JPH04187815A - Cylinder direct injection type spark ignition engine - Google Patents
Cylinder direct injection type spark ignition engineInfo
- Publication number
- JPH04187815A JPH04187815A JP2314089A JP31408990A JPH04187815A JP H04187815 A JPH04187815 A JP H04187815A JP 2314089 A JP2314089 A JP 2314089A JP 31408990 A JP31408990 A JP 31408990A JP H04187815 A JPH04187815 A JP H04187815A
- Authority
- JP
- Japan
- Prior art keywords
- fuel
- injection nozzle
- combustion chamber
- piston
- cylinder
- 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
- 238000002347 injection Methods 0.000 title claims abstract description 62
- 239000007924 injection Substances 0.000 title claims abstract description 62
- 239000000446 fuel Substances 0.000 claims abstract description 69
- 238000002485 combustion reaction Methods 0.000 claims abstract description 51
- 230000035515 penetration Effects 0.000 claims description 6
- 239000000203 mixture Substances 0.000 abstract description 15
- 239000007788 liquid Substances 0.000 abstract description 6
- 230000000149 penetrating effect Effects 0.000 abstract description 6
- 238000000889 atomisation Methods 0.000 abstract description 5
- 230000006835 compression Effects 0.000 description 6
- 238000007906 compression Methods 0.000 description 6
- 239000010687 lubricating oil Substances 0.000 description 5
- 239000012141 concentrate Substances 0.000 description 1
- 238000010790 dilution Methods 0.000 description 1
- 239000012895 dilution Substances 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
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
- F02B23/104—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 a side position of the cylinder
-
- 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
-
- 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
Abstract
Description
【発明の詳細な説明】
〔産業上の利用分野〕
本発明は、ピストン頂面に凹形状の燃焼室を有し、筒内
に直接燃料を噴射して火花点火により燃焼させるように
した筒内直接噴射式火花点火機関に関する。[Detailed Description of the Invention] [Field of Industrial Application] The present invention relates to a cylinder having a concave combustion chamber on the top surface of a piston, and in which fuel is directly injected into the cylinder and burned by spark ignition. Relating to direct injection spark ignition engines.
燃料を筒内に直接噴射するノズルと、ピストン頂面の凹
形状の燃焼室と、点火プラグとを有するエンジンが、特
開昭６２−１９１６２２号公報に記載されている。JP-A-62-191622 discloses an engine having a nozzle for directly injecting fuel into a cylinder, a concave combustion chamber on the top surface of a piston, and a spark plug.
これは、単一の前記噴射ノズルによってエンジンの低負
荷域から高負荷域まで燃料を筒内に供給するものであり
、前記噴射ノズルは、必要に応じて燃料の噴射状態を変
える構造となっている。This uses a single injection nozzle to supply fuel into the cylinder from a low load range to a high load range of the engine, and the injection nozzle is structured to change the fuel injection state as necessary. There is.
エンジンが中・低負荷域の運転状態にある場合、前記噴
射ノズルは、ピストンが圧縮上死点近傍に位置する時、
前８己燃焼室の壁面に向って燃料を貫徹力の強い液柱状
態で必要な量だけ供給する。供給された燃料は、一部が
高温度の前記燃焼室の壁面で蒸発して希薄な混合気を前
記燃焼量内に形成し、その他が蒸発しながら前記燃焼室
の壁面に沿って点火プラグの近傍に集中し、着火性の良
い濃厚な混合気を形成する。それにより前８己燃焼室内
での緩慢な成層燃焼が得られる。When the engine is operating in a medium/low load range, when the piston is located near compression top dead center, the injection nozzle
The required amount of fuel is supplied in the form of a liquid column with strong penetrating force toward the wall of the front combustion chamber. Part of the supplied fuel evaporates on the high-temperature wall of the combustion chamber to form a lean air-fuel mixture within the combustion volume, and the rest of the fuel evaporates along the wall of the combustion chamber toward the spark plug. It concentrates in the vicinity and forms a rich mixture with good ignitability. As a result, slow stratified combustion can be achieved within the front eight self-combustion chambers.
