a low temperature when the atmospheric temperature exceeds 120 degrees Celsius, the amount of fuel oil injected is increased for the start, and the fuel oil has a low latent heat of vaporization such as methanol. In order to generate a mixture that is difficult to vaporize and can assist the ignition plug, it requires a lot of heating time, and measures such as increasing the heat generation capacity of the glow plug are required, and the battery capacity and starting This was not desirable from the viewpoint of time and the like.
［発明の目的］
本発明は上記種々の問題点を解消するために創案された
ものである。本発明の目的はアルコール。[Object of the Invention] The present invention has been devised to solve the various problems mentioned above. The object of this invention is alcohol.
ガソリン等の低セタン価・揮発性燃料油を低温始動時を
含む全負荷運転領域で良好に燃焼させることのできる内
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 for an internal combustion engine that can burn a low cetane number, volatile fuel oil such as gasoline well in a full load operation range including at low temperature startup.
し発明の概要］
本発明は上記１′１的を達成づるためにビス１−ン頂部
を窪まぜてＨいに連通ずる主燃焼室と副燃焼室とを並設
りると共に、主噴口が主燃焼室を臨みｒＷｌ噴口が副燃
焼室を臨む噴１１１１’Ｊノズルを配没し、上記副燃焼
室内にグロープラグとスパークプラグとを並設したもの
で、機関始動時を含む軽負伺時には１噴にＩに対して先
行して開放される副噴口からの微粒化燃料噴霧とグロー
プラグにより加熱される圧縮空気とを混合させることに
より着火燃焼性の良い混合気を生成して、イの混合気を
スパークプラグにて着火燃焼させ、機関中高負荷時には
、この副燃焼室内の燃焼エネル〜二にて主燃焼室内に噴
射される燃料噴霧を加速的に蒸発させて主燃焼室内に上
記混合気を生成し、この混合気が副燃焼室内の火炎伝播
をうけて着火燃焼Ｊるようにしたものである。[Summary of the invention] In order to achieve the above object 1'1, the present invention has a main combustion chamber and a sub-combustion chamber that are arranged side by side and communicate with each other by recessing the top of the screw cylinder, and also has a main nozzle. The rWl nozzle facing the main combustion chamber is equipped with the 1111'J nozzle facing the auxiliary combustion chamber, and a glow plug and a spark plug are installed side by side in the auxiliary combustion chamber. By mixing the atomized fuel spray from the auxiliary nozzle that is opened prior to I in one injection with the compressed air heated by the glow plug, an air-fuel mixture with good ignition and combustibility is generated. The air-fuel mixture is ignited and combusted by a spark plug, and when the engine is under medium or high load, the fuel spray injected into the main combustion chamber is evaporated at an accelerated rate using the combustion energy in this sub-combustion chamber, and the above-mentioned air-fuel mixture is stored in the main combustion chamber. This air-fuel mixture is ignited and combusted by flame propagation in the auxiliary combustion chamber.
し実施例］
以下に本発明の内燃機関の燃焼室の好適一実施例を添付
図面に基づいて説明する。Embodiment] A preferred embodiment of a combustion chamber of an internal combustion engine according to the present invention will be described below with reference to the accompanying drawings.
第１図及び第２図に示される如くピストン頂部１には、
これより窪まされて主燃焼室２と副燃焼室３とが、それ
ぞれ上部を１；１１放された例えば円形断面形状をなす
ように形成されている。また、主燃焼室２と副燃焼室３
とは、互いの内側壁２ａ。As shown in FIGS. 1 and 2, the piston top 1 includes:
The main combustion chamber 2 and the auxiliary combustion chamber 3 are recessed from this, and are formed to have, for example, a circular cross-sectional shape with their upper portions spaced apart by 1:11. In addition, the main combustion chamber 2 and the sub-combustion chamber 3
and the inner walls 2a of each other.
