JPH063137B2 - Combustion chamber of internal combustion engine - Google Patents
Combustion chamber of internal combustion engineInfo
- Publication number
- JPH063137B2 JPH063137B2 JP61116175A JP11617586A JPH063137B2 JP H063137 B2 JPH063137 B2 JP H063137B2 JP 61116175 A JP61116175 A JP 61116175A JP 11617586 A JP11617586 A JP 11617586A JP H063137 B2 JPH063137 B2 JP H063137B2
- Authority
- JP
- Japan
- Prior art keywords
- combustion chamber
- fuel
- sub
- swirl
- auxiliary
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Lifetime
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
- F02B75/00—Other engines
- F02B75/12—Other methods of operation
- F02B2075/125—Direct injection in the combustion chamber for spark ignition engines, i.e. not in pre-combustion chamber
Landscapes
- Combustion Methods Of Internal-Combustion Engines (AREA)
- Fuel-Injection Apparatus (AREA)
- Ignition Installations For Internal Combustion Engines (AREA)
Description
【発明の詳細な説明】 ［産業上の利用分野］ 本発明は燃焼室内に燃料を直接噴射する内燃機関の燃焼
室に係り、特に燃料油としてガソリン，アルコール等の
低セタン価・揮発性燃料油を低温始動時を含むあらゆる
使用負荷運転領域で使用できる内燃機関の燃焼室に関す
る。Description: TECHNICAL FIELD The present invention relates to a combustion chamber of an internal combustion engine that directly injects fuel into a combustion chamber, and particularly to a low cetane number / volatile fuel oil such as gasoline or alcohol as fuel oil. The present invention relates to a combustion chamber of an internal combustion engine that can be used in any operating range of load including cold start.
［従来の技術］ 軽油をはじめガソリン，アルコール等の低セタン価・揮
発性燃料油を燃焼させることのできる内燃機関の燃焼室
としては本出願人の先の提案（特願昭59−210519号）の
直噴式ディーゼルエンジン燃焼室がある。[Prior Art] As a combustion chamber of an internal combustion engine capable of burning a low cetane number and volatile fuel oil such as light oil, gasoline, alcohol, etc., the applicant's previous proposal (Japanese Patent Application No. 59-210519). There is a direct injection diesel engine combustion chamber.
第４図に示すようにこの提案はピストン頂部ａに互いに
連通させて主燃焼室ｂと副燃焼室ｃとを並設し、それら
燃焼室内に燃料油を噴出する燃料噴射ノズルを配設して
直噴式ディーゼルエンジン燃焼室を構成するものであ
る。As shown in FIG. 4, in this proposal, a main combustion chamber b and a sub-combustion chamber c are arranged side by side in communication with each other at the piston top a, and a fuel injection nozzle for ejecting fuel oil is arranged in these combustion chambers. It constitutes a direct injection type diesel engine combustion chamber.
［発明が解決しようとする問題点］ ところが、上記の提案の上記副燃焼室ｃの中心はピスト
ンｅの軸心Ｏに対して偏心された位置におかれたため
に、副燃焼室ｃの中心とスワールポートからのスワール
S2の旋回中心O1とが一致されなくなって、実質的に副燃
焼室ｃのスワールS2は減衰されていた。したがってスワ
ールS2の求心力によって質量の軽いもの即ち燃料蒸気と
の混合気ｍを副燃焼室ｃの中心に分布させることが困難
になるため、例えばスパークプラグを配設しても着火し
にくい状態となっていた。ここでスパークプラグを副燃
焼室ｃの内壁ｄ近傍に位置させた場合にあっても、混合
気ｍは内壁ｄに沿って下流側に流れるため、スパークプ
ラグのプラグギャップ部（放電部）近傍に可燃性混合気
が存在される確率が低下し、そのギャップ部近傍がリー
ンとなり、失火しに陥ってしまうという問題があった。[Problems to be Solved by the Invention] However, since the center of the auxiliary combustion chamber c of the above proposal is placed at a position eccentric to the axis O of the piston e, the center of the auxiliary combustion chamber c is Swirl from swirl port
The swirl center O 1 of S 2 no longer coincides with the swirl S 2 of the sub-combustion chamber c, and the swirl S 2 is substantially damped. Therefore, it becomes difficult to distribute the light-mass substance, that is, the air-fuel mixture m with the fuel vapor, in the center of the auxiliary combustion chamber c by the centripetal force of the swirl S 2 , and it is difficult to ignite even if the spark plug is provided. Was becoming. Even when the spark plug is positioned near the inner wall d of the auxiliary combustion chamber c, the air-fuel mixture m flows to the downstream side along the inner wall d, so that it is near the plug gap part (discharge part) of the spark plug. There is a problem that the probability that the flammable air-fuel mixture exists is reduced, the vicinity of the gap becomes lean, and a misfire occurs.
