JPH07208173A - Direct injection type combustion chamber device of diesel engine - Google Patents
Direct injection type combustion chamber device of diesel engineInfo
- Publication number
- JPH07208173A JPH07208173A JP6002321A JP232194A JPH07208173A JP H07208173 A JPH07208173 A JP H07208173A JP 6002321 A JP6002321 A JP 6002321A JP 232194 A JP232194 A JP 232194A JP H07208173 A JPH07208173 A JP H07208173A
- Authority
- JP
- Japan
- Prior art keywords
- combustion chamber
- fuel
- top surface
- fuel injection
- land portion
- 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
- F02B23/0645—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
- F02B23/0696—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
- 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)
Abstract
Description
【０００１】[0001]
【産業上の利用分野】この発明は、ディーゼルエンジン
の直噴式燃焼室装置に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a direct injection type combustion chamber device for a diesel engine.
【０００２】[0002]
【従来の技術】この種の装置としては従来より、例えば
実開平１−６９０２３号公報に開示されたものが知られ
ている。ここで図５は上記従来例を示し、同図(Ａ)はデ
ィーゼルエンジンの要部の縦断面図、同図(Ｂ)は同図
(Ａ)中の要部の拡大図である。この従来例は図５(Ａ)
(Ｂ)に示すように、ピストンヘッド１０１の中央寄り部
に燃焼室１０２を凹入形成するとともに、その燃焼室１
０２の底面の略中央部にランド部１０３を突設し、当該
燃料噴射ノズル１０５の複数のノズル噴口を上記燃焼室
１０２に臨ませ、噴射燃料１０７を上記燃焼室１０２内
の周壁と上記ランド部１０３とに向けて噴射させ、噴射
燃料１０７を上記ランド部１０３で反射させて新たな可
燃領域を形成するように構成されている。なお、上記燃
料噴射ノズル１０５は、吸排気弁１１３等との干渉を回
避するため、ピストンヘッド１０１の頂面に対して斜め
に配設されている。2. Description of the Related Art As a device of this type, a device disclosed in Japanese Utility Model Laid-Open No. 1-69023 has been known. Here, FIG. 5 shows the above conventional example, FIG. 5 (A) is a longitudinal sectional view of a main part of a diesel engine, and FIG. 5 (B) is the same figure.
It is an enlarged view of the principal part in (A). This conventional example is shown in FIG.
As shown in (B), the combustion chamber 102 is formed in a recessed portion near the center of the piston head 101.
02, a land portion 103 is provided at a substantially central portion of the bottom surface of the fuel injection nozzle 105 so that a plurality of nozzle nozzles of the fuel injection nozzle 105 face the combustion chamber 102, and the injected fuel 107 is injected into the peripheral wall of the combustion chamber 102 and the land portion. It is configured so that the fuel 103 is injected toward and the injected fuel 107 is reflected by the land portion 103 to form a new combustible region. The fuel injection nozzle 105 is arranged obliquely with respect to the top surface of the piston head 101 in order to avoid interference with the intake / exhaust valve 113 and the like.
【０００３】[0003]
【発明が解決しようとする課題】上記従来例では、以下
のような難点がある。噴射燃料１０７を上記ランド部１
０３で反射させて新たな可燃領域を形成するように構成
されているが、上記燃料噴射ノズル１０５は、ピストン
ヘッド１０１の頂面に対して斜めに配設されている関係
上、上記ランド部１０３で反射した燃料は燃料噴射ノズ
ル１０５の傾斜方向のみに反射することになるため、噴
射燃料１０７を空気と均等にミキシングさせることが困
難になる。The above-mentioned conventional example has the following problems. The injected fuel 107 is supplied to the land portion 1
The fuel injection nozzle 105 is arranged so as to be inclined with respect to the top surface of the piston head 101, so that the land portion 103 is reflected. Since the fuel reflected by (2) is reflected only in the tilt direction of the fuel injection nozzle 105, it becomes difficult to mix the injected fuel 107 with the air evenly.
