JPS6316123A - Internal combustion engine - Google Patents
Internal combustion engineInfo
- Publication number
- JPS6316123A JPS6316123A JP15797386A JP15797386A JPS6316123A JP S6316123 A JPS6316123 A JP S6316123A JP 15797386 A JP15797386 A JP 15797386A JP 15797386 A JP15797386 A JP 15797386A JP S6316123 A JPS6316123 A JP S6316123A
- Authority
- JP
- Japan
- Prior art keywords
- swirl
- fuel
- combustion chamber
- internal combustion
- normal flow
- 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.)
- Granted
Links
- 238000002485 combustion reaction Methods 0.000 title claims abstract description 51
- 239000000446 fuel Substances 0.000 claims abstract description 27
- 239000007921 spray Substances 0.000 claims description 8
- 238000002347 injection Methods 0.000 abstract description 14
- 239000007924 injection Substances 0.000 abstract description 14
- 239000003595 mist Substances 0.000 abstract 2
- 238000010586 diagram Methods 0.000 description 3
- 230000000694 effects Effects 0.000 description 3
- UFHFLCQGNIYNRP-UHFFFAOYSA-N Hydrogen Chemical compound [H][H] UFHFLCQGNIYNRP-UHFFFAOYSA-N 0.000 description 1
- 238000003763 carbonization Methods 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 239000007789 gas Substances 0.000 description 1
- 239000001257 hydrogen Substances 0.000 description 1
- 229910052739 hydrogen Inorganic materials 0.000 description 1
- 239000000203 mixture Substances 0.000 description 1
Abstract
Description
【発明の詳細な説明】
〔発明の技術分野〕
本発明は、主として層状給気式の往復動型の内燃機関に
関し、詳しくは低負荷時及び高負荷時にも良好な燃焼の
得られる主燃焼室を有する内燃機関に関するものである
。Detailed Description of the Invention [Technical Field of the Invention] The present invention mainly relates to a stratified air supply type reciprocating internal combustion engine, and more specifically, to a main combustion chamber that provides good combustion even under low load and high load. The invention relates to an internal combustion engine having a
ピストン頂部に主燃焼室を形成した層状給気式の往復動
型の内燃機関において、第4図の従来例に示すごとく、
ピストンの頂部に設けられた主燃焼室7内に燃料噴射弁
8からの2本の燃料噴霧を矢印Fのごとく噴射する場合
、これら2本の燃料噴霧Fを主燃焼室7の空気旋回流で
あるスワールSの順流にそって噴射した場合、その内燃
機関の最低燃費と最大出力とは良好であるが、低負荷の
燃焼安定性と排気エミッションとが悪化するという問題
がある。In a stratified air supply type reciprocating internal combustion engine with a main combustion chamber formed at the top of the piston, as shown in the conventional example in Fig. 4,
When two fuel sprays from the fuel injection valve 8 are injected into the main combustion chamber 7 provided at the top of the piston as shown by the arrow F, these two fuel sprays F are injected into the main combustion chamber 7 by the air swirl flow. When injecting along the forward flow of a certain swirl S, the minimum fuel consumption and maximum output of the internal combustion engine are good, but there is a problem that low-load combustion stability and exhaust emissions deteriorate.
一方、第5図の従来例に示すごとく、燃料噴霧Fをスワ
ールSの順流に対向して噴霧した場合、即ち、スワール
逆流噴射の場合には、微量噴射の場合も良好な混合気が
形成され、着火が安定し、排気エミッション中の未燃燃
料も減少し、低負荷燃焼は改善され、良好な燃焼性能が
得られるが、この場合、大出力時に空気利用率が低下す
るため、最大出力と最低燃費とが悪化するという問題が
ある。On the other hand, as shown in the conventional example shown in Fig. 5, when the fuel spray F is sprayed against the forward flow of the swirl S, that is, in the case of swirl backflow injection, a good air-fuel mixture is not formed even in the case of small amount injection. , ignition is stabilized, unburned fuel in exhaust emissions is reduced, low-load combustion is improved, and good combustion performance is obtained, but in this case, the air utilization rate decreases at high power, so There is a problem that the minimum fuel consumption is deteriorated.
本発明は前記従来の問題点を解消するためになされたも
のであり、主燃焼室内のスワールに対し逆流方向に燃料
噴霧を噴射した場合の着火安定性及び良好な排気エミッ
ションの長所を生しながら、最大出力増大と最低燃費の
低減をはかりうる内燃機関を提供することを目的とした
ものである。The present invention has been made to solve the above-mentioned conventional problems, and has the advantages of ignition stability and good exhaust emissions when fuel spray is injected in a direction opposite to the swirl in the main combustion chamber. The purpose of this invention is to provide an internal combustion engine that can increase maximum output and reduce minimum fuel consumption.
