JPS59218328A - Direct-injection type diesel engine - Google Patents
Direct-injection type diesel engineInfo
- Publication number
- JPS59218328A JPS59218328A JP58091425A JP9142583A JPS59218328A JP S59218328 A JPS59218328 A JP S59218328A JP 58091425 A JP58091425 A JP 58091425A JP 9142583 A JP9142583 A JP 9142583A JP S59218328 A JPS59218328 A JP S59218328A
- Authority
- JP
- Japan
- Prior art keywords
- combustion chamber
- squish
- diesel engine
- piston
- inclined surface
- 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
- F02B23/0618—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
- F02B23/0672—Omega-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 center 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
- 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
-
- 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
- F02F2001/244—Arrangement of valve stems in cylinder heads
- F02F2001/247—Arrangement of valve stems in cylinder heads the valve stems being orientated in parallel with the cylinder axis
-
- 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
Abstract
Description
【発明の詳細な説明】
[発明の技術分野1
本発明は直接噴射式ディーゼル機関に係り、特に燃焼室
内に生じる圧縮空気の渦流を効果的に形成して圧縮空気
と燃料との混合を促進し、燃料を完全燃焼させて出力及
びトルクの可及的向上を図るとともにスモーク、−酸化
炭素の排出低減に寄与し得る直接噴射式ディーゼル機関
に関するものである。Detailed Description of the Invention [Technical Field of the Invention 1] The present invention relates to a direct injection diesel engine, and in particular to a direct injection diesel engine that effectively forms a vortex of compressed air within a combustion chamber to promote mixing of compressed air and fuel. The present invention relates to a direct injection diesel engine that completely burns fuel to improve output and torque as much as possible, and also contributes to reducing smoke and carbon oxide emissions.
[発明の技術的背景とその問題点]
一般に直接噴射式ディーゼル機関にあっては、ビス1〜
ンが上死点付近に達したとき燃料が噴射ノズルから燃焼
室に直接噴射される。このとぎ、燃料と圧縮空気とを充
分に混合させるために、燃焼室に圧縮空気の渦流を生じ
させるように構成されている。即ち、第1図に示づ゛如
く、ピストンaの頭頂面すがその略中央に空洞状に陥没
され、且つその陥没部の底部Cの略中火に上方へ突出さ
れて突起部dが形成されて燃焼室eが構成されている。[Technical background of the invention and its problems] Generally, in a direct injection diesel engine, screws 1 to
When the engine reaches near top dead center, fuel is injected directly into the combustion chamber from the injection nozzle. At this time, in order to sufficiently mix the fuel and compressed air, the combustion chamber is configured to generate a vortex flow of compressed air. That is, as shown in FIG. 1, the top surface of the piston a is depressed into a hollow shape approximately at the center thereof, and the bottom C of the depression is projected upward to form a protrusion d. The combustion chamber e is configured by the combustion chamber e.
ところで、ピストンaがシリンダf内の空気を圧縮すべ
く上昇すると、シリンダ室すの径方向外方から内方へ向
って流れる圧縮空気流(以下、スキッシュと呼ぶ)と、
燃焼室e内で突起部dを略中心としてその周方向に沿っ
て流れ、平面的に旋回する圧縮空気の渦流(以下、スワ
ールと呼ぶ)とが生じ(このスワールは吸気ポートによ
って予め生成される〉、このスワールが生じているとこ
ろへ燃料が噴射ノズルhから噴射される。By the way, when the piston a rises to compress the air in the cylinder f, a compressed air flow (hereinafter referred to as squish) flows from the outside in the radial direction of the cylinder chamber to the inside.
In the combustion chamber e, a vortex of compressed air (hereinafter referred to as a swirl) that flows along the circumferential direction around the protrusion d and swirls in a plane is generated (this swirl is generated in advance by the intake port). >, fuel is injected from the injection nozzle h to the area where this swirl is occurring.
このようにして、燃焼室e内で燃料と圧縮空気とが充分
に混合するためには上述のスキッシュ及びスワールが重
要な要素として作用することになる。In this way, the above-mentioned squish and swirl act as important factors in order to sufficiently mix the fuel and compressed air within the combustion chamber e.
