JPS601322A - Cylinder fuel injection type spark ignition internal- combustion engine - Google Patents
Cylinder fuel injection type spark ignition internal- combustion engineInfo
- Publication number
- JPS601322A JPS601322A JP58108085A JP10808583A JPS601322A JP S601322 A JPS601322 A JP S601322A JP 58108085 A JP58108085 A JP 58108085A JP 10808583 A JP10808583 A JP 10808583A JP S601322 A JPS601322 A JP S601322A
- Authority
- JP
- Japan
- Prior art keywords
- fuel
- fuel injection
- combustion engine
- internal combustion
- ignition internal
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B19/00—Engines characterised by precombustion chambers
- F02B19/12—Engines characterised by precombustion chambers with positive ignition
-
- 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
- F02B23/101—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 being placed on or close to the cylinder centre axis, e.g. with mixture formation using spray guided concepts
-
- 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)
- Combustion Methods Of Internal-Combustion Engines (AREA)
Abstract
Description
【発明の詳細な説明】
本発明は、自動車等の車輌に用いられる火花点火式内燃
機関に係わり、特に燃料噴射ノズルより燃料を燃焼室に
直接噴射供給され、該燃料と空気との混合気を火花放電
手段の火花放電により点火し、これの燃焼を行う筒内燃
料噴射式火花点火内燃機関に係わる。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a spark ignition internal combustion engine used in vehicles such as automobiles, and particularly relates to a spark ignition internal combustion engine in which fuel is directly injected into a combustion chamber from a fuel injection nozzle, and a mixture of the fuel and air is produced. The present invention relates to an in-cylinder fuel injection type spark ignition internal combustion engine that ignites and burns the ignition by spark discharge from a spark discharge means.
筒内燃料噴射式火花点火内燃機関は、層状給気機関、ま
たは成層燃焼機関と云われる種類の内燃機関の一種であ
り、この種の火花点火式内燃ｖａＩ３Ｑは、火花放電手
段の火花放電ギャップイ」近に可燃適正空燃比の混合気
が存在すれば、他の部分に存在する混合気が可燃適正空
燃比以外の空燃比のものであっても、即ち不均一混合気
であっても火花放電による良好な燃焼を行い、しかもデ
ィービル機関の如く燃料噴射量が制御されることにより
負荷制御され、部分負荷運転時に吸気を絞られる必要が
ないから、ガソリン機関とディーゼル機関の長所を兼備
え、熱効率が高く、燃料軽済性及び排気ガス性能に優れ
、そのうえ燃料の粗悪化に対応する多燃料性にも優れて
いる。The in-cylinder fuel injection type spark ignition internal combustion engine is a type of internal combustion engine called a stratified charge engine or stratified combustion engine, and this type of spark ignition type internal combustion VAI3Q has a spark discharge gap I of the spark discharge means. If there is an air-fuel mixture with the appropriate flammable air-fuel ratio nearby, even if the air-fuel mixture existing in other parts has an air-fuel ratio other than the appropriate flammable air-fuel ratio, that is, even if it is a non-uniform mixture, it will not be caused by spark discharge. It has good combustion, and the load is controlled by controlling the fuel injection amount like a Deville engine, and there is no need to throttle the intake air during partial load operation, so it combines the advantages of gasoline and diesel engines, and has high thermal efficiency. It has high fuel efficiency, excellent fuel economy and exhaust gas performance, and also has excellent fuel efficiency to cope with poor fuel quality.
筒内燃料噴射式火花点火式内燃機関は、一般に、球形天
井部を有している如き渦空或いはピストン頂部に設けら
れた平断面形状が円形の燃焼室窪みの如く湾曲した内壁
により郭定された燃焼室を有し、該燃焼室に吸気スワー
ルの如く前記内壁に沿って流れる吸気旋回流を生じ、燃
料噴射ノズルの一つの燃料噴口より前記吸気旋回流を横
切る方向へ一つの噴射主流をもうて燃料を噴射供給され
、その燃料の噴霧特性と前記吸気旋回流との適合によっ
て火花放電手段の火花放電ギャップ付近に可燃適正空燃
比の混合気の領域を形成するようになっている。In-cylinder fuel injection spark ignition internal combustion engines generally have a vortex air space with a spherical ceiling or a combustion chamber provided at the top of the piston that is defined by a curved inner wall resembling a recess in a combustion chamber with a circular planar cross section. The combustion chamber has an intake swirl flow flowing along the inner wall like an intake swirl in the combustion chamber, and one injection main stream is emitted from one fuel injection port of the fuel injection nozzle in a direction transverse to the intake swirl flow. Fuel is injected and supplied, and by matching the spray characteristics of the fuel with the intake air swirling flow, a region of a combustible air-fuel mixture having an appropriate air-fuel ratio is formed near the spark discharge gap of the spark discharge means.
