JPS599734B2 - Direct injection diesel engine piston - Google Patents
Direct injection diesel engine pistonInfo
- Publication number
- JPS599734B2 JPS599734B2 JP53150316A JP15031678A JPS599734B2 JP S599734 B2 JPS599734 B2 JP S599734B2 JP 53150316 A JP53150316 A JP 53150316A JP 15031678 A JP15031678 A JP 15031678A JP S599734 B2 JPS599734 B2 JP S599734B2
- Authority
- JP
- Japan
- Prior art keywords
- recess
- diesel engine
- fuel
- combustion
- direct injection
- 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.)
- Expired
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
- F02B23/0678—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
- F02B23/0693—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 the combustion space consisting of step-wise widened multiple zones of different depth
-
- 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
- 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
- F02B23/0624—Swirl 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
- 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)
- Dispersion Chemistry (AREA)
- Combustion Methods Of Internal-Combustion Engines (AREA)
Description
【発明の詳細な説明】
本発明は燃焼を段階的に行わせることにより排気中のＮ
Ｏｘ成分を低減させた直接噴射式ディーゼルエンジンの
ピストンに関する。DETAILED DESCRIPTION OF THE INVENTION The present invention reduces nitrogen in exhaust gas by performing combustion in stages.
This invention relates to a piston for a direct injection diesel engine with reduced Ox components.
直接噴射式ディーゼルエンジンではＮＯｘ低減対策とし
て燃料噴射時期の遅延を行わせている。In direct injection diesel engines, fuel injection timing is delayed as a measure to reduce NOx.
しかしながら、燃料噴射時期の遅延は、ディーゼル黒煙
の増加、出力、燃費の悪化をもたらすものとなる。ＮＯ
ｘは、高温高圧下の燃焼時に吸気中の窒素（Ｎ２）と酸
素（Ｏ２）とが化学反応して生成されるものと云われて
いる。However, a delay in fuel injection timing results in an increase in diesel black smoke and a deterioration in output and fuel efficiency. NO
It is said that x is produced by a chemical reaction between nitrogen (N2) and oxygen (O2) in intake air during combustion under high temperature and high pressure.
直接噴射式ディーゼルエンジンの燃焼は、急激に立上つ
て生ずるものであるため、燃焼温度及び燃焼圧力の上昇
が急激なものとなつている。Since combustion in a direct injection diesel engine occurs rapidly, the combustion temperature and combustion pressure rise rapidly.
このため、必然的にＮＯｘの生成量も多量となつてしま
う。そこで本発明の目的は、燃焼を段階的に行わせ、燃
焼温度及び燃焼圧力の急激な上昇を抑えＮＯｘ生成量を
低減させた直接噴射式ディーゼルエンジンのピストンを
提供するにある。Therefore, the amount of NOx produced will inevitably increase. SUMMARY OF THE INVENTION An object of the present invention is to provide a piston for a direct injection diesel engine that allows combustion to occur in stages, suppresses rapid increases in combustion temperature and pressure, and reduces the amount of NOx produced.
以下図によつて詳しく説明する。This will be explained in detail below with reference to the figures.
第１図は、本発明の一実施例を示す断面図である。FIG. 1 is a sectional view showing one embodiment of the present invention.
ピストン１の頂部には、キャビティー２が形成されてい
る該キャビティー２は、底部へ向かうにしたがつて内径
が縮少する３個の凹所２１、２２、２３、からなつてい
る。A cavity 2 is formed at the top of the piston 1. The cavity 2 consists of three recesses 21, 22, and 23 whose inner diameter decreases toward the bottom.
燃料噴射ノズル３は、噴霧の中心が凹所２３の肩部４へ
向けられて取り付けられている。肩部４は、内方へリッ
プ状に突出して形成されており、凹所２３の底面には中
央突起５が形成されている。以上の如く構成された本発
明の作用を第２図を参照して以下述べる。The fuel injection nozzle 3 is attached so that the center of the spray is directed toward the shoulder 4 of the recess 23. The shoulder portion 4 is formed to protrude inward in a lip shape, and a central protrusion 5 is formed on the bottom surface of the recess 23. The operation of the present invention constructed as described above will be described below with reference to FIG.
イに示す如く、圧縮行程の終了付近の所定時期に燃料噴
射ノズル３から燃料が噴射される。As shown in A, fuel is injected from the fuel injection nozzle 3 at a predetermined time near the end of the compression stroke.