エンジンが高負荷域の場合は、高出力を得るた杓に、前
記燃焼室内の燃焼をシリンダ内に広げる必要があり、中
・低負荷域の場合と同様な燃焼室内への燃料供給に加え
て、それ以前にピストンが吸気行程から圧縮行程前半の
位置にある時、前記噴射ノズルから燃料を霧化しやすい
ように貫徹力の弱い状態でシリンダ内への燃料供給を行
なう。When the engine is in a high load range, in order to obtain high output, it is necessary to spread the combustion in the combustion chamber into the cylinder, and in addition to supplying fuel into the combustion chamber as in the case of medium and low load ranges. Before that, when the piston is in a position from the intake stroke to the first half of the compression stroke, fuel is supplied into the cylinder with a weak penetration force so that the fuel can be easily atomized from the injection nozzle.
この場合の燃料は、吸気行程でシリンダ内に形成される
スワールを利用して霧化され、シリンダ内に薄い混合気
を形成する。In this case, the fuel is atomized using the swirl formed within the cylinder during the intake stroke, forming a thin air-fuel mixture within the cylinder.
前述のように、中・低負荷域及び高負荷域の燃焼室内へ
の燃料供給は、ピストンが圧縮上死点近傍の時、ピスト
ン頂面の凹形状の前記燃焼室の壁面に向けられなければ
ならず、したがって前記噴射ノズルは、ピストン頂面に
対して浅い角度に向けられている。As mentioned above, the fuel supply into the combustion chamber in the medium/low load range and high load range must be directed toward the concave wall of the combustion chamber on the top surface of the piston when the piston is near compression top dead center. Therefore, the injection nozzle is oriented at a shallow angle with respect to the top surface of the piston.
このために、高負荷域におけるシリンダ内への燃料供給
に際して、噴射燃料はシリンダ壁面に向けられており、
また前記噴射ノズルの噴射口からシリンダ壁面までにあ
まり距離がとれない。For this reason, when supplying fuel into the cylinder in a high load range, the injected fuel is directed toward the cylinder wall.
Further, there is not much distance between the injection port of the injection nozzle and the cylinder wall surface.
前述の高負荷域におけるシリンダ内への燃料供給は、霧
化しやすい状態で燃料を噴射するため１こ少量の内はス
ワールによりシリンダ壁面に到達する前に霧化されるが
、さらに高負荷となってシリンダ内への燃料供給量が増
大すると、霧化されない液状の燃料がシリンダ壁面に当
るようになる。In the above-mentioned high load range, when fuel is supplied into the cylinder, the fuel is injected in a state where it is easily atomized, so a small amount of fuel is atomized by swirl before reaching the cylinder wall surface. When the amount of fuel supplied into the cylinder increases, unatomized liquid fuel comes into contact with the cylinder wall.
その結果、燃料の霧化・混合が悪くなるばかりか、シリ
ンダ壁面の潤滑油が燃料によって洗い落されて、ピスト
ンとシリンダの摩擦が増大し、また潤滑油の消費量を増
大させ、さらに潤滑油に燃料が混入して希釈を生じさせ
る。As a result, not only does the atomization and mixing of the fuel deteriorate, but the lubricating oil on the cylinder wall is washed away by the fuel, increasing the friction between the piston and cylinder, increasing the amount of lubricating oil consumed, and further increasing the amount of lubricating oil consumed. fuel gets mixed in and causes dilution.
したがって本発明の目的は、中・低負荷域の燃焼室内へ
の燃料供給はそのままに、高負荷域における前述の問題
を改良した筒内直接噴射式火花点火機関を提供すること
である。Therefore, an object of the present invention is to provide an in-cylinder direct injection spark ignition engine that improves the above-mentioned problems in the high load range while maintaining the supply of fuel into the combustion chamber in the medium and low load ranges.
