JPH06146904A - Double intake port type intake device of direct injection diesel engine - Google Patents
Double intake port type intake device of direct injection diesel engineInfo
- Publication number
- JPH06146904A JPH06146904A JP4322786A JP32278692A JPH06146904A JP H06146904 A JPH06146904 A JP H06146904A JP 4322786 A JP4322786 A JP 4322786A JP 32278692 A JP32278692 A JP 32278692A JP H06146904 A JPH06146904 A JP H06146904A
- Authority
- JP
- Japan
- Prior art keywords
- port
- intake port
- swirl
- cylinder chamber
- center
- 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
- F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
- F02F1/00—Cylinders; Cylinder heads
- F02F1/24—Cylinder heads
- F02F1/42—Shape or arrangement of intake or exhaust channels in cylinder heads
- F02F1/4214—Shape or arrangement of intake or exhaust channels in cylinder heads specially adapted for four or more valves per 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
- F02B2275/10—Diamond configuration of valves in cylinder heads
-
- 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
- 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)
- Cylinder Crankcases Of Internal Combustion Engines (AREA)
Abstract
Description
【０００１】[0001]
【産業上の利用分野】この発明は、直接噴射式ディーゼ
ルエンジンのダブル吸気ポート式吸気装置に関し、特に
ダイレクト吸気ポートとヘリカル吸気ポートを有するも
のに関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a double intake port type intake device for a direct injection diesel engine, and more particularly to a device having a direct intake port and a helical intake port.
【０００２】[0002]
【基本構造】この種のダブル吸気ポート式吸気装置とし
ては、従来より例えば特公昭５２−７４８５号公報に開
示されたものが知られている。その基本構造は、図３で
示すように、ディーゼルエンジンの１つのシリンダ室１
０１に対してダイレクト吸気ポート１０５とヘリカル吸
気ポート１０６とをシリンダヘッド１０２に形成し、各
吸気ポート１０５・１０６のポート入り口１０５ａ・１０
６ａをシリンダヘッド１０２の同じ横側面１０３に開口
するとともに、各ポート出口１０５ｂ・１０６ｂをシリ
ンダ室側端面に開口して構成されている。そして、前記
ダイレクト吸気ポート１０５のポート出口１０５ｂと前
記ヘリカル吸気ポート１０６のポート出口１０６ｂと
は、シリンダ室１０１の中心Ｃから略等距離に配置し、
両ポート出口１０５ｂ・１０６ｂがシリンダ室１０１の
中心Ｃに対してなす角θは、略直角となるように配置し
て形成されている。[Basic Structure] As a double intake port type intake device of this type, the one disclosed in Japanese Patent Publication No. 52-7485 is conventionally known. Its basic structure is, as shown in FIG. 3, one cylinder chamber 1 of a diesel engine.
01, the direct intake port 105 and the helical intake port 106 are formed in the cylinder head 102, and the port inlets 105a and 10 of the respective intake ports 105 and 106 are formed.
6a is opened on the same lateral surface 103 of the cylinder head 102, and each port outlet 105b, 106b is opened on the end surface on the cylinder chamber side. The port outlet 105b of the direct intake port 105 and the port outlet 106b of the helical intake port 106 are arranged at substantially the same distance from the center C of the cylinder chamber 101,
The angles θ formed by the two port outlets 105b and 106b with respect to the center C of the cylinder chamber 101 are formed so as to be substantially right angles.
【０００３】[0003]
【従来の技術】上記従来例では、図３で示すように、上
記ダイレクト吸気ポート１０５のポート出口１０５ｂが
シリンダ室１の中心Ｃより左寄りに偏位し、上記ヘリカ
ル吸気ポート１０６のポート出口１０６ｂが、シリンダ
ヘッド１０２の前記横側面１０３寄りに配置して形成さ
れている。2. Description of the Related Art In the above conventional example, as shown in FIG. 3, the port outlet 105b of the direct intake port 105 is displaced to the left from the center C of the cylinder chamber 1, and the port outlet 106b of the helical intake port 106 is displaced. The cylinder head 102 is formed near the lateral side surface 103.
