JPH057502Y2 - - Google Patents
Info
- Publication number
- JPH057502Y2 JPH057502Y2 JP1987017193U JP1719387U JPH057502Y2 JP H057502 Y2 JPH057502 Y2 JP H057502Y2 JP 1987017193 U JP1987017193 U JP 1987017193U JP 1719387 U JP1719387 U JP 1719387U JP H057502 Y2 JPH057502 Y2 JP H057502Y2
- Authority
- JP
- Japan
- Prior art keywords
- nozzle
- small
- fuel
- spray
- fuel valve
- 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
- 239000000446 fuel Substances 0.000 claims description 35
- 238000002485 combustion reaction Methods 0.000 claims description 16
- 238000002347 injection Methods 0.000 claims description 16
- 239000007924 injection Substances 0.000 claims description 16
- 239000007921 spray Substances 0.000 description 25
- 239000000567 combustion gas Substances 0.000 description 3
- 230000000694 effects Effects 0.000 description 3
- 230000000149 penetrating effect Effects 0.000 description 3
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 239000007789 gas Substances 0.000 description 1
- 239000003595 mist Substances 0.000 description 1
- 230000035515 penetration Effects 0.000 description 1
- 238000005507 spraying Methods 0.000 description 1
- 239000000126 substance Substances 0.000 description 1
Landscapes
- Combustion Methods Of Internal-Combustion Engines (AREA)
- Fuel-Injection Apparatus (AREA)
Description
【考案の詳細な説明】
〔産業上の利用分野〕
本考案は直接噴射式デイーゼルエンジンの燃焼
装置に関する。[Detailed Description of the Invention] [Industrial Field of Application] The present invention relates to a combustion device for a direct injection diesel engine.
従来の直接噴射式デイーゼルエンジンでは、第
５図、第６図に示すように、ピストン８とシリン
ダライナ９とシリンダヘツドによつて形成される
燃焼室空間２へ燃料を高圧で噴射し燃料噴霧３を
形成し、噴孔１２の径と噴射圧力によつて支配さ
れる到達能力及び空気スワールによつて燃料が分
散される。高温高圧に圧縮された空気中で自己着
火し噴霧火炎を形成し燃焼する。この時、燃焼弁
は第７図、第８図に示すようにほぼ等孔径の噴孔
からなつている。なお、１は燃料弁本体、４は排
気弁、５は給気弁、６は排気孔、７は給気孔、１
１は針弁、２００は給気スワールを示す。
In a conventional direct injection diesel engine, as shown in FIGS. 5 and 6, fuel is injected at high pressure into a combustion chamber space 2 formed by a piston 8, a cylinder liner 9, and a cylinder head, and a fuel spray 3 is created. , and the fuel is dispersed by the air swirl and the delivery capacity governed by the diameter of the nozzle hole 12 and the injection pressure. It self-ignites in high-temperature, high-pressure compressed air, forming a spray flame and burning. At this time, the combustion valve consists of nozzle holes of approximately equal diameter, as shown in FIGS. 7 and 8. In addition, 1 is the fuel valve body, 4 is the exhaust valve, 5 is the air supply valve, 6 is the exhaust hole, 7 is the air supply hole, 1
1 indicates a needle valve, and 200 indicates a supply air swirl.
従来の直接噴射式デイーゼルエンジンでは、燃
焼室のほぼ中央からほぼ孔径の等しい何個かの噴
孔を有する多噴孔噴射弁より噴射した噴霧でそれ
ぞれ独立した火炎を形成せしめ、燃焼させてい
る。この噴霧火炎では燃焼噴霧の周囲から空気の
みを吸引して燃焼が進行するため、比較的高濃度
のNOXを生成しやすいという欠点を有する。
In a conventional direct-injection diesel engine, a multi-hole injection valve having several nozzle holes of approximately the same diameter is injected from approximately the center of a combustion chamber to form independent flames and combust them. In this spray flame, combustion proceeds by sucking only air from around the combustion spray, so it has the disadvantage of easily producing relatively high concentrations of NOx .