前述の目的を達成するために、本発明は、筒内にスワー
ル流を発生させる手段と、ピストン頂面に設けられた凹
形状の燃焼室と、前記燃焼室に臨む点火プラグと、前記
ピストンが圧縮上死点近傍にある時、前記燃焼室の壁面
に向って燃料を噴射するための第１噴射ノズルとを有し
、さらに前記ピストンが吸気行程後半にある時、前記ピ
ストンの頂面に向けて燃料を貫徹力の弱い状態で噴射す
るための第２噴射ノズルが設けられていることを特徴と
する筒内直接噴射式火花点火機関を提供する。In order to achieve the above-mentioned object, the present invention provides means for generating a swirl flow in a cylinder, a concave combustion chamber provided on the top surface of a piston, a spark plug facing the combustion chamber, and a piston having a concave shape. a first injection nozzle for injecting fuel toward the wall surface of the combustion chamber when the piston is near compression top dead center, and further toward the top surface of the piston when the piston is in the latter half of the intake stroke. To provide an in-cylinder direct injection spark ignition engine, characterized in that a second injection nozzle is provided for injecting fuel with a weak penetration force.
前述の構造とすると、中・低負荷域は、第１噴射ノズル
によって燃焼室内への良好な燃料供給を行なうことがで
きる。高負荷域は、前記第１噴射ノズルによる燃料供給
に加えて、それ以前に第２噴射ノズルから貫徹力の弱い
状態で、吸気行程後半に位置するピストン頂面に向けて
燃料噴射が行なわれる。With the above structure, the first injection nozzle can provide good fuel supply into the combustion chamber in the middle and low load ranges. In the high load region, in addition to the fuel supplied by the first injection nozzle, fuel is injected from the second injection nozzle with a weak penetration force toward the top surface of the piston located in the latter half of the intake stroke.
この時、前記第２噴射ノズルが適当な噴射範囲角度を有
していれば、さらに高負荷となって噴射量が増加しても
、噴射された燃料がシリンダ壁面に当ることはない。At this time, if the second injection nozzle has an appropriate injection range angle, the injected fuel will not hit the cylinder wall even if the load becomes higher and the injection amount increases.
このように噴射された燃料は、前記第２噴射ノズルの噴
射口からピストン頂面までに十分な距離があるために、
噴射量が増加しても、ピストンの頂面に接触することな
くシリンダ内に形成されたスワールによって霧化且つ気
化され、噴射量に応じた濃度の混合気を形成する。Since the fuel injected in this way has a sufficient distance from the injection port of the second injection nozzle to the top surface of the piston,
Even if the injection amount increases, the mixture is atomized and vaporized by the swirl formed inside the cylinder without contacting the top surface of the piston, forming an air-fuel mixture with a concentration corresponding to the injection amount.
第１．２図に第１の実施例を示す。同図において、１は
シリンダ壁面、２はピストン、３はシリンダヘッドを示
す。ピストン２の頂面には、凹形状の燃焼室４と、燃焼
室４に一部が重なるように形成されたプラグポケット５
とが設けられている。A first embodiment is shown in FIG. 1.2. In the figure, 1 is a cylinder wall surface, 2 is a piston, and 3 is a cylinder head. The top surface of the piston 2 has a concave combustion chamber 4 and a plug pocket 5 formed so as to partially overlap the combustion chamber 4.
and is provided.