上記の目的を達成するため、本発明の内燃機関はピスト
ン頂部に形成した主燃焼室内に燃料噴霧を噴射する噴口
を、スワール順流及びスワール逆流にそれぞれ対向する
2方向に形成すると共に、スワール順流に対向する噴口
径を他の方向の噴口径よりも小さくすることにより構成
される。In order to achieve the above object, the internal combustion engine of the present invention has nozzles for injecting fuel spray into the main combustion chamber formed at the top of the piston in two directions opposite to the swirl forward flow and the swirl reverse flow, and also in the swirl forward flow. It is constructed by making the opposing nozzle diameter smaller than the nozzle diameter in the other direction.
以下図面を参照して本発明の詳細な説明するが、第1図
は本発明の一実施例における内燃機関の燃焼室の要部断
面で示す平面図、第2図は第1図のn−n方向の樅断面
図、第3図は第1図の主燃焼室内のスワールを示す要部
平面図である。The present invention will be described in detail below with reference to the drawings. FIG. 1 is a plan view showing a cross section of a main part of a combustion chamber of an internal combustion engine in an embodiment of the present invention, and FIG. FIG. 3 is a cross-sectional view of the fir tree in the n direction, and a plan view of the main part showing the swirl inside the main combustion chamber of FIG. 1.
まず、この内燃機関の燃焼室は第1図及び第2図に示す
ごとく、シリンダ内を上下に往復動するピストン10頂
部に半径Rの凹状の球面部とシリンダヘッド2の下面と
からなる主燃焼室7を形成し、この主燃焼室7に対して
切欠き11を介して開口した点火室10内に燃料噴射弁
8及び点火プラグ9を設けている。First, as shown in Figs. 1 and 2, the combustion chamber of this internal combustion engine consists of a concave spherical part with a radius R at the top of a piston 10 that reciprocates up and down within the cylinder, and a main combustion chamber consisting of a bottom surface of the cylinder head 2. A fuel injection valve 8 and a spark plug 9 are provided in an ignition chamber 10 which forms a chamber 7 and is open to the main combustion chamber 7 through a notch 11 .
また、この燃焼室には吸気弁6を有する吸気ポート5が
ら空気を導入し、矢印Sで示すごとき空気旋回流、即ち
、スワール順流を発生させるようになっており、主燃焼
室7内に燃料噴霧Fを噴射し、着火させ、燃焼後の排気
ガスを排気弁4を有する排気ボート3から排出するよう
にしている。In addition, air is introduced into this combustion chamber through an intake port 5 having an intake valve 6 to generate an air swirling flow as shown by arrow S, that is, a swirl forward flow, so that the fuel flows into the main combustion chamber 7. The spray F is injected and ignited, and the exhaust gas after combustion is discharged from an exhaust boat 3 having an exhaust valve 4.
そこで、燃料噴射弁8の先端に2個の噴口8A、8Bを
設け、それらの噴口8A、8.Bから点火室10を通し
て主燃焼室7内にそれぞれ噴射する燃料噴霧F1.F2
を、第3図に示すごとくスワールSの順流に対向する燃
料噴霧F+及びスワールSの逆流に対向する燃料噴霧F
2の2方向にするように各噴口8A、8Bを2方向に形
成している。Therefore, two nozzle ports 8A, 8B are provided at the tip of the fuel injection valve 8, and these nozzle ports 8A, 8. B injected into the main combustion chamber 7 through the ignition chamber 10, respectively. F2
As shown in FIG.
Each nozzle 8A, 8B is formed in two directions so as to have two directions.
更に、上記の2つの噴口8A、8Bにおいて、噴口8A
の噴口径が噴口8Bよりも小さくなるように形成してい
る。Furthermore, in the two nozzles 8A and 8B, the nozzle 8A
The nozzle diameter of the nozzle 8B is smaller than that of the nozzle 8B.
即ち、例えば第4図及び第5図の各従来例における燃料
噴iF用の各噴口径を0.4mmとすると、第3図の本
発明の場合の噴口8Aの噴口径を0.35mm、噴口8
Bの噴口径を0.45 mmとしている。That is, for example, if the diameter of each nozzle port for fuel injection iF in each of the conventional examples shown in FIGS. 4 and 5 is 0.4 mm, the diameter of the nozzle port 8A in the case of the present invention shown in FIG. 8
The nozzle diameter of B is 0.45 mm.
以上に説明した第1図の本発明の実施例における燃焼室
を有する内燃機関ならびに第4図及び第5図の各従来例
の燃焼室を有する内燃機関において、それぞれ正味平均
有効圧力と、全炭化水素(THC)即ち、排気エミッシ
ョンの状態、燃焼安定性ならびに燃料消費率との関係を
第6図の各線図で示しており、第1図の本発明の場合を
一点鎖線のAで、第4図の従来例の場合を実線Bで、そ
して第5図の従来例の場合を破線Cでそれぞれ示してい
る。In the internal combustion engine having the combustion chamber according to the embodiment of the present invention shown in FIG. 1 and the conventional combustion chamber shown in FIGS. 4 and 5 described above, the net average effective pressure and the total carbonization The relationship between hydrogen (THC), that is, the state of exhaust emissions, combustion stability, and fuel consumption rate, is shown in each diagram in FIG. 6. The case of the present invention in FIG. The case of the conventional example in the figure is shown by a solid line B, and the case of the conventional example in FIG. 5 is shown by a broken line C, respectively.