噴霧Ｐの中心は肩部４へ向けられているが、噴霧Ｐは所
定の拡がりを有しているので、噴霧燃料は第２の凹所２
２と第３の凹所２３の両方へ分散され、夫々の凹所２２
、２３内のスワールＳ２、５３に乗つて空気と混合する
。凹所２２と凹所２３とに分散される燃料比は、凹所２
３の空燃比が濃く、凹所２２の空燃比が薄くなるように
分散される。The center of the spray P is directed toward the shoulder 4, but since the spray P has a predetermined spread, the spray fuel is directed to the second recess 2.
distributed to both the second and third recesses 23, and the respective recesses 22
, 23 and mixes with air. The fuel ratio distributed between the recess 22 and the recess 23 is the same as that of the recess 2.
It is distributed so that the air-fuel ratio in the recess 3 is rich and the air-fuel ratio in the recess 22 is thin.
ピストン１がさらに上昇すると、口に示す如く、第１の
凹所２１には第１のスキツシユ流５１が導入され、第３
の凹所２３には第２のスキツシユ流Ｓ２が導入され、夫
々凹所２１，２３内を撹乱する。When the piston 1 further rises, the first squishing flow 51 is introduced into the first recess 21, as shown at the mouth, and the third
A second squishing flow S2 is introduced into the recess 23 and disturbs the inside of the recesses 21 and 23, respectively.
凹所２３内の空燃比は濃いため、先ず凹所２３内で着火
が生ずる。ハに示す如く、凹所２３内で生じた火炎は、
逆スキツシユＱ，を生じて凹所２２へ拡散する。凹所２
２内の空燃比は、それ自体希薄であるが、強力な逆スキ
ツシユ火炎Ｑ，によつて燃焼される。次いで二に示す如
く、凹所２２内の燃焼は凹所２，へＱ２の如く拡散する
。Since the air-fuel ratio within the recess 23 is rich, ignition occurs within the recess 23 first. As shown in C, the flame generated within the recess 23 is
A reverse squish Q occurs and diffuses into the recess 22. recess 2
The air-fuel ratio within 2 is itself lean, but is burned by the powerful reverse skiff flame Q,. Then, as shown in Figure 2, the combustion within the recess 22 diffuses into the recess 2, as shown in Q2.
上記燃焼過程において、凹所２３内の燃焼比が濃いので
燃焼ガス温度も低く、ＮＯｘの生成量も少なくなつてい
る。In the above combustion process, since the combustion ratio in the recess 23 is high, the temperature of the combustion gas is low, and the amount of NOx produced is also small.
又、キャビティー２内の燃焼の拡散も段階的となつてい
るため、急激な燃焼とはならず、燃焼圧力も低くなつて
ＮＯｘ生成量をさらに低減させる。第３図は、噴射時期
遅延タイプと、本発明タイプを燃焼圧で比較した特性線
図である。Further, since the combustion within the cavity 2 is diffused in stages, combustion does not occur suddenly, and the combustion pressure is lowered, further reducing the amount of NOx produced. FIG. 3 is a characteristic diagram comparing the injection timing delay type and the present invention type in terms of combustion pressure.
噴射時期遅延タイプの曲線Ｕは、ｋ′点で着火燃焼し、
ｌ′点で最高圧となるが、これに対し、本発明タイプの
曲線ｖは、ｋ′点より前のｋ点で着火し、２点で最高圧
となる。The injection timing delay type curve U ignites and burns at point k',
The maximum pressure is reached at point l', whereas in the curve v of the present invention, ignition occurs at point k before point k', and the maximum pressure is reached at two points.
このｌ点の圧力は、段階的燃焼であるため、ｌ′点の圧
力よりも低いものとなつている。上記燃焼特性を、Ｐ−
Ｖ線図で表わしたものが第４図であり、本発明タイプの
曲線ｗは、噴射時期遅延タイプの曲線Ｘと比べて、図の
Ｙで示す部分だけ出力、燃費が向上する゛ものとなる。The pressure at point l is lower than the pressure at point l' because of staged combustion. The above combustion characteristics are expressed as P-
Figure 4 shows the V diagram, and the curve w of the present invention type improves the output and fuel efficiency by the portion indicated by Y in the figure, compared to the curve X of the injection timing delay type. .
