JPS60147525A - Combustion device for diesel engine - Google Patents
Combustion device for diesel engineInfo
- Publication number
- JPS60147525A JPS60147525A JP59001394A JP139484A JPS60147525A JP S60147525 A JPS60147525 A JP S60147525A JP 59001394 A JP59001394 A JP 59001394A JP 139484 A JP139484 A JP 139484A JP S60147525 A JPS60147525 A JP S60147525A
- Authority
- JP
- Japan
- Prior art keywords
- spray
- nozzle
- combustion chamber
- nozzle holes
- fuel
- 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 49
- 239000000446 fuel Substances 0.000 claims abstract description 48
- 238000002347 injection Methods 0.000 claims abstract description 9
- 239000007924 injection Substances 0.000 claims abstract description 9
- 239000007921 spray Substances 0.000 claims description 81
- 238000013459 approach Methods 0.000 claims description 4
- 238000004581 coalescence Methods 0.000 claims description 4
- 230000015572 biosynthetic process Effects 0.000 claims 1
- 230000002093 peripheral effect Effects 0.000 abstract 2
- 238000005553 drilling Methods 0.000 abstract 1
- 238000010586 diagram Methods 0.000 description 11
- 230000000694 effects Effects 0.000 description 8
- 230000035515 penetration Effects 0.000 description 8
- 230000007423 decrease Effects 0.000 description 3
- IJGRMHOSHXDMSA-UHFFFAOYSA-N Atomic nitrogen Chemical compound N#N IJGRMHOSHXDMSA-UHFFFAOYSA-N 0.000 description 2
- 239000006185 dispersion Substances 0.000 description 2
- 238000000889 atomisation Methods 0.000 description 1
- 230000005764 inhibitory process Effects 0.000 description 1
- 230000002452 interceptive effect Effects 0.000 description 1
- 230000014759 maintenance of location Effects 0.000 description 1
- 229910052757 nitrogen Inorganic materials 0.000 description 1
- 230000000149 penetrating effect Effects 0.000 description 1
- 238000011144 upstream manufacturing Methods 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
- F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
- F02M61/18—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for
- F02M61/1806—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for characterised by the arrangement of discharge orifices, e.g. orientation or size
- F02M61/182—Discharge orifices being situated in different transversal planes with respect to valve member direction of movement
-
- 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
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
- F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
- F02M61/18—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for
- F02M61/1806—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for characterised by the arrangement of discharge orifices, e.g. orientation or size
- F02M61/1846—Dimensional characteristics of discharge orifices
-
- 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)
- Fuel-Injection Apparatus (AREA)
Abstract
Description
【発明の詳細な説明】
本発明は側方噴射式（中央噴射式に対して）ディーゼル
機関に関する。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to side-injection (versus central-injection) diesel engines.
第１図はこの種機関の要部を示す断面図である。FIG. 1 is a sectional view showing the main parts of this type of engine.
０１は燃焼室、０２はピストン、０３は排気弁。01 is the combustion chamber, 02 is the piston, and 03 is the exhaust valve.
０４は燃料弁、０５は燃料噴霧である。第２図は第１図
の■−Ｂ矢視断面図で、０４は燃料弁。04 is a fuel valve, and 05 is a fuel spray. Fig. 2 is a cross-sectional view taken along the arrow ■-B in Fig. 1, and 04 is a fuel valve.
０６．０７．０８は燃料噴霧を示す。第３図は第１図の
燃料弁０４の先端図で、０９，１０．１１は噴口（等噴
口径１等間隔）である。06.07.08 shows fuel spray. FIG. 3 is a top view of the fuel valve 04 shown in FIG. 1, and 09, 10.11 are nozzle ports (equal nozzle diameter and 1 equal interval).
上記構成において、ピストン０２の上昇によシ燃焼室０
１内の空気は圧縮され高温高圧となシ。In the above configuration, as the piston 02 rises, the combustion chamber 0
The air inside 1 is compressed and becomes high temperature and high pressure.
