JPS6158650B2 - - Google Patents
Info
- Publication number
- JPS6158650B2 JPS6158650B2 JP56051985A JP5198581A JPS6158650B2 JP S6158650 B2 JPS6158650 B2 JP S6158650B2 JP 56051985 A JP56051985 A JP 56051985A JP 5198581 A JP5198581 A JP 5198581A JP S6158650 B2 JPS6158650 B2 JP S6158650B2
- Authority
- JP
- Japan
- Prior art keywords
- main
- nozzle
- chamber
- sub
- cavity
- 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
Links
- 239000000446 fuel Substances 0.000 claims description 17
- 238000002485 combustion reaction Methods 0.000 claims description 14
- 238000002347 injection Methods 0.000 claims description 6
- 239000007924 injection Substances 0.000 claims description 6
- 239000007789 gas Substances 0.000 description 10
- 239000000779 smoke Substances 0.000 description 4
- QVGXLLKOCUKJST-UHFFFAOYSA-N atomic oxygen Chemical compound [O] QVGXLLKOCUKJST-UHFFFAOYSA-N 0.000 description 2
- 239000001301 oxygen Substances 0.000 description 2
- 229910052760 oxygen Inorganic materials 0.000 description 2
- 239000000567 combustion gas Substances 0.000 description 1
- 230000002950 deficient Effects 0.000 description 1
- 239000007788 liquid Substances 0.000 description 1
- 239000000126 substance Substances 0.000 description 1
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
-
- 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)
Description
【発明の詳細な説明】
本発明は、渦流室式デイーゼルエンジンの燃焼
室に関し、詳しくは渦流室と主室とを連通する主
噴口の他に副噴口を設けて燃焼を改善するように
した燃焼室の改良に関する。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a combustion chamber for a swirl chamber type diesel engine, and more specifically to a combustion chamber for improving combustion by providing a sub-nozzle in addition to a main nozzle that communicates the swirl chamber with a main chamber. Concerning room improvements.
高速デイーゼルエンジンに適した燃焼室の形式
として渦流室式が知られているが、その燃焼性状
をさらに改善する目的で第１図および第２図に示
したようなものが提案されている。（実公昭36−
9602号公報参照）。 The swirl chamber type is known as a type of combustion chamber suitable for high-speed diesel engines, but the type shown in FIGS. 1 and 2 has been proposed for the purpose of further improving combustion characteristics. (Jikko Sho 36-
(See Publication No. 9602).
これを説明すると、渦流室１はエンジンシリン
ダヘツド２とその下面２Ａから嵌合した口金３と
の間に略球状に形成されており、主噴口４と比較
的小径の副噴口５を介して主室６に連通してい
る。 To explain this, the vortex chamber 1 is formed in a substantially spherical shape between an engine cylinder head 2 and a mouthpiece 3 fitted from its lower surface 2A, and the vortex chamber 1 is formed into a substantially spherical shape between an engine cylinder head 2 and a mouthpiece 3 fitted from its lower surface 2A. It communicates with room 6.
主噴口４は、その渦流室１側の開口部４Ａが球
状渦流室１の接線方向に、他方主室６側の開口部
４Ｂがややシリンダ中心寄りに開口するように形
成してあり、燃焼時の渦流室１からのガス噴流が
主室６の中央方向に噴出するようにしてある。こ
れに対して、小径の副噴口５は、渦流室１に面し
た燃料噴射弁７の噴射方向に沿つて開口し、着火
遅れの間に噴射燃料の一部が主室６へと流出する
ようにしてある。 The main injection port 4 is formed so that an opening 4A on the swirl chamber 1 side opens in the tangential direction of the spherical swirl chamber 1, and an opening 4B on the main chamber 6 side opens slightly toward the center of the cylinder. The gas jet from the swirl chamber 1 is ejected toward the center of the main chamber 6. On the other hand, the small-diameter sub-nozzle 5 opens along the injection direction of the fuel injection valve 7 facing the swirl chamber 1, so that a part of the injected fuel flows out into the main chamber 6 during the ignition delay. It is set as.
