JPH0747931B2 - Multiple pre-combustion chamber type internal combustion engine - Google Patents
Multiple pre-combustion chamber type internal combustion engineInfo
- Publication number
- JPH0747931B2 JPH0747931B2 JP1276088A JP27608889A JPH0747931B2 JP H0747931 B2 JPH0747931 B2 JP H0747931B2 JP 1276088 A JP1276088 A JP 1276088A JP 27608889 A JP27608889 A JP 27608889A JP H0747931 B2 JPH0747931 B2 JP H0747931B2
- Authority
- JP
- Japan
- Prior art keywords
- combustion chamber
- combustion
- main
- small
- cylinder
- 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
- F02B19/00—Engines characterised by precombustion chambers
- F02B19/14—Engines characterised by precombustion chambers 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)
Description
【発明の詳細な説明】 〔産業上の利用分野〕 本発明は、複数の予燃焼室を備えた内燃機関に関するも
のである。TECHNICAL FIELD The present invention relates to an internal combustion engine having a plurality of precombustion chambers.
オイルショック以降、低燃費化の観点から、ディーゼル
機関の燃焼方式としては直噴式が多く採用されるように
なった。また現在では、固定型及び自動車用ディーゼル
機関に関して、燃費の改善だけでなく、環境保全の見地
から排気ガスにおけるNOX及びばい塵の低減化が非常に
強く要請されるようになっている。Since the oil shock, the direct injection type has been widely adopted as the combustion method for diesel engines from the viewpoint of fuel efficiency. In addition, nowadays, for fixed and automobile diesel engines, not only improvement of fuel consumption but also reduction of NO X and dust in exhaust gas is very strongly demanded from the viewpoint of environmental protection.
（発明が解決しようとする課題） 前記直噴式は、予燃焼室よりも燃費は良いものの、排気
ガス中のNOXは高く、また同じNOXの場合には予燃焼室式
よりもばい塵が多い傾向があるという問題があった。(Problems to be Solved by the Invention) Although the direct injection type has better fuel efficiency than the pre-combustion chamber, NO X in the exhaust gas is high, and in the case of the same NO X , more dust is generated than the pre-combustion chamber type. There was a problem that there were many tendencies.
ところが、従来の予燃焼室式によってNOX及びばい塵を
低減しようとすると、特に固定型ディーゼル機関は出力
率が高レベルであるため、予燃焼室等の熱負荷が増大し
てしまうという問題がある。However, when attempting to reduce NO X and soot and dust by the conventional pre-combustion chamber type, there is a problem that the heat load of the pre-combustion chamber or the like increases because the fixed diesel engine has a high output rate. is there.
また、現在の予燃焼室式は直噴式よりもNOXは低い傾向
にあるものの、さらにNOXを低減化しようとするとばい
塵が増加してしまうという問題があった。Further, although the current pre-combustion chamber type tends to have lower NO X than the direct injection type, there is a problem that soot and dust increase when further reducing NO X.
本発明は以上の問題点に鑑みてなされたものであり、ば
い塵や燃費の悪化を極力抑えるとともに、現状のNOXレ
ベルを大幅に低減させることのできる内燃機関を提供す
ることを目的としている。The present invention has been made in view of the above problems, and an object of the present invention is to provide an internal combustion engine that can significantly reduce the current NO X level while suppressing the dust and the deterioration of fuel efficiency as much as possible. .
本願の複予燃焼室式内燃機関は、燃料の噴射供給量に対
して容積が小さく、細径の先端筒部がシリンダ内の主燃
焼室内に突出した縦長筒状の主燃焼室に連通する連絡噴
口が大きい主予燃焼室と、燃料の噴射供給量に対して容
積が大きく、細径の先端筒部がシリンダ内の主燃焼室内
に突出した縦長筒状の主燃焼室に連通する連絡噴口が小
さい副予燃焼室とを具備し、前記主予燃焼室から主燃焼
室に噴出した燃焼ガスに対して前記副予燃焼室から噴出
した燃焼ガスが衝突するように、前記両予燃焼室の連絡
噴口の噴出方向を設定したことを特徴としている。The compound pre-combustion chamber type internal combustion engine of the present application has a small volume with respect to the fuel injection supply amount, and has a small-diameter tip cylinder portion that communicates with the vertically long cylindrical main combustion chamber protruding into the main combustion chamber in the cylinder. There is a main pre-combustion chamber with a large injection port, and a communication injection port that communicates with a vertically long cylindrical main combustion chamber that has a large volume for the fuel injection supply amount and has a thin tip cylinder protruding into the main combustion chamber in the cylinder. A small auxiliary pre-combustion chamber is provided, and the two pre-combustion chambers are connected so that the combustion gas ejected from the main pre-combustion chamber to the combustion gas ejected from the auxiliary pre-combustion chamber collides with the combustion gas ejected from the main pre-combustion chamber. The feature is that the ejection direction of the nozzle is set.
