JP2685668B2 - Combustion chamber of direct injection diesel engine - Google Patents

Combustion chamber of direct injection diesel engine

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Publication number
JP2685668B2
JP2685668B2 JP3231764A JP23176491A JP2685668B2 JP 2685668 B2 JP2685668 B2 JP 2685668B2 JP 3231764 A JP3231764 A JP 3231764A JP 23176491 A JP23176491 A JP 23176491A JP 2685668 B2 JP2685668 B2 JP 2685668B2
Authority
JP
Japan
Prior art keywords
combustion chamber
wall surface
nozzle
injection
spray
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 - Lifetime
Application number
JP3231764A
Other languages
Japanese (ja)
Other versions
JPH0571346A (en
Inventor
小森正憲
辻村欽司
Original Assignee
株式会社新燃焼システム研究所
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Publication date
Application filed by 株式会社新燃焼システム研究所 filed Critical 株式会社新燃焼システム研究所
Priority to JP3231764A priority Critical patent/JP2685668B2/en
Publication of JPH0571346A publication Critical patent/JPH0571346A/en
Application granted granted Critical
Publication of JP2685668B2 publication Critical patent/JP2685668B2/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • 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
    • 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
    • F02B23/0669—Details related to the fuel injector or the fuel spray having multiple fuel spray jets per injector nozzle
    • 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
    • F02B23/0678—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
    • 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】DETAILED DESCRIPTION OF THE INVENTION

【０００１】[0001]

【産業上の利用分野】本発明は、スモークおよびＮＯX
の大幅な低減を図るための直接噴射式ディーゼル機関の
燃焼室に関する。BACKGROUND OF THE INVENTION This invention is, smoke and NO X
The present invention relates to a combustion chamber of a direct injection diesel engine for achieving a significant reduction of

【０００２】[0002]

【従来の技術】直接噴射式ディーゼル機関において、現
在広く用いられている低圧噴射の場合、噴霧はノズル近
傍で着火した後、全体が火炎に包まれながら進行し、こ
の時、噴霧は、空気と同時に自己の生成した既燃ガスを
巻き込みながら燃焼するので、噴霧中心部において高温
部、酸素不足部が形成されスモークの生成要因となり、
既燃ガスの巻き込みはマイナス要因として働くと言われ
ている。このためスモークを低減するには、燃料と空気
を迅速に混合する必要があり、スワール、スキッシュ等
により空気利用率を向上する方法が採られているが、こ
れでは着火遅れの間の燃料、空気混合速度も増大するた
め、予混合燃焼の増加により燃焼初期の熱発生率が増大
し、ＮＯX の増大を招くという相反する問題を有してお
り、これがスモークとＮＯX の同時低減を困難にしてい
る。2. Description of the Related Art In the case of low-pressure injection, which is widely used in direct injection type diesel engines, the spray is ignited in the vicinity of the nozzle and then progresses while being surrounded by flames. At the same time, it burns while burning the burned gas generated by itself, so a high temperature part and an oxygen deficient part are formed in the center of the spray, which becomes a cause of smoke generation,
It is said that the burning of burned gas acts as a negative factor. Therefore, in order to reduce smoke, it is necessary to mix fuel and air quickly, and a method of improving the air utilization rate by swirling, squishing, etc. has been adopted. since mixing speed also increases, the increase of premixed combustion increases the initial combustion of the heat generation rate has a contradictory problem that causes an increase in NO X, which is difficult to simultaneously reduce the smoke and NO X ing.