燃料噴射ノズルの燃料噴射特性が一定で、且燃焼室に生
じる吸気旋回流の強さく流速）が内燃機関の運転状態の
変化に拘わらず一定であれば、燃焼室に於て可燃適正空
燃比の混合気が存在する領域の位置は変化しないから、
この場合にはその領域内に一つの火花放電ギャップが配
置されるように点火プラグの如き火花放電手段が設けら
れれば良いが、しかし実際には、特に自動車用内燃機関
に於ては、その常用回転数域が大きいためにＩＮ関回転
数の変化による吸気流速の変化にＪ：り吸気スワールの
如き吸気旋回流の流速が比較的大きく変化し、この吸気
旋回流により燃料噴射ノズルより噴射された燃料の噴霧
束が流されることにより該吸気旋回流の流速の変化に応
じて燃料噴射主流の方向が変化し、これに伴ない可燃適
正空燃比の混合気が存在する領域の位置が変動し、この
ため従来の筒内燃料噴射式火花点火内燃機関は特定の回
転数域でしか良好な成層燃焼を行わない。If the fuel injection characteristics of the fuel injection nozzle are constant, and if the strength and flow velocity of the intake air swirl generated in the combustion chamber are constant regardless of changes in the operating conditions of the internal combustion engine, the optimum flammable air-fuel ratio in the combustion chamber can be maintained. Since the position of the region where the mixture exists does not change,
In this case, a spark discharge means such as a spark plug may be provided so that one spark discharge gap is arranged in that area, but in practice, especially in internal combustion engines for automobiles, it is difficult to use the spark discharge means normally. Because the rotational speed range is large, the flow rate of the intake swirling flow, such as an intake swirl, changes relatively significantly due to changes in the intake airflow velocity due to changes in the IN engine rotational speed, and this intake swirling flow causes the fuel to be injected from the fuel injection nozzle. By flowing the fuel spray bundle, the direction of the main fuel injection main stream changes in accordance with the change in the flow velocity of the intake swirl flow, and accordingly, the position of the region where a combustible air-fuel mixture with an appropriate air-fuel ratio exists changes, For this reason, conventional in-cylinder fuel injection type spark ignition internal combustion engines perform good stratified combustion only in a specific rotation speed range.
本発明は、従来の筒内燃料噴射式火花点火内燃機関の於
ける上述の不具合に鑑み、可燃適正空燃比の混合気が存
在する領域の拡大を図り、これによって吸気旋回流の強
さの変化に応じて燃料噴射主流の方向が変化しても火花
放電手段の火花放電ギャップ付近に可燃適正空燃比の混
合気が存在し、広い回転数域に厘って良好な成層燃焼を
行う改良された筒内燃料噴射式火花点火式内燃機関を提
供することを目的としている。In view of the above-mentioned problems with conventional in-cylinder fuel injection type spark ignition internal combustion engines, the present invention aims to expand the region where a combustible air-fuel mixture with an appropriate air-fuel ratio exists, thereby changing the strength of the intake swirl flow. Even if the direction of the main flow of fuel injection changes in accordance with The purpose is to provide a spark-ignition internal combustion engine with direct fuel injection.