【０００４】そして、上記ヘリカル吸気ポート１０６の
ポート出口１０６ｂからシリンダ室１０１内に流入した
吸気は、右旋回のスワールを発生する。一方上記ダイレ
クト吸気ポート１０５のポート出口１０５ｂが、シリン
ダ室１０１の中心Ｃより左寄りに偏位しているため、こ
のポート出口１０５ｂからシリンダ室１０１内に流入し
た吸気は、シリンダ室１０１の内壁に沿って右旋回し、
上記ヘリカル吸気ポート１０６による右旋回のスワール
を一層強化する。なお図３中の符号１０７・１０８は吸
気弁軸、１１０は排気ポートである。The intake air that has flowed into the cylinder chamber 101 from the port outlet 106b of the helical intake port 106 generates a swirl to the right. On the other hand, since the port outlet 105b of the direct intake port 105 is displaced to the left from the center C of the cylinder chamber 101, the intake air flowing into the cylinder chamber 101 from this port outlet 105b is along the inner wall of the cylinder chamber 101. Turn right,
The swirl of turning right by the helical intake port 106 is further enhanced. Note that reference numerals 107 and 108 in FIG. 3 denote intake valve shafts, and 110 denotes an exhaust port.
【０００５】[0005]
【発明が解決しようとする課題】一般に、ヘリカル吸気
ポートを備える直接噴射式ディーゼルエンジンでは、定
格運転時に最適スワールを発生させて最良の空燃混合を
得るように設定される。このため、低速運転時には少し
スワール不足気味に、高速運転時にはスワール過剰気味
になる傾向がある。Generally, in a direct injection diesel engine equipped with a helical intake port, optimum swirl is generated during rated operation to obtain the best air-fuel mixture. For this reason, there is a tendency that the swirl becomes a little insufficient at low speed operation and the swirl becomes excessive at high speed operation.
【０００６】即ち、図２(Ｂ)で示すように、噴射ノズル
から噴射された雰霧燃料の雰霧領域Ｊは、スワールによ
り矢印Ｓ方向へ拡散されるが、スワール不足の時は拡散
領域Ｋに止まり、スワール過剰の時は拡散領域Ｌにまで
達する。このため、例えば定格負荷としたとき、特に高
速運転（スワール過剰）時において、空燃混合が一層不
均一になるため、不完全燃焼によりスモークを発生す
る。That is, as shown in FIG. 2B, the mist region J of the mist fuel injected from the injection nozzle is diffused in the direction of arrow S by the swirl, but when the swirl is insufficient, the diffusion region K And reaches the diffusion region L when the swirl is excessive. Therefore, for example, when the load is rated, particularly during high-speed operation (excessive swirl), the air-fuel mixture becomes more uneven, and smoke is generated due to incomplete combustion.
【０００７】上記従来技術では、ダイレクト吸気ポート
１０５がスワールを一層強化するため、特に高速運転時
において過剰なスワールを発生し、これに起因して多量
のスモークを発生する。本発明はこのような事情を考慮
してなされたもので、定格運転時はもとより、特に高速
運転時において空燃混合を一層均一にして、スモークの
発生を防止することを技術課題とする。In the above-mentioned prior art, since the direct intake port 105 further strengthens the swirl, excessive swirl is generated especially at high speed operation, and a large amount of smoke is generated due to this. The present invention has been made in view of such circumstances, and an object of the present invention is to make the air-fuel mixture more uniform not only during rated operation but also during high-speed operation to prevent smoke from occurring.