シリンダヘッド３には、ピストン２の頂面に対して浅い
角度で燃料を燃焼室４内へ噴射するための第１噴射ノズ
ル６と、ピストン２の頂面の方向に燃料を貫徹力が弱い
状態で噴射するための第２噴射ノズル７と、プラグポケ
ット５に臨む点火プラグ８と、吸気バルブ９及び排気バ
ルブ１０とが設けられている。吸気バルブ９には、吸気
行程でシリンダ内にスワールを発生させるような形状に
作られた吸気管１１が接続されている。第１噴射ノズル
６は、燃料を貫徹力の強い液柱状態で燃焼室４内の二方
向に噴射するものであり、噴射方向をＣ１Ｄで示す。第
２噴射ノズル７は、第３図に示したピントルノズノペま
たは第４図に示した外聞弁であり、噴口面積を小さくし
て燃料を貫徹力の弱い霧化しやすい状態で噴射するもの
である。The cylinder head 3 includes a first injection nozzle 6 for injecting fuel into the combustion chamber 4 at a shallow angle with respect to the top surface of the piston 2, and a first injection nozzle 6 for injecting fuel into the combustion chamber 4 at a shallow angle with respect to the top surface of the piston 2. A second injection nozzle 7 for injecting the fuel, a spark plug 8 facing the plug pocket 5, an intake valve 9 and an exhaust valve 10 are provided. An intake pipe 11 is connected to the intake valve 9 and is shaped to generate a swirl within the cylinder during the intake stroke. The first injection nozzle 6 injects fuel in two directions within the combustion chamber 4 in the form of a liquid column with a strong penetrating force, and the injection direction is indicated by C1D. The second injection nozzle 7 is the pintle nozzle shown in FIG. 3 or the outer valve shown in FIG. 4, and has a small nozzle area to inject the fuel in a state where it is easily atomized with a weak penetration force.
本実施例の筒内直接噴射式火花点火機関は、以下のよう
に動作する。The in-cylinder direct injection spark ignition engine of this embodiment operates as follows.
中・低負荷域の場合は、ピストン２が圧縮行程終期の上
死点近傍（位置Ａ）にある時、必要な量の燃料を第１噴
射ノズル６から燃焼室４内の方向Ｃ，Ｄへ液柱状態で噴
射する。方向り、Ｅへ噴射された燃料の一部は、燃焼室
４の溝４ａに沿って蒸発霧化されながらプラグポケット
５に集中して比較的濃い混合気を形成する。またその他
の燃料も燃焼室４の壁面で蒸発霧化され燃焼室４内に混
合気を形成する。この時点火プラグ９を作動させれば、
プラグポケット５内の混合気が容易に着火し、その燃焼
が燃焼室４内に広がる。In the case of medium/low load ranges, when the piston 2 is near top dead center (position A) at the end of the compression stroke, the necessary amount of fuel is injected from the first injection nozzle 6 into the combustion chamber 4 in directions C and D. Injects in a liquid column. A part of the fuel injected in the direction E is evaporated and atomized along the groove 4a of the combustion chamber 4 and concentrated in the plug pocket 5 to form a relatively rich air-fuel mixture. Further, other fuels are also evaporated and atomized on the wall surface of the combustion chamber 4 to form an air-fuel mixture within the combustion chamber 4. If the spark plug 9 is activated at this point,
The air-fuel mixture in the plug pocket 5 is easily ignited, and its combustion spreads into the combustion chamber 4.
高負荷域の場合、燃焼室４内の燃焼までは、中・低負荷
域と同様であるが、高出力を得るためには、シリンダ内
に燃焼を広げる必要がある。この燃焼に必要な量の燃料
は、ピストン２が吸気行程後半（位置Ｂ）にある時、第
２噴射ノズル７から貫徹力の弱い状態でピストン２の頂
面に向けて噴射される。In the case of a high load range, combustion within the combustion chamber 4 is the same as in the medium/low load range, but in order to obtain high output, combustion must spread within the cylinder. The amount of fuel necessary for this combustion is injected from the second injection nozzle 7 toward the top surface of the piston 2 with a weak penetration force when the piston 2 is in the latter half of the intake stroke (position B).
この時、前記第２噴射ノズルが適当な噴射範囲角度を有
していれば、さらに高負荷となって噴射量が増加しても
、噴射燃料がシリンダ壁面１に当ることはなく、シリン
ダ壁面１の潤滑油を落とすなどの問題を生じることを防
止できる。At this time, if the second injection nozzle has an appropriate injection range angle, even if the load becomes higher and the injection amount increases, the injected fuel will not hit the cylinder wall surface 1. This can prevent problems such as dropping the lubricating oil.