上記、本願の発明によれば、２個の予燃焼室を有するた
めに各予燃焼室ごとの熱負荷が軽減される。また、主予
燃焼室は噴口が大きく、燃料の噴射供給量に対して容積
が小さいので、排気ガス中のNOXは低減するが、この主
予燃焼室から噴出した燃焼ガスの燃焼は悪化する。とこ
ろが、噴口が小さい副予燃焼室からはタイミングが遅れ
て燃焼ガスが噴出し、主予燃焼室から噴出した燃焼ガス
に衝突して乱れを促進するので、これによって主燃焼室
内での燃焼が改善され、NOXを上昇させることなく燃費
が向上する。According to the invention of the present application, since the two pre-combustion chambers are provided, the heat load of each pre-combustion chamber is reduced. Also, since the main pre-combustion chamber has a large injection port and a small volume with respect to the fuel injection supply amount, NO X in the exhaust gas is reduced, but combustion of the combustion gas ejected from this main pre-combustion chamber is deteriorated. . However, the combustion gas is ejected from the secondary pre-combustion chamber with a small injection port at a delayed timing, and the combustion gas ejected from the main pre-combustion chamber collides with it to promote turbulence, which improves combustion in the main combustion chamber. As a result, fuel consumption is improved without increasing NO X.
第１図及び第２図によって、本発明の実施例である複予
燃焼室式内燃機関を説明する。An embodiment of the present invention will be described with reference to FIG. 1 and FIG.
第１図に示すように、この内燃機関のシリンダヘッド11
には、各シリンダごとに２個の吸気弁12,12と２個の排
気弁13,13が設けられ、さらに互いに構造の異なる主予
燃焼室14と副予燃焼室15が、シリンダの中心軸に関して
対称な位置に互いに連絡噴口16,17を対向させて配設さ
れている。As shown in FIG. 1, the cylinder head 11 of this internal combustion engine
Is provided with two intake valves 12 and 12 and two exhaust valves 13 and 13 for each cylinder, and a main pre-combustion chamber 14 and a sub-pre-combustion chamber 15 having different structures from each other are provided in the central axis of the cylinder. With respect to each other, the communication nozzles 16 and 17 are arranged to face each other.
各予燃焼室14,15の基本的構造は、第２図に示すよう
に、細径の先端筒部がシリンダ内の主燃焼室12内に突出
した筒体であり、内部には燃料弁18、19が設けられてい
る。各予燃焼室14,15は、先端筒部に貫設された円形の
複数個の連絡噴口16、17を介して共通する主燃焼室21に
連通している。本実施例の主予燃焼室14の容積は燃料弁
18から噴射される燃料の量に対して小さく、連絡噴口16
の断面積は大きく設定されている。これに対し、副予燃
焼室15の容積は燃料弁19から噴射される燃料の量に対し
て比較的大きく、連絡噴口17の断面積は小さく設定され
ている。As shown in FIG. 2, the basic structure of each of the pre-combustion chambers 14 and 15 is a tubular body in which a small-diameter tip tubular portion projects into the main combustion chamber 12 in the cylinder, and a fuel valve 18 is provided inside. , 19 are provided. Each of the pre-combustion chambers 14 and 15 is in communication with a common main combustion chamber 21 via a plurality of circular connecting injection holes 16 and 17 penetrating the tip cylinder portion. In this embodiment, the volume of the main pre-combustion chamber 14 is the fuel valve.
Small compared to the amount of fuel injected from 18, the communication nozzle 16
The cross-sectional area of is set large. On the other hand, the volume of the auxiliary pre-combustion chamber 15 is relatively large with respect to the amount of fuel injected from the fuel valve 19, and the cross-sectional area of the communication injection port 17 is set small.
そして前述した通り、両予燃焼室14,15の各連絡噴口16,
17は対向していて、燃焼ガスが衝突するようになってい
る。And, as described above, the connecting injection ports 16, 15 of both the pre-combustion chambers 14, 15
17 are opposed to each other so that combustion gas collides with each other.
次に、以上の構成を有する内燃機関を駆動した場合の作
用を説明する。Next, the operation when the internal combustion engine having the above configuration is driven will be described.
まず、従来と異なり予燃焼室が複数個設けられているの
で、各予燃焼室の熱負荷が低減して耐久性が向上する。First, unlike the prior art, since a plurality of pre-combustion chambers are provided, the heat load of each pre-combustion chamber is reduced and the durability is improved.