これらの線図から判るように、本発明を採用した内燃機
関では低負荷及び高負荷ともに燃焼が良好になる。As can be seen from these diagrams, the internal combustion engine employing the present invention has good combustion under both low and high loads.
以上に説明したように、本発明の内燃機関では、スワー
ルに対し逆流方向に燃料噴射した場合の着火安定性及び
良好な排気エミッションの長所を生かしながら、最大出
力増大と最低燃費の低減をはかりうるという利点がある
。As explained above, in the internal combustion engine of the present invention, it is possible to increase the maximum output and reduce the minimum fuel consumption while taking advantage of the ignition stability and good exhaust emissions when fuel is injected in a direction opposite to the swirl. There is an advantage.
即ち、本発明により、広い回転数及び負荷範囲にわたる
全運転域において、良好な燃焼安定性、排気エミッショ
ン及び熱効率が得られるという効果がある。That is, the present invention has the effect that good combustion stability, exhaust emissions, and thermal efficiency can be obtained in the entire operating range over a wide rotational speed and load range.
なお、本発明は主として点火室を有する層状給気式の往
復動型内燃機関に対して有効に適用できるものであり、
この場合、単気筒及び多気筒のいづれの場合にも適用可
能である。The present invention can be effectively applied mainly to a stratified air supply type reciprocating internal combustion engine having an ignition chamber.
In this case, it is applicable to both single-cylinder and multi-cylinder cases.
第1図は本発明の一実施例における内燃機関の燃焼室の
要部断面で示す平面図、第2図は第1図の■−■方向の
縦断面図、第3図は第1図の主燃焼室内のスワールを示
す要部平面図、第4図及び第5図はそれぞれ異なる従来
例の内燃機関の主燃焼室内のスワールを示す要部平面図
、第6図は第1図の本発明の実施例、第4図及び第5図
の各従来例における内燃機関の正味平均有効圧力と各燃
焼効果とを比較した線図である。
1・・・ピストン、7・・・主燃焼室、8・・・燃料噴
射弁、8A、8B・・・噴口、Fl、F2・・・燃料噴
霧、S・・・スワール。FIG. 1 is a plan view showing a main part of a combustion chamber of an internal combustion engine according to an embodiment of the present invention, FIG. 2 is a vertical sectional view taken along the direction ■-■ of FIG. 4 and 5 are plan views of main parts showing swirls in the main combustion chamber of different conventional internal combustion engines, and FIG. 6 is a plan view of main parts showing swirls in the main combustion chambers of different conventional internal combustion engines. FIG. 5 is a diagram comparing the net average effective pressure of the internal combustion engine and each combustion effect in the example of FIG. DESCRIPTION OF SYMBOLS 1...Piston, 7...Main combustion chamber, 8...Fuel injection valve, 8A, 8B...Nozzle port, Fl, F2...Fuel spray, S...Swirl.
Claims (1)
する噴口を、スワール順流及びスワール逆流にそれぞれ
対向する2方向に形成すると共に、スワール順流に対向
する噴口径を他方向の噴口径よりも小さくした内燃機関
。The nozzles that inject the fuel spray into the main combustion chamber formed at the top of the piston are formed in two directions, each facing the forward swirl flow and the reverse swirl flow, and the diameter of the nozzle facing the forward swirl flow is smaller than the nozzle diameter in the other direction. Internal combustion engine.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP15797386A JPH0658062B2 (en) | 1986-07-07 | 1986-07-07 | Internal combustion engine |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP15797386A JPH0658062B2 (en) | 1986-07-07 | 1986-07-07 | Internal combustion engine |
Publications (2)
Publication Number | Publication Date |
---|---|
JPS6316123A true JPS6316123A (en) | 1988-01-23 |
JPH0658062B2 JPH0658062B2 (en) | 1994-08-03 |
Family
ID=15661475
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP15797386A Expired - Lifetime JPH0658062B2 (en) | 1986-07-07 | 1986-07-07 | Internal combustion engine |
Country Status (1)
Country | Link |
---|---|
JP (1) | JPH0658062B2 (en) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS62114149U (en) * | 1986-01-10 | 1987-07-20 | ||
JPS62114150U (en) * | 1986-01-13 | 1987-07-20 |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH0325053A (en) * | 1989-06-23 | 1991-02-01 | Takata Kk | Pretensioner device |
-
1986
- 1986-07-07 JP JP15797386A patent/JPH0658062B2/en not_active Expired - Lifetime
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS62114149U (en) * | 1986-01-10 | 1987-07-20 | ||
JPH0430354Y2 (en) * | 1986-01-10 | 1992-07-22 | ||
JPS62114150U (en) * | 1986-01-13 | 1987-07-20 |
Also Published As
Publication number | Publication date |
---|---|
JPH0658062B2 (en) | 1994-08-03 |
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