［問題点を解決するための手段］ 本発明は上記問題点を解決することを目的としており、
その燃焼室中心をピストンの軸芯に一致させてピストン
頂部に浅く窪ませられて設けられた副燃焼室と、ピスト
ン頂部にその副燃焼室の外側にかつその副燃焼室に相隣
接させて深く窪ませて設けられその開口径及び容積が副
燃焼室に対して大きく形成された主燃焼室と、これら副
燃焼室及び主燃焼室を互いに区画する周側壁上部を半径
方向に開放させて設けられた連通部と、上記副燃焼室中
心にその点火部を位置させて設けられた点火手段と、上
記連通路に臨ませて設けられ上記主燃焼室及び副燃焼室
内に低セタン価・揮発性燃料をそれぞれ供給する燃料噴
射ノズルであって、機関のあらゆる使用負荷時に上記副
燃焼室の内壁にスワール方向に沿って濃噴霧層を生成す
ると共にその濃噴霧層の内側にスワール方向に沿って可
燃性混合気を生成すべく、副燃焼室内にそのスワールの
順方向でかつ副燃焼室の中心より外側の内壁へ向けて微
粒子化燃料を供給する副噴口及び低負荷を越えたときか
ら主燃料室の内壁にスワール方向に沿って噴霧層を生成
すると共にその噴霧層の内側にスワール方向に沿って可
燃性混合気を生成すべく、主燃焼室にそのスワールの順
方向でかつ主燃焼室の中心より外側の内壁へ向けて上記
微粒子化燃料より燃料の粒子径が大きい燃料噴霧を供給
する主噴口とを有する燃料噴射ノズルとを備えたもので
ある。[Means for Solving Problems] The present invention aims to solve the above problems,
The combustion chamber center is aligned with the axis of the piston, and the auxiliary combustion chamber is provided as a shallow depression at the top of the piston, and the piston top is deep outside the auxiliary combustion chamber and adjacent to the auxiliary combustion chamber. The main combustion chamber is formed in a recessed shape and has an opening diameter and a volume larger than that of the auxiliary combustion chamber, and an upper peripheral side wall that divides the auxiliary combustion chamber and the main combustion chamber from each other is opened in the radial direction. Communication part, ignition means provided with the ignition part located at the center of the auxiliary combustion chamber, and low cetane number / volatile fuel in the main combustion chamber and the auxiliary combustion chamber provided facing the communication passage. The fuel injection nozzles for supplying each of the above, which generate a rich spray layer along the swirl direction on the inner wall of the sub-combustion chamber at any load of the engine and are flammable inside the rich spray layer along the swirl direction. Generate a mixture Therefore, in the swirl direction in the sub-combustion chamber in the forward direction of the swirl and from the sub-injection port that supplies the atomized fuel toward the inner wall outside the center of the sub-combustion chamber and the low load Toward the inner wall of the main combustion chamber in the forward direction of the swirl and outside the center of the main combustion chamber to generate a spray layer along the swirl direction inside the spray layer and along the swirl direction. And a fuel injection nozzle having a main injection port for supplying a fuel spray having a larger particle size of the fuel than the atomized fuel.