さて、予燃焼室式の内燃機関では、連絡噴口の断面積が
大きい程、そして予燃焼室の容積が小さい程、排気ガス
中のNOXを低減できるが、この場合には逆にばい塵が増
加して燃費が悪化してしまう。従って、主予燃焼室14か
ら噴出した燃焼ガスにはNOXは少ないが、ばい塵は多く
なっている。In a pre-combustion chamber type internal combustion engine, the larger the cross-sectional area of the communication nozzle and the smaller the volume of the pre-combustion chamber, the more the NO x in the exhaust gas can be reduced. It will increase and fuel efficiency will deteriorate. Therefore, the combustion gas ejected from the main pre-combustion chamber 14 has a small amount of NO X but a large amount of dust.
また、前記各予燃焼室14,15の燃焼ガスは、断面積が異
なる各予燃焼室14,15の連絡噴口16,17を介して主燃焼室
21内に噴出するので、各連絡噴口16,17で受ける抵抗の
相違によって噴出タイミングがずれてくる。即ち、副予
燃焼室15からの燃焼ガスの噴出開始が遅れ、また噴出割
合も少なくなる。Further, the combustion gas in each of the pre-combustion chambers 14 and 15 passes through the communication nozzles 16 and 17 of each of the pre-combustion chambers 14 and 15 having different cross-sectional areas into the main combustion chamber.
Since it jets out into the inside 21, the jetting timing is deviated due to the difference in resistance received at each of the connecting jets 16 and 17. That is, the start of ejection of the combustion gas from the auxiliary pre-combustion chamber 15 is delayed, and the ejection rate is reduced.
従って、主予燃焼室14から先に噴出した燃焼ガスに対
し、遅れたタイミングで副予燃焼室15から噴出した燃焼
ガスが衝突し、主燃焼室21内において燃焼ガスの乱れを
促進する。これによって、主燃焼室21内での燃焼が改善
され、NOXを上昇させることなく燃費を向上させてばい
塵を減らすことができる。Therefore, the combustion gas ejected from the main pre-combustion chamber 14 collides with the combustion gas ejected from the sub-pre-combustion chamber 15 at a delayed timing to promote the turbulence of the combustion gas in the main combustion chamber 21. As a result, the combustion in the main combustion chamber 21 is improved, and it is possible to improve the fuel consumption and raise the dust without increasing NO X.
本願の発明によれば、仕様の異なる２つの予燃焼室を設
け、主燃焼室に噴出したNOXの低い燃焼ガスに、遅れて
噴出した燃焼ガスを衝突させて主燃焼室内の燃焼ガスの
乱れを促進するようにしている。従って、この発明によ
れば、予燃焼室の熱負荷を低減して耐久性を確保し、NO
Xを上昇させることなく燃費を改善することができる。According to the present invention, the two pre-combustion chamber having different specifications provided, into the main combustion chamber low erupted NO X in the combustion gases, by colliding the late ejected combustion gas of the main combustion chamber of the combustion gas turbulence Trying to promote. Therefore, according to the present invention, the heat load of the pre-combustion chamber is reduced to ensure the durability, and the NO
Fuel efficiency can be improved without increasing X.
第１図は本発明の実施例においてピストン側から見たシ
リンダヘッドの触火面を示す図、第２図は同実施例にお
ける主燃焼室及び予燃焼室近傍の断面図である。 21……主燃焼室、16,17……連絡噴口、14……主予燃焼
室、15……副予燃焼室。FIG. 1 is a view showing the ignition surface of a cylinder head as seen from the piston side in an embodiment of the present invention, and FIG. 2 is a sectional view in the vicinity of a main combustion chamber and a pre-combustion chamber in the same embodiment. 21 …… Main combustion chamber, 16,17 …… Communication nozzle, 14 …… Main pre-combustion chamber, 15 …… Sub-pre-combustion chamber
Claims (1)
細径の先端筒部がシリンダ内の主燃焼室内に突出した縦
長筒状の主燃焼室に連通する連絡噴口が大きい主予燃焼
室と、燃料の噴射供給量に対して容積が大きく、細径の
先端筒部がシリンダ内の主燃焼室内に突出した縦長筒状
の主燃焼室に連通する連絡噴口が小さい副予燃焼室とを
具備し、前記主予燃焼室から主燃焼室に噴出した燃焼ガ
スに対して前記副予燃焼室から噴出した燃焼ガスが衝突
するように、前記両予燃焼室の連絡噴口の噴出方向を設
定したことを特徴とする複予燃焼室式内燃機関。1. A volume is small with respect to a fuel injection supply amount,
The main pre-combustion chamber has a large communication nozzle that communicates with the vertically long cylindrical main combustion chamber, which has a small diameter tip cylinder protruding into the main combustion chamber in the cylinder, and a large volume for the fuel injection supply amount. A combustion chamber that has a small pre-combustion chamber with a small communication nozzle that communicates with the vertically-long cylindrical main combustion chamber whose tip cylindrical portion projects into the main combustion chamber in the cylinder; A dual pre-combustion chamber type internal combustion engine, wherein the ejection directions of the communication nozzles of the pre-combustion chambers are set so that the combustion gas ejected from the sub-pre-combustion chamber collides with the gas.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1276088A JPH0747931B2 (en) | 1989-10-25 | 1989-10-25 | Multiple pre-combustion chamber type internal combustion engine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1276088A JPH0747931B2 (en) | 1989-10-25 | 1989-10-25 | Multiple pre-combustion chamber type internal combustion engine |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH03141818A JPH03141818A (en) | 1991-06-17 |