上述は、本発明の一実施例であり、本発明は、さらに、
第５図に示すような構成とすることができる。第５図は
第３の凹所１３を四辺形状とするものであり、第３の凹
所１３内のスワールＳ′３を乱流とするに役立ち、第３
の凹所１３内の燃焼を改善するものである。The above is one embodiment of the present invention, and the present invention further includes:
A configuration as shown in FIG. 5 can be adopted. In FIG. 5, the third recess 13 is made into a quadrilateral shape, which helps to make the swirl S'3 in the third recess 13 turbulent.
This improves combustion within the recess 13 of the fuel cell.
なお、第１図における第３の凹所２３を公知のトロイダ
ル型式とすることもできる。Note that the third recess 23 in FIG. 1 may be of a known toroidal type.
以上のとおり、本発明によると、燃料噴射時期の遅延を
行うことなくＮＯｘ低減が可能となり、黒煙、出力、燃
費を向上させることができる。As described above, according to the present invention, it is possible to reduce NOx without delaying the fuel injection timing, and it is possible to improve black smoke, output, and fuel efficiency.
第１図は、本発明の一実施例を示す断面図、第２図のイ
、口、ハ及び二は、本発明の作用説明図、第３図は、本
発明と噴射時期遅延タイプとを比較した燃焼圧特性線図
、第４図は、本発明と噴射時期遅延タイプとを比較した
Ｐ−■線図、第５図は本発明の他の実施例を示す図であ
る。
１：ピストン、２：キヤビテイー。Fig. 1 is a sectional view showing one embodiment of the present invention, A, C, C and 2 of Fig. 2 are explanatory diagrams of the operation of the present invention, and Fig. 3 shows the present invention and the injection timing delay type. Comparative combustion pressure characteristic diagrams, FIG. 4 are P-■ diagrams comparing the present invention and the injection timing delay type, and FIG. 5 is a diagram showing another embodiment of the present invention. 1: Piston, 2: Cavity.
Claims (1)
ィー内へ燃料を直接噴射するディーゼルエンジンにおい
て、ピストン頂部に形成されたキャビティーが徐々に内
径が縮少する３段の凹所からなり、燃料噴霧が３段目の
凹所の肩部へ向けられ、燃料噴霧の分散比が３段目の凹
所に濃く、２段目の凹所に薄く分散されるように燃料噴
射ノズルを設けてなることを特徴とする直接噴射式ディ
ーゼルエンジンのピストン。1 In a diesel engine that forms a cavity at the top of the piston and injects fuel directly into the face cavity, the cavity formed at the top of the piston consists of three recesses whose inner diameter gradually decreases, and the fuel is sprayed. is directed toward the shoulder of the third-stage recess, and the fuel injection nozzle is provided so that the dispersion ratio of the fuel spray is concentrated in the third-stage recess and thinly dispersed in the second-stage recess. A direct injection diesel engine piston featuring
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP53150316A JPS599734B2 (en) | 1978-12-05 | 1978-12-05 | Direct injection diesel engine piston |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP53150316A JPS599734B2 (en) | 1978-12-05 | 1978-12-05 | Direct injection diesel engine piston |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS5575530A JPS5575530A (en) | 1980-06-06 |
| JPS599734B2 true JPS599734B2 (en) | 1984-03-05 |
Family
ID=15494350
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP53150316A Expired JPS599734B2 (en) | 1978-12-05 | 1978-12-05 | Direct injection diesel engine piston |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS599734B2 (en) |
Families Citing this family (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR2534970A1 (en) * | 1982-10-22 | 1984-04-27 | Chenesseau | INTERNAL COMBUSTION ENGINE FOR USE WITH HIGH VAPORIZATION HEAT FUEL |
| US5109816A (en) * | 1990-04-27 | 1992-05-05 | Toyota Jidosha Kabushiki Kaisha | Direct fuel injection type spark ignition internal combustion engine |
| FR2947009B1 (en) * | 2009-06-23 | 2014-05-09 | Peugeot Citroen Automobiles Sa | PISTON FOR DIESEL ENGINE COMBUSTION CHAMBER. |
| JP2014238011A (en) * | 2013-06-06 | 2014-12-18 | 日野自動車株式会社 | Combustion chamber structure of direct injection type diesel engine |
| JP6238702B2 (en) * | 2013-11-28 | 2017-11-29 | 株式会社豊田中央研究所 | diesel engine |
| CN105134370B (en) * | 2015-07-23 | 2017-12-19 | 北京理工大学 | A kind of Split swirl combustion system |
-
1978
- 1978-12-05 JP JP53150316A patent/JPS599734B2/en not_active Expired
Also Published As
| Publication number | Publication date |
|---|---|
| JPS5575530A (en) | 1980-06-06 |
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