JPH04259662A - Multi-jet type two-step injecting automatic fuel injector of diesel engine - Google Patents

Multi-jet type two-step injecting automatic fuel injector of diesel engine

Info

Publication number
JPH04259662A
JPH04259662A JP4133891A JP4133891A JPH04259662A JP H04259662 A JPH04259662 A JP H04259662A JP 4133891 A JP4133891 A JP 4133891A JP 4133891 A JP4133891 A JP 4133891A JP H04259662 A JPH04259662 A JP H04259662A
Authority
JP
Japan
Prior art keywords
valve
pressure
low
nozzle
low pressure
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.)
Pending
Application number
JP4133891A
Other languages
Japanese (ja)
Inventor
Satoshi Fujii
聡 藤井
Seiji Kioka
木岡 精二
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Kubota Corp
Original Assignee
Kubota Corp
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Kubota Corp filed Critical Kubota Corp
Priority to JP4133891A priority Critical patent/JPH04259662A/en
Publication of JPH04259662A publication Critical patent/JPH04259662A/en
Pending legal-status Critical Current

Links

Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02BINTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B3/00Engines characterised by air compression and subsequent fuel addition
    • F02B3/06Engines characterised by air compression and subsequent fuel addition with compression ignition

Landscapes

  • Fuel-Injection Apparatus (AREA)

Abstract

PURPOSE:To prevent bluish white smoking resulting from drop of the penetration force of the injected fuel in the condition that the injection is made with minor quantity and low pressure at the time of low load bearing. CONSTITUTION:A nozzle valve 6 is formed by fitting a cylindrical nozzle valve 6b for low pressure on a nozzle valve 6a for high pressure with possibility of sliding with the tightness held. The high pressure nozzle valve 6a is put by a valve shutting spring for high pressure 7 in closed contact with a valve seat for high pressure 3a, while the low pressure nozzle valve 6b put by a low pressure valve shutting spring 8 in closed contact with a valve seat for low pressure 3b. A working chamber 2 for valve opening consists of a high- pressure valve opening chamber 2a situated between the two valve seats 3a, 3b and a low-pressure valve opening chamber 2b located at the periphery of the low pressure valve seat 3b. At this low-pressure valve opening chamber 2b, a plurality of jets 9 for low pressure are opened. The fuel is injected only from these low pressure jets 9 having a minor bore in the condition that the injection is made in a minor quantity and with low pressure at the time of low load bearing, which should ensure securing the penetration force.

Description

【発明の詳細な説明】[Detailed description of the invention]

【0001】0001

【産業上の利用分野】本発明は、ディーゼルエンジンの
多孔形2段噴射式燃料自動噴射器に関する。
BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a multi-hole two-stage automatic fuel injector for diesel engines.

【0002】0002

【前提構造】本発明のディーゼルエンジンの多孔形2段
噴射式燃料自動噴射器は、例えば図1または図3に示す
ように、次に示す前提構造を有するものを前提とする。 すなわち、多孔ノズルのノズル本体1の内部に、開弁用
作動室2・弁座3・分流室4・及び周方向に並ぶ複数本
の噴口5…を順に連通させて設け、このノズル本体1内
にノズル弁6を挿入してある。そして、このノズル弁6
は、高圧用閉弁ばね7及び低圧用閉弁ばね8で上記弁座
3に閉弁接当させるのに対し、上記開弁用作動室2内の
燃料圧で、まず低圧用閉弁ばね8に抗して開弁作動させ
、次いで高圧用閉弁ばね7で開弁作動させるように構成
してある。この前提構造は、ディーゼルノックを防止す
る利点がある。噴射開始時には、ノズル弁6の弁開量が
小さいうえ噴射圧が低いため、噴射量が少なく、発火遅
れ期間中の噴射燃料の蓄積量が少なくなり、ディーゼル
ノックが起こりにくくなるのである。
[Prerequisite Structure] The multi-hole two-stage automatic fuel injector for a diesel engine of the present invention is predicated on having the following prerequisite structure, as shown in FIG. 1 or 3, for example. That is, inside the nozzle body 1 of the multi-hole nozzle, a valve opening operating chamber 2, a valve seat 3, a flow dividing chamber 4, and a plurality of jet ports 5 arranged in the circumferential direction are provided in order to communicate with each other. A nozzle valve 6 is inserted into the hole. And this nozzle valve 6
In this case, the high-pressure valve-closing spring 7 and the low-pressure valve-closing spring 8 are brought into valve-closing contact with the valve seat 3, whereas the low-pressure valve-closing spring 8 is first brought into contact with the fuel pressure in the valve-opening working chamber 2. The valve is opened against the pressure, and then the high pressure valve closing spring 7 is used to open the valve. This prerequisite structure has the advantage of preventing diesel knock. At the start of injection, the opening amount of the nozzle valve 6 is small and the injection pressure is low, so the injection amount is small, and the amount of accumulated fuel injected during the ignition delay period is small, making diesel knock less likely to occur.