| JPH0747931B2 true JPH0747931B2 (en) | 1995-05-24 |
Family
ID=17564635
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP1276088A Expired - Lifetime JPH0747931B2 (en) | 1989-10-25 | 1989-10-25 | Multiple pre-combustion chamber type internal combustion engine |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH0747931B2 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2004285928A (en) * | 2003-03-24 | 2004-10-14 | Osaka Gas Co Ltd | Engine and its operation method |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US9142832B2 (en) | 2010-08-11 | 2015-09-22 | Jx Nippon Oil & Energy Corporation | Graphite material for negative electrodes of lithium ion secondary battery, manufacturing method for said material, and lithium ion secondary battery using same |
Family Cites Families (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS575915U (en) * | 1980-06-11 | 1982-01-12 | ||
| JPS6084726U (en) * | 1983-11-18 | 1985-06-11 | 篠塚 正男 | Side compartment diesel engine |
| JPS6158651A (en) * | 1984-08-31 | 1986-03-25 | 松下電器産業株式会社 | Ultrasonic probe |
| JPS61106914A (en) * | 1984-10-30 | 1986-05-24 | Mitsubishi Heavy Ind Ltd | Combustion chamber in internal combustion engine |
-
1989
- 1989-10-25 JP JP1276088A patent/JPH0747931B2/en not_active Expired - Lifetime
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2004285928A (en) * | 2003-03-24 | 2004-10-14 | Osaka Gas Co Ltd | Engine and its operation method |
Also Published As
| Publication number | Publication date |
|---|---|
| JPH03141818A (en) | 1991-06-17 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US20020179039A1 (en) | Fuel injection system | |
| US6742493B2 (en) | Fuel injection system and method for injection | |
| JP3598880B2 (en) | Direct injection spark ignition type internal combustion engine | |
| US6659070B2 (en) | Fuel injection system | |
| US6267096B1 (en) | Three-valve cylinder head system | |
| JP2002089267A (en) | Gasoline direct injection engine | |
| JP4215517B2 (en) | Fuel injection system | |
| JP3332694B2 (en) | Combustion chamber of subchamber internal combustion engine | |
| JPH0747931B2 (en) | Multiple pre-combustion chamber type internal combustion engine | |
| US20190376442A1 (en) | Diesel engine | |
| JP3160455B2 (en) | Large side injection methanol engine | |
| JPS6316123A (en) | Internal combustion engine | |
| JPH0681654A (en) | Combustion chamber structure of direct cylinder injection type engine | |
| JP4026406B2 (en) | Direct-injection spark ignition internal combustion engine | |
| JP2809759B2 (en) | Diesel engine combustion chamber | |
| JPH036824Y2 (en) | ||
| JP2971247B2 (en) | Combustion chamber of a swirl chamber type diesel engine | |
| JP2006057604A (en) | Cylinder direct injection internal combustion engine | |
| JP3275470B2 (en) | Subchamber engine | |
| JP2000064839A (en) | Precombustion chamber system gas engine | |
| JPS5926772B2 (en) | Pre-chamber internal combustion engine | |
| JPH04105941U (en) | Pre-chamber cap of pre-chamber internal combustion engine | |
| JP2001098946A (en) | Direct-injection spark ignition type internal combustion engine | |
| JPH0619801Y2 (en) | Combustion chamber of a sub-chamber internal combustion engine | |
| JP2552596Y2 (en) | Combustion chamber of a swirl chamber type diesel engine |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| R250 | Receipt of annual fees |
Free format text: JAPANESE INTERMEDIATE CODE: R250 |
|
| R250 | Receipt of annual fees |
Free format text: JAPANESE INTERMEDIATE CODE: R250 |
|
| R250 | Receipt of annual fees |
Free format text: JAPANESE INTERMEDIATE CODE: R250 |
|
| R250 | Receipt of annual fees |
Free format text: JAPANESE INTERMEDIATE CODE: R250 |
|
| FPAY | Renewal fee payment (event date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20090524 Year of fee payment: 14 |
|
| FPAY | Renewal fee payment (event date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20090524 Year of fee payment: 14 |
|
| FPAY | Renewal fee payment (event date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20100524 Year of fee payment: 15 |
|
| EXPY | Cancellation because of completion of term | ||
| FPAY | Renewal fee payment (event date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20100524 Year of fee payment: 15 |