【０００４】つまり、上記ランド部１０３の燃料反射側
では多量の噴霧燃料が、これと反対側では少ない噴霧燃
料が分布することになる。このため、特に燃料噴射量が
多くなる始動時や高負荷運転時には、多量の未揮発燃料
が燃焼室１０２内の圧縮空気と十分に混合されないまま
不完全燃焼を起こし、燃焼性能を低下させる。これによ
り、エンジンの出力が低下し、スモークの発生量が多く
なる。That is, a large amount of atomized fuel is distributed on the fuel reflection side of the land portion 103, and a small amount of atomized fuel is distributed on the opposite side. For this reason, particularly at the time of start-up or high-load operation in which the fuel injection amount is large, a large amount of non-volatile fuel causes incomplete combustion without being sufficiently mixed with the compressed air in the combustion chamber 102, which deteriorates combustion performance. As a result, the output of the engine decreases and the amount of smoke generated increases.
【０００５】本発明はこのような事情を考慮してなされ
たもので、 燃料噴射ノズルが斜めに配設されていると否とにか
かわらず、燃料を四方八方へ均等に飛散させること、 燃料噴射量が多くなる始動時や高負荷運転時におい
ても、噴射燃料を燃焼室内の圧縮空気と十分に混合させ
て燃焼性能を向上させること、 これにより、エンジンの出力アップとスモークの低減を
図ることを技術課題とする。The present invention has been made in view of the above circumstances, and makes it possible to evenly disperse fuel in all directions regardless of whether or not the fuel injection nozzle is obliquely arranged. Even at the time of start-up or high-load operation when the amount becomes large, it is possible to improve the combustion performance by thoroughly mixing the injected fuel with the compressed air in the combustion chamber, thereby increasing the engine output and reducing smoke. This is a technical issue.
【０００６】[0006]
【課題を解決するための手段】請求項１の発明は、ピス
トンヘッド１の中央寄り部に燃焼室２を凹入形成すると
ともに、その燃焼室２の底面の略中央部にランド部３を
突設し、燃料噴射ノズル５のノズル噴口６を上記燃焼室
２に臨ませて配設するとともに、噴射燃料７を上記ラン
ド部３に向けて噴射するように構成したディーゼルエン
ジンの直噴式燃焼室装置において、上記ランド部３の頂
面４を凹凸状に形成するとともに、上記燃料噴射ノズル
５の燃料噴射軸線Ｚを上記頂面４の略中央部に向けて配
置し、上記噴射燃料７を当該頂面４のほぼ全域に亙って
噴射させるように構成したことを特徴とする。According to a first aspect of the present invention, a combustion chamber 2 is formed in a recessed portion in the central portion of a piston head 1, and a land portion 3 is projected in a substantially central portion of the bottom surface of the combustion chamber 2. A direct injection combustion chamber device for a diesel engine, in which a nozzle injection port 6 of a fuel injection nozzle 5 is provided so as to face the combustion chamber 2 and an injection fuel 7 is injected toward the land portion 3. In addition, the top surface 4 of the land portion 3 is formed in an uneven shape, and the fuel injection axis Z of the fuel injection nozzle 5 is arranged toward the substantially central portion of the top surface 4, and the injected fuel 7 is applied to the top surface 4. It is characterized in that it is configured so as to eject over substantially the entire area of the surface 4.
【０００７】また、請求項２の発明は、請求項１に記載
したディーゼルエンジンの直噴式燃焼室装置において、
上記ランド部３の頂面４を鋳型成型により平面視で四角
形に形成するとともに、当該頂面４の凹凸を多数の溝線
(4a)により形成し、この溝線４ａの方向を上記燃料噴射
ノズル５の燃料噴射軸線Ｚと直交する方向に形成したこ
とを特徴とする。The invention of claim 2 provides the direct injection type combustion chamber device for a diesel engine according to claim 1,
The top surface 4 of the land portion 3 is formed into a quadrangle in plan view by molding, and the unevenness of the top surface 4 is formed by a large number of groove lines.
(4a), and the groove line 4a is formed in a direction orthogonal to the fuel injection axis Z of the fuel injection nozzle 5.