【０００８】[0008]
【課題を解決するための手段】上記課題を解決するため
に、本発明が採用した手段は、前記基本構造を有する直
接噴射式ディーゼルエンジンのダブル吸気ポート式吸気
装置において、前記ダイレクト吸気ポート５は、縦スワ
ールＳ1を発生する形状で、そのポート入り口５ａから
ポート出口５ｂに向かう方向が、平面視でシリンダ室１
の中心Ｃへ略直進状に向かう形状に形成し、前記ヘリカ
ル吸気ポート６は、横スワールＳ2を発生する形状で、
そのポート出口６ｂは、上記シリンダ室１の中心Ｃから
左右いずれかに偏位させて形成したことを特徴とするも
のである。In order to solve the above-mentioned problems, the means adopted by the present invention is a double intake port type intake device for a direct injection diesel engine having the above basic structure, wherein the direct intake port 5 is , The vertical swirl S 1 is generated, and the direction from the port inlet 5a to the port outlet 5b is the cylinder chamber 1 in plan view.
The helical intake port 6 is formed in a shape that goes substantially straight to the center C of the helical intake port 6, and the helical intake port 6 has a shape that generates a lateral swirl S 2 .
The port outlet 6b is characterized by being formed so as to be offset from the center C of the cylinder chamber 1 to the left or right.
【０００９】[0009]
【発明の作用】本発明では、ダイレクト吸気ポート５が
縦スワールＳ1が発生し、ヘリカル吸気ポート６が横ス
ワールＳ2を発生する。そして、ダイレクト吸気ポート
５のポート入り口５ａからポート出口５ｂに向かう方向
が、平面視でシリンダ室１の中心Ｃへ略直進状に向かう
形状であり、ヘリカル吸気ポート６のポート出口６ｂ
が、シリンダ室１の中心Ｃから一方のポート出口５ｂと
略等距離に配置され、かつ、そのポート出口６ｂが、上
記シリンダ室１の中心Ｃから左右いずれかに偏位させて
形成されているので、ヘリカル吸気ポート６による横ス
ワールＳ2と、上記ダイレクト吸気ポート５による縦ス
ワールＳ1とが適度に干渉する。According to the present invention, the direct intake port 5 produces the vertical swirl S 1 , and the helical intake port 6 produces the lateral swirl S 2 . The direction from the port inlet 5a of the direct intake port 5 to the port outlet 5b has a shape that goes substantially straight to the center C of the cylinder chamber 1 in a plan view, and the port outlet 6b of the helical intake port 6 is provided.
Are arranged at a substantially equal distance from the center C of the cylinder chamber 1 to the one port outlet 5b, and the port outlet 6b is formed so as to be offset from the center C of the cylinder chamber 1 to the left or right. Therefore, the lateral swirl S 2 due to the helical intake port 6 and the vertical swirl S 1 due to the direct intake port 5 interfere appropriately.
【００１０】[0010]
【発明の効果】即ち、定格負荷・定格運転時に最適スワ
ールを発生させて最良の空燃混合を得るように設定され
た直接噴射式ディーゼルエンジンにおいて、高速運転時
には、ヘリカル吸気ポート６による横スワールＳ2は一
層強められるが、他方のダイレクト吸気ポート５による
縦スワールＳ1も強まり、この横スワールＳ2を適度に弱
める。これにより、最適スワールを維持して、スモーク
の発生を防止することができる。That is, in the direct injection diesel engine set to generate the optimum swirl at the rated load / rated operation to obtain the best air-fuel mixture, the lateral swirl S by the helical intake port 6 is operated at the high speed operation. 2 is further strengthened, but the vertical swirl S 1 by the other direct intake port 5 is also strengthened, and this lateral swirl S 2 is appropriately weakened. This makes it possible to maintain the optimum swirl and prevent the occurrence of smoke.
【００１１】[0011]
【実施例】以下図面に基づいてさらに詳しく説明する。
図１は本発明の実施例を示し、同図(Ａ)は図(Ｂ)のシリ
ンダヘッドのＤ−Ｄ線矢視横断平面図、同図(Ｂ)は図
(Ａ)のシリンダヘッドのＣ−Ｃ線矢視縦断面図である。DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS A detailed description will be given below with reference to the drawings.