このように噴射された燃料は、第２噴射ノズル７の噴射
口からピストン２の頂面までに十分な距離があり、また
霧化しやすい状態で噴射されるために、噴射量が増加し
ても噴射燃料の微粒化促進域１２をピストン２の頂面よ
り上部に設定でき、前記微粒化促進域１２において、ス
ワール１３によって第２図で示した方向Ｅに飛散しなが
ら容易に噴射量に応じた混合気を形成する。The fuel injected in this way has a sufficient distance from the injection port of the second injection nozzle 7 to the top surface of the piston 2, and is injected in a state where it is easy to atomize, so even if the injection amount increases, The atomization promotion area 12 of the injected fuel can be set above the top surface of the piston 2, and in the atomization promotion area 12, the fuel can be easily dispersed in the direction E shown in FIG. 2 by the swirl 13 according to the injection amount. Form a mixture.
したがってこの噴射燃料は、燃焼室４内に入りにくく、
燃焼室４内に点火直前に形成される混合気を濃くしすぎ
ることはない。Therefore, this injected fuel is difficult to enter into the combustion chamber 4,
The air-fuel mixture formed in the combustion chamber 4 immediately before ignition is not made too rich.
このように形成されたシリンダ内の混合気が、圧縮行程
で圧縮され、これに中・低負荷域と同様な燃焼室４内の
燃焼が広がる。The air-fuel mixture in the cylinder thus formed is compressed in the compression stroke, and combustion in the combustion chamber 4 spreads in the same manner as in the medium/low load range.
第６．７図に第２の実施例を示す。この実施例は、第２
噴射ノズル７がシリンダヘッド３の中心付近に配置され
たものである。A second embodiment is shown in Figure 6.7. In this example, the second
The injection nozzle 7 is arranged near the center of the cylinder head 3.
このように、本発明の筒内直接噴射式火花点火機関によ
れば、低・中負荷域においては、ピストン頂面に設けら
れた燃焼室内だけに燃料を第１噴射ノズルから噴射して
良好な点火・燃焼が得られ、高負荷域において、燃焼室
内の燃焼以外に必要な燃料が予め第２噴射ノズルから噴
射され吸気のスワール流によって良く霧化されるので、
シリンダ壁面の潤滑油を落とすことなしに、シリンダ内
に高負荷の度合に応じた燃料量の混合気を形成すること
ができ、燃焼室からの火焔伝播によって着火燃焼する。As described above, according to the in-cylinder direct injection type spark ignition engine of the present invention, in low to medium load ranges, fuel is injected only into the combustion chamber provided on the top surface of the piston from the first injection nozzle, resulting in good performance. Ignition and combustion are obtained, and in the high load range, the fuel necessary for purposes other than combustion in the combustion chamber is injected in advance from the second injection nozzle and well atomized by the swirl flow of intake air.
A fuel mixture with an amount of fuel corresponding to the degree of high load can be formed in the cylinder without removing lubricating oil from the cylinder wall surface, and ignition combustion occurs by flame propagation from the combustion chamber.
それにより低負荷域から高負荷域まで良好な成層燃焼が
得られ、これは、必要とする最少量の燃料を使用するに
すぎないために、燃費の良い機関を実現することができ
る。As a result, good stratified charge combustion can be obtained from a low load range to a high load range, and since only the minimum amount of fuel is used, an engine with good fuel efficiency can be realized.
第１図は本発明による第１の実施例の筒内直接噴射式火
花点火機関の断面側面図、第２図は第１図の断面平面図
、第３図は第２噴射ノズルの断面図、第４図は第３図と
異なる形状の第２噴射ノズルの断面図、第５図は本発明
による第一２の実施例の筒内直接噴射式火花点火機関の
断面側面図、第６図は第５図の断面平面図である。
１・・・シリンダ壁面、 ２・・・ピストン、４・
・・燃焼室、 ５・・・プラグポケット、６
・・・第１噴射ノズノペ ７・・・第２噴射ノズル、１
１・・・吸気’ｌ、１３・・・スワール。
畠 １ 口 ｓ−・・プラグポケッ
ト６・・・第１噴射ノズル
第２−
第３図
処４図
７・・・第２噴射ノズルFIG. 1 is a cross-sectional side view of a direct injection spark ignition engine according to a first embodiment of the present invention, FIG. 2 is a cross-sectional plan view of FIG. 1, and FIG. 3 is a cross-sectional view of a second injection nozzle. FIG. 4 is a cross-sectional view of a second injection nozzle having a shape different from that in FIG. 3, FIG. FIG. 6 is a cross-sectional plan view of FIG. 5; 1... Cylinder wall surface, 2... Piston, 4...
