JPS58131308A - Direct injection type internal-combustion engine - Google Patents

Direct injection type internal-combustion engine

Info

Publication number
JPS58131308A
JPS58131308A JP57013791A JP1379182A JPS58131308A JP S58131308 A JPS58131308 A JP S58131308A JP 57013791 A JP57013791 A JP 57013791A JP 1379182 A JP1379182 A JP 1379182A JP S58131308 A JPS58131308 A JP S58131308A
Authority
JP
Japan
Prior art keywords
injection valve
fuel
spray
recess
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.)
Pending
Application number
JP57013791A
Other languages
Japanese (ja)
Inventor
Taro Aoyama
太郎 青山
Junichi Mizuta
準一 水田
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Toyota Central R&D Labs Inc
Original Assignee
Toyota Central R&D Labs Inc
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Toyota Central R&D Labs Inc filed Critical Toyota Central R&D Labs Inc
Priority to JP57013791A priority Critical patent/JPS58131308A/en
Publication of JPS58131308A publication Critical patent/JPS58131308A/en
Pending legal-status Critical Current

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
    • F02B23/0675—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 being substantially spherical, hemispherical, ellipsoid or parabolic
    • 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
    • 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
    • F02B23/066—Details related to the fuel injector or the fuel spray the injector being located substantially off-set from the cylinder centre 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)

Abstract

PURPOSE:To favorably distribute fuel spray and yet prevent fuel spray from adhering to the wall surface of a combustion chamber by a structure wherein a swirl type injection valve, which swirlily and conically sprays fuel, is used as a fuel injection valve and the spray cone angle of the swirl type injection valve is set at a specified value. CONSTITUTION:A nearly spherical cavity 3 is formed on the crown of a piston 2 and the swirl type injection valve 10, which swirlily and nearly conically sprays fuel, is used as a fuel injection valve. In addition, the spray axis center line is located eccentrically and parallel to the center axis of the cavity. Let(t) and (d) respectively denote the distance in the direction parallel to the spray axis center line and that in the direction perpendicular thereto between the nozzle 11 of the swirl type injection valve at fuel injection and the opening edge of the cavity at the position nearest to the nozzle 11 and also let theta be the spray cone angle of the swirl type injection valve, then (t), (d) and theta and set so as to satisfy with the relationship: tan (theta/2)<d/t. In such a manner as mentioned above, the favorable distribution of fuel spray and the prevention of fuel spray from adhering to the wall surface of the combustion chamber can be resulted.

Description

【発明の詳細な説明】 本発明は、燃焼室に燃料を直接噴射する内燃機関に関す
る。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to an internal combustion engine that injects fuel directly into a combustion chamber.

直接噴射式内燃機関は、その性能を向上するには、燃焼
室に直接噴射した燃料噴ｌｌを、良好に分散し、かつ、
燃焼室壁面に付着させないことが必要である。そのため
、従来の小型機関においては。In order to improve the performance of a direct injection internal combustion engine, the fuel injection directly injected into the combustion chamber must be well distributed, and
It is necessary to prevent it from adhering to the combustion chamber wall. Therefore, in conventional small engines.

燃焼室の吸気の旋回流を強くして−るが、しかし。However, the swirling flow of intake air in the combustion chamber is strengthened.

吸気渦流強さが大きくなると、燃焼室壁面への熱損失が
増大し、かつ、吸気の流動損失の増大によって吸気の充
填効率が低下する。ｔた、従来の大型機関に訃いては、
燃焼室への燃料の噴射圧力を高くして−るが、しかし、
高圧噴射になると、燃料噴射装置が高圧用になってその
重量が増大する等の不具合が生ずる。When the intake air vortex strength increases, heat loss to the combustion chamber wall increases, and intake air filling efficiency decreases due to an increase in intake air flow loss. However, if the conventional large-scale engine dies,
Although the injection pressure of fuel into the combustion chamber is increased,
High-pressure injection results in problems such as increased weight of the fuel injection device as it becomes a high-pressure device.