FIG. 1 shows an embodiment of the present invention, FIG. 1A is a cross-sectional plan view of the cylinder head of FIG.
It is a longitudinal cross-sectional view of the cylinder head of FIG.
【００１２】この実施例は、前記従来例と同様の基本構
造を具備して成る。即ち、直接噴射式ディーゼルエンジ
ンの１つのシリンダ室１に対してダイレクト吸気ポート
５とヘリカル吸気ポート６とをシリンダヘッド２に形成
し、両吸気ポート５・６のポート入り口５ａ・６ａをシ
リンダヘッド２の同じ横側面３に開口するとともに、各
ポート出口５ｂ・６ｂをシリンダ室側端面４に開口し、
上記各ポート出口５ｂ・６ｂを、シリンダ室１の中心Ｃ
から略等距離に配置し、両ポート出口５ｂ・６ｂがシリ
ンダ室１の中心Ｃに対してなす角θが、略直角となるよ
うに配置して形成されている。This embodiment has the same basic structure as the conventional example. That is, the direct intake port 5 and the helical intake port 6 are formed in the cylinder head 2 for one cylinder chamber 1 of the direct injection diesel engine, and the port inlets 5a and 6a of both intake ports 5 and 6 are connected to the cylinder head 2. Of the same side surface 3 of the above, and each port outlet 5b, 6b to the cylinder chamber side end surface 4,
Center each of the port outlets 5b and 6b at the center C of the cylinder chamber 1.
Are formed substantially equidistant from each other so that the angle θ formed by the two port outlets 5b and 6b with respect to the center C of the cylinder chamber 1 is substantially right angle.
【００１３】なお、同図中の符号７・８は吸気弁軸、９
は排気弁軸、１０は排気ポート、１１はウオータジャケ
ット、１２は弁駆動装置のプッシュロッド室、１３はシ
リンダヘッド２の固定ボルト、１４は直接噴射式燃料噴
射器、１５はその燃料噴射器１４の装着孔である。この
実施例では、吸気ポート出口５ｂ・６ｂと排気ポート入
口１０ａとの配置の関係から、燃料噴射器１４をシリン
ダ室１の中心Ｃから偏位させて配置しているが、シリン
ダ室１の中心Ｃに位置させて配置しても良い。Reference numerals 7 and 8 in the figure are intake valve shafts and 9
Is an exhaust valve shaft, 10 is an exhaust port, 11 is a water jacket, 12 is a push rod chamber of a valve drive device, 13 is a fixing bolt of the cylinder head 2, 14 is a direct injection fuel injector, and 15 is its fuel injector 14. This is the mounting hole. In this embodiment, the fuel injector 14 is arranged so as to be deviated from the center C of the cylinder chamber 1 because of the arrangement relationship between the intake port outlets 5b and 6b and the exhaust port inlet 10a. It may be positioned at C and arranged.
【００１４】以下、本発明の特徴について説明する。上
記ダイレクト吸気ポート５は、縦スワールＳ1を発生す
るように下り勾配で、その縦向きの曲率半径がポート出
口５ｂに近づくにつれて次第に小さく形成され、そのポ
ート入り口５ａからポート出口５ｂに向かう方向は、平
面視でシリンダ室１の中心Ｃへ略直進状に向かうように
形成してある。The features of the present invention will be described below. The direct intake port 5 has a downward slope so as to generate a vertical swirl S 1 , and its vertical radius of curvature is gradually reduced toward the port outlet 5b. The direction from the port inlet 5a to the port outlet 5b is It is formed so as to extend in a substantially straight line shape toward the center C of the cylinder chamber 1 in a plan view.