【0003】0003

【従来の技術】上記の前提構造において、燃料を2段噴
射するための具体的構造として、従来技術では図3に示
すものがある。すなわち、前記ノズル弁6は、低圧用閉
弁ばね8と高圧ばね受具7aとを順に介して高圧用閉弁
ばね7で閉弁側へ弾圧される。高圧ばね受具7aは閉弁
ストロークの途中でストッパ7bに受け止められる。ノ
ズル弁6は開弁ストロークの途中で高圧ばね受具7aに
接当する。開弁用作動室2が圧力上昇して行く過程にお
いて、低圧開弁設定圧P1(例えば180kg/cm2
)を越えた時に、ノズル弁6が低圧用閉弁ばね8に抗し
て開弁され、高圧ばね受具7aで受け止められて弁半開
状態に保たれる。そして、高圧開弁設定圧P2(例えば
230kg/cm2)を越えた時に、ノズル弁6が高圧
用閉弁ばね7に抗して弁全開状態になる。
2. Description of the Related Art In the above-mentioned prerequisite structure, a specific structure for two-stage injection of fuel is shown in FIG. 3 in the prior art. That is, the nozzle valve 6 is urged toward the valve closing side by the high pressure valve closing spring 7 via the low pressure valve closing spring 8 and the high pressure spring receiver 7a in this order. The high pressure spring receiver 7a is received by the stopper 7b during the valve closing stroke. The nozzle valve 6 comes into contact with the high pressure spring receiver 7a during the valve opening stroke. In the process of increasing the pressure in the valve opening working chamber 2, the low valve opening setting pressure P1 (for example, 180 kg/cm2
. Then, when the high pressure valve opening setting pressure P2 (for example, 230 kg/cm2) is exceeded, the nozzle valve 6 resists the high pressure valve closing spring 7 and becomes fully open.

【0004】0004

【発明が解決しようとする課題】上記の従来技術では、
軽負荷ないし無負荷時には、青白煙が発生し易いと言う
問題がある。エンジンの定格負荷時には、燃料の噴射量
が多くて、噴射圧が高圧開弁設定圧P2よりも高い高圧
状態で噴射される。各噴口5…の口径D1は、この定格
負荷時の高圧噴射状態で、噴射燃料の噴射率と貫徹力と
が両立する寸法に設定されている。ところが、軽負荷な
いし無負荷時には、噴射量が少なくて、噴射圧が高圧開
弁設定圧P2に達しない低圧状態で噴射される。この低
圧噴射状態に対しては、上記噴口5…の口径D1の寸法
が大き過ぎることになるため、噴射燃料の貫徹力が弱く
なり過ぎて、混合性能が低下し、青白煙が発生し易くな
るのである。本発明は、定格負荷時には、噴射燃料の噴
射率と貫徹力とを適正に保持しながらも、軽負荷ないし
無負荷時には、噴射燃料の貫徹力の低下による青白煙の
発生を防止することを、課題とする。
[Problem to be solved by the invention] In the above conventional technology,
There is a problem in that blue and white smoke is likely to be generated when the load is light or no load. When the engine is under rated load, the amount of fuel injected is large and the fuel is injected at a high pressure state where the injection pressure is higher than the high pressure valve opening setting pressure P2. The diameter D1 of each nozzle port 5 is set to a size that achieves both the injection rate and penetration force of the injected fuel in the high-pressure injection state at the rated load. However, when the load is light or no load, the injection amount is small and the injection pressure is injected at a low pressure that does not reach the high pressure valve opening setting pressure P2. For this low-pressure injection state, the size of the diameter D1 of the nozzle 5 is too large, so the penetration force of the injected fuel becomes too weak, the mixing performance deteriorates, and blue-white smoke is likely to occur. It is. The present invention aims to prevent the generation of blue-white smoke due to a decrease in the penetration force of the injected fuel at light loads or no loads, while maintaining the injection rate and penetration force of the injected fuel appropriately at the rated load. Take it as a challenge.