【０００８】[0008]
【発明の作用・効果】請求項１の発明では、以下のよう
な作用・効果を奏する。図３(Ｂ)で示すように、圧縮行
程において、燃焼室２内ではランド部３を旋回中心とす
る旋回スワールＳ1 と燃焼室２の周壁に沿う縦向きのス
キッシュ流Ｓ2とが形成される。これらの旋回スワール
Ｓ1 とスキッシュ流Ｓ2 とは合流してランド部３を旋回
中心とする螺旋状のスワールＳとなる。According to the invention of claim 1, the following actions and effects are exhibited. As shown in FIG. 3B, in the compression stroke, a swirl swirl S 1 with the land portion 3 as the swirl center and a vertical squish flow S 2 along the peripheral wall of the combustion chamber 2 are formed in the combustion chamber 2. It The swirl swirl S 1 and the squish flow S 2 join to form a spiral swirl S having the land portion 3 as the swirl center.
【０００９】また、請求項１の発明では、上記ランド部
３の頂面４を凹凸状に形成するとともに、上記燃料噴射
ノズル５の燃料噴射軸線Ｚを上記頂面４の略中央部に向
けて配置し、上記噴射燃料７を当該頂面４のほぼ全域に
亙って噴射させるように構成したことから、圧縮行程の
終期において噴射される噴射燃料７は、燃料噴射ノズル
５の傾きと無関係に、上記凹凸状頂面４の全域に当たっ
て四方八方へ拡散し、螺旋状スワールＳと混合される。
つまり、燃料噴射量７が多くなる始動時や高負荷運転時
においても、上記噴射燃料７は燃焼室２内の螺旋状スワ
ールＳと十分に混合されて燃焼性能が一層向上する。こ
れにより、エンジンの出力を高め、スモークを一層低減
することができる。Further, in the invention of claim 1, the top surface 4 of the land portion 3 is formed in an uneven shape, and the fuel injection axis Z of the fuel injection nozzle 5 is directed toward the substantially central portion of the top surface 4. Since it is arranged so that the injected fuel 7 is injected over almost the entire area of the top surface 4, the injected fuel 7 injected at the end of the compression stroke is independent of the inclination of the fuel injection nozzle 5. The entire surface of the uneven top surface 4 is diffused in all directions and mixed with the spiral swirl S.
That is, even at the time of start-up or high-load operation where the fuel injection amount 7 increases, the injected fuel 7 is sufficiently mixed with the spiral swirl S in the combustion chamber 2 to further improve the combustion performance. As a result, the output of the engine can be increased and smoke can be further reduced.
【００１０】請求項２の発明では、頂面４の凹凸を多数
の溝線(4a)により形成し、この溝線４ａの方向を上記燃
料噴射ノズル５の燃料噴射軸線Ｚと直交する方向に形成
したことから、圧縮行程の終期において噴射される噴射
燃料７は、燃料噴射ノズル５の傾きと無関係に、上記凹
凸状頂面４の全域に当たって四方八方へ拡散し、螺旋状
スワールＳと混合され、請求項１の発明と同様に燃焼性
能が向上する。In the second aspect of the present invention, the unevenness of the top surface 4 is formed by a large number of groove lines (4a), and the direction of the groove lines 4a is formed in the direction orthogonal to the fuel injection axis Z of the fuel injection nozzle 5. Therefore, the injected fuel 7 injected at the end of the compression stroke hits the entire area of the uneven top surface 4 regardless of the inclination of the fuel injection nozzle 5, diffuses in all directions, and is mixed with the spiral swirl S, Combustion performance is improved as in the first aspect of the invention.
【００１１】また、請求項２の発明では、上記ランド部
３を鋳型成型により形成したことから、当該ランド部３
に機械加工を加えないで鋳肌のままとし、凹凸状の頂面
４を適宜の形状にすることが可能となる。また、後で機
械加工することによる燃焼室２の容積にバラツキが生じ
るのを回避することもできる。さらに、ランド部３の頂
部を平面視で略四角形に形成してことから、上記螺旋状
スワールＳが少し乱れることになるので、凹凸状の頂面
４で反射・拡散され噴射燃料７は、少し乱れた螺旋状ス
ワールＳと十分に混合され、燃焼性能が一層向上するこ
とになる。Further, in the invention of claim 2, since the land portion 3 is formed by molding, the land portion 3 is formed.