【０００３】上記問題を解決するために、高圧噴射、小
噴孔径ノズル、浅皿燃焼室および低スワールを組合せる
方式が知られている。これを図３により説明すると、１
はピストン、２はピストンリング、３はシリンダライナ
ー、４はガスケット、５はシリンダヘッド、６はノズル
７を有する燃料噴射弁を示し、ピストン１の頂部には燃
焼室９が形成されている。ピストン１が上昇し上死点付
近に達したとき、ノズル７から噴射された燃料の噴霧
は、壁面１０で一気に着火した後、火炎は、燃焼室９中
心に向かって膨張するが、噴射の終了まで中心部は不燃
域として残る。すなわち、噴霧は壁面１０に到達するま
で燃焼室９中心に近い不燃域側で十分に空気を巻き込み
ながら進行し、壁面１０側では既燃ガスを導入しながら
壁面１０に衝突する二段の燃焼経路をたどる。高圧噴射
の場合、噴射時期を大幅に遅らせても火がつくため噴射
時期遅延との組み合わせで、低圧噴射と比較してスモー
クおよびＮＯX の同時低減を図ることができる。In order to solve the above problems, a system is known in which high pressure injection, a small nozzle hole diameter nozzle, a shallow dish combustion chamber and a low swirl are combined. To explain this by 3, 1
Is a piston, 2 is a piston ring, 3 is a cylinder liner, 4 is a gasket, 5 is a cylinder head, 6 is a fuel injection valve having a nozzle 7, and a combustion chamber 9 is formed at the top of the piston 1. When the piston 1 rises and reaches the vicinity of the top dead center, the fuel spray injected from the nozzle 7 ignites at once on the wall surface 10, and then the flame expands toward the center of the combustion chamber 9, but the injection ends. The central part remains as a non-combustible area. That is, the spray progresses while sufficiently entraining air on the non-combustible region side near the center of the combustion chamber 9 until reaching the wall surface 10, and on the wall surface 10 side, a two-stage combustion path in which burned gas is introduced and collides with the wall surface 10. Follow For high-pressure injection, in combination with the injection timing delays catch fire since greatly delayed injection timing, it is possible to simultaneously reduce the smoke and NO X compared to the low-pressure injection.

【０００４】[0004]

【発明が解決しようとする課題】しかしながら、高圧噴
射は、低圧噴射と比較して同一噴射時期ではＮＯx の発
生が多いという問題を有している。その理由としては、 燃焼室が円筒形状であるため、着火後の噴霧への既
燃ガスの導入が少ない。すなわち、図３（Ａ）に示すよ
うに、ＡとＢの火炎は壁面１０で衝突するが、速度ベク
トルが同じであるため、力のバランスが保たれ、衝突に
よりお互いの火炎を乱すことなく、内側に曲げられ、燃
焼室９中心に向かって膨張する。しかし、噴霧の持つエ
ネルギーが火炎の膨張エネルギーより大きいため、図の
ように火炎と噴霧の間には空気層１１が出来、噴射期間
中これが保たれ、既燃ガスの導入が起こらない。 急速な圧力上昇による断熱圧縮により火炎温度が高
い。 ＮＯx 発生原因となる最高温度領域が広い。等のこ
とがあげられる。[SUMMARY OF THE INVENTION However, high-pressure injection has the problem that generation of the NO x in the same injection timing as compared to the low-pressure injection is large. The reason for this is that the combustion chamber has a cylindrical shape, so there is little introduction of burnt gas into the spray after ignition. That is, as shown in FIG. 3 (A), the flames A and B collide with each other on the wall surface 10, but since the velocity vectors are the same, the balance of forces is maintained, and the flames do not disturb each other due to the collision. It is bent inward and expands toward the center of the combustion chamber 9. However, since the energy of the spray is larger than the expansion energy of the flame, an air layer 11 is formed between the flame and the spray as shown in the figure, and this is maintained during the injection period, and the introduction of burned gas does not occur. High flame temperature due to adiabatic compression due to rapid pressure rise. The maximum temperature range that causes NO x is wide. And so on.