かかる目的は、本発明によれば、燃焼室に燃料噴射ノズ
ルより燃料を噴射供給され、該燃料と空気との混合気を
火花放電手段の火花放電ギャップにより点火する筒内燃
料噴射火花点火内燃ｌ１ｒＩＡに於て、前記燃料噴射ノ
ズルは互いに異なった方向へ燃料を噴射する二つの燃料
噴口を有し、前記火花放電手段は前記二つの燃料噴口よ
り噴射される燃料の噴射主流に挾まれた領域に火花放電
ギャップを有している如き筒内燃料噴射式火花点火内燃
機関によって達成される。According to the present invention, this object is achieved by an in-cylinder fuel injection spark ignition internal combustion system in which fuel is injected into a combustion chamber from a fuel injection nozzle and a mixture of the fuel and air is ignited by a spark discharge gap of a spark discharge means. In the fuel injection nozzle, the fuel injection nozzle has two fuel injection holes that inject fuel in different directions, and the spark discharge means is arranged in an area sandwiched between main streams of fuel injected from the two fuel injection holes. This is achieved by a spark ignition internal combustion engine with direct fuel injection, such as one having a spark discharge gap.
かかる構成によれば、二つの燃料噴口より噴射される燃
料の噴射主流の相対角度が予め適宜に定められているこ
とによりその二つの燃料主流に囲まれた領域に単一噴射
の場合に比して二倍に近い大きさの比較的大きい可燃適
正混合気領域が生じ、これにより吸気旋回流の強さの変
化に応じて燃料噴射主流の方向が変化しても火花放電手
段の火花放電ギヤップイ１近に可燃適正空燃比の混合気
が存在し、内燃機関は広い回転数域に亙って良好な成層
燃焼を行う。According to this configuration, since the relative angle of the main streams of fuel injected from the two fuel nozzles is appropriately determined in advance, the area surrounded by the two main streams of fuel is injected more easily than in the case of single injection. A relatively large suitable flammable air-fuel mixture region, which is nearly twice as large, is generated, and even if the direction of the main flow of fuel injection changes in response to changes in the strength of the intake swirl flow, the spark discharge gear 1 of the spark discharge means remains unchanged. A combustible air-fuel mixture with an appropriate air-fuel ratio exists nearby, and the internal combustion engine performs good stratified combustion over a wide rotation speed range.
本発明による筒内燃料噴射式火花点火内燃機関は、機関
本体に渦室の如き副室を有するりヵルド方式内燃機関、
或いは副室に代えてピストン頂部に円形の平断面形状の
燃焼室窪みを有するテキザゴＴＣＣ８方式内燃機関を基
本とする方式の内燃機関であってよい。The in-cylinder fuel injection type spark ignition internal combustion engine according to the present invention is a Caldo type internal combustion engine having a auxiliary chamber such as a vortex chamber in the engine body;
Alternatively, it may be an internal combustion engine based on the Texago TCC8 internal combustion engine, which has a combustion chamber recess with a circular planar cross section at the top of the piston in place of the auxiliary chamber.
以下に添付の図を参照して本発明を実施例について詳細
に説明する。The invention will now be described in detail by way of example embodiments with reference to the accompanying drawings.
第１図及び第２図は本発明による筒内燃料噴射式火花点
火内燃機関を副室式内燃機関に適用した一つの実施例を
その要部について示′！＃縦断面図である。これらの図
に於て、１及び２は筒内燃料噴射式火花点火内燃機関の
ＩＩＩ関本体を構成Ｊるシリンダヘッド及びシリンダブ
ロックを各々示しており、これらはガスケット３を介し
て互いに締結されている。シリンダブロック２にはシリ
ンダライナ４が取付けられており、該シリンダライナは
その内側のシリンダボア５内にピストン６を図にて上下
方向に往復動を可能に受入れている。FIGS. 1 and 2 show the main parts of an embodiment in which the in-cylinder fuel injection type spark ignition internal combustion engine according to the present invention is applied to a pre-chamber type internal combustion engine! #This is a vertical cross-sectional view. In these figures, 1 and 2 respectively indicate a cylinder head and a cylinder block that constitute the main body of the cylinder fuel injection type spark ignition internal combustion engine, and these are connected to each other via a gasket 3. There is. A cylinder liner 4 is attached to the cylinder block 2, and the cylinder liner receives a piston 6 in a cylinder bore 5 inside thereof so as to be able to reciprocate in the vertical direction as shown in the figure.
シリンダヘッド１には渦室７が設・プられている。A vortex chamber 7 is provided in the cylinder head 1 .
