JPH09217626A - Direct injection four valve diesel engine - Google Patents
Direct injection four valve diesel engineInfo
- Publication number
- JPH09217626A JPH09217626A JP8025174A JP2517496A JPH09217626A JP H09217626 A JPH09217626 A JP H09217626A JP 8025174 A JP8025174 A JP 8025174A JP 2517496 A JP2517496 A JP 2517496A JP H09217626 A JPH09217626 A JP H09217626A
- Authority
- JP
- Japan
- Prior art keywords
- combustion chamber
- fuel injection
- injection nozzle
- axis
- cylinder head
- 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
- F02B23/00—Other engines characterised by special shape or construction of combustion chambers to improve operation
- F02B23/02—Other engines characterised by special shape or construction of combustion chambers to improve operation with compression ignition
- F02B23/06—Other engines characterised by special shape or construction of combustion chambers to improve operation with compression ignition the combustion space being arranged in working piston
- F02B23/0696—W-piston bowl, i.e. the combustion space having a central projection pointing towards the cylinder head and the surrounding wall being inclined towards the cylinder wall
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
- F02F1/00—Cylinders; Cylinder heads
- F02F1/24—Cylinder heads
- F02F1/42—Shape or arrangement of intake or exhaust channels in cylinder heads
- F02F1/4214—Shape or arrangement of intake or exhaust channels in cylinder heads specially adapted for four or more valves per 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
- F02B2275/00—Other engines, components or details, not provided for in other groups of this subclass
- F02B2275/14—Direct injection into combustion chamber
-
- 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
- F02B23/02—Other engines characterised by special shape or construction of combustion chambers to improve operation with compression ignition
- F02B23/06—Other engines characterised by special shape or construction of combustion chambers to improve operation with compression ignition the combustion space being arranged in working piston
- F02B23/0678—Unconventional, complex or non-rotationally symmetrical shapes of the combustion space, e.g. flower like, having special shapes related to the orientation of the fuel spray jets
- F02B23/069—Unconventional, complex or non-rotationally symmetrical shapes of the combustion space, e.g. flower like, having special shapes related to the orientation of the fuel spray jets characterised by its eccentricity from the cylinder axis
-
- 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
- F02B3/00—Engines characterised by air compression and subsequent fuel addition
- F02B3/06—Engines characterised by air compression and subsequent fuel addition with compression ignition
-
- 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)
- Fuel-Injection Apparatus (AREA)
Abstract
Description
【０００１】[0001]
【発明の属する技術分野】本発明は、直接噴射式４バル
ブディーゼルエンジンに関する。TECHNICAL FIELD The present invention relates to a direct injection four-valve diesel engine.
【０００２】[0002]
【従来の技術】直接噴射式４バルブディーゼルエンジン
は、シリンダヘッドに燃焼噴射ノズルと４つの吸気バル
ブ及び排気バルブを備え、シリンダヘッドとピストン頭
部の間に設けられた燃焼室の中に、燃料噴射ノズルから
燃料を噴射して自然発火により燃焼させるようにしたも
のである。2. Description of the Related Art A direct injection type four-valve diesel engine is equipped with a combustion injection nozzle, four intake valves and an exhaust valve in a cylinder head, and a fuel is introduced into a combustion chamber provided between the cylinder head and the piston head. The fuel is injected from an injection nozzle and burned by spontaneous combustion.
【０００３】この種の直接噴射式４バルブディーゼルエ
ンジンでは、燃焼ムラをなくし燃焼を均一にすることに
よって燃焼速度を早くするため、燃料噴射ノズルを燃焼
室の中心線に一致させている。In this type of direct injection type four-valve diesel engine, the fuel injection nozzle is aligned with the center line of the combustion chamber in order to speed up the combustion speed by eliminating uneven combustion and uniform combustion.
【０００４】[0004]
【発明が解決しようとする課題】混合気にスワールを発
生させる場合、スワール速度は燃焼室の中心から遠ざか
るにつれて大きくなり、また空気の密度も燃焼室の外周
側の方が内周側よりも大きくなっている。When a swirl is generated in a mixture, the swirl velocity increases as the distance from the center of the combustion chamber increases, and the air density on the outer peripheral side of the combustion chamber is larger than that on the inner peripheral side. Has become.