【０００５】画像解析を用いた二色法による火炎温度分
布測定結果によると、高圧噴射の場合、図３（Ａ）に示
すように、高温の火炎は、噴霧が壁面１０に衝突し次々
に燃焼するに従って、燃焼室９の中心に向かって押し出
されていく火炎の先端近傍に分布し、壁面１０に近づく
ほど温度が低いという不均一な温度分布となっている
（図中、ＴH、ＴM、ＴL は火炎温度を示し、ＴH＞ＴM＞
ＴL ）。したがって、高温部と低温部をうまく混ぜあわ
せ、高温部分を少なくすることができれば、ＮＯx の発
生を抑制することができる。According to the flame temperature distribution measurement result by the two-color method using image analysis , in the case of high-pressure injection, as shown in FIG. 3 (A), the high-temperature flame causes the spray to collide with the wall surface 10 and burn one after another. according to, in distributed in the vicinity of the tip of the flame going pushed toward the center of the combustion chamber 9, the temperature closer to the wall 10 has a non-uniform temperature distribution of low (Fig, T H, T M , T L indicates the flame temperature, and T H > T M ＞
TL ). Therefore, if the high temperature portion and the low temperature portion can be mixed well and the high temperature portion can be reduced, the generation of NO x can be suppressed.

【０００６】本発明は、上記問題および課題を解決する
ものであって、燃焼室の構造を従来の単純な浅皿燃焼室
より改善するだけで、スモーク及びＮＯX を同時にかつ
大幅に低減させることができる直接噴射式ディーゼル機
関の燃焼室を提供することを目的とする。[0006] The present invention has been made to solve the above problems and challenges, only the structure of the combustion chamber is improved over conventional simple shallow dish combustion chamber, thereby simultaneously and significantly reduce the smoke and NO X The object is to provide a combustion chamber of a direct injection type diesel engine capable of

【０００７】[0007]

【課題を解決するための手段】そのために本発明の直接
噴射式ディーゼル機関の燃焼室は、ピストン１の頂部に
形成された燃焼室９と、シリンダヘッド５に配設された
燃料噴射弁６と、該燃料噴射弁６のノズル７に設けられ
た複数の噴孔と、これら複数の噴孔に対向して交互に、
前記燃焼室９の壁面１０に形成された突出壁面１０ａと
を備え、該突出壁面１０ａをノズル７からの燃料噴霧方
向に対して円周方向に傾斜させたことを特徴とするもの
である。なお、上記構成に付加した番号は、本発明の理
解を容易にするために図面と対比させるためのもので、
これにより本発明の構成が何ら限定されるものではな
い。Therefore, the combustion chamber of the direct injection type diesel engine of the present invention comprises a combustion chamber 9 formed at the top of the piston 1 and a fuel injection valve 6 arranged in the cylinder head 5. , A plurality of injection holes provided in the nozzle 7 of the fuel injection valve 6 and alternately facing the plurality of injection holes,
A projecting wall surface 10a formed on the wall surface 10 of the combustion chamber 9 is provided, and the projecting wall surface 10a is inclined in the circumferential direction with respect to the fuel spray direction from the nozzle 7. The numbers added to the above configuration are for comparison with the drawings in order to facilitate understanding of the present invention.
This does not limit the structure of the present invention.

【０００８】[0008]

【作用および発明の効果】本発明によれば、ピストンの
頂部に形成された燃焼室と、シリンダヘッドに配設され
た燃料噴射弁と、該燃料噴射弁のノズルに設けられた複
数の噴孔と、これら複数の噴孔に対向して交互に、前記
燃焼室の壁面に形成された突出壁面とを備え、該突出壁
面をノズルからの燃料噴霧方向に対して円周方向に傾斜
させたため、図２の噴霧Ｆの左側では、壁面１０および
突出壁面１０ａにおける衝突面の速度ベクトルが大きく
異なるためバランスがくずれ、お互いに混合が促進され
高温部と低温部が混ざり、温度が低下するため、ＮＯx
の発生が抑制され、一方、図２の噴霧Ｆの右側では、壁
面１０で着火した火炎の既燃ガス導入が促進されるとい
う効果を生じる。従って、燃焼室の構造を従来の単純な
浅皿燃焼室より改善するだけで、スモーク及びＮＯX を
同時にかつ大幅に低減させることができる。According to the present invention, the combustion chamber formed at the top of the piston, the fuel injection valve provided in the cylinder head, and the plurality of injection holes provided in the nozzle of the fuel injection valve And alternately facing the plurality of injection holes, a projecting wall surface formed on the wall surface of the combustion chamber is provided, and the projecting wall surface is inclined in the circumferential direction with respect to the fuel spray direction from the nozzle, On the left side of the spray F in FIG. 2, the velocity vectors of the collision surfaces on the wall surface 10 and the projecting wall surface 10a are greatly different from each other, resulting in imbalance, and mixing is promoted to mix a high temperature portion and a low temperature portion, resulting in a decrease in temperature. x
2 is suppressed, and on the other hand, on the right side of the spray F in FIG. 2, the effect of promoting burned gas introduction of the flame ignited on the wall surface 10 is produced. Therefore, the structure of the combustion chamber only improve than conventional simple shallow dish combustion chamber, it is possible to simultaneously and significantly reduce the smoke and NO X.