It is possible to form the uneven top surface 4 into an appropriate shape by leaving the casting surface as it is without machining. It is also possible to avoid variations in the volume of the combustion chamber 2 due to later machining. Furthermore, since the top of the land portion 3 is formed in a substantially quadrangular shape in a plan view, the spiral swirl S is slightly disturbed, so that the injected fuel 7 is reflected / diffused by the uneven top surface 4 and slightly injected. It is sufficiently mixed with the disordered spiral swirl S, and the combustion performance is further improved.
【００１２】[0012]
【実施例】以下本発明の実施例を図面に基づいてさらに
詳しく説明する。図１は本発明の第１の実施例を示し、
同図(Ａ)はディーゼルエンジンの要部の縦断側面図、同
図(Ｂ)は図１(Ａ)中の要部の拡大平面図、同図(Ｃ)は図
１(Ｂ)の変形例を示す平面図、図２はシリンダヘッドの
横断平面図である。この実施例は、図１に示すように、
従来例と同様の基本構造を具備して成る。即ち、この直
噴式燃焼室装置は、ピストンヘッド１の中央寄り部に燃
焼室２を凹入形成するとともに、その燃焼室２の底面の
略中央部にランド部３を突設し、燃料噴射ノズル５を上
記ピストンヘッド１の頂面に対して斜めに配設するとと
もに、当該燃料噴射ノズル５のノズル噴口６を上記燃焼
室２に臨ませ、噴射燃料７を上記ランド部３に向けて噴
射するように構成されている。Embodiments of the present invention will now be described in more detail with reference to the drawings. FIG. 1 shows a first embodiment of the present invention,
1A is a vertical sectional side view of a main part of a diesel engine, FIG. 1B is an enlarged plan view of the main part in FIG. 1A, and FIG. 1C is a modification of FIG. 1B. FIG. 2 is a cross-sectional plan view of the cylinder head. This embodiment, as shown in FIG.
It has the same basic structure as the conventional example. That is, in this direct injection type combustion chamber device, a combustion chamber 2 is formed in a recessed portion near the center of the piston head 1, and a land portion 3 is provided so as to project substantially at the center of the bottom surface of the combustion chamber 2 to provide a fuel injection nozzle. 5 is arranged obliquely with respect to the top surface of the piston head 1, the nozzle injection port 6 of the fuel injection nozzle 5 faces the combustion chamber 2, and the injected fuel 7 is injected toward the land portion 3. Is configured.
【００１３】本実施例では、図１(Ａ)(Ｂ)に示すよう
に、上記ランド部３を鋳型成型により平面視で四角形に
形成するとともに、当該頂面４に多数の溝線４ａを形成
する。この溝線４ａは、上記燃料噴射ノズル５の燃料噴
射軸線Ｚと直交する方向に形成するとともに、上記燃料
噴射ノズル５をその燃料噴射軸線Ｚが頂面４の略中央部
に向くように配置する。そして上記噴射燃料７を当該頂
面４のほぼ全域に亙って噴射させるように構成する。な
お、多数の溝線４ａは、図１(Ｂ)に示す直線状のものに
限らず、図１(Ｃ)に示す円弧状のものや同心円状のもの
でもよい。In this embodiment, as shown in FIGS. 1 (A) and 1 (B), the land portion 3 is formed into a quadrangle in plan view by molding, and a large number of groove lines 4a are formed on the top surface 4. To do. The groove line 4a is formed in a direction orthogonal to the fuel injection axis Z of the fuel injection nozzle 5, and the fuel injection nozzle 5 is arranged so that the fuel injection axis Z faces the substantially central portion of the top surface 4. . Then, the injected fuel 7 is configured to be injected over substantially the entire area of the top surface 4. The large number of groove lines 4a are not limited to the linear shape shown in FIG. 1 (B), but may be the arcuate shape or the concentric shape shown in FIG. 1 (C).