本発明の目的は、上記のような従来の状況からして、燃
焼室の吸気渦流強さを大きくすることなく％また、燃焼
室への燃料噴射圧力を高くすることなく、燃焼室の燃料
噴霧の分散を良好にし、かつ、燃焼室壁面への付着を防
止することのてきる直接噴射式内燃機関【提供すること
である。In view of the above-mentioned conventional situation, it is an object of the present invention to reduce the amount of fuel spray in the combustion chamber without increasing the strength of the intake vortex flow in the combustion chamber, and without increasing the fuel injection pressure into the combustion chamber. An object of the present invention is to provide a direct injection internal combustion engine which can improve the dispersion of fuel and prevent it from adhering to the wall surface of the combustion chamber.

本発明者は、上記の目的を達成する九め、先ず、低い噴
射圧力によって燃料を旋回しっつは埋円錐状に噴霧する
渦巻噴射弁に着購したのである。この渦巻噴射弁は、噴
射圧力が低くて高圧噴射装置が不要である上に、噴霧の
微粒化が良くて噴霧角が大きいので、噴霧の分散を良好
にするのに都合が良く、また、噴霧の貫徹力が弱いので
、噴霧の壁面付着【防止するのに都合が良く、更に、噴
霧の微粒化が良くて貫徹力が弱いことから、弱い吸気渦
流に噴霧を混合するのに適し、吸気渦流強さを大きくす
る必要がない。In order to achieve the above object, the inventor first purchased a swirl injection valve that swirls the fuel and atomizes it in the shape of a sunken cone using a low injection pressure. This spiral injection valve has a low injection pressure and does not require a high-pressure injection device, and also has good spray atomization and a large spray angle, so it is convenient for improving spray dispersion. Since the penetration force is weak, it is convenient to prevent the spray from adhering to the wall surface.In addition, since the spray is atomized well and the penetration force is weak, it is suitable for mixing the spray with the weak intake vortex. There is no need to increase the strength.

次に、本発明者は、上記のような渦巻噴射弁の利点を充
分に生かすため、渦巻噴射弁の取付位置について研究し
たのである。渦巻噴射弁をその噴射軸芯が燃焼室に設け
た凹所の中心軸と偏芯して平行する位置に設は友場合、
渦巻噴射弁を凹所の中心軸からの偏芯量を多くして凹所
の開口縁ないし側面側に近づけるに従って％また、噴霧
角を大きくするに従って、噴霧が凹所の開口縁ないし側
面に付着するＭＪ能性が大きくなり、また、噴霧が凹所
の吸気渦流の主流に混入する量が減少する。Next, in order to fully utilize the advantages of the swirl injection valve as described above, the inventor conducted research on the mounting position of the swirl injection valve. If the spiral injection valve is installed in a position where its injection axis is eccentrically parallel to the central axis of the recess provided in the combustion chamber,
As the amount of eccentricity of the swirl injection valve from the central axis of the recess is increased and it is moved closer to the opening edge or side of the recess, the spray will adhere to the opening edge or side of the recess. This increases the MJ ability, and reduces the amount of spray mixed into the mainstream of the intake vortex in the recess.

そこで、燃料噴射時における渦巻噴射弁の噴口とこの噴
口に最も近接した位置の凹所開口縁間の、渦巻噴射弁の
噴射軸芯と平行する方向の距離をｔとし、直交する方向
の距離をｄとし、渦巻噴射弁の噴霧角をθとすると、 θ ｄ）を自ｔａｎ−なｔｉ”Ｌ　　θ＜　２　ａｒａｔａ
ｎ　ｄ−ｔ の関係を満していれば、噴霧が凹所の開口縁ないし側面
に付着する可能性が小さくなり、また、噴霧が凹所の吸
気渦流の主流に混入する量が増大することを知得したの
である。Therefore, the distance in the direction parallel to the injection axis of the swirl injection valve between the nozzle of the swirl injection valve and the recess opening edge closest to the nozzle during fuel injection is defined as t, and the distance in the orthogonal direction is defined as t. d) and the spray angle of the volute injection valve is θ, then θ d) is self-tan-ti”L θ<2 arata
If the relationship n d - t is satisfied, the possibility of the spray adhering to the opening edge or side surface of the recess will be reduced, and the amount of the spray mixed into the mainstream of the intake vortex of the recess will be increased. I learned that.