【０００９】[0009]

【実施例】以下、本発明の実施例を図面を参照しつつ説
明する。図１は本発明の原理を説明するための図であ
り、図Ａは平面図、図Ｂは図ＡのＸ−Ｘ線に沿って矢印
方向から見た断面図である。１はピストン、２はピスト
ンリング、３はシリンダライナー、４はガスケット、５
はシリンダヘッド、６はノズル７を有する燃料噴射弁、
９は燃焼室を示し、ノズル７には、燃料を噴射する６つ
の噴孔が設けられているが、噴孔の数は限定されるもの
ではない。燃焼室９の形状は、ノズル７の噴孔に対向し
て交互に、燃焼室９の壁面１０に突出壁面１０ａを形成
している。なお、ノズル７と突出壁面１０ａとの距離Ｌ
1 および衝突壁面１０ａの幅Ｌ2 は、スモークおよびＮ
Ｏx の排出状況に応じて適宜変更する。Embodiments of the present invention will be described below with reference to the drawings. FIG. 1 is a diagram for explaining the principle of the present invention .
Ri, Figure A is a plan view, FIG. B is a sectional view seen from the arrow direction along the line X-X in Figure A. 1 is a piston, 2 is a piston ring, 3 is a cylinder liner, 4 is a gasket, 5
Is a cylinder head, 6 is a fuel injection valve having a nozzle 7,
Reference numeral 9 denotes a combustion chamber, and the nozzle 7 is provided with six injection holes for injecting fuel, but the number of injection holes is not limited. The combustion chamber 9 has a shape in which projecting wall surfaces 10 a are alternately formed on the wall surface 10 of the combustion chamber 9 so as to face the injection holes of the nozzle 7. The distance L between the nozzle 7 and the protruding wall surface 10a
1 and the width L 2 of the collision wall surface 10a are smoke and N
It is changed as appropriate according to the emission status of O x .

【００１０】上記構成からなる直接噴射式ディーゼル機
関の作用について説明する。ピストン１が上昇し上死点
付近に達したとき、ノズル７から噴射された燃料の噴霧
は、壁面１０および突出壁面１０ａで一気に着火した
後、突出壁面１０ａで着火した火炎Ａは、ノズル７中心
方向ａ、およびこれと直角な方向ｂに広がり、ａ方向へ
の火炎の広がりは、壁面１０で着火した火炎Ｂの既燃ガ
スの導入を促進する。さらに、火炎Ａのｂ方向への膨
張、および火炎Ｂのｃ方向への膨張は、壁面１０および
突出壁面１０ａにおける衝突面の速度ベクトルが異なる
ためバランスがくずれ、お互いに混合が促進され高温部
と低温部が混ざり、温度が低下するため、ＮＯx の発生
が抑制される。その結果、高圧噴射によるスモーク低減
効果を損なうこと無く、ＮＯx の大幅な低減が可能であ
る。A direct injection diesel engine having the above structure
The function of Seki will be described. When the piston 1 rises and reaches the vicinity of the top dead center, the spray of fuel injected from the nozzle 7 is ignited at once by the wall surface 10 and the protruding wall surface 10a, and then the flame A ignited by the protruding wall surface 10a is at the center of the nozzle 7. The spread of the flame in the direction a and the direction b perpendicular thereto, and the spread of the flame in the direction a promotes the introduction of the burned gas of the flame B ignited on the wall surface 10. Further, the expansion of the flame A in the b direction and the expansion of the flame B in the c direction are out of balance because the velocity vectors of the collision surfaces on the wall surface 10 and the projecting wall surface 10a are different, so that they are mixed with each other to promote high temperature portions. Since the low temperature part is mixed and the temperature is lowered, the generation of NO x is suppressed. As a result, it is possible to significantly reduce NO x without impairing the smoke reduction effect of the high pressure injection.

