JPS5960027A - Combustion chamber of diesel engine - Google Patents
Combustion chamber of diesel engineInfo
- Publication number
- JPS5960027A JPS5960027A JP57172552A JP17255282A JPS5960027A JP S5960027 A JPS5960027 A JP S5960027A JP 57172552 A JP57172552 A JP 57172552A JP 17255282 A JP17255282 A JP 17255282A JP S5960027 A JPS5960027 A JP S5960027A
- Authority
- JP
- Japan
- Prior art keywords
- combustion chamber
- side wall
- combustion
- fuel
- piston
- 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
- 238000002485 combustion reaction Methods 0.000 title claims abstract description 72
- 239000000446 fuel Substances 0.000 claims abstract description 35
- 239000007921 spray Substances 0.000 claims description 15
- 238000002347 injection Methods 0.000 claims description 6
- 239000007924 injection Substances 0.000 claims description 6
- 230000008020 evaporation Effects 0.000 abstract description 6
- 238000001704 evaporation Methods 0.000 abstract description 6
- 230000003116 impacting effect Effects 0.000 abstract 4
- 238000000034 method Methods 0.000 abstract 1
- 238000009841 combustion method Methods 0.000 description 3
- 230000015572 biosynthetic process Effects 0.000 description 2
- 238000009792 diffusion process Methods 0.000 description 2
- 230000001965 increasing effect Effects 0.000 description 2
- 238000004519 manufacturing process Methods 0.000 description 2
- 238000010586 diagram Methods 0.000 description 1
- 230000020169 heat generation Effects 0.000 description 1
- 230000001939 inductive effect Effects 0.000 description 1
- 239000003595 mist Substances 0.000 description 1
- 239000000049 pigment Substances 0.000 description 1
- 230000001737 promoting effect Effects 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
- F02B23/02—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
- F02B23/0636—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 the combustion space having a substantially flat and horizontal bottom
- F02B23/0639—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 the combustion space having a substantially flat and horizontal bottom the combustion space having substantially the shape of a 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
- F02B23/0618—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 having in-cylinder means to influence the charge motion
- F02B23/0621—Squish flow
-
- 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
- F02B23/0645—Details related to the fuel injector or the fuel spray
- F02B23/0648—Means or methods to improve the spray dispersion, evaporation or ignition
- F02B23/0651—Means or methods to improve the spray dispersion, evaporation or ignition the fuel spray impinging on reflecting surfaces or being specially guided throughout the combustion space
-
- 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)
Abstract
Description
【発明の詳細な説明】
本発明は、ピストンの頂面に凹設した燃焼室に燃料を直
接噴射供給するようにしたディーゼル機関の燃焼室に関
するものである。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a combustion chamber of a diesel engine in which fuel is directly injected and supplied to a combustion chamber recessed in the top surface of a piston.
従来のこの種の燃焼室としては、混合燃焼方式の燃焼室
、蒸発燃焼方式の燃焼室等がある。Conventional combustion chambers of this type include a mixed combustion type combustion chamber, an evaporative combustion type combustion chamber, and the like.
前者の混合燃焼方式のものでは、通常は燃焼室側壁に対
し、直角に近い角度で燃料が衝突するため燃料噴霧のは
ね返り量が多く、従って第１期燃焼が多くなって排気対
策を実行するうえで不利である。又、後者の特公昭５０
−２９０８５に示されるような蒸発燃焼方式の燃焼室で
は、第１期燃焼を抑制し易いので排気中のＮＯＸ濃度等
を低減させるには極めて有効であるが、燃焼室の温度が
低い時には燃料の蒸発が不充分となってしまうので、始
動性が悪化すると共に、無負荷及び軽負荷運転時に不完
全燃焼を起し易いという欠点があった。更に、これらの
燃焼方式の不利な点を解消するために、例えば、特公昭
５２−３３２４２号公報にみられるように、燃焼室の側
壁と噴霧とのなす角を一定角度に押えることも提案され
ている。In the former mixed combustion method, the fuel usually collides with the side wall of the combustion chamber at an angle close to right angles, resulting in a large amount of fuel spray bouncing back, resulting in a large amount of first-stage combustion, which makes it difficult to implement exhaust gas countermeasures. It is disadvantageous. Also, the latter special public service in the 1970s
The evaporative combustion type combustion chamber shown in the 29085 is extremely effective in reducing the NOx concentration in the exhaust gas because it is easy to suppress the first stage combustion, but when the temperature of the combustion chamber is low, the fuel Since evaporation is insufficient, there are disadvantages in that startability deteriorates and incomplete combustion tends to occur during no-load or light-load operation. Furthermore, in order to eliminate the disadvantages of these combustion methods, it has been proposed, for example, to suppress the angle between the side wall of the combustion chamber and the spray to a constant angle, as seen in Japanese Patent Publication No. 52-33242. ing.