上死点近傍で燃料弁０４よシ燃料が噴射されて。Fuel was injected through fuel valve 04 near top dead center.
第２図に３噴口の場合を示すように、燃料噴霧０６〜０
８を形成する。これらの噴霧はできるだけ燃焼室内の全
領域の空気を利用できるように形成され、さらに比較的
強い空気渦流によｐ燃料と空気の混合が促進されるため
、空気利用率、燃焼効率の高い燃焼が行われるが以下に
示すような欠点を有している。As shown in Figure 2 for the case of 3 nozzles, fuel spray 06~0
form 8. These sprays are formed to utilize as much air as possible in the entire area within the combustion chamber, and the relatively strong air vortex promotes the mixing of p-fuel and air, resulting in combustion with high air utilization and combustion efficiency. However, it has the following drawbacks.
第２図に示すように、噴霧された燃料は空気渦流Ｓｗに
よシ曲けられながら火炎となって発達する。As shown in FIG. 2, the sprayed fuel develops into a flame while being bent by the air vortex Sw.
このとき燃料噴霧と空気渦流の相対速度の差及び渦流の
上流、下流の位置の相違によシ、窒気渦流の影響は燃焼
室中央側の噴霧に強く、外周側の噴霧に弱く働く。とこ
ろが、噴霧の貫徹力はそれぞれの噴霧とも同等であるだ
め、中央側の噴霧は大きく曲げられ、外周側の噴霧は曲
げられる量が少ない。従って、全噴総が−かた捷シの形
で発達し。At this time, due to the difference in relative speed between the fuel spray and the air vortex and the difference in the upstream and downstream positions of the vortex, the influence of the nitrogen vortex is strong on the spray on the center side of the combustion chamber and weak on the spray on the outer circumferential side. However, since the penetration force of each spray is the same, the spray on the center side is largely bent, and the spray on the outer circumference side is bent less. Therefore, the entire eruption system develops in the form of a -kata kashi.
この領域では噴霧あるいは火炎同志が干渉し燃焼が阻害
される。さらに中央部の噴霧が大きく曲げられるため、
燃焼室中央部に空気の±利用領域が存在し、空気利用率
が低下する。さらに１全燃料噴霧が同時に向い側の燃焼
室壁に到達するため。In this region, the spray or flames interfere with each other and combustion is inhibited. Furthermore, since the spray in the center is greatly bent,
There is an air utilization area in the center of the combustion chamber, and the air utilization rate decreases. Furthermore, all fuel sprays reach the opposite combustion chamber wall at the same time.
この部分で空気不足の状態となシ燃焼が阻害される。There is a lack of air in this area and combustion is inhibited.
これらにより、従来のシステムでは燃焼室内への空間的
１時間的な燃料配分が適当でなく、空気利用率、燃焼効
率が不十分となる。As a result, in the conventional system, spatial and hourly fuel distribution within the combustion chamber is not appropriate, resulting in insufficient air utilization and combustion efficiency.