渦室７は、シリンダヘッド１に形成された窪み部により
直接与えられる半球状の球形天井部８と、シリンダヘッ
ド１の取付孔９内に嵌挿されてシリンダヘッド１に固定
された噴口部材１０より与えられる偏平底部１１とを有
し、噴口部材１０に形成されたシリンダ軸線に対し傾斜
した連絡孔１２によってシリンダボア５内に連通したコ
メット型の渦室であり、この渦室７にはその内部に圧縮
行程時にピストン６の上昇に伴ないシリンダボア５内の
吸気が連絡孔１２を経て流入することによりその内壁に
沿って流れる縦回りの吸気旋回流Ｓが生じるようになっ
ている。The vortex chamber 7 includes a hemispherical spherical ceiling portion 8 directly provided by a recess formed in the cylinder head 1, and a nozzle member 10 that is fitted into a mounting hole 9 of the cylinder head 1 and fixed to the cylinder head 1. This is a comet-shaped vortex chamber which has a flat bottom 11 given by During the compression stroke, the intake air in the cylinder bore 5 flows through the communication hole 12 as the piston 6 rises, thereby creating a vertical intake swirl flow S flowing along the inner wall thereof.
シリンダヘッド１には渦室７の天井部に間口したノズル
取付孔１３が設けられており、該ノズル取付孔には燃料
噴射ノズル１４がねじ式に取付られている。燃料噴射ノ
ズル１４は、例えばマルチホール型のものであり、連絡
孔１２と同方向に傾斜してシリンダヘッド１に取付られ
ており、その先端部に二つの燃料噴口１５ａ及び１５ｂ
を有し、この二つの燃料噴口の各々より噴射孔２１を経
て渦室７内へ該渦室内に生じる吸気旋回流Ｓを横切る方
向へガソリン、アルコール或いはその他の液体燃料を所
定の噴霧拡散角をもって噴射供給づるようになっている
。燃料噴口１５ａと１５ｂは、互いに異なった方向へ燃
料を噴射Ｊるが、これら燃料噴口より噴射される燃料の
噴射主流ＡとＢが共に吸気旋回流Ｓに実質的に平行な一
つの仮想平面に含まれるべく燃料噴射を行うよう間口し
ており、燃料噴口１５ｂは燃料噴口１５ａに比して球形
天井部８の内壁よりあまり隔たらない位置へ向けて燃料
を噴射するようになっている。The cylinder head 1 is provided with a nozzle mounting hole 13 opening in the ceiling of the vortex chamber 7, and a fuel injection nozzle 14 is screwed into the nozzle mounting hole. The fuel injection nozzle 14 is, for example, a multi-hole type, and is attached to the cylinder head 1 with an inclination in the same direction as the communication hole 12, and has two fuel injection ports 15a and 15b at its tip.
Gasoline, alcohol, or other liquid fuel is sprayed from each of these two fuel nozzles into the swirl chamber 7 through the injection hole 21 in a direction across the intake swirl flow S generated in the swirl chamber at a predetermined spray diffusion angle. It is designed to supply injection. Although the fuel nozzles 15a and 15b inject fuel in different directions, the injection main streams A and B of the fuel injected from these fuel nozzles are both on one virtual plane substantially parallel to the intake swirl flow S. The fuel injection port 15b is designed to inject fuel toward a position that is less distant from the inner wall of the spherical ceiling portion 8 than the fuel injection port 15a.
シリンダヘッド１には渦室７の天井部に開口したプラグ
取付孔１６が設番ノられて４３す、該プラグ取付孔には
点火プラグ１７がねじ式に取付られている。点火プラク
１６は、火花点火式内燃機関に用いられる一般的な点火
プラグと実質的に同一のものであってよく、中心電極１
８と接地電極１９とを有し、その二つの電極によって一
つの火花放電ギャップ２０を構成している。火花放電ギ
１７ツプ２０は、点火プラグ１７がシリンダヘッド１に
正規の状態にて取付番ノられると、前記二つの燃料噴射
主流ＡとＢとに挾まれた領域に位置するようになってい
る。点火プラグ１７は周知の点火回路によってその中心
電極１８と接地電極１９との間に高電圧を間歇的に印加
されることにより火花放電ギャップ２０に間歇的に火花
放電を生じる。A plug mounting hole 16 is provided in the cylinder head 1 and opens into the ceiling of the vortex chamber 7. A spark plug 17 is screwed into the plug mounting hole. The spark plug 16 may be substantially the same as a typical spark plug used in spark-ignited internal combustion engines, and the center electrode 1
8 and a ground electrode 19, and these two electrodes constitute one spark discharge gap 20. When the spark plug 17 is properly installed in the cylinder head 1, the spark discharge gear 17 and 20 are located in an area sandwiched between the two fuel injection main streams A and B. There is. The spark plug 17 intermittently generates spark discharge in the spark discharge gap 20 by intermittently applying a high voltage between its center electrode 18 and ground electrode 19 by a well-known ignition circuit.