【００１１】図２は、本発明の１実施例を示す平面図で
あり、図１と同一の構成および作用については同一番号
を付けて説明を省略する。図１の構造では、突出壁面１
０ａをノズル７からの燃料噴霧方向に対して直角として
いるが、本発明においては、突出壁面１０ａをノズル７
からの燃料噴霧方向に対して円周方向に傾斜させるよう
にしている。これにより、図１で説明した火炎Ａのｂ方
向への膨張がさらに強調される。即ち、図２の噴霧Ｆの
左側では、壁面１０および突出壁面１０ａにおける衝突
面の速度ベクトルが大きく異なるためバランスがくず
れ、お互いに混合が促進され高温部と低温部が混ざり、
温度が低下するため、ＮＯx の発生が抑制される。一
方、図２の噴霧Ｆの右側では、壁面１０で着火した火炎
の既燃ガス導入が促進されるという効果を生じる。FIG. 2 is a plan view showing an embodiment of the present invention, and the same configurations and operations as those in FIG. 1 are designated by the same reference numerals and their description is omitted. In the structure of FIG. 1, the protruding wall surface 1
0a is perpendicular to the direction of fuel spray from the nozzle 7, but in the present invention, the protruding wall surface 10a is the nozzle 7
Is inclined in the circumferential direction with respect to the fuel spray direction. As a result, the expansion of the flame A described in FIG. 1 in the b direction is further emphasized. That is, on the left side of the spray F in FIG. 2, the velocity vectors of the collision surfaces on the wall surface 10 and the projecting wall surface 10a are greatly different from each other, so that the balance is lost, mixing is promoted, and a high temperature portion and a low temperature portion are mixed,
Since the temperature is lowered, the generation of NO x is suppressed. On the other hand, on the right side of the spray F in FIG. 2, there is an effect that the introduction of burned gas of the flame ignited on the wall surface 10 is promoted.

【００１２】ディーゼルエンジンにはスワールが存在し
（図２の例ではスワール方向は反時計方向である）、噴
霧の左右ではスワールの作用によって元来、燃焼状態が
対称とはならない性質をもっているが、本発明のよう
に、該突出壁面をノズルからの燃料噴霧方向に対して円
周方向に傾斜させることにより、噴霧Ｆの左右のバラン
スのくずれを任意に設定することができ、エンジンにマ
ッチングした燃料噴霧の配置を選ぶことができる。The diesel engine has a swirl (in the example of FIG. 2, the swirl direction is counterclockwise), and the left and right sides of the spray have a property that the combustion state is not originally symmetrical due to the action of the swirl. As in the present invention, the protruding wall surface is circular with respect to the direction of fuel spray from the nozzle.
By tilting in the circumferential direction, the left and right balance deviation of the spray F can be arbitrarily set, and the arrangement of the fuel spray that matches the engine can be selected.

【００１３】なお、本発明は上記実施例に限定されるも
のではなく種々の変更が可能である。例えば、上記実施
例においては、ノズル７の同一噴孔径から同時に燃料を
噴射しているが、壁面１０と突出壁面１０ａ用の噴孔径
を別々にしてもよいし、パイロット噴射により噴射時期
を変えて噴射するようにしてもよい。Note that the present invention is not limited to the above embodiment, and various modifications can be made. For example, in the above embodiment, the fuel is injected simultaneously from the same injection hole diameter of the nozzle 7, but the injection hole diameters for the wall surface 10 and the protruding wall surface 10a may be different, or the injection timing may be changed by pilot injection. You may make it eject.