ここでスキッシュの発生状況を更に詳述すると、ピスト
ンaの上昇と共にシリンダ室9内の空気は圧縮されつつ
流動し、クランク角麿において上死点の前約10度でそ
の流速は最大となり、ピストンaの頭頂面すとシリンダ
ヘッドiの下端面jとの間の空隙でシリンダ室g内の径
方向外方から内方へ向って流動する。従ってスキッシュ
は丁度燃焼室eの上方で互いに衝突するがシリンダ室g
の軸方向への速度成分を持たないため、衝突後に燃焼室
e内へ方向転換されるスキッシュの流速を充分に高める
ことができない。よって、燃焼室e内での燃料と圧縮空
気との混合には、主にスワールのみが作用し、スキッシ
ュによる効果は充分に発揮されていなかった。このため
燃料の完全燃焼が充分に行われず、スモーク、−酸化炭
素等の排出量を充分に抑制できない。また出力及びトル
クを充分に得られない問題があった。To explain in more detail how squish occurs, the air in the cylinder chamber 9 is compressed and flows as the piston a rises, and the flow velocity reaches its maximum at about 10 degrees before the top dead center at the crank angle. It flows from the outside in the radial direction in the cylinder chamber g to the inside in the gap between the top surface of the cylinder head a and the lower end surface j of the cylinder head i. Therefore, the squish collide with each other just above the combustion chamber e, but the cylinder chamber g
Since the squish does not have a velocity component in the axial direction, it is not possible to sufficiently increase the flow velocity of the squish that is diverted into the combustion chamber e after the collision. Therefore, only the swirl mainly acts on the mixing of the fuel and compressed air in the combustion chamber e, and the effect of the squish is not sufficiently exhibited. For this reason, complete combustion of the fuel is not performed sufficiently, and the amount of smoke, carbon oxide, etc., emitted cannot be sufficiently suppressed. There was also the problem that sufficient output and torque could not be obtained.
また、第2図に示す如く燃焼室eの間口径を極端に絞り
、燃焼室e内に流入するスキッシュの流速を高める燃焼
室形状が知られ(いるが、この燃焼室形状にあっては燃
焼ガスが燃焼室eから膨張してシリンダ室g内へ流動す
るに際して熱損失が大きく、充分な出力が得られない問
題があった。Furthermore, as shown in Fig. 2, a combustion chamber shape is known in which the diameter of the combustion chamber e is extremely narrowed to increase the flow velocity of squish flowing into the combustion chamber e. When the gas expands from the combustion chamber e and flows into the cylinder chamber g, there is a problem in that heat loss is large and sufficient output cannot be obtained.
[発明の目的]
本発明は上述の如き問題点に鑑み、これらを有効に解決
すべく創案されたものである。[Object of the Invention] The present invention has been devised in view of the above problems and to effectively solve them.
本発明の目的は、燃焼室内に生じるスワールにスキッシ
ュによるシリンダの軸方向成分を合成して、立体的なト
ロイダルフロー(燃焼室内で上下方向に対流しながら周
方向に沿って環状に順次連続する螺旋旋回流)を形成す
ることにより圧縮空気と燃料との混合を促進し、燃料を
完全燃焼させて出力及びトルクの可及的向上を図ると共
にスモーク、−酸化炭素等の排出低減に寄与する直接噴
射式ディーゼル機関を提供することにある。The purpose of the present invention is to combine the axial component of the cylinder caused by the squish with the swirl generated within the combustion chamber to create a three-dimensional toroidal flow (a spiral that continues in an annular manner in the circumferential direction while convecting vertically within the combustion chamber). Direct injection that promotes the mixing of compressed air and fuel by forming a swirling flow, completely combusts the fuel, and improves output and torque as much as possible, while also contributing to reducing emissions of smoke, carbon oxide, etc. The objective is to provide a type diesel engine.
[発明の実施例]
以下に本発明の好適一実施例について添付図面に従って
説明する。[Embodiments of the Invention] A preferred embodiment of the present invention will be described below with reference to the accompanying drawings.
第3図は本発明に係る直接噴射式ディーゼル機関の燃焼
室を示すものである。FIG. 3 shows a combustion chamber of a direct injection diesel engine according to the present invention.
ピストン1の頭頂面2にはその略中火に陥没されて空洞
状に燃焼室3が形成されている。燃焼室3の底部4の略
中火には上方へ突出されて突起部5が形成されいる。A combustion chamber 3 is formed in the top surface 2 of the piston 1 in the shape of a cavity by recessing the piston 1 to a substantially medium extent. A protrusion 5 is formed on the bottom 4 of the combustion chamber 3 at a substantially medium flame level and protrudes upward.
燃焼室3の略中火に臨むシリンダヘッド6の下端面7は
に燃料噴射ノズル8がノズルチップ9を露出させている
。噴射ノズル8はシリンダヘッド6内に固定されており
、ノズルチップ8の周辺にはシリンダヘッド6の下端面
7にプラグ状に圧入されるスキッシュディフレクタ10
が設cノられてその外周部が周方向に沿って囲繞されて
いる。A fuel injection nozzle 8 has a nozzle tip 9 exposed on the lower end surface 7 of the cylinder head 6 facing the substantially medium flame of the combustion chamber 3. The injection nozzle 8 is fixed within the cylinder head 6, and around the nozzle tip 8 there is a squish deflector 10 that is press-fitted into the lower end surface 7 of the cylinder head 6 in the form of a plug.
is provided, and its outer periphery is surrounded along the circumferential direction.