次に第１図及び第２図を参照して燃料噴射ノズル１４よ
り噴射される燃料の噴霧の挙動と点火プラグ１７の火花
放電ギ１１ツブ２０の燃料噴霧に対する位置関係につい
て説明する。第１図は機関回転数が比較的低い時の状態
を、第２図は機関回転数が比較的高い時の状態を各々示
している。燃料噴射ノズル１４の燃料噴［１］１５ａ及
び１５ｂより噴射された液体燃料の噴霧は各々燃料噴射
主流Ａと８の周りに円錐状に末広がりに拡散する。この
時、可燃適正空燃比の混合気は、燃料噴口１５ａと１５
ｂの各々Ｊ、り噴射された燃料とその周りにある空気と
の混合により形成され、この可燃適正空燃比の混合気は
二つの燃料噴霧束の外周領域に各々存在する。従って燃
料噴口１５ａと１５ｂとの相対的噴射方向角が適宜に定
められいることにより前記燃料噴射主流ＡとＢとに挾ま
れた領域には燃料噴射主流Ａの周りに存在する可燃適正
空燃比の混合気と燃料噴射主流Ｂの周りに存在する可燃
適正空燃比の混合気とによって単一噴射の場合に比して
二倍に近い大きさの比較的大きい可燃適正比混合気領域
が生じる。この可燃適正化混合気領域は機関回転数の増
大に伴なって吸気旋回流が速くなるに従って燃料噴口１
５ａ及び１５１＋Ｊ：り噴射された燃料の噴霧が流され
ることに従い渦室７の内壁へ近づく方向に変位するが、
この領域が比較的大きいことにより広い機関回転数域に
亙って火花放電ギャップ２０の周りにはこの可燃適正混
合気が存在し、火花放電ギャップ２ｏに於ける火花放電
によってその混合気の点火が確実に行われる。これによ
り内燃機関は広い回転数域に亙って良好な成層燃焼を行
う。Next, the behavior of the fuel spray injected from the fuel injection nozzle 14 and the positional relationship of the spark discharge gear 11 knob 20 of the ignition plug 17 with respect to the fuel spray will be explained with reference to FIGS. 1 and 2. FIG. 1 shows the state when the engine speed is relatively low, and FIG. 2 shows the state when the engine speed is relatively high. The liquid fuel spray injected from the fuel injection [1] 15a and 15b of the fuel injection nozzle 14 spreads out in a conical shape around the fuel injection main streams A and 8, respectively. At this time, the air-fuel mixture with the proper combustible air-fuel ratio is formed between the fuel nozzles 15a and 15.
Each of the injected fuel J and b is formed by mixing with the air surrounding it, and this combustible air-fuel mixture with an appropriate air-fuel ratio is present in the outer peripheral region of the two fuel spray bundles. Therefore, by appropriately determining the relative injection direction angle between the fuel injection ports 15a and 15b, the region sandwiched between the fuel injection main streams A and B has the proper combustible air-fuel ratio existing around the fuel injection main stream A. The air-fuel mixture and the air-fuel mixture with the appropriate combustible air-fuel ratio existing around the fuel injection main stream B create a relatively large air-fuel mixture region with the appropriate combustible ratio, which is nearly twice as large as in the case of single injection. This optimized combustible air-fuel mixture region changes as the intake swirl flow becomes faster as the engine speed increases.
5a and 151+J: The injected fuel spray is displaced in the direction approaching the inner wall of the vortex chamber 7 as it is flowed;
Because this region is relatively large, this appropriate combustible air-fuel mixture exists around the spark discharge gap 20 over a wide engine speed range, and the spark discharge in the spark discharge gap 2o ignites the air-fuel mixture. It will definitely be done. As a result, the internal combustion engine performs good stratified combustion over a wide rotation speed range.