３ａの一部を開放してバンク部４が形成されている。副
燃焼室３と主燃焼室２との容積比は、副燃焼室３より主
燃焼室２が大容積に形成され、具体的には上記主燃焼室
２の円形断面が副燃焼ｖ３の円形断面より大径に形成さ
れると共に主燃焼室２より１１燃焼室３が浅く窪まされ
ている。A bank portion 4 is formed by opening a portion of 3a. The volume ratio of the auxiliary combustion chamber 3 and the main combustion chamber 2 is such that the main combustion chamber 2 has a larger volume than the auxiliary combustion chamber 3, and specifically, the circular cross section of the main combustion chamber 2 is the same as the circular cross section of the secondary combustion chamber v3. The combustion chamber 11 is formed to have a larger diameter and is recessed shallower than the main combustion chamber 2.
このように形成された上記主燃焼室２と、１１燃焼室３
とのバンクｌ！ａＳ４には、そのバンク部４を臨むよう
に噴射ノズル５が設（づられ、この噴射ノズル５は図示
しないシリンダヘッドにそれら燃焼室を臨んで取り付け
られる。また噴口・ｊノズル５の主な構成としては、第
３図に示すようにシリンダヘッドに取り付けられるノズ
ルボディ７内の弁座８に対して昇降自在に着座してそれ
を間ｌｌｌ−するデーパ部９を有Ｊるニードル弁１０と
、その弁座８より間口されて貞微力の小さな微粒化燃料
噴霧を噴出する副噴口１１と、上記ノズルボディ７内端
部にｎつ上記ニードル弁１０の軸芯方向に沿って開口さ
れると共に、上記ニードルか１０の縮径部１２を収容し
、これが開放されることにより０微力の大ぎな燃料噴霧
を噴出する主噴口１３とから形成される。The main combustion chamber 2 formed in this way and the 11 combustion chamber 3
Bank l with! An injection nozzle 5 is installed in the aS4 so as to face the bank portion 4, and this injection nozzle 5 is attached to a cylinder head (not shown) so as to face the combustion chambers. As shown in FIG. 3, a needle valve 10 has a tapered portion 9 that is movable up and down against a valve seat 8 in a nozzle body 7 attached to a cylinder head. A sub-nozzle 11 which is opened from the valve seat 8 and ejects atomized fuel spray with a small force, and n openings along the axial direction of the needle valve 10 at the inner end of the nozzle body 7; It is formed from a main nozzle 13 which accommodates the reduced diameter part 12 of the needle 10 and which, when opened, ejects a large fuel spray with zero force.
また、上記副噴口１１と主噴口１３とは、上記ニードル
弁１０のリフト量でそれぞれ開口されるようになってお
り、機関が低負荷時には、所定リフト以下で副噴口１１
が開放され、そのリフト以上で副噴口１１及び主噴口１
３が開放されてイれぞれ燃焼室２．３内に燃料が噴射供
給される。Further, the sub-nozzle port 11 and the main nozzle port 13 are each opened according to the lift amount of the needle valve 10, and when the engine is under low load, the sub-nozzle port 11 is opened at a predetermined lift or less.
is opened, and above that lift, the sub-nozzle 11 and the main nozzle 1
3 are opened and fuel is injected and supplied into the combustion chambers 2 and 3, respectively.
さて、本発明の実施例において、上記噴射ノズル５から
噴午１される燃料がガソリン、純アルコール等の低セタ
ン価燃料である場合は、その燃料を、低温大気中、低負
荷時に確実に着火燃焼させるために、スパークプラグ１
５及びグロープラグ１６が設けられる。スパークプラグ
１５及びグロープラグ１６は、副燃焼室３内に突出して
設（〕られており、副燃焼室３に設けられるグロープラ
グ１Ｇに対してスパークプラグ１５は、そのグロープラ
グ１６近傍のスワール方向下流側に位置して設けられる
。Now, in the embodiment of the present invention, when the fuel injected from the injection nozzle 5 is a low cetane fuel such as gasoline or pure alcohol, the fuel is reliably ignited in a low-temperature atmosphere at a low load. Spark plug 1 for combustion
5 and a glow plug 16 are provided. The spark plug 15 and the glow plug 16 are provided to protrude into the sub-combustion chamber 3, and the spark plug 15 is disposed in the swirl direction near the glow plug 16 with respect to the glow plug 1G provided in the sub-combustion chamber 3. It is located on the downstream side.