［作用］ 上記構成により、低セタン価・揮発性燃料を使用して、
あらゆる使用負荷において副燃焼室の急速燃焼を達成さ
れ、また低負荷を越えたときに副燃焼室のみならず主燃
焼室でも急速燃焼を達成される。したがって、機関の負
荷に応じて燃費、出力が改善され、ＨＣ，スモークが改
善される。[Operation] With the above configuration, using a low cetane number and volatile fuel,
Rapid combustion of the auxiliary combustion chamber is achieved under any load, and rapid combustion is achieved not only in the auxiliary combustion chamber but also in the main combustion chamber when the load is exceeded. Therefore, fuel consumption and output are improved according to the load of the engine, and HC and smoke are improved.
［実施例］ 以下にこの発明の内面機関の燃焼室の好適一実施例を添
付図面に基づいて説明する。[Embodiment] A preferred embodiment of the combustion chamber of the internal combustion engine of the present invention will be described below with reference to the accompanying drawings.
第１図及び第２図に示す１は内燃機関のシリンダ（図示
せず）内に、そのシリンダに沿って往復動自在に収容さ
れるピストン、２はそのピストン１の頂面を形成するピ
ストン頂部、３は主燃焼室、４は副燃焼室である。1 and 2 are a piston 1 accommodated in a cylinder (not shown) of an internal combustion engine so as to be reciprocally movable along the cylinder, and 2 is a piston top portion forming a top surface of the piston 1. Reference numeral 3 is a main combustion chamber, and 4 is a sub combustion chamber.
図示されるようにピストン１のピストン頂部２にはその
ピストン１の幅方向に沿って主燃焼室３が窪まされて設
けられている。また、ピストン頂部２には、上記主燃焼
室３に並行に、副燃焼室４が窪まされて設けられてお
り、この実施例ではピストン１の軸芯Ｏを通る主燃焼室
３及び副燃焼室４の垂直断面は、共に円形の上部を截頭
された形状に、且つピストン頂部２に対して平行な水平
断面は、共に円形となるように形成される。As shown in the drawing, a main combustion chamber 3 is provided in the piston top portion 2 of the piston 1 along the width direction of the piston 1 so as to be recessed. In addition, a sub combustion chamber 4 is provided in the piston top 2 in parallel with the main combustion chamber 3, and in this embodiment, the main combustion chamber 3 and the sub combustion chamber passing through the axis O of the piston 1 are provided. The vertical cross sections of 4 are both formed so that the tops of both circles are truncated, and the horizontal cross sections parallel to the piston top 2 are both round.
窪み深さについては、副燃焼室４が主燃焼室３に対して
浅く窪まされ、容積については、副燃焼室４の容積が主
燃焼室３の容積に対して小さく形成されている。主燃焼
室３と副燃焼室４との間で互いに共有する周側壁を成す
バンク部５には、そのバンク部５の上部に、主燃焼室３
と副燃焼室４とを連通する連通路７が形成される。Regarding the depth of the depression, the auxiliary combustion chamber 4 is shallowly depressed with respect to the main combustion chamber 3, and regarding the volume, the volume of the auxiliary combustion chamber 4 is formed smaller than the volume of the main combustion chamber 3. The main combustion chamber 3 and the sub-combustion chamber 4 have a bank portion 5 forming a peripheral side wall shared by each other.
A communication passage 7 that communicates with the sub combustion chamber 4 is formed.
ここで副燃焼室４はピストン１の軸芯Ｏに対して副燃焼
室４の中心O1が略一致し且つ、シリンダ内へのスワール
S 1の中心がその副燃焼室４の中心O1と一致される位置に
形成される。したがって副燃焼室４に対して主燃焼室３
はピストン１の外周側に形成される。Here, the auxiliary combustion chamber 4 is an auxiliary combustion with respect to the axis O of the piston 1.
Center O of room 41And the swirl into the cylinder
S The center of 1 is the center O of the auxiliary combustion chamber 4.1In a position that is matched with
It is formed. Therefore, the main combustion chamber 3 with respect to the auxiliary combustion chamber 4
Is formed on the outer peripheral side of the piston 1.