第３図及び第４図は本発明による筒内燃料噴射式火花点
火内燃機関を副室を有していない単室式内燃機関に適応
した一つの実施例・を示して（する。FIGS. 3 and 4 show an embodiment in which the in-cylinder fuel injection type spark ignition internal combustion engine according to the present invention is adapted to a single-chamber type internal combustion engine having no auxiliary chamber.
これらの図に放て、３０はシリンダヘラ１：を、３１は
シリンダブロックを、３２（よピストンを各々示してお
り、ピストン３２はその頂部に円形の平断面形状を有り
゛るトロイダル型の燃焼室窪み３３を有している。シリ
ンダヘッド３０に番よ吸気４（−ト３４と排気ボート３
５とが設けられており、吸気ボート３４Ｊ：り燃焼室内
に吸入される吸気流によって燃焼室窪み３３内に図に放
て矢印で示されている如ぎ吸気旋回流Ｓが生じるように
なっても）る。In these figures, 30 shows the cylinder spatula 1, 31 shows the cylinder block, and 32 shows the piston. The cylinder head 30 has a recess 33.
5 is provided, and an intake swirling flow S as shown by the arrow in the figure is generated in the combustion chamber recess 33 by the intake air flow taken into the combustion chamber by the intake boat 34J. Also).
シリンダヘッド３０には燃料噴射ノズル３６が取付られ
ている。燃料噴射ノズル３６（よ、例え番ｆマルチホー
ル型のものであり、先端部に二つの燃料噴口３７ａと３
７ｂを有し、ピストン３２が上死魚位置近くにある時に
前記二つの燃料噴口の各々より燃焼室窪み３３内へ向１
すて該燃焼室窪み内に生じている吸気旋回流Ｓを横切る
方向へ液体燃料を所定の噴霧拡散角をもってＩＩＩＩ射
供給するようになっている。燃料噴口３７ａと３７ｂ【
よ互し１に異なった方向へ燃料を噴射するようになって
おり、燃料噴口３７ｂは燃料噴口３７ａに比して燃焼室
窪み３３の側周壁よりさほど隔たらない方向へ燃料噴射
を行うようになっている。尚、図に於て、符号Ａは燃料
噴口３７ａより噴射される燃料の噴射主流を、符号Ｂは
燃料噴口３７ｂより噴射される燃料の噴射主流を各々示
している。A fuel injection nozzle 36 is attached to the cylinder head 30. The fuel injection nozzle 36 (for example, number f) is a multi-hole type with two fuel injection ports 37a and 3 at the tip
7b, and when the piston 32 is near the upper dead position, a direction 1 is directed into the combustion chamber recess 33 from each of the two fuel nozzles.
The liquid fuel is injected and supplied at a predetermined spray diffusion angle in a direction across the intake swirl flow S generated in the recess of the combustion chamber. Fuel nozzles 37a and 37b [
The fuel injection port 37b is designed to inject fuel in different directions from each other, and the fuel injection port 37b injects fuel in a direction that is not far away from the side peripheral wall of the combustion chamber recess 33 compared to the fuel injection port 37a. It has become. In the figure, the symbol A indicates the main stream of fuel injected from the fuel nozzle 37a, and the symbol B indicates the main stream of fuel injected from the fuel nozzle 37b.
シリンダヘッド３０には点火プラグ３８が取付番プられ
でいる。点火プラグ３８は、中心電極３９と接地電極４
０とを有し、その二つの電極によって火花放電ギャップ
４１を構成している。火花放電ギャップ４１は点火プラ
グ３８がシリンダヘッド３０に正規の状態にて取付けら
れると、燃料噴口３７より噴射される燃料の噴射主ｍＡ
と燃料噴口３７ｂより噴射される燃料の噴射主流Ｂとに
より挾まれた領域に位置するようになっている。A spark plug 38 is attached to the cylinder head 30 with a mounting number. The spark plug 38 has a center electrode 39 and a ground electrode 4.
0, and these two electrodes constitute a spark discharge gap 41. When the spark plug 38 is installed in the cylinder head 30 in a normal state, the spark discharge gap 41 is the injection main mA of the fuel injected from the fuel nozzle 37.
It is located in a region sandwiched between the main flow B of fuel injected from the fuel nozzle 37b and the main flow B of fuel injected from the fuel injection port 37b.