また、ピストン８の頂面８Ａには、上死点位置
近傍で主噴口開口部４Ｂとほぼ対向する部位から
内方に向けて窪み状のキヤビテイ部９が形成され
ている。このキヤビテイ部９は、主噴口４からの
未燃成分を伴つたガス噴流を主室６のほぼ中央部
に案内しつつ空気との混合を促し、これにより空
気利用率を高めて燃焼を改善する（第２図参
照）。 Further, on the top surface 8A of the piston 8, a recessed cavity portion 9 is formed inward from a portion substantially facing the main nozzle opening 4B in the vicinity of the top dead center position. This cavity part 9 guides the gas jet containing unburned components from the main nozzle 4 to the approximate center of the main chamber 6 and promotes mixing with air, thereby increasing the air utilization rate and improving combustion. (See Figure 2).
ところで、このような副噴口５を設けた渦流室
式燃焼室によると、すでに述べたように噴射燃料
の一部が副噴口５を介して主室６にも供給される
ため、主室６の渦流室１との双方で燃焼が行なわ
れ、この結果噴射燃料の全量を渦流室１のみに供
給して燃焼させた場合に較べて最高燃焼温度が低
くなるので、有害物質であるNOxの発生を抑制
できるという利点が得られる。 By the way, according to the swirl chamber type combustion chamber provided with such a sub-nozzle 5, a part of the injected fuel is also supplied to the main chamber 6 via the sub-nozzle 5, as described above. Combustion occurs both in the swirl chamber 1 and as a result, the maximum combustion temperature is lower than in the case where the entire amount of injected fuel is supplied only to the swirl chamber 1 and combusted, which reduces the generation of NOx, which is a harmful substance. The advantage is that it can be suppressed.
しかしながらその反面、副噴口５を介して主室
６に流出した燃料が不完全燃焼し、多量のスモー
クを発生するという問題点もある。これは、副噴
口５からの燃料がキヤビテイ部９で徐々に燃焼し
ているときに、主噴口４からの燃焼ガス噴流に晒
されて酸素不足の状態で急速に燃焼するからであ
る。 However, on the other hand, there is also a problem in that the fuel that has flowed into the main chamber 6 through the sub-nozzle port 5 is incompletely combusted and a large amount of smoke is generated. This is because while the fuel from the auxiliary nozzle 5 is being gradually combusted in the cavity 9, it is exposed to the combustion gas jet from the main nozzle 4 and is rapidly combusted in an oxygen-deficient state.
本発明はこのような点に着目し、主噴口からの
ガス噴流を案内する主キヤビテイ部の他に、副噴
口からの燃料を主キヤビテイ部と異なる方向に案
内する副キヤビテイ部を形成し、副噴口を介して
主室に直接的に供給された燃料が燃焼する領域
と、渦流室からのガス噴流が燃焼する領域とを分
散することにより上記従来の問題点を解消する。 The present invention has focused on such points, and in addition to the main cavity part that guides the gas jet from the main nozzle, a sub cavity part that guides the fuel from the auxiliary nozzle in a direction different from that of the main cavity part is formed. The above-mentioned conventional problems are solved by dispersing the region where the fuel directly supplied to the main chamber through the nozzle is combusted and the region where the gas jet from the swirl chamber is combusted.
以下、図面に示した実施例に基づいて本発明を
説明する。なお、シリンダヘツド側の構成につい
ては従来と同様であるので、説明上適宜第１図の
符号を引用する。 The present invention will be described below based on embodiments shown in the drawings. The structure on the cylinder head side is the same as the conventional one, so the reference numerals in FIG. 1 will be cited as appropriate for the purpose of explanation.
第３図Ａ，Ｂにおいて、１０はピストン、１１
はピストン頂面１０Ａに形成した主キヤビテイ
部、１２は同じく副キヤビテイ部である。 In Fig. 3A and B, 10 is a piston, 11
1 is a main cavity formed on the piston top surface 10A, and 12 is a sub cavity.