本発明の目的は上記の点に着目し、側方噴射式（中央噴
射に対して）ディーゼル機関において、燃焼室内への空
間的２時間的な燃料の分散全良好にし、空気利用率、燃
焼効率の高い燃焼を行うことのできる燃焼装置を提供す
ることであシ、その特徴とするところは、シリングヘッ
ドの燃焼室周辺部にそれぞれ複数個の噴口金持つ複数個
の燃料弁を有し同燃焼室内に空気渦流が形成されるディ
ーゼル機関の燃焼装置において、上記燃料弁の複数個の
噴口のうち、燃焼室の中央部である内側に噴霧を形成す
る複数の噴口群と燃焼室の外周＆ｌＳである外側に噴霧
を形成する複数の噴口群とのそれぞれでは、隣接する噴
口の噴口径ｄと噴口間隔Ｓとの比がＳ／ｄ （５であシ
、水平面への投影における各噴口の軸心線のなす角度α
と垂直面への投影における各噴口の軸心線のなす角度β
が、噴口から離れるにつれて軸心線が近づく場合を正と
して。The purpose of the present invention is to improve the spatial and 2-hour distribution of fuel within the combustion chamber in a side-injection type (versus central injection) diesel engine, and improve air utilization efficiency and combustion efficiency. The purpose of the present invention is to provide a combustion device that can perform high combustion, and its feature is that it has a plurality of fuel valves each having a plurality of nozzle fittings around the combustion chamber of the shilling head. In a combustion device for a diesel engine in which an air vortex is formed indoors, among the plurality of nozzles of the fuel valve, there are a plurality of nozzle groups that form a spray inside the central part of the combustion chamber, and a group of nozzles that form a spray inside the central part of the combustion chamber. For each of a plurality of nozzle groups that form a spray on the outside, the ratio of the nozzle diameter d of adjacent nozzles to the nozzle spacing S is S/d (5), and the axis of each nozzle when projected onto a horizontal plane is Angle α between the lines
and the angle β between the axis of each nozzle when projected onto the vertical plane
However, if the axis gets closer as you move away from the nozzle, it is considered positive.
それぞれ−９°〈α〈１１°かっ一９°〈β＜１１°と
なるように噴口が形成され、形成された内側の噴霧群と
外側の噴霧群がそれぞれ合体し２合体した噴霧群は一本
の噴霧として発達すると共に、上記の合体によシ噴ロ数
がｎを正の整数とすると２ｎ個の場合は全体としてｎ本
の噴霧を形成しまた２ｎ＋１個の場合は全体としてｎ＋
１本の噴霧を形成することである。The nozzles are formed so that -9°〈α〈11°〉〈9〈〈β〈11°, respectively, and the formed inner spray group and outer spray group are respectively combined, and the two combined spray groups are one When the number of sprays is 2n, n sprays are formed as a whole, and when the number of sprays is 2n+1, n+ sprays are formed as a whole.
It is to form one spray.
以下図面を参照して本発明による実施例につき説明する
。Embodiments of the present invention will be described below with reference to the drawings.
第４図は本発明にょる１実施例の燃料弁の先端部を示す
説明図、第５図は本発明による燃料弁を用いた場合の隣
接する２本の噴霧の合体を示す説明図である。噴口Ｎ３
とＮ４の例、噴口Ｎ１とＮ２も同様である。第６図は噴
口及び噴口軸心線の水平面への投影図、即ち第４図の■
矢視図、第３図は噴口及び噴口軸心線の垂直面への投影
図。FIG. 4 is an explanatory diagram showing the tip of a fuel valve according to an embodiment of the present invention, and FIG. 5 is an explanatory diagram showing the combination of two adjacent sprays when using the fuel valve according to the present invention. . Spout N3
and N4, and the nozzles N1 and N2 are also similar. Figure 6 is a projection of the nozzle and the axis of the nozzle onto a horizontal plane, i.e.
The arrow view and FIG. 3 are projection views of the nozzle and the nozzle axis on a vertical plane.
即ち第４図のＶＵ矢視図である。第８図はα＝β＝０の
場合のＳ／ｄによる合体の到達距離増大への効果を示す
線図で、ＸＱは噴霧一本の到達距離、Ｘは合体時の到達
距離である。第９図はα、βによる合体の到達距離への
効果を示す線図である。第１０図は本発明による実施例
の燃料弁を用いた場合の燃焼室内の燃料分散状態を示す
説明図である。That is, it is a view taken along the VU arrow in FIG. 4. FIG. 8 is a diagram showing the effect of S/d on increasing the reach of a single spray when α=β=0, where XQ is the reach of a single spray and X is the reach when combined. FIG. 9 is a diagram showing the effect of α and β on the reach distance of the combination. FIG. 10 is an explanatory diagram showing the state of fuel distribution within the combustion chamber when the fuel valve of the embodiment of the present invention is used.