スキッシュディフレクタ10はその周縁下端部に環状突
起部11が形成され、スキフシ1デイフレクタ10がシ
リンダヘッド6内に嵌装されるとその環状突起部11が
シリンダヘッド6の下端面7下に突出するように構成さ
れている。環状突起部11はその外周側面が下方へ窄め
られてテーパ状に成形され、この面に衝突するスキッシ
ュが下方へ方向転換されるように傾斜面12に成形さi
tている。The squish deflector 10 has an annular protrusion 11 formed at the lower end of its periphery, so that when the squish deflector 10 is fitted into the cylinder head 6, the annular protrusion 11 protrudes below the lower end surface 7 of the cylinder head 6. It is composed of The annular protrusion 11 is formed into a tapered shape with its outer peripheral side narrowed downward, and is formed into an inclined surface 12 so that squish colliding with this surface is deflected downward.
I'm here.
前述した燃焼室3内の突起部5の周側面13は、上記傾
斜面12により方向転換されたスキッシュがこれに沿っ
て流れて螺旋流となるように末広がりの曲線を外形線と
して描くように形成されて(Xる。The circumferential side surface 13 of the protrusion 5 in the combustion chamber 3 described above is formed to draw a curve that widens towards the end as an outline line so that the squish whose direction is changed by the inclined surface 12 flows along this to form a spiral flow. Been (Xru)
次に本発明の作用について説明する。Next, the operation of the present invention will be explained.
ピストン1の上昇に伴なってシリンダ室13内の空気は
圧縮されつつシリンダ室13の周縁部から中央部へ向っ
て流れ、スキッシュを形成する。As the piston 1 rises, the air in the cylinder chamber 13 is compressed and flows from the peripheral edge of the cylinder chamber 13 toward the center, forming a squish.
ピストン1の上昇と共にその流速は増大し、クランク角
度の上死点前約10度の位置でその流速が最大となる。The flow velocity increases as the piston 1 rises, and reaches its maximum at a position approximately 10 degrees before the top dead center of the crank angle.
スキッシュはスキッシュディフレクタ10の環状突起部
11に衝突し、その傾斜面12に沿って下方へ方向転換
されるがその流速は維持されたまま燃焼室3内に流入す
る。スキッシュは更に突起部5の周側面15に沿って下
降し燃焼室3の底部4から内側壁14に沿って上昇し上
下方向の対流を形成する。また燃焼室3内ではその周方
向に沿って平面的に旋回するスワールが形成されており
、スキッシュの鉛直面内成分とスワールの水平面内成分
とが合成され立体的なトロイダルフロー(螺旋旋回流)
が形成される。The squish collides with the annular protrusion 11 of the squish deflector 10 and is diverted downward along the inclined surface 12, but flows into the combustion chamber 3 while maintaining its flow velocity. The squish further descends along the circumferential side 15 of the protrusion 5 and rises from the bottom 4 of the combustion chamber 3 along the inner wall 14, forming vertical convection. In addition, a swirl is formed in the combustion chamber 3 that rotates in a plane along its circumferential direction, and the component in the vertical plane of the squish and the component in the horizontal plane of the swirl are combined to form a three-dimensional toroidal flow (helical swirling flow).
is formed.
トロイダルフローが形成された燃焼室3内に燃料が噴射
されると平面的なスワールに比して飛躍的に圧縮空気と
燃料との混合が促進されるので、燃料は完全燃焼し、ス
モーク、−酸化炭素等の発生は最小限に抑制される。。When fuel is injected into the combustion chamber 3 where a toroidal flow is formed, the mixing of compressed air and fuel is promoted dramatically compared to a flat swirl, so the fuel is completely combusted, resulting in smoke and - Generation of carbon oxide, etc. is suppressed to a minimum. .
また燃焼ガスは燃焼室3内からシリンダ室13へ容易に
膨部することができ熱損失も小さく高出力及び大トルク
が得られる。Furthermore, the combustion gas can easily expand from the inside of the combustion chamber 3 to the cylinder chamber 13, resulting in low heat loss and high output and large torque.
尚、第4図に示す如くシリンダヘッド6の下端面7を燃
焼室3の略中央上方へ漸次下降する緩やかな傾斜を持た
せた曲面形状に鋳造によって成形しても良い。Incidentally, as shown in FIG. 4, the lower end surface 7 of the cylinder head 6 may be formed by casting into a curved shape having a gentle slope that gradually descends toward the upper center of the combustion chamber 3.
し発明の効果]
以上の説明より明らかなように本発明によれば次の如き
優れた効果を発揮する。Effects of the Invention] As is clear from the above description, the present invention exhibits the following excellent effects.