【０００５】ところで、アイドル時及び軽負荷時におい
て、燃料噴射ノズルからの噴射圧が低い場合、着火は燃
料噴射ノズルの噴孔近傍で発生するが、上記従来例で
は、燃料噴射ノズルの噴孔が燃焼室の中心に位置するた
め、着火が燃焼室の中心で発生している。ところが、上
述したように、燃焼室の中心ではスワール速度が小さい
ためスワールアシストが弱く、また空気密度も小さいこ
とから、噴霧と空気のミクシングが不良となって不完全
燃焼を起こし、これが原因で排気ガス中における白煙や
黒煙の発生を招くことがあった。By the way, when the injection pressure from the fuel injection nozzle is low at idle and at light load, ignition occurs near the injection hole of the fuel injection nozzle. Since it is located in the center of the combustion chamber, ignition occurs in the center of the combustion chamber. However, as mentioned above, the swirl speed is low in the center of the combustion chamber, so the swirl assist is weak and the air density is low, resulting in poor mixing of spray and air, causing incomplete combustion, which causes exhaust gas. Occasionally, white smoke or black smoke was generated in the gas.
【０００６】本発明は、上記問題点に鑑みてなされたも
ので、アイドル時及び軽負荷時に噴霧と空気のミキシン
グを促進して燃焼の改善を図った直接噴射式４バルブデ
ィーゼルエンジンを提供することを目的とする。The present invention has been made in view of the above problems, and provides a direct injection type four-valve diesel engine that promotes mixing of spray and air at the time of idling and light load to improve combustion. With the goal.
【０００７】[0007]
【課題を解決するための手段】請求項１に記載の発明
は、シリンダ壁とシリンダヘッドとピストン頭部との間
に設けられた燃焼室と、前記シリンダヘッドに設けられ
た一対の吸気バルブ及び一対の排気バルブと、前記シリ
ンダヘッドに設けられ、前記燃焼室の軸線に対してほぼ
平行な軸線を有する燃料噴射ノズルとを有し、前記燃焼
室の軸線と前記燃料噴射ノズルの軸線とは該燃焼室の半
径方向においてその一方が他方からオフセットされてい
る。According to a first aspect of the present invention, there is provided a combustion chamber provided between a cylinder wall, a cylinder head and a piston head, a pair of intake valves provided at the cylinder head, and A pair of exhaust valves and a fuel injection nozzle provided in the cylinder head and having an axis substantially parallel to the axis of the combustion chamber are provided, and the axis of the combustion chamber and the axis of the fuel injection nozzle are One of them is offset from the other in the radial direction of the combustion chamber.
【０００８】（作用）アイドル時又は軽負荷時におい
て、燃料噴射ノズルからの噴射圧が低い場合、着火が燃
料噴射ノズルの噴孔近傍で発生する。しかし、燃料噴射
ノズルの軸線と燃焼室の軸線とは、その一方が他方から
オフセットし燃料噴射ノズルの噴孔は燃焼室の中心から
離れた位置にあるので、着火は燃焼室の中心から離れた
ところで発生する。この着火発生位置はスワールアシス
トが強くかつ空気密度も大であるため、噴霧と空気との
ミクシングが促進される。(Operation) When the injection pressure from the fuel injection nozzle is low at idle or when the load is light, ignition occurs near the injection hole of the fuel injection nozzle. However, one of the axis of the fuel injection nozzle and the axis of the combustion chamber is offset from the other, and the injection hole of the fuel injection nozzle is located away from the center of the combustion chamber, so the ignition is separated from the center of the combustion chamber. It happens by the way. Since the swirl assist is strong and the air density is high at this ignition occurrence position, mixing of spray and air is promoted.
【０００９】[0009]
【発明の実施の形態】以下、本発明の実施形態を図面を
参照しながら説明する。図１及び図２は請求項１に記載
の発明に係る直接噴射式４バルブディーゼルエンジンの
一実施形態を示すものである。１はシリンダ、２はシリ
ンダ１内を往復動するピストン、３はシリンダ１の上部
に固定されたシリンダヘッド、４は燃焼室である。燃焼
室４はピストン２が上死点にあるときのシリンダ１の内
周壁とシリンダヘッド３とピストン２の頭部とで囲まれ
た部屋である。Embodiments of the present invention will be described below with reference to the drawings. 1 and 2 show an embodiment of a direct injection type four-valve diesel engine according to the invention described in claim 1. Reference numeral 1 is a cylinder, 2 is a piston that reciprocates in the cylinder 1, 3 is a cylinder head fixed to the upper portion of the cylinder 1, and 4 is a combustion chamber. The combustion chamber 4 is a chamber surrounded by the inner peripheral wall of the cylinder 1, the cylinder head 3, and the head of the piston 2 when the piston 2 is at the top dead center.