４噴口で燃焼室中央付近の２本の噴霧と燃焼室外周部の
２本の噴霧をそれぞれ合体させ全体として２本の噴霧全
形成した場合を示す。A case is shown in which two sprays near the center of the combustion chamber and two sprays at the outer periphery of the combustion chamber are respectively combined with four nozzles to form two sprays as a whole.
一般に噴口数が２ｎ個の場合（ｎは正の整数）。Generally, when the number of nozzles is 2n (n is a positive integer).
合体によシ全体としてｎ本の噴霧を形成する。また、噴
口数が２ｎ千１個の場合２合体により全体としてｎ＋１
本の噴霧を形成する。The coalescence forms a total of n sprays. In addition, when the number of nozzles is 2n,1,000, the total is n+1 by combining the two.
Forming a book spray.
第４図のＮ１−Ｎ４は本発明による燃料弁の噴口（４噴
口の場合）を示す。N1-N4 in FIG. 4 indicate the nozzle ports (in the case of 4 nozzles) of the fuel valve according to the present invention.
第５図の２θは噴口の拡がシ角度を示す。2θ in FIG. 5 indicates the expansion angle of the nozzle.
第６図のαは第４図に示す燃料弁の水平面への投影にお
いて、隣接する噴口の軸心線がなす角を示す（噴口から
遠ざかるにつれて接近する場合を正とする）。α in FIG. 6 indicates the angle formed by the axes of adjacent nozzles when projected onto the horizontal plane of the fuel valve shown in FIG. 4 (the case where the axes approach each other as they move away from the nozzle is considered positive).
第７図のβは同じく垂直面への投影におい゛て。Similarly, β in Fig. 7 is projected onto the vertical plane.
隣接する噴口の軸心線がなす角を示す（噴口から遠ざか
るにつれて接近する場合を正とする）。Indicates the angle formed by the axes of adjacent nozzles (positive if they approach each other as they move away from the nozzle).
第１０図において、１２は燃焼室、１３は燃料弁、１４
〜１７は本発明の燃料弁を用いた場合に形成される燃料
噴Ｍ、Ｓｗは燃焼室内空気渦流を示す、。In FIG. 10, 12 is a combustion chamber, 13 is a fuel valve, and 14 is a combustion chamber.
17 indicates a fuel injection M formed when the fuel valve of the present invention is used, and Sw indicates an air vortex flow within the combustion chamber.
上記構成の場合の作用について述べる。The operation in the case of the above configuration will be described.
本発明による燃料弁を用いた場合、全体の噴口面積をそ
ろえて、噴口数を増した時（たとえば３孔から４孔にし
た場合）、−噴口あたシの噴口面積は絞られ、各噴霧は
微粒化が促進されて空気導入のよい噴霧が形成される。When using the fuel valve according to the present invention, when the total nozzle area is made the same and the number of nozzles is increased (for example, from 3 holes to 4 holes), - the nozzle area of the nozzle hole is narrowed down, and each spray Atomization is promoted and a spray with good air introduction is formed.
さらに、燃焼室中央側の複数の噴霧及び外側の噴：４貌
をそれぞれ合体させているため、それぞれの噴霧は単独
の噴霧の場合よりも貫徹力が増す。Furthermore, since the plurality of sprays on the central side of the combustion chamber and the four sprays on the outside are combined, the penetration power of each spray is increased compared to the case of a single spray.
上記のように本発明による燃料弁を用いた場合。When using the fuel valve according to the invention as described above.
第１０図に４孔の例を示すように、空気導入特性が良く
、かつ貫徹力が強く到達距離の長い燃料噴霧が全体とし
て２本形成される。As shown in an example of four holes in FIG. 10, two fuel sprays with good air introduction characteristics, strong penetrating force, and long reach are formed as a whole.
上述の場合には次の効果がある。The above case has the following effects.