【００１５】他方のヘリカル吸気ポート６は、左旋回の
横スワールＳ2を発生するように左旋回の下り勾配で、
左旋回の曲率半径がポート出口６ｂに近づくにつれて次
第に小さく形成され、そのポート出口６ｂは、上記シリ
ンダ室１の中心Ｃから右方に偏位させて形成されてい
る。なお、このポート出口６ｂを、上記シリンダ室１の
中心Ｃから左方に偏位させて形成しても良く、その場合
には、右旋回の横スワールを発生させるように右旋回の
下り勾配で、右旋回の曲率半径がポート出口６ｂに近づ
くにつれて次第に小さく形成する。The other helical intake port 6 has a downward slope of left turn so as to generate a lateral swirl S 2 of left turn,
The radius of curvature of the left turn is gradually reduced as it approaches the port outlet 6b, and the port outlet 6b is formed to be deviated to the right from the center C of the cylinder chamber 1. The port outlet 6b may be formed so as to be deviated to the left from the center C of the cylinder chamber 1. In that case, a right turn downward is generated so as to generate a right turn lateral swirl. The slope is formed so that the radius of curvature of the right turn gradually becomes smaller as it approaches the port outlet 6b.
【００１６】上記構成によれば、ダイレクト吸気ポート
５により縦スワールＳ1が発生し、他方のヘリカル吸気
ポート６により左旋回の横スワールＳ２が発生する。そ
して横スワールＳ２と、縦スワールＳ１とが図１（Ｂ）
で示すように、適度に干渉する。つまり、定格負荷・定
格運転時に最適スワールを発生させて最良の空燃混合を
得るように設定された直接噴射式ディーゼルエンジンに
おいて、高速運転時には、左旋回の横スワールＳ２は一
層強められるが、これに対応してダイレクト吸気ポート
５による縦スワールＳ１も強まり、横スワールＳ２を適
度に弱める。これにより、図２(Ａ)で示すように、最適
スワールを維持して空燃混合を最適状態に維持し、スモ
ークの発生を防止する。According to the above construction, the vertical swirl S 1 is generated by the direct intake port 5, and the left swirl lateral swirl S 2 is generated by the other helical intake port 6. The horizontal swirl S 2 and the vertical swirl S 1 are shown in FIG . 1 (B).
As shown by, it interferes moderately. That is, in the direct injection diesel engine set to generate the optimum swirl at the rated load / rated operation to obtain the best air-fuel mixture, at the time of high speed operation, the lateral swirl S 2 of the left turn is further strengthened, Correspondingly, the vertical swirl S 1 by the direct intake port 5 is also strengthened, and the horizontal swirl S 2 is appropriately weakened. As a result, as shown in FIG. 2 (A), the optimum swirl is maintained, the air-fuel mixture is maintained in the optimum state, and the occurrence of smoke is prevented.
【００１７】なお、上記実施例では、シリンダヘッド２
の固定ボルト１３を略等間隔に配置するため、ダイレク
ト吸気ポート５とヘリカル吸気ポート６の各ポート入り
口５ａ・６ａとを、上下に重なる配置で開口形成してい
るが、これには限らない。また、ダイレクト吸気ポート
５とヘリカル吸気ポート６の上下の配置を、図１とは逆
の関係となるように配置しても良い。さらに上記実施例
では、排気弁が１つの排気ポート１０を備える３弁式の
直接噴射式ディーゼルエンジンについて例示したが、本
発明は上記実施例に限るものではなく、排気弁が２つの
排気ポートを備える４弁式のについても実施できる。In the above embodiment, the cylinder head 2
Since the fixing bolts 13 are arranged at substantially equal intervals, the direct intake port 5 and the respective port inlets 5a and 6a of the helical intake port 6 are formed so as to be vertically overlapped with each other, but the invention is not limited to this. Further, the direct intake port 5 and the helical intake port 6 may be arranged vertically so as to have an inverse relationship to that of FIG. Further, in the above-mentioned embodiment, the three-valve direct injection diesel engine in which the exhaust valve has one exhaust port 10 has been illustrated, but the present invention is not limited to the above-mentioned embodiment, and the exhaust valve has two exhaust ports. A four-valve type provided can be implemented.