即ち１本発明は、燃焼室に吸気が流入して旋回する凹所
を設け、凹所の開口に噴口が臨む燃料噴射弁を設は九直
接噴射式内燃機関にお９で、燃料噴射弁に燃料を旋回し
つつほぼ円錐状に噴霧する渦巻噴射弁を用い、渦巻噴射
弁をその噴霧軸芯が凹所の中１Ｌ＞軸と偏芯して平行す
る位置に配置し、燃料噴射時における渦巻噴射弁の噴口
とこの噴口に最も近接した位置の凹所開口縁間の、渦巻
噴射弁の噴射軸芯と平行する方向の距離をｔとし、直交
する方向の距離をｄとし、渦巻噴射弁の噴霧角をθとす
ると、 θ　　　　ｄ ｔａｎ−＜　　− ｔ の関係ｆ：満すことを特徴とする直接噴射式内燃機関で
ある。That is, the present invention provides a direct injection internal combustion engine with a recess in which intake air flows into the combustion chamber and swirls, and a fuel injection valve with a nozzle facing the opening of the recess. A swirl injection valve that sprays fuel in an almost conical shape while swirling the fuel is used, and the swirl injection valve is placed at a position where its spray axis is eccentrically parallel to the 1L> axis in the recess to prevent swirling during fuel injection. The distance between the nozzle of the injection valve and the recess opening edge at the position closest to the nozzle in the direction parallel to the injection axis of the swirl injection valve is t, the distance in the perpendicular direction is d, and The direct injection internal combustion engine is characterized by satisfying the relationship f: θ d tan−<−t, where the spray angle is θ.

本発明の直接噴射式内燃機関においては、上記の本発明
に至る経過説明から明らかなよりに、燃焼室の凹所の吸
気渦流強さを大きくすることなく、また、凹所への燃料
噴射圧力を高くすることなく、凹所の燃料噴霧の分散を
良好にし、かつ、凹所の開口縁ないし側面への燃料噴霧
の付着を防止することができ、吸気渦流強さを太きくす
ることに基く、また、燃料噴射圧力を高くすることに基
〈従来の欠点を除去することができる。In the direct injection internal combustion engine of the present invention, as is clear from the above description of the process leading up to the present invention, it is possible to reduce the fuel injection pressure into the recess without increasing the intake swirl strength in the recess of the combustion chamber. It is possible to improve the dispersion of the fuel spray in the recess without increasing the height of the recess, and to prevent the fuel spray from adhering to the opening edge or side of the recess. Moreover, by increasing the fuel injection pressure, the drawbacks of the conventional method can be eliminated.

次に１本発明の実施例について説明する。Next, one embodiment of the present invention will be described.

第１図乃至第３図に示す本例の直接噴射式内燃機関ハ、
ディーゼルエンジンであり、シリンダ（１）に摺嵌した
ピストン（２）の頂面に略球形状の凹所（３）をピスト
ンの中心軸から偏芯して穿設し、シリンダ（１）の開口
頂端に吸気通路（５）と排気通路（７）を設けたシリン
ダヘッド（４）を重合して取付け、吸気弁（６）管設け
た吸気通路（５）の吸電口と排気弁（８）を設けた排気
通路（７）の排気口をそれぞれピストン（２）の頂面に
対面して配置し、シリンダ（１）とピストン（２）及び
シリンダヘッド（４）によって燃焼室（９）を構成し、
シリンダヘッド（４）に低圧用燃料噴射装置の渦巻噴射
弁α１を、その噴口Ｕυが燃焼室（９）の一部である凹
所（３）の開口に臨み、かつ、その噴射軸芯が凹所（３
）の中心軸と偏芯して平行する位置に取付けており、吸
気通路（５）を経て燃焼室（９）に流入した吸気が凹所
（３）に流入して旋回し、凹所（３）の吸気渦流の主流
に渦巻噴射弁α呻から燃料が旋回しつつほぼ中空円錐状
に噴霧され為ように装置している。The direct injection internal combustion engine of this example shown in FIGS. 1 to 3 c,
This is a diesel engine, and a substantially spherical recess (3) is bored eccentrically from the central axis of the piston on the top surface of a piston (2) that is slidably fitted into a cylinder (1), and the opening of the cylinder (1) is A cylinder head (4) with an intake passage (5) and an exhaust passage (7) provided at the top end is superimposed and installed, and an intake valve (6) and an intake port of the intake passage (5) provided with a pipe and an exhaust valve (8) are installed. The exhaust ports of the exhaust passages (7) provided with are arranged to face the top surface of the piston (2), and the cylinder (1), the piston (2), and the cylinder head (4) constitute a combustion chamber (9). death,
The spiral injection valve α1 of the low-pressure fuel injection device is installed in the cylinder head (4), with its injection port Uυ facing the opening of the recess (3) which is a part of the combustion chamber (9), and whose injection axis is recessed. Tokoro (3)
) is installed eccentrically and parallel to the central axis of the recess (3), and the intake air that has flowed into the combustion chamber (9) through the intake passage (5) flows into the recess (3) and swirls. ) The fuel is sprayed into the main stream of the intake vortex from the swirl injection valve α in a substantially hollow conical shape while swirling.