この実施例にあってその連通路７は、バンク部５の上部
に形成されて互いを各燃焼室３，４の略中心方向に沿っ
て連通する切欠溝となっている。In this embodiment, the communication passage 7 is a notch groove formed in the upper portion of the bank portion 5 and communicating with each other along substantially the center direction of each combustion chamber 3, 4.
以上のように、ピストン頂部２には、互いに連通され
て、上部が開放された主燃焼室３と副燃焼室４が並設さ
れる。またこれら主燃焼室３及び副燃焼室４には、開口
上部に、その上部開口縁９ａ，９ｂに沿って半径方向内
方に適宜突出され各燃焼室３，４内にそれぞれ独立した
スワールS1，S2とスキッシュとを生成するためのリップ
部２５ａ，２５ｂが形成されている。As described above, the main combustion chamber 3 and the sub-combustion chamber 4, which are in communication with each other and whose upper portions are open, are arranged in parallel on the piston top 2. In addition, in the main combustion chamber 3 and the auxiliary combustion chamber 4, swirls S 1 which are independently projected in the combustion chambers 3 and 4 are appropriately projected inward in the radial direction along the upper opening edges 9a and 9b. , S 2 and squish are formed with lip portions 25a, 25b.
燃料噴射ノズルは、この実施例では例えば第３図の形式
が採用される。In this embodiment, the fuel injection nozzle is of the type shown in FIG. 3, for example.
図示されるようにノズルボディ１３の先端に、針弁１５
のスロットル部１８が着座される弁座１４を形成し、そ
の弁座１４より先端側に向って軸方向へ***され、上記
スロットル部１８の動作によって燃料油室（図示せず）
との連通が開閉される燃料噴射室２０を形成し、上記弁
座１４に極細直径の副噴口１６が、上記燃料噴射室２０
に主噴口１７が開口されて構成されている。As illustrated, the needle valve 15 is attached to the tip of the nozzle body 13.
Forming a valve seat 14 on which the throttle portion 18 is seated, and is raised in the axial direction from the valve seat 14 toward the tip end side, and the fuel oil chamber (not shown) is operated by the operation of the throttle portion 18.
A fuel injection chamber 20 that is opened and closed in communication with the fuel injection chamber 20.
The main injection port 17 is opened in the.
この燃料噴射ノズル１２は、共に針弁１５のリフト値が
所定値に至るまでは副噴口１６のみを開放し、そのリフ
ト値を越えたときに、副噴口１６と主噴口１７とを開放
するように構成される。いいかえれば主噴口１７に対し
て副噴口１６が先行して開放されるように構成された、
いわゆるピントークスタイプのものとなっている。In this fuel injection nozzle 12, only the sub injection port 16 is opened until the lift value of the needle valve 15 reaches a predetermined value, and when the lift value is exceeded, the sub injection port 16 and the main injection port 17 are opened. Is composed of. In other words, the sub nozzle 16 is configured to be opened prior to the main nozzle 17,
It is a so-called Pintox type.
さて燃料噴射ノズル１２は、第１図乃至第２図にも示す
ように、噴口側が上記連通路７に臨んでシリンダヘッド
（図示せず）に一体的に配設されており、副噴口１６が
副燃焼室４内に、主噴口１７が主燃焼室３内に臨ませら
れている。副燃焼室４内にはその略中央位置にスパーク
プラグ３０のプラグギャップ部ＰGが収容されており、
そのスパークプラグ３０は、シリンダヘッド１０に一体
的に収容されている。As shown in FIGS. 1 and 2, the fuel injection nozzle 12 is disposed integrally with a cylinder head (not shown) with the injection port side facing the communication passage 7, and the auxiliary injection port 16 is provided. A main injection port 17 faces the main combustion chamber 3 in the sub combustion chamber 4. A plug gap portion PG of the spark plug 30 is housed in the auxiliary combustion chamber 4 at a substantially central position thereof.