従来の燃料弁を用いた装置では、各噴霧の貫徹力は同等
であるため空気渦流により内側の噴霧が大きく曲げられ
噴霧同志の干渉が多くなシ燃焼が阻害され、また燃焼室
中央に未利用の空間が残シ。In devices using conventional fuel valves, the penetration force of each spray is the same, so the inner spray is greatly bent by the air vortex, and there is a lot of interference between the sprays, which inhibits combustion. There is still space left.
空気利用率が低下する。さらに、全体の噴霧内への空気
導入量を増すため、噴霧の数を増すと、必然的に各噴口
の噴口径が小さくな）、噴霧の貫徹力が減少して相対的
に空気渦流の影響が大きい状態となり、上記の燃焼阻害
、空気利用率の低下がよシ大きくなる。Air utilization rate decreases. Furthermore, when increasing the number of sprays to increase the amount of air introduced into the overall spray, the diameter of each nozzle inevitably becomes smaller), the penetration force of the spray decreases and the relative effect of air vortex flow increases. becomes large, and the above-mentioned combustion inhibition and reduction in air utilization become even greater.
本発明による場合は、外側の噴霧群と内側の噴霧群を第
５図に示すように、それぞれ合体させることにより、そ
れぞれの噴霧の貫徹力が増し空気渦流Ｓｗの影響を強く
受ける燃焼室中央側の噴霧が大きく曲げられ゛Ｃ外側の
噴霧と干渉しあうことを防ぐことができる。また、噴霧
の直進性が増し燃焼室中央部付近の空間に燃料を分散さ
せることができる。In the case of the present invention, as shown in FIG. 5, by combining the outer spray group and the inner spray group, the penetration power of each spray increases, and the center side of the combustion chamber is strongly affected by the air vortex Sw. It is possible to prevent the spray from being greatly bent and interfering with the spray from outside. Furthermore, the straightness of the spray increases and the fuel can be dispersed in the space near the center of the combustion chamber.
ことで噴霧の拡が多角は第５図に示す２θであシ、２θ
＝ ２ ｆ、ｍ−１（０，４，２７（ｐａ／ρ、）０°
３５ ）、 ｐ８−空気留度、ρ、：燃料密度であるた
め１通常は２θ＝１５゜前後である。また、第６図に示
すように、隣接する二本の噴霧の水平面への投影におい
て、各噴霧の軸心線のなす角度をαとし、同様に垂直面
への投影における各噴霧の軸心線のなす角度をβとする
（α、βとも噴口から遠ざかるにつれ噴霧が接近する場
合を正とする）。隣接する二噴霧が平行の場合（即ち、
α＝β−０の場合う、噴口径ｄと噴口出口の間隔Ｓの比
Ｓ／ｄによシ合体の状態がきまり、第８図に実験結果を
示すように、 Ｓ／ｄ （５で特に合体による貫徹力増
大の効果が犬きり傷ら九。As a result, the polygon of the spray spread is 2θ as shown in Figure 5.
= 2 f, m-1 (0, 4, 27 (pa/ρ,) 0°
35), p8 - air retention, ρ: Since it is the fuel density, 1 is usually around 2θ=15°. In addition, as shown in Figure 6, when two adjacent sprays are projected onto a horizontal plane, the angle formed by the axis of each spray is α, and similarly when projected onto a vertical plane, the axis of each spray is The angle formed by this is assumed to be β (both α and β are positive when the spray approaches as it moves away from the nozzle). When two adjacent sprays are parallel (i.e.
When α=β−0, the state of coalescence is determined by the ratio S/d of the nozzle diameter d and the interval S between the nozzle outlet and S/d (particularly in 5), as shown in the experimental results in Figure 8. The effect of increasing the penetration power by combining is nine.
Ｓ／ｄは５以下とすることが望ましい（Ｘは隣接する２
本の噴霧の全体としての到達距離＋ Ｘ、 ｏは噴霧一
本の場合の到達距離）。It is desirable that S/d be 5 or less (X is the number of adjacent 2
The total distance traveled by the book spray + X, o is the distance traveled by a single spray).