燃焼室（９）の行程容積は１Ｉ４０ｄで、圧縮比は／ざ
であり、凹所（３）の容積は２２ａＩで、凹所（３）の
−口径＃ｉ３／ざ１であり、燃料噴射時期ｄ上死点前２
０’であり、燃料噴射時における渦巻噴射弁の噴口（ｌ
υとこの噴口に最も近接し九位置の凹所（３）開口縁間
の、渦巻噴射弁明の噴射軸芯と平行する方向の距離ｔは
３．３　ｆｌで、直交する方向の距離ｄは７り鰭であり
、渦巻噴射弁α０の噴霧角θけりＯｏである。従って。The stroke volume of the combustion chamber (9) is 1I40d, the compression ratio is /za, the volume of the recess (3) is 22aI, the diameter of the recess (3) is #i3/za1, and the fuel injection timing is d2 before top dead center
0', and the nozzle (l
The distance t in the direction parallel to the injection axis of the spiral injection valve between υ and the recess (3) opening edge at the 9th position closest to this nozzle is 3.3 fl, and the distance d in the orthogonal direction is 7. The spray angle θ of the spiral injection valve α0 is Oo. Therefore.

ｔ　　ｚ　５，３　ｍ ｄ　＝Ｚワタ −＝りＯ″ であるから、 θ ｊａｎ　−＝　１ 一キ１．４９ θ　ｄ ｔａｎ−ｚ＜τ の関係を満している。t z 5,3 m d = Z cotton -=riO″ Because it is, θ jan −= 1 Ikki 1.49 θ　d tan-z<τ Meet the relationship.

本例のディーゼルエンジンにおいては、凹所（３）の弱
い吸ｇｃ＃Ｉ流の主流に渦巻噴射弁Ｑｌから燃料が低い
噴射圧力によって噴霧され、噴霧の分散が良好であると
共に、凹所（３）の開口縁ないし側面への噴霧の付着が
極めて少ない。In the diesel engine of this example, fuel is sprayed from the swirl injection valve Ql into the mainstream of the weakly sucked gc#I flow in the recess (3) at a low injection pressure, and the spray is well dispersed. ) There is very little spray adhesion to the opening edges or sides.

上記の実施例のディーゼルエンジンにおいては、凹所（
３）の開口が真円であったが、第ｑ図と第５図又は第６
図と第７図に示すように、凹所（３）の開口縁に窪みＷ
６四又は膨出部ｑ３が渦巻噴射弁の噴口Ｃ１ηに近接し
て存在する場合は、前記の距離ｄとｔは、それらの各図
に示すように採り、燃料噴射時における渦巻噴射弁の噴
口（ロ）とこの噴口に最も近接した位置の凹所（３）Ｒ
口縁との間の距離とする。In the diesel engine of the above embodiment, the recess (
The opening in 3) was a perfect circle, but in Figure q and Figure 5 or 6.
As shown in the figure and Fig. 7, there is a depression W on the opening edge of the depression (3).
64 or bulge q3 is located close to the nozzle C1η of the swirl injection valve, the distances d and t mentioned above are taken as shown in those figures, and the nozzle of the swirl injection valve at the time of fuel injection. (b) and the recess located closest to this nozzle (3) R
The distance from the rim of the mouth.