この実施例に於ても、燃料噴口３７ａより噴射される燃
料の噴射主流Ａと燃料噴口３７Ｂより噴射される燃料の
噴射主流とにより挾まれた領域にはその両燃料噴口より
噴射された燃料とその燃料噴霧束の外周囲に存在する空
気とにより単一噴射の場合に比して二倍に近い大きさの
領域に亙っで可燃適正混合気の領域が生じる。従って、
機関回転数の変化に伴なって吸気旋回流Ｓの強さが変化
し、これに伴なって燃料噴口３７ａと３７ｂより噴射さ
れた燃料が流されて可燃適正混合気の領域が変動しても
火花放電ギャップ４１はその領域より外れることがなく
、この結果、広い機関回転数域に亙って火花放電ギャッ
プ４１の於る火花放電によって゛混合気の点火が確実に
行われる。これにより内燃機関は広い回転数域に亙っで
良好な成層燃焼を行う。In this embodiment as well, the area sandwiched between the main injection main stream A of fuel injected from the fuel injection port 37a and the main injection main stream of fuel injected from the fuel injection port 37B contains the fuel injected from both fuel injection ports. Due to the air existing around the outer periphery of the fuel spray bundle, a suitable combustible air-fuel mixture region is created over an area nearly twice as large as in the case of single injection. Therefore,
Even if the strength of the intake swirl flow S changes as the engine speed changes, and the fuel injected from the fuel nozzles 37a and 37b is flowed accordingly, the region of the appropriate flammable mixture changes. The spark discharge gap 41 does not deviate from this area, and as a result, the ignition of the air-fuel mixture is reliably performed by the spark discharge in the spark discharge gap 41 over a wide range of engine speeds. As a result, the internal combustion engine performs good stratified combustion over a wide rotation speed range.
以上に於ては、本発明を特定の実施例について詳細に説
明したが、本発明は、これらに限定されるものではなく
、本発明の範囲内にて種々の実施例が可能であることは
当業者にとって明らかであろう。Although the present invention has been described in detail with respect to specific embodiments above, the present invention is not limited to these, and it is understood that various embodiments can be made within the scope of the present invention. It will be clear to those skilled in the art.
第、１図及び第２図は本発明による筒内燃料噴射式点火
内燃ｔａ関を０１室式内燃ｌｉ閑に適用した一つの実施
例をその要部について示す縦断面図、第３図は本発明に
よる筒内燃料噴射式火花点火内燃機関を単室式内燃機関
に適用した一つの実施例をその要部について示す解重的
平面図、第４図は第３図の線ＩＶ−ＩＶに沿う断面図で
ある。
１・・・シリンダヘッド、２・・・シリンダブロック。
３・・・ガスケット、４・・・シリンダヘッド、５・・
・シリンダボア、６・・・ピストン、７・・・渦室、８
・・・球形天井部、９・・・取付孔、１０・・・噴口部
材、１１・・・偏平底部、１２・・・連絡孔、１３・・
・ノズル取付孔、１４・・・燃料噴射ノズル、１５ａ、
１５ｂ・・・燃料噴口。
１６・・・プラグ取付孔、１７・・・点火プラグ、１８
・・・中心電極、１９・・・接地電極、２０・・・火花
放電ギャップ、２１・・・噴射孔、３０・・・シリンダ
ヘッド、３１・・・シリンダブロック、３２・・・ピス
トン、３３・・・燃焼室窪み、３４・・・吸気ボート、
３５・・・ＪＪＩ気ボート、３６・・・燃料噴射ノズル
、３７ａ 、３７ｂ・・・燃料噴０．３８・・・点火プ
ラグ、３９・・・中心電極、４０・・・接地電極、４１
・・・火花放電ギャップ第１図
第２図1 and 2 are longitudinal sectional views showing the main parts of one embodiment in which the in-cylinder fuel injection type ignition internal combustion engine according to the present invention is applied to a 01 chamber type internal combustion engine, and Figure 3 is a longitudinal sectional view of the main part thereof. FIG. 4 is a deconstructed plan view showing the main parts of an embodiment in which the in-cylinder fuel injection type spark ignition internal combustion engine according to the invention is applied to a single-chamber internal combustion engine, and FIG. 4 is taken along line IV-IV in FIG. 3. FIG. 1... Cylinder head, 2... Cylinder block. 3...Gasket, 4...Cylinder head, 5...