本考案の目的は上記の点に着目し、燃料噴霧運
動と空気スワールとの相対的な関係を利用して燃
焼室内でのNOX生成を低減する装置を提供する
ことであり、その特徴とするところは、燃焼室の
ほぼ中央に、大噴口と該大噴口よりも小径の小噴
口を有する多噴孔燃料弁を設けるとともに、燃焼
室内に給気スワールを生成させる手段を備えた直
接噴射式デイーゼルエンジンにおいて、上記燃料
弁は同数の大噴口と小噴口を有し、小噴口の方が
大噴口よりも上部に位置するとともに、大噴口と
小噴口とがピストン中心線に直角な平面への投影
において重なり合うように配置され、かつ小噴口
の噴射角を大噴口の噴射角よりも小さく構成した
ことである。
The purpose of the present invention is to focus on the above-mentioned points and to provide a device that utilizes the relative relationship between fuel spray motion and air swirl to reduce NO However, a direct injection diesel engine is equipped with a multi-hole fuel valve that has a large nozzle and a small nozzle with a smaller diameter than the large nozzle approximately in the center of the combustion chamber, and also has a means for generating air supply swirl within the combustion chamber. In an engine, the fuel valve has the same number of large nozzles and small nozzles, the small nozzle is located above the large nozzle, and the large nozzle and the small nozzle are projected onto a plane perpendicular to the piston center line. The injection angle of the small nozzle is smaller than that of the large nozzle.
即ち、燃料弁の噴孔を大噴孔径と小噴孔径とを
対にし、何組かを持つノズルを利用し、給気スワ
ールを作用させることによつて、小噴孔径のノズ
ルによつて形成される燃料噴霧は噴霧の貫徹力が
弱く空気スワールによつて曲げられてしまうた
め、燃料弁まわりから遠くへ貫徹することなく、
燃料弁近くに噴霧火炎を形成する。一方大噴孔に
よつて形成される燃料噴霧は貫徹力が強く空気ス
ワールによつて強く曲げられることもなく、燃焼
室壁面まで到達する。しかも大噴孔径から噴射す
る燃料量が多いので主たる噴霧火炎となる。 In other words, the nozzle holes of the fuel valve are formed by pairing a large nozzle hole diameter and a small nozzle hole diameter, and by using several pairs of nozzles and creating a supply air swirl. The fuel spray that is sprayed has a weak penetration power and is bent by the air swirl, so it does not penetrate far from around the fuel valve.
Forms a spray flame near the fuel valve. On the other hand, the fuel spray formed by the large nozzle holes has a strong penetrating force and reaches the wall surface of the combustion chamber without being strongly bent by the air swirl. Moreover, since the amount of fuel injected from the large nozzle hole is large, it becomes the main spray flame.
小噴孔によつて形成された燃料弁まわりの噴霧
火炎の燃焼ガスが大噴孔によつて形成される主噴
霧火炎内に吸引され主噴霧火炎の発熱量に対して
噴霧火炎質量が増大し、火炎温度が低下され、
NOX生成が抑えられる。
The combustion gas of the spray flame around the fuel valve formed by the small nozzle hole is sucked into the main spray flame formed by the large nozzle hole, and the mass of the spray flame increases relative to the calorific value of the main spray flame. , the flame temperature is reduced,
NO X generation is suppressed.
以下図面を参照して本考案による実施例を説明
する。第１図は本考案による１実施例の燃料弁の
噴孔部を示す断面図、第２図は第１図の噴孔の配
置を示す平面図、第３図は本考案による燃料噴霧
の発達状況を示すデイーゼルエンジンの断面図、
第４図は第３図のＡ−Ａ矢視図である。
Embodiments of the present invention will be described below with reference to the drawings. Fig. 1 is a sectional view showing the nozzle hole portion of a fuel valve according to an embodiment of the present invention, Fig. 2 is a plan view showing the arrangement of the nozzle holes in Fig. 1, and Fig. 3 is a development of fuel spray according to the present invention. A cross-sectional view of a diesel engine showing the situation,
FIG. 4 is a view taken along the line A--A in FIG. 3.