【0005】[0005]

【課題を解決するための手段】本発明は、前記前提構造
において、上記課題を解決するために、例えば図1及び
図2に示すように、次の特徴構造を追加した事を特徴と
する。すなわち、ノズル弁6は、高圧用ノズル弁6aに
筒形の低圧用ノズル弁6bを保密摺動自在に外嵌させる
。また、弁座3は高圧用弁座3aの外周部に低圧用弁座
3bを設けて成る。その高圧用ノズル弁6aは、高圧用
閉弁ばね7でその高圧用弁座3aに閉止接当させるのに
対し、その低圧用ノズル弁6bは、低圧用閉弁ばね8で
その低圧用弁座3bに閉止接当させる。開弁用作動室2
は、この高圧用弁座3aとこの低圧弁座3bとの間に、
高圧開弁用作動室2aを形成するとともに、その低圧用
弁座3bの外周部に低圧開弁用作動室2bを形成して成
る。その高圧開弁用作動室2aに、複数本の低圧用噴口
9…をその室周方向に並列させて開口して構成する。
[Means for Solving the Problems] In order to solve the above problems, the present invention is characterized by adding the following characteristic structure to the above-mentioned prerequisite structure, as shown in FIGS. 1 and 2, for example. That is, in the nozzle valve 6, a cylindrical low-pressure nozzle valve 6b is fitted onto the high-pressure nozzle valve 6a in a sealed and slidable manner. Further, the valve seat 3 is formed by providing a low pressure valve seat 3b on the outer periphery of a high pressure valve seat 3a. The high-pressure nozzle valve 6a is brought into closing contact with its high-pressure valve seat 3a by a high-pressure valve closing spring 7, whereas the low-pressure nozzle valve 6b is brought into close contact with its low-pressure valve seat 3a by a low-pressure valve closing spring 8. 3b to make a closing contact. Valve opening operating chamber 2
is between this high pressure valve seat 3a and this low pressure valve seat 3b,
A high-pressure valve opening working chamber 2a is formed, and a low-pressure valve opening working chamber 2b is formed on the outer periphery of the low-pressure valve seat 3b. The high-pressure valve-opening working chamber 2a is configured with a plurality of low-pressure nozzles 9 opened in parallel in the circumferential direction of the chamber.

【0006】[0006]

【作用】本発明は次のように作用する。エンジンの定格
負荷時には、燃料噴射量が多いため、開弁用作動室2が
前記高圧開弁設定圧P2以上の高圧噴射状態となり、低
圧用ノズル弁6bも高圧用ノズル弁6aも全開され、各
噴射口5…と各低圧用噴射口9…との両方から燃料が噴
射される。各噴口5…の口径D1と各低圧用噴口9…の
口径D2とは、この定格負荷時の多量・高圧噴射状態で
、噴射燃料の噴射率と貫徹力とが両立する寸法に設定さ
れている。エンジンの軽負荷ないし無負荷時には、燃料
噴射量が少ないため、開弁用作動室2が,前記低圧開弁
設定圧P1よりも高いが高圧開弁設定圧P2よりも低い
,低圧噴射状態となり、低圧用ノズル弁6bのみが開い
て、各低圧用噴射口9…のみから燃料が噴射される。 各低圧用噴射口9…の口径D2は、この軽負荷ないし無
負荷時の少ない燃料噴射量に見合う小さい寸法に設定さ
れているため、噴射燃料の直進性能が高められている。 これにより、軽負荷ないし無負荷時の低圧噴射状態でも
、噴射燃料の噴射率も貫徹力も充分に確保される。
[Operation] The present invention operates as follows. When the engine is under rated load, the fuel injection amount is large, so the valve-opening working chamber 2 enters a high-pressure injection state equal to or higher than the high-pressure valve-opening set pressure P2, and both the low-pressure nozzle valve 6b and the high-pressure nozzle valve 6a are fully opened. Fuel is injected from both the injection ports 5 and each low pressure injection port 9. The diameter D1 of each nozzle 5 and the diameter D2 of each low-pressure nozzle 9 are set to dimensions that achieve both the injection rate and penetration force of the injected fuel in this large-volume, high-pressure injection state at the rated load. . When the engine is under light load or no load, the fuel injection amount is small, so the valve opening working chamber 2 is in a low pressure injection state, which is higher than the low pressure valve opening setting pressure P1 but lower than the high pressure valve opening setting pressure P2, Only the low-pressure nozzle valve 6b opens, and fuel is injected only from each low-pressure injection port 9. The diameter D2 of each low-pressure injection port 9 is set to a small size commensurate with the small fuel injection amount during light load or no-load conditions, so that the straight-line performance of the injected fuel is improved. As a result, sufficient injection rate and penetration force of the injected fuel can be ensured even in a low pressure injection state under light load or no load.