本発明は、このような従来の直接噴射式ディーセルエン
ジンの燃焼室を更に改善したものであり、スキッシュを
生成させるための張出部を燃焼室の側壁上端部に形成し
、との張出部の下面をピストンの頂面に対して略４５°
に顔料させて燃料噴霧の衝突面を形成して燃料のはね返
りｉ′ｆ：減少させると共に、この衝突面の下方におけ
る燃焼室の水平断面を側壁に凹部を設けることで花弁状
に形成することによシ、燃焼室の側壁に沿って流れるス
ワールに乱れを与え、以って、燃焼室（ｉ１１１壁に付
着展延した燃料薄膜の剥離、蒸発を促進させて燃焼効率
を損なうことなく排気特性を改善しようとするものであ
る。The present invention further improves the combustion chamber of such a conventional direct injection diesel engine, in which a protrusion for generating squish is formed at the upper end of the side wall of the combustion chamber. The bottom surface of the piston is approximately 45 degrees to the top surface of the piston.
The impact surface of the fuel spray is made of pigment to reduce fuel rebound i′f, and the horizontal section of the combustion chamber below this impact surface is formed into a petal-like shape by providing a recess in the side wall. In this way, the swirl flowing along the side wall of the combustion chamber is disturbed, thereby promoting the peeling and evaporation of the thin fuel film that has spread on the wall of the combustion chamber (i111), thereby improving the exhaust characteristics without impairing the combustion efficiency. It is something that we try to improve.
以下に本発明を図示された一実施例に基づいて詳細に説
明する。The present invention will be explained in detail below based on an illustrated embodiment.
図示しないシリンダ内で往復動するピストン１の頂面に
は燃焼室２を凹設しており、図示しないシリンダヘッド
に取り付けた燃料噴射ノズル３から前記燃焼室２の側壁
４に向って燃料を噴射するようにして直接噴射式ディー
ゼルエンジンを構成している。A combustion chamber 2 is recessed in the top surface of a piston 1 that reciprocates within a cylinder (not shown), and fuel is injected toward a side wall 4 of the combustion chamber 2 from a fuel injection nozzle 3 attached to a cylinder head (not shown). This is how a direct injection diesel engine is constructed.
前記燃焼室２の側壁４の上端部の全周縁には、中心に向
って延びる張出部５を設けることにょす、より強い、ス
キッシュを得てスワールを強化するようにしている。又
、張出部５の下面をピストン１の頂面１ａに対して略４
５°に傾斜させて燃料噴霧の衝突面６を形成している。By providing an overhang 5 extending toward the center on the entire circumference of the upper end of the side wall 4 of the combustion chamber 2, a stronger squish is obtained and the swirl is strengthened. Also, the lower surface of the overhanging portion 5 is approximately 4 mm relative to the top surface 1a of the piston 1.
It is inclined at 5° to form a fuel spray collision surface 6.
そして、この衝突面６から底壁７に至る略垂直状をなす
側壁４の周方向複数位置に、それぞれ深さ方向の全域に
わたって側壁４と連続する曲面で凹入させてなる凹部８
を設けることによシ、衝突面６より下方における燃焼室
２の水平断面形状を花弁状に形成している。Recesses 8 are formed by recessing curved surfaces that are continuous with the side wall 4 over the entire depth direction at a plurality of positions in the circumferential direction of the substantially vertical side wall 4 from the collision surface 6 to the bottom wall 7.