噴霧が平行でない時及び同一平面上にない場合でも（空
間的にねじれの位置関係にある場合でもう。Even when the sprays are not parallel or coplanar (even when they are in a spatially twisted position).
第９図にＳ／ｄ ＝ ３の時のα、βによる噴霧の到達
距離の実験結果を示すように（Ｘは隣接する二本の噴霧
の全体としての到達距離であ５．Ｘｏは噴霧一本の到達
距離）、特に−９°くα＜１１°かっ一９°くβ＜１１
°の時、到達距離は噴霧一本の場合よシも大きくなシ、
噴霧合体による貫徹力増大の効果が大きく得られる。As shown in Fig. 9, the experimental results of the spray travel distance using α and β when S/d = 3 (X is the overall travel distance of two adjacent sprays5. (reaching distance of a book), especially -9° α < 11° and 9° β < 11
°, the distance traveled is much larger than that of a single spray.
The effect of increasing the penetration force due to spray coalescence can be greatly obtained.
以上のように噴口径ｄと噴口出口の間隔Ｓの比をＳ／ｄ
（５とし、かつ外側の噴霧群及び内側の噴霧群のそれ
ぞれにおいて、隣接する噴霧の軸心線の水平面への投影
の々す角αと、垂直面への投影のなす角βが一９°くα
〈１１°かつ一９°〈β〈１１°となるように、噴口全
形成することにより、第１０図に４噴口で外側の２本の
噴霧と内側の２本の噴霧を合体させた場合を示すように
、それぞれの噴霧群の貫徹力が増し、互いの干渉を防ぐ
ことができ。As mentioned above, the ratio of the nozzle diameter d and the interval S between the nozzle outlet and the nozzle exit is S/d
(5, and in each of the outer spray group and the inner spray group, the angle α of the projection of the axis of the adjacent spray onto the horizontal plane and the angle β of the projection onto the vertical plane are 9°) Kuα
By forming all the nozzles so that the angles are 〈11° and -9〈〈β〈11°, Fig. 10 shows the case where the outer two sprays and the inner two sprays are combined with four nozzles. As shown, the penetration power of each spray group increases and mutual interference can be prevented.
また燃焼室中央近傍の空間に燃料を分散させるこ ４と
ができ、燃焼室内の燃料分散が良好となシ、また噴霧自
体も噴口径を絞っであるため空気導入の良い噴霧が形成
され、空気利用率、燃焼効率の高い燃焼が得られる。In addition, the fuel can be dispersed in the space near the center of the combustion chamber, resulting in good fuel dispersion within the combustion chamber.Also, since the spray itself has a narrowed nozzle diameter, a spray with good air introduction is formed. Combustion with high utilization rate and combustion efficiency can be obtained.
第１図は従来の側方噴射式ディーゼル機関の要部を示す
断面図、第２図は第１図のＴＩ −ｎ矢視断面図、第３
図は第１図の燃料弁の先端部を示す説明図、第４図は本
発明による］実施例の燃料弁の先端部を示す説明図、第
５図は本発明による燃料弁を用いた場合の隣接する２本
の噴霧の合体を示す説明図、第６図は第４図のＶｌ矢視
図、第７図は第４図のＶｆｌ矢視図、第８図はＳ／ｄに
よる合体の到達距離増大への効果を示す線図、第９図は
α、βによる合体の到達距離への効果を示す線図、第１
０図は本発明による実施例の燃料弁を用いた場合の燃焼
室内の燃料分散状態ヲ示す説明図である。
１２・・・燃焼室、１３・・・燃料弁、１４〜１７・・
・燃料噴霧＋Ｎ１〜Ｎ４・・・噴口。
７１図
７２図
沖３図
■
第４ＶFigure 1 is a sectional view showing the main parts of a conventional side injection diesel engine, Figure 2 is a sectional view taken along the TI-n arrow in Figure 1, and Figure 3 is a sectional view showing the main parts of a conventional side injection diesel engine.