【0007】[0007]

【発明の効果】本発明は、上記のように構成され作用す
ることから次の効果を奏する。エンジンの定格負荷時の
多量・高圧噴射状態では、各噴口5…と各低圧用噴口9
…との両方から燃料が噴射されるので、噴射燃料の噴射
率と貫徹力とが両立されて、良好な燃焼性能を確保でき
る。しかも、軽負荷ないし無負荷時の少量・低圧噴射状
態では、小口径の各低圧用噴口9…のみから燃料が噴射
されるので、噴射燃料の噴射率も貫徹力も充分に確保で
き、混合性能が高められ、青白煙の発生を大幅に低減さ
せ又は防止することができる。
[Effects of the Invention] The present invention has the following effects because it is constructed and operates as described above. In the high-volume, high-pressure injection state at the rated load of the engine, each nozzle 5... and each low-pressure nozzle 9
Since fuel is injected from both sides, the injection rate and penetration force of the injected fuel are compatible, and good combustion performance can be ensured. Moreover, in a small amount, low pressure injection state under light load or no load, fuel is injected only from each small-diameter low-pressure nozzle 9..., so the injection rate and penetration force of the injected fuel can be ensured sufficiently, and the mixing performance can be improved. and the generation of blue-white smoke can be significantly reduced or prevented.

【0008】[0008]