図において、２はピストン８の上面中央部に形
成された燃焼室、４は排気弁、５は給気弁、６は
排気孔、７は給気孔、９はシリンダライナであ
り、該給気孔７は燃焼室２内に給気スワール２０
０が生起されるような形状に構成されている。１
００は燃料弁、１０１は針弁、１０２及び１０３
は該燃料弁１００の先端部に穿設された小噴口及
び大噴口である。 In the figure, 2 is a combustion chamber formed in the center of the upper surface of the piston 8, 4 is an exhaust valve, 5 is an air intake valve, 6 is an exhaust hole, 7 is an air intake hole, and 9 is a cylinder liner. is the air supply swirl 20 in the combustion chamber 2.
The shape is such that 0 is generated. 1
00 is the fuel valve, 101 is the needle valve, 102 and 103
are a small nozzle hole and a large nozzle hole bored at the tip of the fuel valve 100.
前記小噴口１０２及び大噴口１０３は、第２図
に示すように、ピストン８の中心線即ちシリンダ
中心線に直角な投影面において互いに重なり合う
ように、円周方向等分に複数個、かつ第１図に示
すように小噴口１０２が大噴口１０３よりも上部
に位置するように配置されている。さらに、第１
図に示すように、前記小噴口１０２の噴射角θ1は
大噴口１０３の噴射角θ2よりも小さくなるように
構成されている。 As shown in FIG. 2, the small nozzle 102 and the large nozzle 103 are arranged in a plurality of equal parts in the circumferential direction so as to overlap each other in a projection plane perpendicular to the center line of the piston 8, that is, the cylinder center line. As shown in the figure, the small nozzle 102 is arranged above the large nozzle 103. Furthermore, the first
As shown in the figure, the injection angle θ 1 of the small injection port 102 is configured to be smaller than the injection angle θ 2 of the large injection port 103.
第１図及び第２図に示すように燃料ノズルを大
噴孔１０３と小噴口１０２とを組合せ、第３図及
び第４図に示すように給気孔７、給気弁５によつ
て生成される給気スワール２００を作用させて圧
縮端近くで燃料弁１００から燃料を噴射する。こ
うすることによつて小噴口１０２から噴射された
燃料噴射霧３１は貫徹力が弱く、燃料弁１００の
近くに給気スワール２００によつて集められ、一
方大噴孔１０３から噴射された燃料噴霧３２は貫
徹力が強く、燃焼室キヤビテイ壁面に到達する。 As shown in FIGS. 1 and 2, the fuel nozzle is formed by combining a large nozzle hole 103 and a small nozzle 102, and as shown in FIGS. The fuel is injected from the fuel valve 100 near the compression end by applying the air supply swirl 200. By doing this, the fuel injection mist 31 injected from the small nozzle hole 102 has a weak penetrating force and is collected near the fuel valve 100 by the air supply swirl 200, while the fuel spray injected from the large nozzle hole 103 No. 32 has a strong penetrating force and reaches the combustion chamber cavity wall.
大噴孔１０３から噴射される噴霧は燃料を多量
に噴射する主たる燃料噴霧を形成し燃焼するが、
燃料弁近くで周囲のガスの吸引力が大きいので燃
料弁近くにかたまつている小噴孔１０２から噴射
された噴霧火炎からの燃焼ガスをまき込みながら
発達する。 The spray injected from the large nozzle hole 103 forms the main fuel spray that injects a large amount of fuel and burns.
Since the suction force of the surrounding gas is large near the fuel valve, it develops while drawing in the combustion gas from the spray flame injected from the small nozzle holes 102 clustered near the fuel valve.
上述の場合には次の効果がある。 The above case has the following effects.
燃料弁近くに形成された小噴孔からの噴霧火炎
の燃焼ガスが大噴孔からの主噴霧火炎内に吸引さ
れるため、主噴霧火炎内の発熱量に対して噴霧火
炎質量が増大し、火炎温度が低下され、NOX生
成が抑えられ、排気有害物質の少ない低公害のデ
イーゼル燃焼を達成できる。 Since the combustion gas of the spray flame from the small nozzle hole formed near the fuel valve is sucked into the main spray flame from the large nozzle hole, the mass of the spray flame increases relative to the calorific value within the main spray flame. The flame temperature is lowered, NOx generation is suppressed, and low-pollution diesel combustion with fewer harmful exhaust substances can be achieved.