The figure is an explanatory diagram showing the tip of the fuel valve of FIG. 1, FIG. 4 is an explanatory diagram showing the tip of the fuel valve of the embodiment according to the present invention, and FIG. 5 is an explanatory diagram showing the tip of the fuel valve according to the present invention. 6 is a view in the direction of the Vl arrow in FIG. 4, FIG. 7 is a view in the direction of the Vfl arrow in FIG. Figure 9 is a diagram showing the effect of increasing the reach distance. Figure 9 is a diagram showing the effect of combining α and β on the reach distance.
FIG. 0 is an explanatory diagram showing the state of fuel dispersion in the combustion chamber when the fuel valve of the embodiment of the present invention is used. 12... Combustion chamber, 13... Fuel valve, 14-17...
・Fuel spray + N1 to N4... Nozzle. 71 Figure 72 Offshore Figure 3 ■ 4th V
Claims (1)
の噴口金持つ複数個の燃料弁を有し同燃焼室内に空気渦
流が形成されるディーゼル機関の燃焼装置において、上
記燃料弁の複数個の噴口のうち、燃焼室の中央部である
内側に噴霧を形成する複数の噴口群と燃焼室の外周部で
ある外側に噴霧を形成する複数の噴口群とのそれぞれで
は、隣接。 する噴口の噴口径ｄと噴口間隔Ｓとの比がＳ／ｄ＜５で
あシ、隣接する噴口の水平面への投影における各噴口の
軸心線のなす角度αと垂直面への投影における各噴口の
軸心線のなす角度βが、噴口から離れるにつれて軸心線
が近づく場合を正と［２て。 それぞれ−９°〈α〈１１°かつ一９°〈β＜１−１°
となるように噴口が形成され、形成された内側の噴霧群
と外側の噴霧群がそれぞれ合体し２合体した噴霧群は一
本の噴霧として発達すると共に、上記の合体によシ噴ロ
数がｎｆ正の整数とすると２ｎ個の場合は全体として１
本の噴霧を形成しまた２ｎ＋１個の場合は全体としてｎ
＋１本の噴霧を形成すること全特徴とするディーゼル機
関の燃焼装置。[Scope of Claims] 1. In a combustion device for a diesel engine in which a cylinder head has a plurality of fuel valves each having a plurality of injection nozzles around the combustion chamber, and an air vortex is formed in the combustion chamber, the above-mentioned fuel Among the plurality of nozzles of the valve, a plurality of nozzle groups that form spray on the inner side, which is the central part of the combustion chamber, and a plurality of nozzle groups, that form spray on the outer side, which is the outer periphery of the combustion chamber, are adjacent to each other. . The ratio of the nozzle diameter d of the nozzles to the nozzle spacing S must be S/d<5, and the angle α formed by the axial center line of each nozzle when projected onto the horizontal plane of adjacent nozzles is The angle β formed by the axial line of the nozzle is positive if the axial line approaches the further away from the nozzle. -9°〈α〈11° and -9°〈β＜1-1° respectively
A nozzle is formed so that the formed inner spray group and outer spray group are respectively merged, and the two merged spray groups develop as one spray, and the number of sprays increases due to the above coalescence. If nf is a positive integer, if there are 2n pieces, the total is 1
Forms a spray of books, and in the case of 2n+1, the total is n
A combustion device for a diesel engine, which is characterized by the formation of one spray.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP59001394A JPH0637851B2 (en) | 1984-01-10 | 1984-01-10 | Combustion device for a diesel engine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP59001394A JPH0637851B2 (en) | 1984-01-10 | 1984-01-10 | Combustion device for a diesel engine |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS60147525A true JPS60147525A (en) | 1985-08-03 |
| JPH0637851B2 JPH0637851B2 (en) | 1994-05-18 |
Family
ID=11500271