【実施例】以下、本発明の実施例を図面で説明する。図
1は、ディーゼルエンジンの多孔形2段噴射式燃料自動
噴射器の縦断面図、図2(A)は、ディーゼルエンジン
の多孔形2段噴射式燃料自動噴射器の要部縦断面図、図
2(B)は、図2(A)のX−X線矢視断面図である。 図において、多孔ノズルのノズル本体1の内部に、開弁
用作動室2・弁座3・分流室4・及び周方向に並ぶ複数
本の噴口5…を順に連通させて設け、このノズル本体1
内にノズル弁6を挿入してある。この弁座3は高圧用弁
座3aの外周部に低圧用弁座3bを設けて成る。上記ノ
ズル弁6は、高圧用ノズル弁6aに筒形の低圧用ノズル
弁6bを保密摺動自在に外嵌させてある。この高圧用ノ
ズル弁6aは、低圧用閉弁ばね8と高圧ばね受具7aと
を順に介して、高圧用閉弁ばね7で上記高圧用弁座3a
に閉弁接当させ、閉弁側へ弾圧される。また、上記低圧
用ノズル弁6bは、低圧用閉弁ばね8で上記低圧用弁座
3bに閉止接当させてある。そして、上記高圧ばね受具
7aは、閉弁ストロークの途中でストッパ7bに受け止
められる。また、低圧ノズル弁6bは、開弁ストローク
の途中で高圧用ノズル弁6aを介して高圧ばね受具7a
に接当して、上記高圧用閉弁ばね7で弾圧される。前記
開弁用作動室2は、上記高圧用弁座3aと上記低圧弁座
3bとの間に、高圧開弁用作動室2aを形成するととも
に、その低圧用弁座3bの外周部に低圧開弁用作動室2
bを形成してある。その高圧開弁用作動室2aに、複数
本の低圧用噴口9…をその室周方向に並列させて開口し
て構成してある。この各噴口5…の口径D1と各低圧用
噴口9…の口径D2とは、定格負荷時の多量・高圧噴射
状態で、噴射燃料の噴射率と貫徹力とが両立する寸法に
設定され、かつ、各低圧用噴射口9…の口径D2は、軽
負荷ないし無負荷時の少ない燃料噴射量に見合う小さい
寸法に設定されている。そして、前記ノズル本体1は、
袋ナット10によりノズルホルダ11に締め付け固定さ
れている。
Embodiments Hereinafter, embodiments of the present invention will be explained with reference to the drawings. Fig. 1 is a longitudinal cross-sectional view of a multi-hole two-stage automatic fuel injector for a diesel engine, and Fig. 2 (A) is a longitudinal cross-sectional view of a main part of a multi-porous two-stage automatic fuel injector for a diesel engine. 2(B) is a sectional view taken along the line X--X in FIG. 2(A). In the figure, inside a nozzle body 1 of a multi-hole nozzle, a valve opening operating chamber 2, a valve seat 3, a flow dividing chamber 4, and a plurality of nozzles 5 arranged in the circumferential direction are provided in order to communicate with each other.
A nozzle valve 6 is inserted inside. This valve seat 3 is formed by providing a low pressure valve seat 3b on the outer periphery of a high pressure valve seat 3a. In the nozzle valve 6, a cylindrical low-pressure nozzle valve 6b is fitted onto the high-pressure nozzle valve 6a in a sealed and slidable manner. This high pressure nozzle valve 6a is connected to the high pressure valve seat 3a by the high pressure valve closing spring 7 via the low pressure valve closing spring 8 and the high pressure spring receiver 7a in this order.
The valve is brought into contact with the valve to close it, and the valve is pressed toward the valve-closing side. Further, the low pressure nozzle valve 6b is brought into close contact with the low pressure valve seat 3b by a low pressure valve closing spring 8. The high-pressure spring receiver 7a is received by the stopper 7b during the valve closing stroke. Further, the low pressure nozzle valve 6b is connected to the high pressure spring receiver 7a via the high pressure nozzle valve 6a during the valve opening stroke.
, and is pressed by the high pressure valve closing spring 7. The valve-opening working chamber 2 forms a high-pressure valve-opening working chamber 2a between the high-pressure valve seat 3a and the low-pressure valve seat 3b, and a low-pressure opening on the outer periphery of the low-pressure valve seat 3b. Valve working chamber 2
b is formed. The high-pressure valve-opening working chamber 2a is configured with a plurality of low-pressure nozzles 9 opened in parallel in the circumferential direction of the chamber. The diameter D1 of each nozzle 5 and the diameter D2 of each low-pressure nozzle 9 are set to dimensions that achieve both the injection rate and penetration force of the injected fuel in a large-volume, high-pressure injection state at rated load, and , the diameter D2 of each low-pressure injection port 9 is set to a small size suitable for a small fuel injection amount under light load or no load. The nozzle body 1 is
It is tightened and fixed to a nozzle holder 11 with a cap nut 10.