【図面の簡単な説明】[Brief description of the drawings]

【図１】図１は本発明の原理を説明するための図であ
り、図Ａは平面図、図Ｂは図ＡのＸ−Ｘ線に沿って矢印
方向から見た断面図である。 FIG. 1 is a diagram for explaining the principle of the present invention .
Ri, Figure A is a plan view, FIG. B is a sectional view seen from the arrow direction along the line X-X in Figure A.

【図２】本発明の１実施例を示す平面図である。 Is a plan view showing one embodiment of the present invention; FIG.

【図３】従来の直接噴射式ディーゼル機関の燃焼室の例
を示し、図Ａは平面図、図Ｂは断面図である。 FIG. 3 Example of combustion chamber of conventional direct injection diesel engine
FIG. A is a plan view and FIG. B is a sectional view.

【符号の説明】[Explanation of symbols]

１…ピストン、５…シリンダヘッド、６…燃料噴射弁、
７…ノズル９…燃焼室、１０…壁面、１０ａ…突出壁面1 ... piston, 5 ... cylinder head, 6 ... fuel injection valve,
7 ... Nozzle 9 ... Combustion chamber, 10 ... Wall surface, 10a ... Projecting wall surface

Claims (1)

(57)【特許請求の範囲】(57) [Claims] 【請求項１】ピストンの頂部に形成された燃焼室と、シ
リンダヘッドに配設された燃料噴射弁と、該燃料噴射弁
のノズルに設けられた複数の噴孔と、これら複数の噴孔
に対向して交互に、前記燃焼室の壁面に形成された突出
壁面とを備え、該突出壁面をノズルからの燃料噴霧方向
に対して円周方向に傾斜させたことを特徴とする直接噴
射式ディーゼル機関の燃焼室。1. A combustion chamber formed at the top of a piston, a fuel injection valve arranged in a cylinder head, a plurality of injection holes provided in a nozzle of the fuel injection valve, and a plurality of injection holes formed in the plurality of injection holes. Direct injection type diesel characterized in that it is provided with projecting wall surfaces formed alternately on the wall surface of the combustion chamber facing each other, and the projecting wall surfaces are inclined in the circumferential direction with respect to the fuel spray direction from the nozzle. Combustion chamber of the engine.
JP3231764A 1991-09-11 1991-09-11 Combustion chamber of direct injection diesel engine Expired - Lifetime JP2685668B2 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP3231764A JP2685668B2 (en) 1991-09-11 1991-09-11 Combustion chamber of direct injection diesel engine

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP3231764A JP2685668B2 (en) 1991-09-11 1991-09-11 Combustion chamber of direct injection diesel engine

Publications (2)

Publication Number Publication Date
JPH0571346A JPH0571346A (en) 1993-03-23
JP2685668B2 true JP2685668B2 (en) 1997-12-03

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Country Link
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Publication number Priority date Publication date Assignee Title
DE102010027637A1 (en) * 2010-07-19 2012-01-19 Mtu Friedrichshafen Gmbh Piston for internal combustion engines, and internal combustion engine for this purpose
DE102010032442B4 (en) * 2010-07-28 2014-10-30 Audi Ag Self-igniting internal combustion engine with piston recesses with swirl graduation
JP5953067B2 (en) * 2012-02-28 2016-07-13 日野自動車株式会社 Direct injection diesel engine and piston for direct injection diesel engine
US10731544B2 (en) * 2018-09-24 2020-08-04 Caterpillar Inc. Internal combustion engine and method for its operation

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* Cited by examiner, † Cited by third party
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JPH04116632U (en) * 1991-03-27 1992-10-19 日産デイーゼル工業株式会社 Combustion chamber structure of direct injection diesel engine

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