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP59001394A Expired - Lifetime JPH0637851B2 (en) | 1984-01-10 | 1984-01-10 | Combustion device for a diesel engine |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH0637851B2 (en) |
Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0286916A (en) * | 1988-09-21 | 1990-03-27 | Mitsui Eng & Shipbuild Co Ltd | Abating method for nox in diesel engine |
| FR2663084A1 (en) * | 1990-06-07 | 1991-12-13 | Semt Pielstick | INJECTION DEVICE FOR AN INTERNAL COMBUSTION ENGINE. |
| CN1050878C (en) * | 1992-09-11 | 2000-03-29 | 瓦特西拉Nsd施丰兹公司 | A process for the injection of fuel in diesel internal combustion engines |
| CN103967673A (en) * | 2013-02-01 | 2014-08-06 | 马自达汽车株式会社 | Diesel engine |
| JP2014173493A (en) * | 2013-03-08 | 2014-09-22 | Mazda Motor Corp | Compression ignition engine |
| JP2014194158A (en) * | 2013-03-28 | 2014-10-09 | Mazda Motor Corp | Fuel injection control device for diesel engine |
| US8869770B2 (en) | 2011-06-17 | 2014-10-28 | Caterpillar Inc. | Compression ignition engine having fuel system for non-sooting combustion and method |
| CN117108395A (en) * | 2023-10-23 | 2023-11-24 | 潍柴动力股份有限公司 | Combustion chamber, combustion system and design method thereof, and engine |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS51126823U (en) * | 1975-04-08 | 1976-10-14 | ||
| JPS5842363U (en) * | 1981-09-18 | 1983-03-22 | 三井造船株式会社 | Fuel injection valve in internal combustion engine |
-
1984
- 1984-01-10 JP JP59001394A patent/JPH0637851B2/en not_active Expired - Lifetime
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS51126823U (en) * | 1975-04-08 | 1976-10-14 | ||
| JPS5842363U (en) * | 1981-09-18 | 1983-03-22 | 三井造船株式会社 | Fuel injection valve in internal combustion engine |
Cited By (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0286916A (en) * | 1988-09-21 | 1990-03-27 | Mitsui Eng & Shipbuild Co Ltd | Abating method for nox in diesel engine |
| FR2663084A1 (en) * | 1990-06-07 | 1991-12-13 | Semt Pielstick | INJECTION DEVICE FOR AN INTERNAL COMBUSTION ENGINE. |
| US5167210A (en) * | 1990-06-07 | 1992-12-01 | S.E.M.T. Pielstick | Injector device for an internal combustion engine |
| CN1050878C (en) * | 1992-09-11 | 2000-03-29 | 瓦特西拉Nsd施丰兹公司 | A process for the injection of fuel in diesel internal combustion engines |
| US8869770B2 (en) | 2011-06-17 | 2014-10-28 | Caterpillar Inc. | Compression ignition engine having fuel system for non-sooting combustion and method |
| CN103967673A (en) * | 2013-02-01 | 2014-08-06 | 马自达汽车株式会社 | Diesel engine |
| JP2014173493A (en) * | 2013-03-08 | 2014-09-22 | Mazda Motor Corp | Compression ignition engine |
| JP2014194158A (en) * | 2013-03-28 | 2014-10-09 | Mazda Motor Corp | Fuel injection control device for diesel engine |
| CN117108395A (en) * | 2023-10-23 | 2023-11-24 | 潍柴动力股份有限公司 | Combustion chamber, combustion system and design method thereof, and engine |
| CN117108395B (en) * | 2023-10-23 | 2024-01-16 | 潍柴动力股份有限公司 | Combustion chamber, combustion system and design method thereof, and engine |
Also Published As
| Publication number | Publication date |
|---|---|
| JPH0637851B2 (en) | 1994-05-18 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| EXPY | Cancellation because of completion of term |