(1)スキッシュとスワールとを効果的に合成すること
ができ燃焼室内に有効なトロイダルフローを形成するこ
とができる。(1) Squish and swirl can be effectively combined, and an effective toroidal flow can be formed within the combustion chamber.
(2)圧縮空気と燃料との混合を可及的に促進すること
ができる。(2) Mixing of compressed air and fuel can be promoted as much as possible.
(3)出力及びトルクの可及的向上が図れる。(3) Output and torque can be improved as much as possible.
(4)スモーク、−酸化炭素等の排出を低減できる。(4) Emissions of smoke, carbon oxide, etc. can be reduced.
(5)構造が簡単で容易に採用し得る。(5) The structure is simple and can be easily adopted.
第1図は直接噴射式ディーゼル機関の従来例を示す側断
面図、第2図は直接噴射式ディーゼル機関の他の従来例
を示す側断面図、第3図は本発明に係る直接噴射式ディ
ーゼル機関の一実施例を示す側断面図、第4図は本発明
に係る直接噴射式ディーゼル機関の他の一実施例を示す
側断面図である。
尚、図中1はピストン、2はその頭頂面、3は燃焼室、
4はその底部、・5は突起部、6はシリンダlベッド、
7はその下端面、11は環状突起部、12は傾斜面、1
3はシリンダ室である。
特許出願人 いすず自動車株式会社
代理人弁理士 絹 谷 信 雄FIG. 1 is a side sectional view showing a conventional example of a direct injection diesel engine, FIG. 2 is a side sectional view showing another conventional example of a direct injection diesel engine, and FIG. 3 is a direct injection diesel engine according to the present invention. FIG. 4 is a side sectional view showing another embodiment of the direct injection diesel engine according to the present invention. In the figure, 1 is the piston, 2 is its top surface, 3 is the combustion chamber,
4 is the bottom, 5 is the protrusion, 6 is the cylinder bed,
7 is its lower end surface, 11 is an annular projection, 12 is an inclined surface, 1
3 is a cylinder chamber. Patent applicant Nobuo Kinuya, patent attorney representing Isuzu Motors Co., Ltd.
Claims (2)
陥没部内略中央にその底部より上方へ突出される突起部
が形成される燃焼室を備え、上記ビス]・ンの頭頂面と
これに臨むシリンダヘッドの下端面どの間でシリンダ室
内の径方向外方より内方へ向って流動する圧縮空気流を
、上記燃焼室内の中央部へ向って方向変換させて上記渦
流を螺旋旋回流に形成させるために上記シリンダlペッ
ドの下端面に傾斜面を形成したことを特徴とする直接噴
射式ディーゼル機関。(1) The piston has a combustion chamber in which the top surface of the piston is depressed into a hollow shape, and a protrusion projecting upward from the bottom of the depression is formed approximately in the center of the depression; The direction of the compressed air flowing from the outside in the cylinder chamber toward the center of the combustion chamber is changed between the lower end surfaces of the cylinder head facing the cylinder head, and the vortex flow is turned into a spiral swirl flow. A direct injection type diesel engine, characterized in that a slope is formed on the lower end surface of the cylinder l ped to form an inclined surface.
ダヘッドの下端面より下方へ突出する環状突起部により
形成された上記特許請求の範囲第1項記載の直接噴射式
ディーゼル機関。(2) The direct injection diesel engine according to claim 1, wherein the inclined surface is formed by an annular projection projecting downward from the lower end surface of the cylinder head facing the center of the combustion chamber.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP58091425A JPS59218328A (en) | 1983-05-26 | 1983-05-26 | Direct-injection type diesel engine |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP58091425A JPS59218328A (en) | 1983-05-26 | 1983-05-26 | Direct-injection type diesel engine |
Publications (1)
Publication Number | Publication Date |
---|---|
JPS59218328A true JPS59218328A (en) | 1984-12-08 |
Family
ID=14026019
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP58091425A Pending JPS59218328A (en) | 1983-05-26 | 1983-05-26 | Direct-injection type diesel engine |
Country Status (1)
Country | Link |
---|---|
JP (1) | JPS59218328A (en) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP1241332A1 (en) * | 2001-03-16 | 2002-09-18 | Renault s.a.s. | Combustion chamber roof |
JP2013185455A (en) * | 2012-03-06 | 2013-09-19 | Mazda Motor Corp | Fuel injection valve, and internal combustion engine comprising the same |
-
1983
- 1983-05-26 JP JP58091425A patent/JPS59218328A/en active Pending
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP1241332A1 (en) * | 2001-03-16 | 2002-09-18 | Renault s.a.s. | Combustion chamber roof |
FR2822192A1 (en) * | 2001-03-16 | 2002-09-20 | Renault | HEAD ROOF |
JP2013185455A (en) * | 2012-03-06 | 2013-09-19 | Mazda Motor Corp | Fuel injection valve, and internal combustion engine comprising the same |
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