By providing this, the horizontal cross-sectional shape of the combustion chamber 2 below the collision surface 6 is formed into a petal shape.
上記の構成において、燃料噴射ノズル３から噴射された
燃料噴ｇ９は、スワールによって押し流されつつ空気と
混合して燃焼室２の側壁４の上端部に形成されている衝
突面６に衝突し、この衝突面６による案内作用で第２図
に二点鎖線で示すように側壁４及び凹部８に沿って反射
される。このために、燃焼室２の中心に向って反射され
る噴霧が減少して第１期燃焼の少ない蒸発燃焼方式に近
い燃焼が行なわれる。In the above configuration, the fuel injection g9 injected from the fuel injection nozzle 3 is swept away by the swirl, mixes with air, and collides with the collision surface 6 formed at the upper end of the side wall 4 of the combustion chamber 2. Due to the guiding action of the collision surface 6, the light is reflected along the side wall 4 and the recess 8, as shown by the two-dot chain line in FIG. Therefore, the amount of spray reflected toward the center of the combustion chamber 2 is reduced, and combustion similar to an evaporative combustion method with less first-stage combustion is performed.
一方、燃焼室２の側壁４の上端部には張出部５を設けて
強いスキッシュを得るようにしているので、燃焼室２内
のスワールが強化される。On the other hand, since the overhang 5 is provided at the upper end of the side wall 4 of the combustion chamber 2 to obtain a strong squish, the swirl within the combustion chamber 2 is strengthened.
そして、燃焼室２の側壁４が凹部８を設けたことで滑ら
かな凹凸状になっているため、この側壁４に沿って周方
向に流れるスワールが半径方向に加振される。このため
に、側壁４の近傍に局部的な渦流（小渦流）が生成され
ることになり、燃焼室２の側壁４及び凹部８等に付着し
ていた燃料薄膜に剥離作用が加わる。従って、側壁４か
らの燃料の蒸発が促進されて短期間のうちに燃焼が完了
するため、高出力が得られる。Since the side wall 4 of the combustion chamber 2 has a smooth uneven shape due to the provision of the recess 8, the swirl flowing in the circumferential direction along the side wall 4 is excited in the radial direction. For this reason, a local vortex (small vortex) is generated in the vicinity of the side wall 4, and a peeling action is applied to the thin fuel film adhering to the side wall 4, recess 8, etc. of the combustion chamber 2. Therefore, evaporation of the fuel from the side wall 4 is promoted and combustion is completed within a short period of time, resulting in high output.
更に、四部８を設けたことで張出部５の長さを部分的に
大きくしているので、張出部５の長さを全体的に大きく
しなくとも充分に強いスキッシュを得ることができるに
も拘らず、張出部５によって一旦燃焼室２に閉じ込めら
れていた火炎が張出長さの短かい部分等から適等な時期
にスキッシュエリアにも噴出する。このために、前記し
た第１期燃焼の減少によるＮＯｘ生成の抑制に加えて、
空気利用率が向上して排煙濃度及５−
び燃料消費率が改善される。Furthermore, by providing the four parts 8, the length of the overhanging part 5 is partially increased, so a sufficiently strong squish can be obtained without increasing the length of the overhanging part 5 as a whole. In spite of this, the flame that was once confined in the combustion chamber 2 by the overhang portion 5 ejects into the squish area at an appropriate time from a portion with a short overhang length. For this purpose, in addition to suppressing NOx production by reducing the first stage combustion as described above,
The air utilization rate improves, and the exhaust gas concentration and fuel consumption rate improve.
尚、従来では、燃料噴霧がピストンの頂面に吹き上げら
れることによる不完全燃焼を抑制するために、ＮＯｘの
生成を多少犠牲にしてまでも燃料噴霧の衝突深さく衝突
面の深さ）を燃焼室の深さの２分の１〜３分の１程度に
設定していたが、本発明でけ張出部５の下面をピストン
１の頂面１ａに対して略４５°に傾斜させることで中心
部及び上方へのはね返シを抑制しているので、燃料噴霧
の衝突深さを燃焼室２の深さの４分の１程度にまで浅く
することができた。In the past, in order to suppress incomplete combustion caused by the fuel spray being blown up to the top surface of the piston, the collision depth of the fuel spray (the depth of the collision surface) was reduced even at the cost of some NOx production. The depth of the chamber was set to about 1/2 to 1/3, but in the present invention, the lower surface of the protruding portion 5 is inclined at approximately 45 degrees with respect to the top surface 1a of the piston 1. Since splashing back to the center and upwards is suppressed, the collision depth of the fuel spray can be made shallow to about one quarter of the depth of the combustion chamber 2.