【図１】本発明の実施例を示し、同図（Ａ）は図（Ｂ）
のシリンダヘッドのＤ−Ｄ線矢視横断平面図、同図
（Ｂ）は図（Ａ）のシリンダヘッドのＣ−Ｃ線矢視縦断
面図である。FIG. 1 shows an embodiment of the present invention, in which FIG.
6B is a cross-sectional plan view taken along the line D-D of the cylinder head of FIG. 2B, and FIG.
【図２】空燃混合の状態を模式的に示す図であり、同図
（Ａ）は本発明による場合を例示した模式図、同図
（Ｂ）は従来例による場合を例示した模式図である。2A and 2B are diagrams schematically showing a state of air-fuel mixture, FIG. 2A is a schematic diagram illustrating a case according to the present invention, and FIG. 2B is a schematic diagram illustrating a case according to a conventional example. is there.
【図３】従来例を示すシリンダヘッドの横断平面図であ
る。FIG. 3 is a cross-sectional plan view of a cylinder head showing a conventional example.
１…シリンダ室、 ２…シリンダヘッ
ド、３…シリンダヘッドの横側面、 ４…シリンダ室
側端面、５…ダイレクト吸気ポート、 ６…ヘリカ
ル吸気ポート、５ａ・６ａ…ポート入り口、 ５ｂ
・６ｂ…ポート出口、Ｃ…シリンダ室の中心、
Ｓ１…縦スワール、Ｓ２…横スワール、 θ…両ポー
ト出口がシリンダ室の中心Ｃに対してなす角。DESCRIPTION OF SYMBOLS 1 ... Cylinder chamber, 2 ... Cylinder head, 3 ... Lateral side surface of the cylinder head, 4 ... Cylinder chamber side end surface, 5 ... Direct intake port, 6 ... Helical intake port, 5a / 6a ... Port inlet, 5b
・ 6b ... Port outlet, C ... Center of cylinder chamber,
S 1 ... Vertical swirl, S 2 ... Horizontal swirl, θ ... Angle formed by both port outlets with respect to the center C of the cylinder chamber.
Claims (1)
シリンダ室(１)に対してダイレクト吸気ポート(５)とヘ
リカル吸気ポート(６)とをシリンダヘッド(２)に形成
し、各吸気ポート(５)・(６)のポート入り口(５ａ)・
(６ａ)をシリンダヘッド(２)の同じ横側面(３)に開口す
るとともに、各ポート出口(５ｂ)・(６ｂ)をシリンダ室
側端面(４)に開口し、 前記ダイレクト吸気ポート(５)のポート出口(５ｂ)と前
記ヘリカル吸気ポート(６)のポート出口(６ｂ)とを、シ
リンダ室(１)の中心(Ｃ)から略等距離に配置し、両ポー
ト出口(５ｂ)・(６ｂ)がシリンダ室(１)の中心(Ｃ)に対
してなす角(θ)が、略直角となるように配置して形成し
た直接噴射式ディーゼルエンジンのダブル吸気ポート式
吸気装置において、 前記ダイレクト吸気ポート(５)は、縦スワール(Ｓ1)を
発生する形状で、そのポート入り口(５ａ)からポート出
口(５ｂ)に向かう方向が、平面視でシリンダ室(１)の中
心(Ｃ)へ略直進状に向かう形状に形成し、 前記ヘリカル吸気ポート(６)は、横スワール(Ｓ2)を発
生する形状で、そのポート出口(６ｂ)は、上記シリンダ
室(１)の中心(Ｃ)から左右いずれかに偏位させて形成し
たことを特徴とする直接噴射式ディーゼルエンジンのダ
ブル吸気ポート式吸気装置。1. A direct intake port (5) and a helical intake port (6) are formed in a cylinder head (2) for one cylinder chamber (1) of a direct injection diesel engine, and each intake port (5) is formed. ) ・ (6) port entrance (5a) ・
(6a) is opened on the same lateral side (3) of the cylinder head (2), and each port outlet (5b) / (6b) is opened on the cylinder chamber side end face (4), and the direct intake port (5) The port outlet (5b) of the helical intake port (6) and the port outlet (6b) of the helical intake port (6) are arranged substantially equidistant from the center (C) of the cylinder chamber (1), and both port outlets (5b), (6b) ) With respect to the center (C) of the cylinder chamber (1), the double intake port type intake device of the direct injection type diesel engine is formed such that the angle (θ) is substantially right angle. The port (5) has a shape that generates a vertical swirl (S 1 ), and the direction from the port inlet (5a) to the port outlet (5b) is approximately the center (C) of the cylinder chamber (1) in plan view. The helical intake port (6) is formed in a straight shape so that a lateral swirl (S 2 ) is generated. A double intake port type intake device for a direct injection diesel engine, characterized in that its port outlet (6b) is formed to be displaced to the left or right from the center (C) of the cylinder chamber (1). .