【００１４】ランド部３は、特に機械加工を加えない
で、鋳肌のままとする。鋳肌のままであれば、頂面４の
凹凸形状を適宜の形状にすることが可能であり、また、
後で機械加工すると燃焼室２の容積にバラツキが生じる
恐れがあるので、これを回避することもできる。なお、
図１中の符号１０はシリンダヘッド、１４は排気ポー
ト、２０はシリンダブロック、１３は排気弁である。ま
た、図２中の符号１１は吸気弁、１２は吸気ポートであ
り、吸気ポート１２と排気ポート１４とは互いにシリン
ダヘッド１０の左右に向けて交互に配設され、排気の熱
が吸気に伝わりにくくしてある。The land portion 3 is left as it is as the casting surface without any special machining. If the casting surface remains, it is possible to make the uneven shape of the top surface 4 into an appropriate shape, and
If machining is performed later, the volume of the combustion chamber 2 may vary, and this can be avoided. In addition,
In FIG. 1, reference numeral 10 is a cylinder head, 14 is an exhaust port, 20 is a cylinder block, and 13 is an exhaust valve. Reference numeral 11 in FIG. 2 is an intake valve, 12 is an intake port, and the intake port 12 and the exhaust port 14 are alternately arranged toward the left and right of the cylinder head 10, and the heat of the exhaust is transferred to the intake air. It's harder.
【００１５】図３は上記実施例装置の作用説明図であ
り、同図(Ａ)は吸気行程、同図(Ｂ)は圧縮行程における
スワールの形成を示す縦断面である。この実施例装置に
よれば以下のように作用する。吸気行程では、図３(Ａ)
で示すように、吸気Ａが吸気ポート１２を通って渦流状
にシリンダ内に導入され、シリンダ壁に沿って渦巻き状
に回転する。そして圧縮行程では、図３(Ｂ)で示すよう
に、燃焼室２内でランド部３の周囲を旋回する旋回スワ
ールＳ1 と燃焼室２の周壁に沿う縦向きのスキッシュ流
Ｓ2とが形成され、これらが合流して上記ランド部３の
周囲を旋回する螺旋状のスワールＳとなる。3 (A) and 3 (B) are longitudinal sectional views showing the formation of swirls in the intake stroke and the compression stroke, respectively. The apparatus of this embodiment operates as follows. In the intake stroke, Fig. 3 (A)
As shown by, the intake air A is introduced into the cylinder in a vortex flow through the intake port 12 and rotates in a spiral shape along the cylinder wall. Then, in the compression stroke, as shown in FIG. 3 (B), a swirl swirl S 1 that swirls around the land portion 3 in the combustion chamber 2 and a vertical squish flow S 2 along the peripheral wall of the combustion chamber 2 are formed. As a result, they merge to form a spiral swirl S that swirls around the land portion 3.
【００１６】一方、圧縮行程の終期において噴射される
噴射燃料７は、その分布が偏ることはなく、上記凹凸状
の頂面４のほぼ全域に当たって反射・拡散し、螺旋状ス
ワールＳと混合される。つまり、燃料噴射量が多くなる
始動時や高負荷運転時においても、噴射燃料７は上記螺
旋状スワールＳと十分に混合され、燃焼性能が一層向上
する。これによりエンジンの出力を高め、スモークを一
層低減することができる。また、ランド部３の頂部を平
面視で略四角形に形成したことから、上記螺旋状スワー
ルＳが少し乱れることになるので、凹凸状の頂面４で反
射・拡散され噴射燃料７は、少し乱れた螺旋状スワール
Ｓと十分に混合され、燃焼性能が一層向上することにな
る。On the other hand, the injected fuel 7 injected at the end of the compression stroke has no uneven distribution, is reflected and diffused over almost the entire area of the uneven top surface 4, and is mixed with the spiral swirl S. . In other words, the injected fuel 7 is sufficiently mixed with the spiral swirl S even at the time of start-up or high-load operation where the fuel injection amount is large, and the combustion performance is further improved. As a result, the output of the engine can be increased and smoke can be further reduced. Further, since the top of the land portion 3 is formed in a substantially quadrangular shape in a plan view, the spiral swirl S is slightly disturbed, and the injected fuel 7 is slightly disturbed by being reflected and diffused by the uneven top surface 4. It is well mixed with the spiral swirl S and the combustion performance is further improved.