又、従来の混合燃焼方式の燃焼室では、燃焼室中央部に
反射される燃料噴霧が多いので、例えば、第４図に破線
で示すように第１期燃焼が多くなっていたが、本発明で
は燃焼室中央部に反射される燃料噴霧が少ないので、同
図に実線で示すように第１期燃焼が少なくなり、強化さ
れたスワールと、このスワールによってひき起される小
渦流とで側壁からの燃料の蒸発がすみやかに行なわれる
結果、拡散燃焼が活発になつ６−
て燃焼期間が短縮されるのである。In addition, in conventional mixed combustion type combustion chambers, a lot of fuel spray is reflected at the center of the combustion chamber, so there is a lot of first-stage combustion, as shown by the broken line in FIG. 4, but the present invention Since there is less fuel spray reflected to the center of the combustion chamber, the first stage combustion is reduced as shown by the solid line in the figure, and the strengthened swirl and the small vortex flow caused by this swirl cause the fuel spray to flow from the side wall. As a result of rapid evaporation of the fuel, diffusion combustion becomes active and the combustion period is shortened.
上記実施例では、燃焼室側壁の上端全周に張出部を設け
ているが、燃料噴霧との衝突部分にのみ張出部を設けて
も所期の目的を達成できる。In the above embodiment, the overhang is provided all around the upper end of the side wall of the combustion chamber, but the desired purpose can also be achieved by providing the overhang only at the portion where it collides with the fuel spray.
父、実施例では、隣接する凹部の間に側壁を面として残
すことにより、凹部間にヒートスポット等が形成される
ことを予防しているが、熱負荷によっては必ずしも隣接
する凹部間に積極的な面を残す必要はない。又、実施例
では、燃焼室（ｉ１１壁の周方内凹箇所に凹部を等配形
成しているが、この凹部の数は実施例に限定されない。In the example, the formation of heat spots etc. between the adjacent recesses is prevented by leaving the side walls as surfaces between the adjacent recesses, but depending on the heat load, it is not always possible to prevent the formation of heat spots between the adjacent recesses. There's no need to leave any side behind. Further, in the embodiment, the recesses are formed at equal intervals in the recessed portions in the circumferential direction of the wall of the combustion chamber (i11), but the number of the recesses is not limited to the embodiment.
以上説明したように本発明によれば、強いスキッシュを
得るために設けた張出部の下面をピストンの頂面に対し
て略４５°に傾斜させて燃料Ｉ！Ｊｔ霧の衝突面を形成
しているので、従来の混合燃焼方式の燃焼室に対比して
燃料噴霧のはねかえりによる浮遊噴霧量が減少する。こ
のために、第１期燃焼の少ない蒸発燃焼が行なわれて排
気特性及び騒音が改善される。又、張出部の存在によっ
て強化さｈたスワールが燃焼室側壁の凹部によって旋回
方向と略直交する方向に加振されて側壁近傍に小渦流を
誘起させるので、壁面に付着している燃料薄膜が剥離作
用を受けて蒸発が促進される。このために、燃料の拡散
燃焼が活発になって燃焼期間が短縮されるので高出力が
得られて燃料消費率が改善され、しかも、従来の蒸発燃
焼方式の燃焼室に見られた始動性不良、軽（無）負荷運
転時の不完全燃焼等も改善できる。As explained above, according to the present invention, the lower surface of the projecting portion provided to obtain a strong squish is inclined at approximately 45 degrees with respect to the top surface of the piston, and the fuel I! Since it forms a collision surface for Jt mist, the amount of floating spray due to the splashing of fuel spray is reduced compared to a conventional mixed combustion type combustion chamber. For this reason, evaporative combustion with less first-stage combustion is performed, improving exhaust characteristics and noise. In addition, the swirl, which is strengthened by the presence of the overhang, is excited by the recess in the side wall of the combustion chamber in a direction substantially perpendicular to the swirling direction, inducing a small vortex near the side wall, which reduces the thin fuel film adhering to the wall surface. is subjected to a peeling action and evaporation is accelerated. As a result, diffusion combustion of the fuel becomes active and the combustion period is shortened, resulting in high output and improved fuel consumption.In addition, it eliminates the poor startability seen in conventional evaporative combustion combustion chambers. , incomplete combustion during light (no) load operation can also be improved.