【0009】上述の本発明実施例では、図示しない燃料
ポンプから圧送された燃料が、図中の矢印の方向からき
て、低圧開弁用作動室2bが圧力上昇して行く過程にお
いて、低圧開弁設定圧P1(例えば180kg/cm2
)を越えた時に、低圧ノズル弁6bが低圧用閉弁ばね8
に抗して開弁され、高圧ノズル弁6aを介して高圧ばね
受具7aで受け止められて、弁半開状態に保たれる。そ
して、エンジンの定格負荷時のように、燃料噴射量が多
く燃料圧力が高くなると、高圧開弁設定圧P2(例えば
230kg/cm2)を越えて、高圧ノズル弁6aが高
圧用閉弁ばね7に抗して弁全開状態になり、低圧用ノズ
ル弁6bも高圧用ノズル弁6aも全開され、各噴射口5
…と各低圧用噴射口9…との両方から燃料が噴射される
。一方、エンジンの軽負荷ないし無負荷時には、燃料噴
射量が少ないため、低圧開弁用作動室2bが、前記低圧
開弁設定圧P1よりも高いが高圧開弁設定圧P2よりも
低い、低圧噴射状態となり、低圧用ノズル弁6bのみが
開いて、各低圧用噴射口9…のみから燃料が噴射される
。この各低圧用噴射口9…の口径D2は、軽負荷ないし
無負荷時の少ない燃料噴射量に見合う、小さい寸法に設
定されているから、軽負荷ないし無負荷時の低圧噴射状
態でも、噴射燃料の噴射率も貫徹力も充分に確保される
。そのため、燃料の噴霧特性が良くなって燃焼性能が高
められ、青白煙が出ると言う問題が無くなる。
In the above embodiment of the present invention, the fuel pumped from the fuel pump (not shown) comes from the direction of the arrow in the figure, and in the process of increasing the pressure in the low pressure valve opening working chamber 2b, the low pressure valve opening is performed. Set pressure P1 (e.g. 180 kg/cm2
), the low pressure nozzle valve 6b closes the low pressure valve closing spring 8.
The valve is opened against the high pressure nozzle valve 6a and is received by the high pressure spring receiver 7a to maintain the valve in a half-open state. When the fuel injection amount is large and the fuel pressure is high, such as when the engine is under rated load, the high-pressure valve opening setting pressure P2 (for example, 230 kg/cm2) is exceeded, and the high-pressure nozzle valve 6a is connected to the high-pressure valve closing spring 7. The valves are fully opened, and both the low-pressure nozzle valve 6b and the high-pressure nozzle valve 6a are fully opened, and each injection port 5
... and each low pressure injection port 9... fuel is injected from both. On the other hand, when the engine is under light load or no load, the fuel injection amount is small, so the low-pressure valve opening working chamber 2b is injected with low-pressure injection, which is higher than the low-pressure valve-opening set pressure P1 but lower than the high-pressure valve-opening set pressure P2. state, only the low-pressure nozzle valve 6b opens, and fuel is injected only from each low-pressure injection port 9. The diameter D2 of each low-pressure injection port 9 is set to a small size that corresponds to the small amount of fuel injection at light load or no load, so even in the low pressure injection state at light load or no load, the injected fuel Sufficient injection rate and penetration force are ensured. Therefore, the atomization characteristics of the fuel are improved, the combustion performance is enhanced, and the problem of blue-white smoke is eliminated.

【図面の簡単な説明】[Brief explanation of the drawing]

【図1】本発明実施例を示し、図1はディーゼルエンジ
ンの多孔形2段噴射式燃料自動噴射器の縦断面図である
FIG. 1 shows an embodiment of the present invention, and FIG. 1 is a longitudinal sectional view of a multi-hole two-stage automatic fuel injector for a diesel engine.

【図2】本発明実施例を示し、図2(A)はディーゼル
エンジンの多孔形2段噴射式燃料自動噴射器の要部縦断
面図、図2(B)は図2(A)のX−X線矢視断面図で
ある。
2 shows an embodiment of the present invention, FIG. 2(A) is a longitudinal cross-sectional view of a main part of a multi-hole two-stage automatic fuel injector for a diesel engine, and FIG. 2(B) is a - It is an X-ray arrow sectional view.

【図3】従来例を示し、図1に相当する図である。FIG. 3 is a diagram showing a conventional example and corresponding to FIG. 1;

【符号の説明】[Explanation of symbols]

1…ノズル本体、2…開弁用作動室、2a…高圧開弁用
作動室、2b…低圧開弁用作動室、3…弁座、3a…高
圧用弁座、3b…低圧用弁座、4…分流室、5…噴口、
6…ノズル弁、6a…高圧用ノズル弁、6b…低圧用ノ
ズル弁、7…高圧用閉弁ばね、8…低圧用閉弁ばね、9
…低圧用噴口。
1... Nozzle body, 2... Working chamber for valve opening, 2a... Working chamber for high pressure valve opening, 2b... Working chamber for low pressure valve opening, 3... Valve seat, 3a... Valve seat for high pressure, 3b... Valve seat for low pressure, 4... Diversion chamber, 5... Nozzle,
6... Nozzle valve, 6a... Nozzle valve for high pressure, 6b... Nozzle valve for low pressure, 7... Valve closing spring for high pressure, 8... Valve closing spring for low pressure, 9
...Low pressure nozzle.