The spark plug 30 is integrally housed in the cylinder head 10.
また燃料噴射ノズル１２の副噴口１６は上記プラグギャ
ップＰGの近傍または、そのプラグギャップＰGに対して
スワールS2の上流側に臨ませられている。The auxiliary injection port 16 of the fuel injection nozzle 12 faces the vicinity of the plug gap PG or the upstream side of the swirl S 2 with respect to the plug gap PG.
以下に本発明の内燃機関の燃焼室の作用を添付図面に基
づいて説明する。The operation of the combustion chamber of the internal combustion engine of the present invention will be described below with reference to the accompanying drawings.
第１図，第２図に示すようにスワールポート（図示せ
ず）から供給される燃焼用空気のスワールは、ピストン
１の上死点位置にあっても角運動量が保存されて主燃焼
室３及び副燃焼室４のそれぞれの内壁３ａ，４ａに沿っ
て独立したスワールS1，S2となる。As shown in FIGS. 1 and 2, the swirl of the combustion air supplied from the swirl port (not shown) retains its angular momentum even at the top dead center position of the piston 1 and maintains the main combustion chamber 3 And independent swirls S 1 and S 2 along the inner walls 3a and 4a of the auxiliary combustion chamber 4, respectively.
内燃機関の始動時及びアイドリング時を含む軽負荷運転
領域では、第３図にも示す針弁１５が所定リフト値以下
のため、副噴口１６のみが開放される。副噴口１６が開
放されると副燃焼室４の内壁４ａに向けて燃料粒子径の
極めて小さな低セタン価・揮発性燃料油の微粒化燃料噴
霧f1が噴出される。この微粒化燃料噴霧f1は、副燃焼室
４の内壁４ａに衝突させられることによって、その一部
がさらに微粒化されて飛散し、圧縮空気の熱によって瞬
時のうちに蒸気化して空気を混合しスワールS2の下流側
へ流れる可燃性混合気m1となり、残部は副燃焼室４の内
壁４ａに沿うように下流側へ蒸発しながら流される噴霧
層F1となる。このとき副燃焼室４の中心O1とピストン１
の軸芯Ｏは一致され且つスワールS2の中心と副燃焼室４
の中心O1が一致されて形成されることにより、スワール
S2はピストン１の軸芯Ｏを中心とする求心力をもつこと
になる。この求心力によって、質量の軽いものは副燃焼
室４の中心O1に集まり反対に重いものは副燃焼室４の内
壁４ａ側に集められるからリッチな噴霧層F1の燃料蒸気
は、スワールの生成されないものに比較して副燃焼室４
の中心O1側へ集められる。ゆえに副燃焼室４の中心O1近
傍には、着火しやすい可燃性混合気m1が多く分布される
ことになり、このことはスパークプラグ３０のプラグギ
ャップ（放電部）ＰGに可燃性混合気m1を存在させる確
率を高め、スワールS2により副燃焼室４の中心O1へ集め
られる。即ち点火と同時に確実に急速燃焼が行なわれ、
この燃焼によって副燃焼室４の内壁４ａ側に分布された
噴霧層F1に火炎伝播される。ここで低温始動時にあって
の針弁１５は、スタータによる内燃機関駆動時の噴射ポ
ンプの回転数が50rpm〜150rpmに設定される、いわゆる
過剰供給状態（全負荷時よりも多い状態）にありながら
燃料流速が極低速のために、副噴口１６のみを開放させ
る低いリフト値に保つことができる。これにより副燃焼
室４内には、微粒化燃料噴霧f1を多量に供給することが
できる。したがって燃焼があらゆる使用負荷運転領域で
あっても急速にでき、これによって燃焼平均温度が上昇
されることになるから、スモーク，青白煙，HCそして未
燃メタノール，アルデヒドの排出を大巾に低減し且つ燃
焼騒音を低減することができる。In the light load operation region including the start-up and idling of the internal combustion engine, the needle valve 15 shown in FIG. 3 is equal to or less than the predetermined lift value, so only the auxiliary injection port 16 is opened. When the sub injection port 16 is opened, the atomized fuel spray f 1 of low cetane number and volatile fuel oil having an extremely small fuel particle diameter is ejected toward the inner wall 4a of the sub combustion chamber 4. When the atomized fuel spray f 1 is collided with the inner wall 4a of the auxiliary combustion chamber 4, a part of the atomized fuel spray f 1 is further atomized and scattered, and is instantly vaporized by the heat of the compressed air to mix the air. Then, the combustible mixture m 1 flowing downstream of the swirl S 2 is formed, and the remaining portion becomes a spray layer F 1 that flows along the inner wall 4a of the auxiliary combustion chamber 4 while being evaporated downstream. At this time, the center O 1 of the auxiliary combustion chamber 4 and the piston 1