主キヤビテイ部１１は、第２図と同様に、主噴
口開口部４Ｂと対向する部位から内方に向いた直
線状の導入部１１Ａと、この導入部１１Ａに続い
てピストン頂面１０Ａの略中央部に形成された平
面上まゆ形状の渦流生起部１１Ｂとからなり、燃
焼行程で主噴口４を介しての渦流室１からの噴出
ガスを渦流生起部１１Ｂに導入し、空気との混合
を促して燃焼を活発化する。 As in FIG. 2, the main cavity portion 11 includes a linear introduction portion 11A facing inward from a portion facing the main nozzle opening 4B, and a linear introduction portion 11A extending from the introduction portion 11A to approximately the center of the piston top surface 10A. The vortex generating part 11B has a cocoon shape on a plane and is formed in the vortex generating part 11B, and during the combustion stroke, the ejected gas from the vortex chamber 1 through the main nozzle 4 is introduced into the vortex generating part 11B to promote mixing with air. to activate combustion.
これに対して、副キヤビテイ部１２は、副噴口
５の主室側開口部５Ｂと対向する部位（この場合
主キヤビテイ導入部１１Ａとオーバラツプしてい
る）から、主キヤビテイ部１１とは異なる方向に
向けて形成される。 On the other hand, the sub-cavity part 12 extends in a direction different from the main cavity part 11 from the part facing the main chamber-side opening 5B of the sub-nozzle 5 (in this case, it overlaps with the main cavity introduction part 11A). formed towards.
この実施例では、副キヤビテイ部１２は主キヤ
ビテイ導入部１１Ａを挾んで対称的な２方向に設
けられ、第３図Ｂに示したように、各々の底面１
２Ａが互いの分岐部１２Ｂを頂点として傾斜し、
次第に深さが増すように形成されている。 In this embodiment, the sub-cavity portions 12 are provided in two symmetrical directions sandwiching the main cavity introduction portion 11A, and as shown in FIG.
2A are inclined with each other's branch part 12B as the apex,
It is formed so that the depth gradually increases.
このような構成に基づき、主室６での空気利用
率が向上してスモークの発生が最小限に抑えられ
る。すなわち、主噴口４を介しての渦流室１から
のガス噴流は、既述したように主噴口４がシリン
ダ中心方向を向いているため、主キヤビテイ導入
部１１Ａに沿つて渦流生起部１１Ｂへと勢いよく
流入し、活発に空気と混合しながら燃焼するが、
その一方副噴口５を介しての燃料の流れは、副キ
ヤビテイ分岐部１２Ｂに衝突して一部拡散すると
ともに、残りの液状部分は傾斜した底面１２Ａに
沿つて２方向へと流れながら次第に気化して着火
燃焼する。このことは、換言すれば、主噴口４か
らの噴出ガスと副噴口５からの燃料とが主室６の
異なる領域で燃焼するということであり、従つて
主室６の空気が有効に利用され、スモークの発生
が少ない良好な燃焼がなされるのである。 Based on such a configuration, the air utilization rate in the main chamber 6 is improved and the occurrence of smoke is minimized. That is, the gas jet from the vortex chamber 1 via the main nozzle 4 flows along the main cavity introduction section 11A to the vortex generating section 11B because the main nozzle 4 faces toward the center of the cylinder as described above. It flows in vigorously and burns while actively mixing with air,
On the other hand, the flow of fuel through the sub-nozzle 5 collides with the sub-cavity branch part 12B and is partially diffused, while the remaining liquid part gradually vaporizes while flowing in two directions along the inclined bottom surface 12A. ignite and burn. In other words, this means that the gas ejected from the main nozzle 4 and the fuel from the auxiliary nozzle 5 burn in different areas of the main chamber 6, so that the air in the main chamber 6 is effectively utilized. This results in good combustion with little smoke generation.