一方、上記噴射ノズル５の副噴口１１の向きは、上記グ
ロープラグ１６に対向するか、または、そのグロープラ
グ１Ｇ近傍に対向して設けられ、主噴口１３は主燃焼室
２の内壁２ａに、且つ主燃焼室２のスワール方向下流側
に向ｔノで設けられる。On the other hand, the sub-nozzle 11 of the injection nozzle 5 is provided facing the glow plug 16 or in the vicinity of the glow plug 1G, and the main nozzle 13 is provided on the inner wall 2a of the main combustion chamber 2. Moreover, it is provided on the downstream side of the main combustion chamber 2 in the swirl direction, facing toward the main combustion chamber 2 .
以下に本発明の内燃機関の燃焼室の実施例の作用につい
て添付図面に基づいて説明する。The operation of the embodiment of the combustion chamber of the internal combustion engine of the present invention will be explained below based on the accompanying drawings.
第１図及び第２図に示されるように、図示しないスワー
ルボートから供給されるスワールＳは、圧縮されながら
も主・副燃焼室２．３内に閉じ込められる。As shown in FIGS. 1 and 2, the swirl S supplied from a swirl boat (not shown) is confined within the main and auxiliary combustion chambers 2.3 while being compressed.
機関が始＃Ｊ時にあっては、噴射ノズル５のニードル弁
１０がリフトされるが、低温始動時にあってのニードル
弁１０は、スタータによる内燃機関駆動時の噴射ポンプ
の回転数が５０ｒｐｍ〜１５０ｒｐＩｌｌに設定される
、いわゆる過剰供給状態（全負荷時よりも多い状態）に
あり４にがら燃料流速が極低速のために、副噴口１１の
みを開放さ１！る低いリフト値に保たれる。これにより
副燃焼室３内には、微粒化燃料噴霧Ｆ１が多量に供給さ
れる。微粒化燃料噴″ｆＡＦ ＋ はグロープラグ１６
またはグロ−プラグ１６近傍に向けて噴出されるため、
グ［］−プラグ１６にＪ、り更に加熱される圧縮空気に
よって加速的に蒸発されて空気と混合し、着火燃焼性に
優れた燃料蒸気層Ｆ３を生成する。この燃料蒸気層Ｆ１
は、スワールＳによりＦ流側に流されてスパークプラグ
１５周辺に分布されるとぎにスパークプラグ１５の点火
を行なうことにより確実な着火がなされる。また、上記
微粒化燃料噴Ｎ Ｆ ＋を、グロープラグ１６３Ｉｉ傍
のスワール方向上流側の副燃焼室内壁３ａに衝突さゼる
ようにした場合は衝突飛散することでさらに燃料噴°霧
の微粒化が促進されて蒸気化・混合気化が速められるこ
とになり、副燃焼室３内には濃混合気が生成されリッチ
燃、焼が行なわれる。低温始動後は、副燃焼室３の内壁
３ａが燃焼エネルギによって暖められ、燃料油を蒸気化
するに十分な壁温に達するため、機関軽イ）傭時におけ
る副噴口１１からの微粒化燃料噴霧Ｆ１を安定しχむ火
燃焼させる。副燃焼室３はバンク部４を介して主燃焼室
２と隔てられていることと副燃焼室３内のスワールＳに
よって副燃焼室３内に燃焼ガスの大半が閉じ込められる
ことから、主燃焼全２内に燃料蒸気を逃ずことなく副燃
焼室３内を所定の空燃比に設定できることになる。この
ためアルコール等の低セタン価・揮発性燃料油を、副燃
焼室３内で急速燃焼させることができる。When the engine is at start #J, the needle valve 10 of the injection nozzle 5 is lifted, but when the engine is started at a low temperature, the needle valve 10 is lifted when the rotation speed of the injection pump is 50 rpm to 150 rpm when the internal combustion engine is driven by the starter. Since the fuel flow rate is extremely low, only the sub-nozzle 11 is opened. The lift value is kept low. As a result, a large amount of atomized fuel spray F1 is supplied into the sub-combustion chamber 3. Atomized fuel injection "fAF +" is glow plug 16
Or because it is ejected toward the vicinity of the glow plug 16,
The fuel vapor in the plug 16 is evaporated at an accelerated rate by the heated compressed air and mixed with air to produce a fuel vapor layer F3 with excellent ignition and combustibility. This fuel vapor layer F1