The axes O of the sub-combustion chamber 4 are aligned with the center of the swirl S 2
The swirl of the center O 1 of the
S 2 has a centripetal force centered on the axis O of the piston 1. Due to this centripetal force, those having a light mass gather at the center O 1 of the auxiliary combustion chamber 4 and those having a heavy mass conversely gather on the inner wall 4a side of the auxiliary combustion chamber 4, so the fuel vapor in the rich spray layer F 1 produces swirl. Sub-combustion chamber 4 compared to those not
Centered on the O 1 side of. Therefore, in the vicinity of the center O 1 of the auxiliary combustion chamber 4, a large amount of combustible air-fuel mixture m 1 which is easy to ignite is distributed, which means that the flammable air-fuel mixture is present in the plug gap (discharge part) PG of the spark plug 30. The probability that m 1 will be present is increased, and it is collected in the center O 1 of the auxiliary combustion chamber 4 by the swirl S 2 . That is, the rapid combustion is surely performed at the same time as the ignition,
By this combustion, flame is propagated to the spray layer F 1 distributed on the inner wall 4a side of the auxiliary combustion chamber 4. Here, the needle valve 15 at the time of cold start is in the so-called excessive supply state (state more than at full load) in which the rotation speed of the injection pump when the internal combustion engine is driven by the starter is set to 50 rpm to 150 rpm. Since the fuel flow velocity is extremely low, it is possible to maintain a low lift value that opens only the auxiliary injection port 16. As a result, a large amount of atomized fuel spray f 1 can be supplied into the auxiliary combustion chamber 4. Therefore, combustion can be performed rapidly even in all operating areas under heavy load, which raises the average combustion temperature, which significantly reduces the emission of smoke, blue-white smoke, HC and unburned methanol and aldehyde. In addition, combustion noise can be reduced.
針弁１５のリフト値が所定リフト値を越える中・高負荷
運転領域では、副噴口１６のみならず主噴口１７も開放
される。In the medium / high load operation region in which the lift value of the needle valve 15 exceeds the predetermined lift value, not only the auxiliary injection port 16 but also the main injection port 17 is opened.
第１図及び第２図に示すように、主噴口１７からの燃料
噴霧f2は副噴口１６からの微粒化燃料噴霧f1よりも飛翔
距離が長く、且つ噴射に際する拡散面積が大きくなって
いる。この燃料噴霧f2は一部が主燃焼室３の内壁３ａに
衝突されることで微粒化され残部が主燃焼室３の内壁３
ａに沿ってスワール方向下流側へ末広がりとなって流れ
る噴霧層F2となる。微粒化された燃料噴霧f2は圧縮空気
熱及び連通路７を介しての副燃焼室４の火炎エネルギに
て可燃性混合気m2になり、噴霧層F2も圧縮空気熱及び壁
熱とにより蒸気化され可燃性混合気m2になる。これらの
可燃性混合気m2は連通路７を介して副燃焼室４の火炎を
伝播されて比較的急速な燃焼が行われ、噴霧層F2を蒸発
燃焼させることができる。As shown in FIG. 1 and FIG. 2, the fuel spray f 2 from the main injection port 17 has a longer flight distance than the atomized fuel spray f 1 from the sub injection port 16 and the diffusion area at the time of injection becomes large. ing. A part of this fuel spray f 2 is atomized by colliding with the inner wall 3 a of the main combustion chamber 3, and the rest is the inner wall 3 of the main combustion chamber 3.