第１図は本考案による１実施例の燃料弁の噴孔
部を示す断面図、第２図は第１図の噴孔の配置を
示す平面図、第３図は本考案による燃料噴霧の発
達状況を示すデイーゼルエンジンの断面図、第４
図は第３図のＡ−Ａ矢視図、第５図は従来のデイ
ーゼルエンジンの燃焼室内の燃料噴霧の発達状況
を示すデイーゼルエンジンの断面図、第６図は第
５図のＡ−Ａ矢視図、第７図は従来の燃料弁の噴
孔部を示す断面図、第８図は第７図の噴孔の配置
を示す平面図である。
１０２……小噴孔、１０３……大噴孔、２００
……給気スワール、３１……大噴孔による噴霧、
３２……小噴孔による噴霧。
Fig. 1 is a sectional view showing the nozzle hole portion of a fuel valve according to an embodiment of the present invention, Fig. 2 is a plan view showing the arrangement of the nozzle holes in Fig. 1, and Fig. 3 is a development of fuel spray according to the present invention. Sectional view of a diesel engine showing the situation, No. 4
The figure is a view taken along the line A-A in Fig. 3, Fig. 5 is a cross-sectional view of a diesel engine showing the development of fuel spray in the combustion chamber of a conventional diesel engine, and Fig. 6 is a view taken along the line A-A in Fig. 5. 7 is a sectional view showing the nozzle hole portion of a conventional fuel valve, and FIG. 8 is a plan view showing the arrangement of the nozzle holes in FIG. 7. 102...Small nozzle hole, 103...Large nozzle hole, 200
... Air supply swirl, 31 ... Spray from large nozzle hole,
32...Spraying from small nozzle holes.
Claims (1)
小径の小噴口を有する多噴孔燃料弁を設けるとと
もに、燃焼室内に給気スワールを生成させる手段
を備えた直接噴射室デイーゼルエンジンにおい
て、上記燃料弁は、同数の大噴口と小噴口を有
し、小噴口の方が大噴口よりも上部に位置すると
ともに、大噴口と小噴口とがピストン中心線に直
角な平面への投影において重なり合うように配置
され、かつ小噴口の噴射角を大噴口の噴射角より
も小さく構成したことを特徴とする直接噴射式デ
イーゼルエンジン。 In a direct injection chamber diesel engine, a multi-nozzle fuel valve having a large nozzle and a small nozzle with a diameter smaller than the large nozzle is provided approximately in the center of the combustion chamber, and a means for generating a supply air swirl within the combustion chamber. The above fuel valve has the same number of large nozzles and small nozzles, the small nozzle is located above the large nozzle, and the large nozzle and the small nozzle overlap when projected onto a plane perpendicular to the piston center line. A direct injection diesel engine characterized in that the injection angle of the small nozzle is smaller than the injection angle of the large nozzle.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1987017193U JPH057502Y2 (en) | 1987-02-10 | 1987-02-10 |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1987017193U JPH057502Y2 (en) | 1987-02-10 | 1987-02-10 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS63125172U JPS63125172U (en) | 1988-08-16 |
| JPH057502Y2 true JPH057502Y2 (en) | 1993-02-25 |
Family
ID=30809728
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP1987017193U Expired - Lifetime JPH057502Y2 (en) | 1987-02-10 | 1987-02-10 |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH057502Y2 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2006299885A (en) * | 2005-04-19 | 2006-11-02 | Yanmar Co Ltd | Direct spray type diesel engine |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2565470Y2 (en) * | 1991-05-24 | 1998-03-18 | 株式会社ゼクセル | Fuel injection nozzle |
Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS474083U (en) * | 1971-01-29 | 1972-09-08 |
-
1987
- 1987-02-10 JP JP1987017193U patent/JPH057502Y2/ja not_active Expired - Lifetime
Patent Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS474083U (en) * | 1971-01-29 | 1972-09-08 |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2006299885A (en) * | 2005-04-19 | 2006-11-02 | Yanmar Co Ltd | Direct spray type diesel engine |
Also Published As
| Publication number | Publication date |
|---|---|
| JPS63125172U (en) | 1988-08-16 |
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