is caused to flow to the F flow side by the swirl S and distributed around the spark plug 15, and then the spark plug 15 is ignited, thereby ensuring reliable ignition. In addition, when the atomized fuel injection N F + is made to collide with the wall 3a of the sub-combustion chamber on the upstream side in the swirl direction near the glow plug 163Ii, the collision and scattering further atomizes the fuel spray mist. This accelerates vaporization and mixture vaporization, and a rich mixture is generated in the sub-combustion chamber 3, resulting in rich combustion. After a low-temperature start, the inner wall 3a of the auxiliary combustion chamber 3 is warmed by the combustion energy and reaches a wall temperature sufficient to vaporize the fuel oil. Burn F1 stably and slowly. Since the sub-combustion chamber 3 is separated from the main combustion chamber 2 via the bank portion 4 and most of the combustion gas is confined within the sub-combustion chamber 3 by the swirl S in the sub-combustion chamber 3, the main combustion This means that the inside of the auxiliary combustion chamber 3 can be set to a predetermined air-fuel ratio without causing fuel vapor to escape into the auxiliary combustion chamber 3. Therefore, low cetane number, volatile fuel oil such as alcohol can be rapidly combusted within the sub-combustion chamber 3.
これによって燃焼温度が上昇し、青白煙の発生及び燃焼
未燃物（ＩＩＣ）の生成を抑制できることになり、低ｆ
１荷１１、ｉには、副燃焼室３内の燃焼平均温度が上背
し、その結果、青白煙の発生及び燃焼未燃物（ＩＩｃ）
の生成を抑制できる。This increases the combustion temperature, suppresses the generation of blue-white smoke and unburned matter (IIC), and lowers the f.
In the first load 11, i, the average combustion temperature in the sub-combustion chamber 3 rises, resulting in the generation of blue-white smoke and the combustion of unburned matter (IIc).
The generation of can be suppressed.
ざらに、高負荷時に於いては、上記主唱口１３よりも主
燃焼室２の内壁２ａに向けて、■つスワールＳの下流方
向に向（）て第１図、第２図に示す如く燃料噴霧が噴（
ト）δれる。主燃焼室２には、主噴口１３からの燃ＩＩ
噴霧Ｆ２が主燃焼室２の内壁２ａに向けて噴射されるた
め、その内２２ａに沿ってスワールＳの下流側に流れる
燃料１１ｕ ｌ−１を生成する。この燃料膜Ｈは副燃焼
室３の燃焼エネルギと高温圧縮空気及び内壁熱ににす、
主燃焼室２内の上記した燃料蒸気ＶＪＦ３を生成する。Roughly speaking, under high load, fuel flows toward the inner wall 2a of the main combustion chamber 2 from the main inlet 13, toward the downstream direction of the swirl S, as shown in FIGS. 1 and 2. The spray is spraying (
g) δ will be. The main combustion chamber 2 contains fuel II from the main nozzle 13.
Since the spray F2 is injected toward the inner wall 2a of the main combustion chamber 2, fuel 11u l-1 is generated that flows downstream of the swirl S along the inner wall 22a. This fuel film H converts the combustion energy of the sub-combustion chamber 3 into high-temperature compressed air and inner wall heat.
The above-mentioned fuel vapor VJF3 in the main combustion chamber 2 is generated.