【００１０】シリンダヘッド３には図２に示すように、
一対の吸気バルブ５と一対の排気バルブ６とが設けられ
ている。これら４つの吸気バルブ５と排気バルブ６とは
燃焼室４の軸線Ｙを中心とする円周上に９０゜の角度を
おいてほぼ等間隔に配列されている。７は燃焼室４内に
燃料を噴射する燃料噴射ノズルで、その軸線Ｘはシリン
ダヘッド３の下面に対して垂直になっている。この燃料
噴射ノズル７の位置であるが、これは燃焼室４の軸線Ｙ
からオフセットした位置に設定されている。In the cylinder head 3, as shown in FIG.
A pair of intake valves 5 and a pair of exhaust valves 6 are provided. These four intake valves 5 and exhaust valves 6 are arranged at substantially equal intervals on the circumference centered on the axis Y of the combustion chamber 4 with an angle of 90 °. Reference numeral 7 is a fuel injection nozzle for injecting fuel into the combustion chamber 4, and its axis X is perpendicular to the lower surface of the cylinder head 3. This is the position of the fuel injection nozzle 7, which is the axis Y of the combustion chamber 4.
It is set at a position offset from.
【００１１】このように燃料噴射ノズル７の位置を、燃
焼室４の軸線Ｙからオフセットさせるのは次の理由によ
る。すなわち、図３に示すように、ピストン２の上死点
付近におけるスワールの速度Ｖは、燃焼室４の軸線Ｙか
ら半径方向に遠ざかるにつれ軸線Ｙからの距離に比例し
て大きくなる特性を有している。また、空気の密度は、
燃焼室４の内周側よりも外周側の方が大きい。The position of the fuel injection nozzle 7 is thus offset from the axis Y of the combustion chamber 4 for the following reason. That is, as shown in FIG. 3, the swirl velocity V near the top dead center of the piston 2 has a characteristic that the swirl velocity V increases in proportion to the distance from the axis Y of the combustion chamber 4 in the radial direction. ing. Also, the density of air is
The outer peripheral side of the combustion chamber 4 is larger than the inner peripheral side thereof.
【００１２】したがって、燃料噴射ノズル７が燃焼室４
の軸線Ｙからオフセットされていると、燃料噴射ノズル
７付近のスワールアシストが大きくかつ空気密度も大で
あることから、アイドル時又は軽負荷時において、燃料
噴射ノズル７の噴射圧が低く、着火が燃料噴射ノズル７
の近傍で発生する場合でも噴霧と空気とのミキシングが
促進されるからである。Therefore, the fuel injection nozzle 7 is installed in the combustion chamber 4
When offset from the axis Y of, the swirl assist in the vicinity of the fuel injection nozzle 7 is large and the air density is also large. Fuel injection nozzle 7
This is because mixing between the spray and the air is promoted even when it occurs in the vicinity of.
【００１３】ただし、燃料噴射ノズル７の位置が燃焼室
４の軸線Ｙからあまりに離れていると、燃焼ムラが生じ
燃焼が遅くなって全負荷時の性能が確保されないことか
ら、燃料噴射ノズル７の設定位置は次式で表される領域
内にあることが好ましい。 ２０％≧ｌ／Ｌ×１００ （１） ここに、ｌは燃料噴射ノズル７のオフセットの量、Ｌは
燃焼室４の直径を表す。However, if the position of the fuel injection nozzle 7 is too far from the axis Y of the combustion chamber 4, uneven combustion will occur and combustion will be delayed, so that the performance at full load cannot be ensured. The setting position is preferably within the area represented by the following equation. 20% ≧ l / L × 100 (1) Here, 1 represents the amount of offset of the fuel injection nozzle 7, and L represents the diameter of the combustion chamber 4.
【００１４】上記においては、燃料噴射ノズル７の位置
を移動させて燃焼室４の中心からオフセットさせた例に
ついて述べたが、これに限らず図４に示すように、燃焼
室４の軸線Ｙを移動させて燃料噴射ノズル７からオフセ
ットさせても上記と同様の作用効果が得られる。次に本
実施形態の作用について説明する。In the above description, an example in which the position of the fuel injection nozzle 7 is moved to be offset from the center of the combustion chamber 4 has been described. However, the present invention is not limited to this, and as shown in FIG. Even if the fuel injection nozzle 7 is moved and offset from the fuel injection nozzle 7, the same effect as the above can be obtained. Next, the operation of the present embodiment will be described.