第４図Ａ，Ｂと第５図は各々本発明の第２、第
３の実施例で、第４図Ａ，Ｂでは、副キヤビテイ
部１２の端部に平面上円形の渦流生起部１２Ｃを
形成し、この渦流生起部１２Ｃに副噴口５からの
燃料とガスの流れを接線方向から導入することに
より渦流となし、これにより主キヤビテイ部１１
と同様にして空気との混合を促す。さらに第５図
では、主キヤビテイ部１１の渦流生起部１１B′を
副キヤビテイ渦流生起部１２Ｃと同様の円形に、
しかも互いにできるだけ離れて位置するように形
成し、これにより両キヤビテイ部１１，１２での
燃焼領域を隔離してさらに空気利用率の向上を図
る。その他の点については各実施例とも同様であ
るので、同一の部分に同一の符号を付して説明を
省略する。 4A and 5 show the second and third embodiments of the present invention, respectively. In FIGS. 4A and 4B, a vortex generating portion 12C that is circular in plan is provided at the end of the sub-cavity portion 12. The flow of fuel and gas from the sub-nozzle 5 is tangentially introduced into this vortex generating part 12C to form a vortex, thereby causing a vortex in the main cavity part 11.
Promote mixing with air in the same way. Furthermore, in FIG. 5, the eddy current generating part 11B' of the main cavity part 11 is shaped circularly like the auxiliary cavity eddy current generating part 12C.
Moreover, they are formed so as to be located as far away from each other as possible, thereby isolating the combustion areas in both cavity parts 11 and 12, and further improving the air utilization efficiency. Other points are the same in each embodiment, so the same parts are denoted by the same reference numerals and description thereof will be omitted.
以上要するに、本発明によれば、ピストンの頂
面に渦流室からのガス噴流を導入する主キヤビテ
イ部と、この主キヤビテイ部と異なる方向に副噴
口からの燃料を導入する副キヤビテイ部とを形成
し、副噴口から流出した燃料に対して主噴口から
噴出した酸素濃度の低いガスが干渉しないように
したので、主室の空気利用率が向上してスモーク
発生量が低減するという効果を生じる。 In summary, according to the present invention, a main cavity part that introduces the gas jet from the swirl chamber into the top surface of the piston, and a sub cavity part that introduces fuel from the sub nozzle in a direction different from this main cavity part are formed. However, since the low oxygen concentration gas ejected from the main nozzle does not interfere with the fuel flowing out from the auxiliary nozzle, the air utilization rate in the main chamber is improved and the amount of smoke generated is reduced.
第１図は従来例の縦断面図、第２図はそのピス
トンの上面図である。第３図Ａは本発明の第１実
施例のピストン上面図、同図ＢはそのＡ−Ａ線に
よる断面図である。第４図Ａは同じく第２実施例
のピストン上面図、同図ＢはそのＢ−Ｂ線による
断面図である。第５図は同じく第３実施例のピス
トン上面図である。
１……渦流室、２……シリンダヘツド、４……
主噴口、５……副噴口、６……主室、７……燃料
噴射弁、８，１０……ピストン、１１……主キヤ
ビテイ部、１２……副キヤビテイ部。
FIG. 1 is a longitudinal sectional view of a conventional example, and FIG. 2 is a top view of the piston. FIG. 3A is a top view of a piston according to a first embodiment of the present invention, and FIG. 3B is a cross-sectional view taken along line A--A. FIG. 4A is a top view of a piston according to the second embodiment, and FIG. 4B is a cross-sectional view taken along the line B--B. FIG. 5 is a top view of the piston of the third embodiment. 1... Vortex chamber, 2... Cylinder head, 4...
Main nozzle, 5...Sub-nozzle, 6...Main chamber, 7...Fuel injection valve, 8, 10...Piston, 11...Main cavity part, 12...Sub-cavity part.