A spray layer F 2 that spreads toward the downstream side in the swirl direction along a. The atomized fuel spray f 2 becomes a combustible mixture m 2 due to the compressed air heat and the flame energy of the auxiliary combustion chamber 4 via the communication passage 7, and the spray layer F 2 also becomes the compressed air heat and the wall heat. Is vaporized into a flammable mixture m 2 . The flammable mixture m 2 is propagated through the flame of the auxiliary combustion chamber 4 through the communication passage 7 and relatively rapidly burns, so that the spray layer F 2 can be vaporized and burned.
［発明の効果］ 以上説明したことから明らかなように本発明の内燃機関
の燃焼室によれば次の如き優れた効果を発揮できる。[Effects of the Invention] As is apparent from the above description, the combustion chamber of the internal combustion engine of the present invention can exhibit the following excellent effects.
副燃焼室に減衰されることのないスワールを生成でき、
そのスワールによって低セタン価・揮発性燃料油のガス
及び可燃性混合気が副燃焼室の中心側に集められるた
め、副燃焼室での急速燃焼が達成される。そして副燃焼
室で生成した火炎が主燃焼室へ伝播されるため両燃焼室
において良好な燃焼を達成できる。It can generate swirls that are not damped in the auxiliary combustion chamber,
Due to the swirl, the gas of low cetane number and volatile fuel oil and the combustible air-fuel mixture are collected on the center side of the auxiliary combustion chamber, so that the rapid combustion in the auxiliary combustion chamber is achieved. Then, since the flame generated in the auxiliary combustion chamber is propagated to the main combustion chamber, good combustion can be achieved in both combustion chambers.
燃費、出力を改善でき、ＨＣ、スモーク、青白煙ならび
に未燃メタノール、アルデヒドの排出量を減少させるこ
とができる。Fuel consumption and output can be improved, and emissions of HC, smoke, blue and white smoke, and unburned methanol and aldehyde can be reduced.
第１図は本発明の内燃機関の燃焼室の好適一実施例を示
す平面図、第２図は第１図のＩＩ−ＩＩ線矢視断面図、
第３図は燃料噴射ノズルを示す部分断面図、第４図は従
来の直噴式ディーゼルエンジン燃焼室を示す概略図であ
る。 図中、１はピストン、２はピストン頂部、３は主燃焼
室、４は副燃焼室、１２は燃料噴射ノズル、１６は副噴
口、１７は主噴口、３０はスパークプラグである。1 is a plan view showing a preferred embodiment of a combustion chamber of an internal combustion engine of the present invention, FIG. 2 is a sectional view taken along the line II-II of FIG.
FIG. 3 is a partial sectional view showing a fuel injection nozzle, and FIG. 4 is a schematic view showing a conventional direct injection type diesel engine combustion chamber. In the drawing, 1 is a piston, 2 is a piston top part, 3 is a main combustion chamber, 4 is a sub combustion chamber, 12 is a fuel injection nozzle, 16 is a sub injection port, 17 is a main injection port, and 30 is a spark plug.