【００１７】図４は本発明の第２の実施例を示し、同図
(Ａ)は要部の縦断面図、同図(Ｂ)はその拡大平面図であ
る。この実施例では、図４(Ａ)に示すように、ランド部
３の頂面４を傾斜させるとともに、上記燃料噴射ノズル
５の燃料噴射軸線Ｚに対して頂面４を直交する方向に形
成する。その他の点は上記第１の実施例と同様に構成す
る。この実施例によれば、圧縮行程の終期において噴射
される噴射燃料７は、上記凹凸状の頂面４のほぼ全域に
当たって四方八方へ反射・拡散され、上記螺旋状スワー
ルＳと十分に混合される。FIG. 4 shows a second embodiment of the present invention.
(A) is a longitudinal cross-sectional view of a main part, and (B) is an enlarged plan view thereof. In this embodiment, as shown in FIG. 4A, the top surface 4 of the land portion 3 is inclined and the top surface 4 is formed in a direction orthogonal to the fuel injection axis Z of the fuel injection nozzle 5. . The other points are the same as those of the first embodiment. According to this embodiment, the injected fuel 7 injected at the end of the compression stroke hits almost the entire area of the uneven top surface 4 and is reflected and diffused in all directions, and is sufficiently mixed with the spiral swirl S. .
【００１８】なお、上記実施例では頂面４の凹凸を溝線
４ａにより形成したものについて例示したが、多数の凹
凸をランダムに形成したものでもよい。In the above embodiment, the unevenness of the top surface 4 is formed by the groove line 4a, but a large number of unevenness may be formed at random.
【図１】本発明の第１の実施例を示し、同図(Ａ)はディ
ーゼルエンジンの要部の縦断側面図、同図(Ｂ)は図(Ａ)
中の要部の拡大平面図、同図(Ｃ)はその変形例を示す平
面図である。1 shows a first embodiment of the present invention, in which FIG. 1 (A) is a vertical cross-sectional side view of a main part of a diesel engine, and FIG. 1 (B) is a drawing (A).
An enlarged plan view of a main part in the inside, and FIG. 6C is a plan view showing a modification thereof.
【図２】実施例に係るシリンダヘッド１０の横断平面図
である。FIG. 2 is a cross-sectional plan view of the cylinder head 10 according to the embodiment.
【図３】実施例装置の作用説明図であり、同図(Ａ)は吸
気行程、同図(Ｂ)は圧縮行程を示す縦断面図である。3A and 3B are explanatory views of the operation of the embodiment apparatus, in which FIG. 3A is an intake stroke and FIG. 3B is a vertical sectional view showing a compression stroke.
【図４】本発明の第２の実施例を示し、同図(Ａ)は要部
の縦断側面図、同図(Ｂ)はその拡大平面図である。FIG. 4 shows a second embodiment of the present invention, FIG. 4 (A) is a vertical sectional side view of a main part, and FIG. 4 (B) is an enlarged plan view thereof.
【図５】従来例を示し、同図(Ａ)はディーゼルエンジン
の要部の縦断面図、同図(Ｂ)は図(Ａ)中の要部の拡大図
である。FIG. 5 shows a conventional example, FIG. 5 (A) is a longitudinal sectional view of a main part of a diesel engine, and FIG. 5 (B) is an enlarged view of the main part in FIG.
１…ピストンヘッド、 ２…燃焼室、３
…ランド部、 ４…ランド部の頂
面、４ａ…頂面の凹凸（溝線）、 ５…燃料噴
射ノズル、Ｚ…燃料噴射ノズルの燃料噴射軸線、 ６…
ノズル噴口、７…噴射燃料。1 ... Piston head, 2 ... Combustion chamber, 3
... Land portion, 4 ... Top surface of land portion, 4a ... Asperity (groove line) on top surface, 5 ... Fuel injection nozzle, Z ... Fuel injection axis line of fuel injection nozzle, 6 ...