【図面の簡単な説明】[Brief explanation of the drawing]

第１図は本発明の実施例の直接噴射式内燃機関の縦断面
図、第２図とｓｇ３図は同側の直接噴射式内燃機関の凹
所の平面図と縦断面図であり、ｓｌＩ図と第５図は他の
実施例の直接噴射式内燃機関の凹所の平面図と縦断面図
であり、第を図と第７図は更に他の実施例の直接噴射式
内燃機関の凹所の平面図と縦断面図である。 ３：凹　所　　　　９：燃焼室 １０：渦巻噴射弁　１１：噴　口 第１図FIG. 1 is a longitudinal sectional view of a direct injection internal combustion engine according to an embodiment of the present invention, FIG. and FIG. 5 are a plan view and a longitudinal cross-sectional view of a recess in a direct injection internal combustion engine according to another embodiment, and FIGS. FIG. 2 is a plan view and a longitudinal sectional view of 3: Concave location 9: Combustion chamber 10: Swirl injection valve 11: Nozzle Figure 1

Claims (1)

【特許請求の範囲】 燃焼室に吸気が流入して旋回する凹所を設け、凹所の開
口に噴口が臨む燃料噴射弁を設けた直接噴射式内燃機関
において、燃料噴射弁に燃料を旋回しつりはぼ円錐状に
噴霧する渦巻噴射弁を用い、渦巻噴射弁をその噴霧軸芯
が凹所の中心軸と偏芯して平行する位置に配置し、燃料
噴射時における渦巻噴射弁の噴口とこの噴口に最も近接
した位置の凹所開口縁間の、渦巻噴射弁の噴射軸芯と平
行する方向の距離をｔとし、直交する方向の距離【ｄと
し、渦巻噴射弁の噴鵬角を０とすると、関。[Scope of Claims] In a direct injection internal combustion engine that is provided with a recess in which intake air flows into a combustion chamber and swirls, and a fuel injection valve with a nozzle facing the opening of the recess, the fuel is swirled into the fuel injection valve. The suspension uses a volute injection valve that sprays in a conical shape, and the volute injection valve is placed in a position where its spray axis is eccentric and parallel to the central axis of the recess, and the nozzle of the volute injection valve during fuel injection is The distance between the opening edges of the recess closest to the nozzle in the direction parallel to the injection axis of the volute injection valve is t, the distance in the orthogonal direction is d, and the injection angle of the volute injection valve is 0. Then, Seki.
JP57013791A 1982-01-29 1982-01-29 Direct injection type internal-combustion engine Pending JPS58131308A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP57013791A JPS58131308A (en) 1982-01-29 1982-01-29 Direct injection type internal-combustion engine

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP57013791A JPS58131308A (en) 1982-01-29 1982-01-29 Direct injection type internal-combustion engine

Publications (1)

Publication Number Publication Date
JPS58131308A true JPS58131308A (en) 1983-08-05

Family

ID=11843067

Family Applications (1)

Application Number Title Priority Date Filing Date
JP57013791A Pending JPS58131308A (en) 1982-01-29 1982-01-29 Direct injection type internal-combustion engine

Country Status (1)

Country Link
JP (1) JPS58131308A (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0140047A2 (en) * 1983-09-05 1985-05-08 Kabushiki Kaisha Toyota Chuo Kenkyusho Direct fuel injection type internal combustion engine

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5474013A (en) * 1977-11-24 1979-06-13 Hino Motors Ltd Combustion chamber for diesel engine
JPS5510584U (en) * 1978-07-07 1980-01-23
JPS567494A (en) * 1979-07-02 1981-01-26 Hitachi Ltd Printed circuit board
JPS56121860A (en) * 1980-02-26 1981-09-24 Mitsubishi Motors Corp Electromagnetic type fuel injection valve

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5474013A (en) * 1977-11-24 1979-06-13 Hino Motors Ltd Combustion chamber for diesel engine
JPS5510584U (en) * 1978-07-07 1980-01-23
JPS567494A (en) * 1979-07-02 1981-01-26 Hitachi Ltd Printed circuit board
JPS56121860A (en) * 1980-02-26 1981-09-24 Mitsubishi Motors Corp Electromagnetic type fuel injection valve

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0140047A2 (en) * 1983-09-05 1985-05-08 Kabushiki Kaisha Toyota Chuo Kenkyusho Direct fuel injection type internal combustion engine

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