Claims (1)
せてピストン頂部に浅く窪ませられて設けられた副燃焼
室と、ピストン頂部にその副燃焼室の外側にかつその副
燃焼室に相隣接させて深く窪ませて設けられその開口径
及び容積が副燃焼室に対して大きく形成された主燃焼室
と、これら副燃焼室及び主燃焼室を互いに区画する周側
壁上部を半径方向に開放させて設けられた連通路と、上
記副燃焼室中心にその点火部を位置させて設けられた点
火手段と、上記連通路に臨ませて設けられ上記主燃焼室
及び副燃焼室内に低セタン価・揮発性燃料をそれぞれ供
給する燃料噴射ノズルであって、機関のあらゆる使用負
荷時に上記副燃焼室の内壁にスワール方向に沿って濃噴
霧層を生成すると共にその濃噴霧層の内側にスワール方
向に沿って可燃性混合気を生成すべく、副燃焼室内にそ
のスワールの順方向でかつ副燃焼室の中心より外側の内
壁へ向けて微粒子化燃料を供給する副噴口及び低負荷を
越えたときから主燃焼室の内壁にスワール方向に沿って
噴霧層を生成すると共にその噴霧層の内側にスワール方
向に沿って可燃性混合気を生成すべく、主燃焼室内にそ
のスワールの順方向でかつ主燃焼室の中心より外側の内
壁へ向けて上記微粒子化燃料より燃料の粒子径が大きい
燃料噴霧を供給する主噴口とを有する燃料噴射ノズルと
を備えたことを特徴とする内燃機関の燃焼室。1. A sub-combustion chamber provided with a shallow depression in the top of the piston, with the center of the combustion chamber aligned with the axis of the piston, and at the top of the piston, outside the sub-combustion chamber and in the sub-combustion chamber. The main combustion chamber, which is provided so as to be adjacent to each other and deeply depressed and whose opening diameter and volume are formed larger than the auxiliary combustion chamber, and the upper part of the peripheral side wall that divides the auxiliary combustion chamber and the main combustion chamber from each other in the radial direction An open communication passage, an ignition means having its ignition portion located at the center of the auxiliary combustion chamber, and a low cetane in the main combustion chamber and the auxiliary combustion chamber that are provided so as to face the communication passage. It is a fuel injection nozzle that supplies valence and volatile fuel respectively, and generates a rich spray layer along the swirl direction on the inner wall of the auxiliary combustion chamber at any load of the engine and swirl direction inside the rich spray layer. Flammable along In order to generate aeration, in the swirl forward direction in the sub-combustion chamber and toward the inner wall outside the center of the sub-combustion chamber, the sub-injection port that supplies atomized fuel and the low combustion load In order to generate a spray layer along the swirl direction on the inner wall and a flammable mixture inside the spray layer along the swirl direction, in the main combustion chamber in the forward direction of the swirl and from the center of the main combustion chamber. A combustion chamber of an internal combustion engine, comprising: a fuel injection nozzle having a main injection port that supplies a fuel spray having a larger particle size of fuel than the atomized fuel toward the outer inner wall.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP61116175A JPH063137B2 (en) | 1986-05-22 | 1986-05-22 | Combustion chamber of internal combustion engine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP61116175A JPH063137B2 (en) | 1986-05-22 | 1986-05-22 | Combustion chamber of internal combustion engine |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS62276216A JPS62276216A (en) | 1987-12-01 |
| JPH063137B2 true JPH063137B2 (en) | 1994-01-12 |
Family
ID=14680649
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP61116175A Expired - Lifetime JPH063137B2 (en) | 1986-05-22 | 1986-05-22 | Combustion chamber of internal combustion engine |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH063137B2 (en) |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5915353A (en) * | 1997-05-21 | 1999-06-29 | Nissan Motor Co., Ltd | Cylinder direct injection spark-ignition engine |
| US7695275B2 (en) | 2004-06-02 | 2010-04-13 | Fuel Management, Inc. | Air:fluid distribution system and method |
Family Cites Families (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5430482U (en) * | 1977-07-30 | 1979-02-28 | ||
| JPS589922U (en) * | 1981-07-13 | 1983-01-22 | 日産自動車株式会社 | direct injection diesel engine |
| JPS59196521U (en) * | 1983-06-14 | 1984-12-27 | トヨタ自動車株式会社 | direct injection internal combustion engine |
| JPS6011626A (en) * | 1983-06-29 | 1985-01-21 | Fuji Heavy Ind Ltd | Combustion chamber for split combustion type engine |
-
1986
- 1986-05-22 JP JP61116175A patent/JPH063137B2/en not_active Expired - Lifetime
Also Published As
| Publication number | Publication date |
|---|---|
| JPS62276216A (en) | 1987-12-01 |
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