【００１５】アイドル時又は軽負荷時において、燃料噴
射ノズル７からの噴射圧が低い場合、着火は燃料噴射ノ
ズル７の噴孔近傍で発生する。いま、仮に燃料噴射ノズ
ル７が燃焼室４の中心に位置するとなると、燃焼室４の
中心ではスワールアシストが弱くかつ空気密度も小さい
ため、噴霧と空気とのミクシングが不良となる。しか
し、本実施形態では、燃料噴射ノズル７は燃焼室４の中
心からオフセットしているので、着火発生位置ではスワ
ールアシストが強くかつ空気密度も大であるため、噴霧
と空気とのミクシングが促進される。When the injection pressure from the fuel injection nozzle 7 is low at the time of idling or at the time of light load, ignition occurs near the injection hole of the fuel injection nozzle 7. Now, assuming that the fuel injection nozzle 7 is located at the center of the combustion chamber 4, the swirl assist is weak and the air density is small at the center of the combustion chamber 4, resulting in poor mixing of spray and air. However, in the present embodiment, since the fuel injection nozzle 7 is offset from the center of the combustion chamber 4, swirl assist is strong and the air density is large at the ignition occurrence position, so mixing of spray and air is promoted. It
【００１６】また、図４に示すように、燃焼室４の軸線
Ｙが燃料噴射ノズル７からオフセットしている場合にも
上記と同一の作用効果が得られる。上述のように、燃料
噴射ノズル７が燃焼室４の軸線Ｙからオフセットしてい
ると燃焼ムラが生ずることがあることから、４バルブデ
ィーゼルエンジンでは、燃料噴射ノズル７は燃焼室４の
中心に位置することが望ましいと言える。Further, as shown in FIG. 4, even when the axis Y of the combustion chamber 4 is offset from the fuel injection nozzle 7, the same effect as the above can be obtained. As described above, when the fuel injection nozzle 7 is offset from the axis Y of the combustion chamber 4, uneven combustion may occur. Therefore, in the 4-valve diesel engine, the fuel injection nozzle 7 is located at the center of the combustion chamber 4. It can be said that it is desirable to do.
【００１７】しかし、本実施形態のように、燃料噴射ノ
ズル７の設定位置が（１）式で示される領域内であれ
ば、燃焼ムラはそれほど大きくないため、燃料噴射ノズ
ル７をオフセットさせても燃焼速度をそれほど遅らせる
ことにはならず、全負荷時の性能確保という観点からは
別段の支障は生じない。However, as in the present embodiment, if the set position of the fuel injection nozzle 7 is within the region shown by the equation (1), the combustion unevenness is not so large, and therefore the fuel injection nozzle 7 can be offset. It does not slow down the combustion speed so much, and from the viewpoint of ensuring performance at full load, there is no particular problem.
【００１８】以上のように、本実施形態では、燃料噴射
ノズル７と燃焼室４とのいずれか一方を他方からオフセ
ットさせるので、アイドル時及び軽負荷時に噴霧と空気
のミクシングが促進され、排気ガス中における白煙や黒
煙の発生が抑制される。ちなみに、実開平５−１９５２
６号公報に記載されているように、直接噴射式２バルブ
ディーゼルエンジンでは燃料噴射ノズルを燃焼室の中心
から偏心させることは通常に行われている。As described above, in the present embodiment, one of the fuel injection nozzle 7 and the combustion chamber 4 is offset from the other, so that the mixing of the spray and the air is promoted at the time of idling and the light load, and the exhaust gas is exhausted. Generation of white smoke and black smoke is suppressed. By the way, Kaikaihei 5-1952
As described in Japanese Patent Publication No. 6, the direct injection type two-valve diesel engine is normally designed to decenter the fuel injection nozzle from the center of the combustion chamber.
【００１９】[0019]
【発明の効果】請求項１に記載の発明では、アイドル時
及び軽負荷時に噴霧と空気のミクシングが促進されるた
め、空気不足による不完全燃焼に起因する排気ガス中に
おける白煙や黒煙の発生が抑制される。According to the invention described in claim 1, since the mixing of the spray and the air is promoted at the time of idling and at the time of light load, the white smoke and the black smoke in the exhaust gas caused by the incomplete combustion due to the insufficient air are generated. Occurrence is suppressed.