この蒸気層Ｆ１が副燃焼室３の火炎を伝播されて良好な
燃焼が行なわれる。その際に、主噴口１３より噴射され
る燃料粒径は副噴口１１より噴％１される燃料粒径より
は大径であり、貫徹力が大ぎいことから、蒸発燃料と圧
縮空気とが混合して生成される燃料蒸気層Ｆ３を過剰に
生成しないため、これが信太しでｂ主燃焼室２内は急激
燃焼とは成り１１ｔない。This vapor layer F1 is propagated by the flame in the sub-combustion chamber 3, resulting in good combustion. At that time, the diameter of the fuel particles injected from the main nozzle 13 is larger than the diameter of the fuel particles injected from the sub-nozzle 11, and the penetration force is large, so the evaporated fuel and compressed air are mixed. Since the fuel vapor layer F3 generated by the combustion is not excessively generated, this is thick and there is no rapid combustion in the main combustion chamber 2, and there is no 11t.
従って、燃料蒸気層Ｆ３が着火することによって発生さ
れた熱により残りの燃料膜ト１を速やかに蒸発ｕしめ、
この然気が燃焼していき緩慢な燃焼が行なわれることに
なり、これによって急激な主燃焼室２内の圧力上昇は抑
制され、さらに騒音を低減できる。また高負荷になる程
主噴口１３より噴射される燃料は増加し、最大では９０
％以上噴Ｑ（されることになるので上記作用は確実に達
成され、副燃焼室３より流入Ｊる火炎によって確実に６
火燃焼が行なわれる。Therefore, the heat generated by the ignition of the fuel vapor layer F3 quickly evaporates the remaining fuel film F3,
This air is combusted and combustion is performed slowly, thereby suppressing a sudden rise in pressure within the main combustion chamber 2 and further reducing noise. In addition, the higher the load, the more fuel is injected from the main nozzle 13, with a maximum of 90
% or more will be injected (Q), so the above effect will be reliably achieved, and the flame flowing in from the sub-combustion chamber 3 will ensure that the 6
Fire burning takes place.
［発明の効果］
以上詳述したように、本発明によれば次のごとき優れた
効果を発揮する。[Effects of the Invention] As detailed above, the present invention provides the following excellent effects.
（１） ピストン頂部に主燃焼室と６９１燃焼室とを
並設し、それ等を互いに連通させた燃焼室を形成して、
上記ａ１燃焼室内にグロープラグ及びスパークプラグを
設けｔこので、スパークプラグのスワールｈ向上次側で
石火性の優れた燃料蒸気層を生成することができ、機関
が低温始動時においても、軽油または純アル：１−ル、
ガソリン等の低セタン価燃料を確実に着火燃焼し、また
、肴火冗れなく緩慢燃焼させ１９るので、肖白炸、燃焼
未燃物（ＩＩｃ）を低減することができる。(1) A main combustion chamber and a 691 combustion chamber are arranged side by side at the top of the piston, and a combustion chamber is formed in which they communicate with each other,
By installing a glow plug and a spark plug in the above a1 combustion chamber, a fuel vapor layer with excellent ignition properties can be generated next to the swirl h of the spark plug, and even when the engine is started at a low temperature, light oil or Pure Al: 1-L,
Since low cetane number fuel such as gasoline is reliably ignited and burnt, and burnt slowly without any sideburns, it is possible to reduce white ash and unburned matter (IIc).
（２） 主燃焼室と副燃焼室とに連通するバンク部を
設けたので、副燃焼室内の燃焼ガスの一部が主燃焼室内
に侵入して、その燃焼ガスによって、主燃焼室内に噴＋
３＝１蒸発された燃料蒸気層に着火燃焼させて速やかに
且つ緩慢燃焼を達成できるので、低負萄から高負荷に至
る広範囲にわたって騒音を防止できる。(2) Since the bank part that communicates with the main combustion chamber and the sub-combustion chamber is provided, a part of the combustion gas in the sub-combustion chamber enters the main combustion chamber, and the combustion gas injects fuel into the main combustion chamber.
3=1 Since the evaporated fuel vapor layer can be ignited and burned to achieve rapid and slow combustion, noise can be prevented over a wide range from low loads to high loads.