Claims (1)
せた渦流室を設け、この渦流室と主室とを連通す
る主噴口に加えてほぼ燃料噴射方向に沿つて副噴
口を開口させたデイーゼルエンジンにおいて、ピ
ストンの頂面に上死点位置近傍で前記主噴口と略
対向する部位から内方に向けて主キヤビテイ部
を、さらに同じく副噴口と略対向する部位から前
記主キヤビテイ部とは異なる方向に向けて副キヤ
ビテイ部を形成し、副噴口を介して主室に直接的
に供給された燃料が燃焼する領域と、渦流室から
のガス噴流が燃焼する領域とを分散させたことを
特徴とする渦流室式デイーゼルエンジンの燃焼
室。1. In a diesel engine, a vortex chamber with a fuel injection valve facing the engine cylinder head is provided, and in addition to a main nozzle that communicates the vortex chamber with the main chamber, a sub-nozzle is opened approximately along the fuel injection direction. A main cavity portion is directed inward from a portion substantially opposite to the main nozzle near the top dead center position, and a main cavity portion is directed inwardly from a portion substantially opposite to the sub-nozzle in a direction different from the main cavity portion. A vortex chamber that forms a sub-cavity portion and is characterized in that a region where fuel directly supplied to the main chamber via a sub-nozzle is combusted and a region where a gas jet from the vortex chamber is combusted are dispersed. Combustion chamber of a diesel engine.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP56051985A JPS57165625A (en) | 1981-04-07 | 1981-04-07 | Combustion chamber for diesel engine with swirl chamber |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP56051985A JPS57165625A (en) | 1981-04-07 | 1981-04-07 | Combustion chamber for diesel engine with swirl chamber |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS57165625A JPS57165625A (en) | 1982-10-12 |
| JPS6158650B2 true JPS6158650B2 (en) | 1986-12-12 |
Family
ID=12902143
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP56051985A Granted JPS57165625A (en) | 1981-04-07 | 1981-04-07 | Combustion chamber for diesel engine with swirl chamber |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS57165625A (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS6218328U (en) * | 1985-07-18 | 1987-02-03 |
-
1981
- 1981-04-07 JP JP56051985A patent/JPS57165625A/en active Granted
Also Published As
| Publication number | Publication date |
|---|---|
| JPS57165625A (en) | 1982-10-12 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| JPH01219311A (en) | Injection engine in spark ignition cylinder | |
| US4881501A (en) | Diesel engine having shaped flame dispersing recess in piston crown | |
| US5024194A (en) | Flame dispersion arrangement for swirl chamber type diesel engine piston crown | |
| JPS6158650B2 (en) | ||
| JPS5851215A (en) | Combustion chamber for vortex chamber type diesel engine | |
| US4116234A (en) | Internal combustion engine with an auxiliary combustion chamber | |
| JPH09125962A (en) | Combustion chamber of direct-injection type diesel engine | |
| JPH0648108Y2 (en) | Combustion chamber of swirl chamber type diesel engine | |
| JPS6118182Y2 (en) | ||
| JP2545357Y2 (en) | Combustion chamber of a swirl chamber type diesel engine | |
| JPS6118184Y2 (en) | ||
| JP2565516Y2 (en) | Combustion chamber of a swirl chamber type diesel engine | |
| JPS6319544Y2 (en) | ||
| JPH0618036Y2 (en) | Vortex chamber type diesel engine combustion chamber | |
| JPH07208168A (en) | Combustion chamber of swirl type diesel engine | |
| JPS5852328Y2 (en) | Combustion chamber of internal combustion engine | |
| JPS6350426Y2 (en) | ||
| JPS6118183Y2 (en) | ||
| JP3013573B2 (en) | Combustion chamber of a swirl chamber type diesel engine | |
| JP2534248Y2 (en) | Combustion chamber of vortex chamber diesel engine | |
| JPH0614033Y2 (en) | Combustion chamber of a sub-chamber internal combustion engine | |
| JPH06173687A (en) | Combustion chamber having subchamber of internal combustion engine | |
| JP2566173Y2 (en) | Combustion chamber of a swirl chamber type diesel engine | |
| JPH10131804A (en) | Structure of piston with auxiliary chamber | |
| JPS6319545Y2 (en) |