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP4322786A JPH06146904A (en) | 1992-11-06 | 1992-11-06 | Double intake port type intake device of direct injection diesel engine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP4322786A JPH06146904A (en) | 1992-11-06 | 1992-11-06 | Double intake port type intake device of direct injection diesel engine |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH06146904A true JPH06146904A (en) | 1994-05-27 |
Family
ID=18147622
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP4322786A Pending JPH06146904A (en) | 1992-11-06 | 1992-11-06 | Double intake port type intake device of direct injection diesel engine |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH06146904A (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2011113742A1 (en) * | 2010-03-18 | 2011-09-22 | Avl List Gmbh | Cylinder head |
Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS58148229A (en) * | 1982-02-27 | 1983-09-03 | Hino Motors Ltd | Intake device of direct-injection diesel engine |
-
1992
- 1992-11-06 JP JP4322786A patent/JPH06146904A/en active Pending
Patent Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS58148229A (en) * | 1982-02-27 | 1983-09-03 | Hino Motors Ltd | Intake device of direct-injection diesel engine |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2011113742A1 (en) * | 2010-03-18 | 2011-09-22 | Avl List Gmbh | Cylinder head |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US4119071A (en) | Exhaust gas recirculating device in an internal combustion engine | |
| EP0824185B1 (en) | Direct fuel injection spark ignition engine | |
| EP0691470B1 (en) | Internal combustion engine and method for forming the combustion charge thereof | |
| US4702207A (en) | Intake arrangement for internal combustion engine | |
| USRE37289E1 (en) | Induction system for engine | |
| JPH09137727A (en) | Ignition control direct fuel injection internal combusion engine | |
| EP0137393B1 (en) | Intake arrangement for internal combustion engine | |
| JPH10317975A (en) | Direct cylinder injection spark ignition engine | |
| US4944266A (en) | Direct-injection diesel engine | |
| US5014662A (en) | Device for controlling the jet of carburetted mixture delivered by a pneumatic injection system | |
| JPH06146904A (en) | Double intake port type intake device of direct injection diesel engine | |
| JPH08135455A (en) | Intake control device for engine | |
| JP2501556Y2 (en) | Internal combustion engine intake system | |
| JPS61201826A (en) | Intake device of internal-combustion engine | |
| JP3644323B2 (en) | Direct-injection spark ignition internal combustion engine | |
| JPH0148379B2 (en) | ||
| JPH07208168A (en) | Combustion chamber of swirl type diesel engine | |
| JP3799800B2 (en) | engine | |
| JPS5968518A (en) | Combustion chamber for engine with pre-chamber | |
| KR100208489B1 (en) | Direct injection typed engine | |
| JPH0332771Y2 (en) | ||
| JPH07189699A (en) | Direct injection type combustion chamber device for diesel engine | |
| JPH10339220A (en) | Intake system of internal combustion engine | |
| JPS6098122A (en) | Suction valve gear for internal-combustion engine | |
| JPS61116066A (en) | Inlet device for fuel injection type engine |