第１図は本発明の内燃は閣の燃焼室の好適一実施例を示
す概略図、第２図は本発明の主燃焼室と副燃焼室とに燃
料を噴射り゛る燃料ｎｒｌ ［１）ｊノズルの噴射方向
を示す概略断面図、第３図は噴射ノズルの概略断面図、
第４図は従来例を示す図である。
図中、１はピストン頂部、２は主燃焼室、３は副燃焼室
、５は噴射ノズル、１１は副噴口、１３は主噴口、１５
はスパークプラグ、１６はグロープラグである。Fig. 1 is a schematic diagram showing a preferred embodiment of the combustion chamber of the internal combustion chamber of the present invention, and Fig. 2 is a schematic diagram showing a preferred embodiment of the combustion chamber of the internal combustion chamber of the present invention. j A schematic sectional view showing the injection direction of the nozzle, FIG. 3 is a schematic sectional view of the injection nozzle,
FIG. 4 is a diagram showing a conventional example. In the figure, 1 is the top of the piston, 2 is the main combustion chamber, 3 is the sub-combustion chamber, 5 is the injection nozzle, 11 is the sub-nozzle, 13 is the main nozzle, 15
is a spark plug, and 16 is a glow plug.
Claims (2)
室と副燃焼室とを並設すると共に、主噴口が主燃焼室を
臨み副噴口が副燃焼室を臨む噴射ノズルを配設し、上記
副燃焼室内にグロープラグとスパークプラグとを並設し
たことを特徴とする内燃機関の燃焼室。(1) A main combustion chamber and a sub-combustion chamber that communicate with each other are arranged side by side by recessing the top of the piston, and an injection nozzle is provided in which the main nozzle port faces the main combustion chamber and the sub-nozzle port faces the sub-combustion chamber. A combustion chamber for an internal combustion engine, characterized in that a glow plug and a spark plug are arranged side by side in the auxiliary combustion chamber.
燃料の流れ方向に対して上記スパークプラグより上流側
に位置された上記特許請求の範囲第１項記載の内燃機関
の燃焼室。(2) The combustion chamber of an internal combustion engine according to claim 1, wherein the glow plug is located upstream of the spark plug with respect to the flow direction of fuel injected from the sub-nozzle.
Priority Applications (4)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP60267401A JPH063133B2 (en) | 1985-11-29 | 1985-11-29 | Combustion chamber of direct injection diesel engine |
| US06/864,673 US4709672A (en) | 1985-05-21 | 1986-05-19 | Combustion chamber for an internal-combustion engine |
| DE8686106824T DE3662426D1 (en) | 1985-05-21 | 1986-05-20 | Combustion chamber for an internal-combustion engine |
| EP86106824A EP0205000B1 (en) | 1985-05-21 | 1986-05-20 | Combustion chamber for an internal-combustion engine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP60267401A JPH063133B2 (en) | 1985-11-29 | 1985-11-29 | Combustion chamber of direct injection diesel engine |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS62129515A true JPS62129515A (en) | 1987-06-11 |
| JPH063133B2 JPH063133B2 (en) | 1994-01-12 |
Family
ID=17444328
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP60267401A Expired - Lifetime JPH063133B2 (en) | 1985-05-21 | 1985-11-29 | Combustion chamber of direct injection diesel engine |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH063133B2 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2018534481A (en) * | 2015-11-17 | 2018-11-22 | モトダン リミテッド | Internal combustion engine |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS54150702U (en) * | 1978-04-14 | 1979-10-19 | ||
| JPS57127818U (en) * | 1981-02-04 | 1982-08-09 |
-
1985
- 1985-11-29 JP JP60267401A patent/JPH063133B2/en not_active Expired - Lifetime
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS54150702U (en) * | 1978-04-14 | 1979-10-19 | ||
| JPS57127818U (en) * | 1981-02-04 | 1982-08-09 |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2018534481A (en) * | 2015-11-17 | 2018-11-22 | モトダン リミテッド | Internal combustion engine |
Also Published As
| Publication number | Publication date |
|---|---|
| JPH063133B2 (en) | 1994-01-12 |
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