【図１】請求項１に記載の発明に係る直接噴射式４バル
ブディーゼルエンジンの一実施形態を示す断面図。FIG. 1 is a sectional view showing an embodiment of a direct injection 4-valve diesel engine according to the invention described in claim 1.
【図２】同じく、燃料噴射ノズルと吸気バルブ及び排気
バルブの配置を示す説明図。FIG. 2 is an explanatory view showing the arrangement of fuel injection nozzles, intake valves and exhaust valves.
【図３】同じく、燃焼室内におけるスワール速度を示す
説明図。FIG. 3 is an explanatory diagram showing a swirl velocity in the combustion chamber.
【図４】同じく、他の実施形態を示す断面図。FIG. 4 is a sectional view showing another embodiment of the present invention.
１ シリンダ ２ ピストン ３ シリンダヘッド ４ 燃焼室 ５ 吸気バルブ ６ 排気バルブ ７ 燃料噴射ノズル Ｘ 燃料噴射ノズルの軸線 Ｙ 燃焼室の軸線 1 cylinder 2 piston 3 cylinder head 4 combustion chamber 5 intake valve 6 exhaust valve 7 fuel injection nozzle X axis line of fuel injection nozzle Y axis line of combustion chamber
Claims (1)
壁とシリンダヘッドとピストン頭部とで形成される燃焼
室と、 前記シリンダヘッドに設けられた一対の吸気バルブ及び
一対の排気バルブと、 前記シリンダヘッドに設けられ、前記燃焼室の軸線に対
してほぼ平行な軸線を有する燃料噴射ノズルとを有し、 前記燃焼室の軸線と前記燃料噴射ノズルの軸線とは該燃
焼室の半径方向においてその一方が他方からオフセット
されていることを特徴とする直接噴射式４バルブディー
ゼルエンジン。1. A combustion chamber formed by a cylinder wall, a cylinder head and a piston head when the piston is at the top dead center, a pair of intake valves and a pair of exhaust valves provided in the cylinder head, A fuel injection nozzle provided on the cylinder head, the fuel injection nozzle having an axis substantially parallel to the axis of the combustion chamber, and the axis of the combustion chamber and the axis of the fuel injection nozzle in a radial direction of the combustion chamber. A direct injection 4-valve diesel engine, characterized in that one of them is offset from the other.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP8025174A JPH09217626A (en) | 1996-02-13 | 1996-02-13 | Direct injection four valve diesel engine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP8025174A JPH09217626A (en) | 1996-02-13 | 1996-02-13 | Direct injection four valve diesel engine |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH09217626A true JPH09217626A (en) | 1997-08-19 |
Family
ID=12158654
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP8025174A Pending JPH09217626A (en) | 1996-02-13 | 1996-02-13 | Direct injection four valve diesel engine |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH09217626A (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2000054908A (en) * | 1998-05-22 | 2000-02-22 | Waertsilae Nsd Schweiz Ag | Cylinder cover and arrangement structure of cylinder cover in two-stroke diesel engine |
| WO2006114946A1 (en) * | 2005-04-19 | 2006-11-02 | Yanmar Co., Ltd. | Direct injection diesel engine |
| JP2011506846A (en) * | 2007-12-19 | 2011-03-03 | ルノー・エス・アー・エス | Combustion chamber of a supercharged direct injection combustion engine |
-
1996
- 1996-02-13 JP JP8025174A patent/JPH09217626A/en active Pending
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2000054908A (en) * | 1998-05-22 | 2000-02-22 | Waertsilae Nsd Schweiz Ag | Cylinder cover and arrangement structure of cylinder cover in two-stroke diesel engine |
| WO2006114946A1 (en) * | 2005-04-19 | 2006-11-02 | Yanmar Co., Ltd. | Direct injection diesel engine |
| EP1876332A1 (en) * | 2005-04-19 | 2008-01-09 | Yanmar Co., Ltd. | Direct injection diesel engine |
| EP1876332A4 (en) * | 2005-04-19 | 2009-06-17 | Yanmar Co Ltd | Direct injection diesel engine |
| JP2011506846A (en) * | 2007-12-19 | 2011-03-03 | ルノー・エス・アー・エス | Combustion chamber of a supercharged direct injection combustion engine |
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