Nozzle nozzle, 7 ... Injected fuel.
Claims (2)
室(２)を凹入形成するとともに、その燃焼室(２)の底面
の略中央部にランド部(３)を突設し、 燃料噴射ノズル(５)のノズル噴口(６)を上記燃焼室(２)
に臨ませて配設するとともに、噴射燃料(７)を上記ラン
ド部(３)に向けて噴射するように構成したディーゼルエ
ンジンの直噴式燃焼室装置において、 上記ランド部(３)の頂面(４)を凹凸状に形成するととも
に、上記燃料噴射ノズル(５)の燃料噴射軸線(Ｚ)を上記
頂面(４)の略中央部に向けて配置し、上記噴射燃料(７)
を当該頂面(４)のほぼ全域に噴射させるように構成した
ことを特徴とするディーゼルエンジンの直噴式燃焼室装
置。1. A combustion chamber (2) is formed in a recessed portion near the center of a piston head (1), and a land portion (3) is provided at a substantially central portion of the bottom surface of the combustion chamber (2). The nozzle injection port (6) of the fuel injection nozzle (5) is connected to the combustion chamber (2).
In the direct injection type combustion chamber device of a diesel engine, which is arranged so as to face the land portion (3) and injects the injected fuel (7) toward the land portion (3), the top surface of the land portion (3) ( 4) is formed in a concavo-convex shape, and the fuel injection axis (Z) of the fuel injection nozzle (5) is arranged toward the substantially central portion of the top surface (4), and the injected fuel (7)
A direct-injection combustion chamber device for a diesel engine, characterized in that the fuel is injected into almost the entire area of the top surface (4).
により平面視で四角形に形成するとともに、当該頂面
(４)の凹凸を多数の溝線(4a)により形成し、この溝線(4
a)の方向を上記燃料噴射ノズル(５)の燃料噴射軸線(Ｚ)
と直交する方向に形成したことを特徴とする請求項１に
記載したディーゼルエンジンの直噴式燃焼室装置。2. The top surface (4) of the land (3) is formed into a quadrangle in plan view by molding, and the top surface (4) is formed.
The unevenness of (4) is formed by a large number of groove lines (4a).
The direction of a) is the fuel injection axis (Z) of the fuel injection nozzle (5).
The direct injection type combustion chamber device for a diesel engine according to claim 1, wherein the direct injection type combustion chamber device is formed in a direction orthogonal to the direction.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP6002321A JPH07208173A (en) | 1994-01-14 | 1994-01-14 | Direct injection type combustion chamber device of diesel engine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP6002321A JPH07208173A (en) | 1994-01-14 | 1994-01-14 | Direct injection type combustion chamber device of diesel engine |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH07208173A true JPH07208173A (en) | 1995-08-08 |
Family
ID=11526064
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP6002321A Pending JPH07208173A (en) | 1994-01-14 | 1994-01-14 | Direct injection type combustion chamber device of diesel engine |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH07208173A (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR2880384A1 (en) * | 2004-12-30 | 2006-07-07 | Renault Sas | Direct injection type internal combustion engine for motor vehicle, has boss with hollowed zone defined by concave surface extending on angular sector corresponding to that of injection layer comprising unbalanced jets of shorter length |
| US8424506B2 (en) | 2007-10-22 | 2013-04-23 | Toyota Jidosha Kabushiki Kaisha | Direct-injection type engine |
-
1994
- 1994-01-14 JP JP6002321A patent/JPH07208173A/en active Pending
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR2880384A1 (en) * | 2004-12-30 | 2006-07-07 | Renault Sas | Direct injection type internal combustion engine for motor vehicle, has boss with hollowed zone defined by concave surface extending on angular sector corresponding to that of injection layer comprising unbalanced jets of shorter length |
| EP1683950A1 (en) * | 2004-12-30 | 2006-07-26 | Renault | Internal combustion engine having a piston with projection in the combustion bowl foreseen with a deepened zone |
| US8424506B2 (en) | 2007-10-22 | 2013-04-23 | Toyota Jidosha Kabushiki Kaisha | Direct-injection type engine |
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