第１図は本発明の一実施例を備えたピストンの斜視図、
第２図は同上燃焼室の縦断面図、第３図は第２図のｌ−
１１１断面図、第４図は従来の混合燃焼方式の燃焼室と
本発明による燃焼室との熱発生率の対比図である。FIG. 1 is a perspective view of a piston equipped with an embodiment of the present invention;
Figure 2 is a vertical sectional view of the combustion chamber as above, and Figure 3 is the l-
111 sectional view and FIG. 4 are comparison diagrams of heat generation rates between a conventional mixed combustion type combustion chamber and a combustion chamber according to the present invention.
Claims (1)
着した燃料噴射ノズルから前記燃焼室の側壁に向って燃
料を噴射するようにしたディーゼルエンジンにおいて、
中心に向って延出する張出部を燃焼室の側壁上端部に形
成し、該張出部の下面をピストンの頂面に対して略４５
゜に傾斜させて燃料噴霧の衝突面を形成すると共に、燃
焼室側壁の周方向複数位置に該側壁と連続する凹部を設
けて前記衝突面よし下方における燃焼室の水平断面形状
を花弁状にしたことを特徴とするディーゼルエンジンの
燃焼室。A diesel engine in which a combustion chamber is recessed in the top surface of a piston, and fuel is injected from a fuel injection nozzle attached to a cylinder head toward a side wall of the combustion chamber,
A projecting portion extending toward the center is formed at the upper end of the side wall of the combustion chamber, and the lower surface of the projecting portion is approximately 45 mm from the top surface of the piston.
The fuel spray impingement surface is inclined at an angle of .degree., and concave portions continuous with the side wall are provided at multiple positions in the circumferential direction of the side wall of the combustion chamber, so that the horizontal cross-sectional shape of the combustion chamber below the collision surface is shaped like a petal. The combustion chamber of a diesel engine is characterized by:
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP57172552A JPS5960027A (en) | 1982-09-30 | 1982-09-30 | Combustion chamber of diesel engine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP57172552A JPS5960027A (en) | 1982-09-30 | 1982-09-30 | Combustion chamber of diesel engine |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPS5960027A true JPS5960027A (en) | 1984-04-05 |
Family
ID=15943976
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP57172552A Pending JPS5960027A (en) | 1982-09-30 | 1982-09-30 | Combustion chamber of diesel engine |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS5960027A (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH02118133U (en) * | 1989-03-10 | 1990-09-21 | ||
| CN114320573A (en) * | 2021-12-29 | 2022-04-12 | 天津大学 | Piston combustion chamber for air valve type two-four stroke convertible high power diesel engine |
Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5554623A (en) * | 1978-10-19 | 1980-04-22 | Nissan Diesel Motor Co Ltd | Combustion chamber of direct-injection type internal combustion engine |
-
1982
- 1982-09-30 JP JP57172552A patent/JPS5960027A/en active Pending
Patent Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5554623A (en) * | 1978-10-19 | 1980-04-22 | Nissan Diesel Motor Co Ltd | Combustion chamber of direct-injection type internal combustion engine |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH02118133U (en) * | 1989-03-10 | 1990-09-21 | ||
| CN114320573A (en) * | 2021-12-29 | 2022-04-12 | 天津大学 | Piston combustion chamber for air valve type two-four stroke convertible high power diesel engine |
| CN114320573B (en) * | 2021-12-29 | 2024-04-19 | 天津大学 | Piston combustion chamber for air valve type two-four stroke changeable high power diesel engine |
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