・Cylinder bore, 6... Piston, 7... Vortex chamber, 8
... Spherical ceiling part, 9 ... Mounting hole, 10 ... Nozzle member, 11 ... Flat bottom, 12 ... Communication hole, 13 ...
・Nozzle mounting hole, 14...Fuel injection nozzle, 15a,
15b...fuel nozzle. 16... Plug mounting hole, 17... Spark plug, 18
... Center electrode, 19 ... Ground electrode, 20 ... Spark discharge gap, 21 ... Injection hole, 30 ... Cylinder head, 31 ... Cylinder block, 32 ... Piston, 33 ... ... Combustion chamber recess, 34... Intake boat,
35... JJI boat, 36... Fuel injection nozzle, 37a, 37b... Fuel injection 0.38... Spark plug, 39... Center electrode, 40... Ground electrode, 41
...Spark discharge gap Figure 1 Figure 2
Claims (1)
れ、該燃料と空気との混合気を火花放電手段の火花放電
により点火する筒内燃料噴射式火花点火内燃機関に於て
、前記燃料噴射ノズルは互いに異なった方向へ燃料を噴
射する二つの燃料噴口を有し、前記火花放電手段は前記
二つの燃料噴口より噴射される燃料の噴射主流に挾まれ
た領域に火花放電ギャップを有している筒内燃料噴射式
火花点火内燃機関。 （２、特許請求の範囲第１項に記載された筒内燃料噴射
式火花点火内燃機関に於て、前記燃焼室はＩｌｌ木本体
設（プられた渦空であることを特徴とする筒内燃料噴射
式火花点火内燃機関。 （３）特許請求の範囲第１項に記載された筒内燃料噴射
式火花点火内燃機関に於て、前記燃焼室はピストンの頂
部に設けられた燃焼室窪みであることを特徴とする筒内
燃料噴射式火花点火内燃機関。[Scope of Claims] (1) An in-cylinder fuel injection type spark ignition internal combustion engine in which fuel is injected into the combustion chamber from a fuel injection nozzle, and the mixture of fuel and air is ignited by spark discharge from a spark discharge means. In the fuel injection nozzle, the fuel injection nozzle has two fuel injection holes that inject fuel in different directions, and the spark discharge means is arranged in an area sandwiched between main streams of fuel injected from the two fuel injection holes. A spark-ignition internal combustion engine with direct fuel injection and a spark discharge gap. (2. In the in-cylinder fuel injection type spark ignition internal combustion engine recited in claim 1, the combustion chamber has an Ill wood body structure (in-cylinder structure characterized by a depressed vortex air space). Fuel injection type spark ignition internal combustion engine. (3) In the cylinder fuel injection type spark ignition internal combustion engine described in claim 1, the combustion chamber is a combustion chamber recess provided at the top of the piston. An in-cylinder fuel injection spark ignition internal combustion engine characterized by:
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP58108085A JPS601322A (en) | 1983-06-16 | 1983-06-16 | Cylinder fuel injection type spark ignition internal- combustion engine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP58108085A JPS601322A (en) | 1983-06-16 | 1983-06-16 | Cylinder fuel injection type spark ignition internal- combustion engine |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPS601322A true JPS601322A (en) | 1985-01-07 |
Family
ID=14475490
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP58108085A Pending JPS601322A (en) | 1983-06-16 | 1983-06-16 | Cylinder fuel injection type spark ignition internal- combustion engine |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS601322A (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5058548A (en) * | 1989-06-26 | 1991-10-22 | Fuji Jukogyo Kabushiki Kaisha | Combustion chamber of an internal combustion engine |
Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS55104517A (en) * | 1979-01-31 | 1980-08-11 | Toyota Central Res & Dev Lab Inc | Double combustion chamber type internal combustion engine |
-
1983
- 1983-06-16 JP JP58108085A patent/JPS601322A/en active Pending
Patent Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS55104517A (en) * | 1979-01-31 | 1980-08-11 | Toyota Central Res & Dev Lab Inc | Double combustion chamber type internal combustion engine |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5058548A (en) * | 1989-06-26 | 1991-10-22 | Fuji Jukogyo Kabushiki Kaisha | Combustion chamber of an internal combustion engine |
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