... Combustion chamber, 5... Plug pocket, 6
...First injection nozzle 7...Second injection nozzle, 1
1... Intake 'l, 13... Swirl. Hatake 1 Mouth s-... Plug pocket 6... 1st injection nozzle 2nd- 3rd figure 4 figure 7... 2nd injection nozzle
Claims (1)
設けられた凹形状の燃焼室と、前記燃焼室に臨む点火プ
ラグと、前記ピストンが圧縮上死点近傍にある時、前記
燃焼室の壁面に向って燃料を噴射するための第１噴射ノ
ズルとを有し、さらに前記ピストンが吸気行程後半にあ
る時、前記ピストン頂面に向けて燃料を貫徹力の弱い状
態で噴射するための第２噴射ノズルが設けられているこ
とを特徴とする筒内直接噴射式火花点火機関。means for generating a swirl flow in the cylinder; a concave combustion chamber provided on the top surface of the piston; a spark plug facing the combustion chamber; a first injection nozzle for injecting fuel toward a wall surface, and a first injection nozzle for injecting fuel toward a top surface of the piston with a weak penetration force when the piston is in the latter half of the intake stroke. An in-cylinder direct injection spark ignition engine characterized by being provided with two injection nozzles.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2314089A JPH04187815A (en) | 1990-11-21 | 1990-11-21 | Cylinder direct injection type spark ignition engine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2314089A JPH04187815A (en) | 1990-11-21 | 1990-11-21 | Cylinder direct injection type spark ignition engine |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH04187815A true JPH04187815A (en) | 1992-07-06 |
Family
ID=18049108
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP2314089A Pending JPH04187815A (en) | 1990-11-21 | 1990-11-21 | Cylinder direct injection type spark ignition engine |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH04187815A (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5983630A (en) * | 1997-07-01 | 1999-11-16 | Toyota Jidosha Kabushiki Kaisha | Fuel injecting device for an engine |
| JP2004044498A (en) * | 2002-07-12 | 2004-02-12 | Toyota Motor Corp | Internal combustion engine for compressed-self-igniting fuel-air mixture, and method for controlling internal combustion engine |
| WO2017199574A1 (en) * | 2016-05-19 | 2017-11-23 | 日立オートモティブシステムズ株式会社 | Internal combustion engine control device |
-
1990
- 1990-11-21 JP JP2314089A patent/JPH04187815A/en active Pending
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5983630A (en) * | 1997-07-01 | 1999-11-16 | Toyota Jidosha Kabushiki Kaisha | Fuel injecting device for an engine |
| EP0889220A3 (en) * | 1997-07-01 | 2000-06-14 | Toyota Jidosha Kabushiki Kaisha | A fuel injecting device for an engine |
| JP2004044498A (en) * | 2002-07-12 | 2004-02-12 | Toyota Motor Corp | Internal combustion engine for compressed-self-igniting fuel-air mixture, and method for controlling internal combustion engine |
| WO2017199574A1 (en) * | 2016-05-19 | 2017-11-23 | 日立オートモティブシステムズ株式会社 | Internal combustion engine control device |
| JP2017207011A (en) * | 2016-05-19 | 2017-11-24 | 日立オートモティブシステムズ株式会社 | Internal combustion engine controller |
| EP3460223A4 (en) * | 2016-05-19 | 2019-11-27 | Hitachi Automotive Systems, Ltd. | Internal combustion engine control device |
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