Claims (1)

【特許請求の範囲】[Claims] 【請求項1】  多孔ノズルのノズル本体(1)の内部
に、開弁用作動室(2)・弁座(3)・分流室(4)・
及び周方向に並ぶ複数本の噴口(5…)を順に連通させ
て設け、このノズル本体(1)内にノズル弁(6)を挿
入し、このノズル弁(6)は高圧用閉弁ばね(7)及び
低圧用閉弁ばね(8)で上記弁座(3)に閉弁接当させ
るのに対し、上記開弁用作動室(2)内の燃料圧で、ま
ず低圧用閉弁ばね(8)に抗して開弁作動させ、次いで
高圧用閉弁ばね(7)で開弁作動させるように構成した
ディーゼルエンジンの多孔形2段噴射式燃料自動噴射器
において、前記ノズル弁(6)は高圧用ノズル弁(6a
)に筒形の低圧用ノズル弁(6b)を保密摺動自在に外
嵌させて成り、前記弁座(3)は高圧用弁座(3a)の
外周部に低圧用弁座(3b)を設けて成り、その高圧用
ノズル弁(6a)は、前記高圧用閉弁ばね(7)でその
高圧用弁座(3a)に閉止接当させるのに対し、その低
圧用ノズル弁(6b)は、前記低圧用閉弁ばね(8)で
その低圧用弁座(3b)に閉止接当させ、前記開弁用作
動室(2)は、この高圧用弁座(3a)とこの低圧弁座
(3b)との間に、高圧開弁用作動室(2a)を形成す
るとともに、その低圧用弁座(3b)の外周部に低圧開
弁用作動室(2b)を形成して成り、その高圧開弁用作
動室(2a)に、複数本の低圧用噴口(9…)をその室
周方向に並列させて開口して構成したことを特徴とする
ディーゼルエンジンの多孔形2段噴射式燃料自動噴射器
[Claim 1] Inside the nozzle body (1) of the multi-hole nozzle, a valve opening operating chamber (2), a valve seat (3), a diversion chamber (4),
A plurality of nozzle ports (5...) arranged in the circumferential direction are provided in order to communicate with each other, and a nozzle valve (6) is inserted into this nozzle body (1), and this nozzle valve (6) is equipped with a high pressure valve closing spring ( 7) and the low pressure valve closing spring (8) are brought into valve closing contact with the valve seat (3), whereas the low pressure valve closing spring (8) is first brought into contact with the fuel pressure in the valve opening working chamber (2). In the multi-hole two-stage automatic fuel injector for a diesel engine, the nozzle valve (6) is configured to open the valve against the pressure of the nozzle valve (6) and then open the valve using the high-pressure valve closing spring (7). is the high pressure nozzle valve (6a
) is fitted with a cylindrical low pressure nozzle valve (6b) in a sealed and slidable manner, and the valve seat (3) has a low pressure valve seat (3b) on the outer periphery of the high pressure valve seat (3a). The high-pressure nozzle valve (6a) is brought into closing contact with the high-pressure valve seat (3a) by the high-pressure valve closing spring (7), whereas the low-pressure nozzle valve (6b) , the low pressure valve closing spring (8) is brought into close contact with the low pressure valve seat (3b), and the valve opening working chamber (2) is connected to the high pressure valve seat (3a) and the low pressure valve seat (3a). A high-pressure valve opening working chamber (2a) is formed between the high-pressure valve seat (3b) and a low-pressure valve-opening working chamber (2b) is formed on the outer periphery of the low-pressure valve seat (3b). A multi-hole two-stage injection fuel automatic for a diesel engine, characterized in that a valve opening working chamber (2a) has a plurality of low pressure nozzles (9...) opened in parallel in the circumferential direction of the chamber. Injector.
JP4133891A 1991-02-12 1991-02-12 Multi-jet type two-step injecting automatic fuel injector of diesel engine Pending JPH04259662A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP4133891A JPH04259662A (en) 1991-02-12 1991-02-12 Multi-jet type two-step injecting automatic fuel injector of diesel engine

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP4133891A JPH04259662A (en) 1991-02-12 1991-02-12 Multi-jet type two-step injecting automatic fuel injector of diesel engine

Publications (1)

Publication Number Publication Date
JPH04259662A true JPH04259662A (en) 1992-09-16

Family

ID=12605736

Family Applications (1)

Application Number Title Priority Date Filing Date
JP4133891A Pending JPH04259662A (en) 1991-02-12 1991-02-12 Multi-jet type two-step injecting automatic fuel injector of diesel engine

Country Status (1)

Country Link
JP (1) JPH04259662A (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2016008505A (en) * 2014-06-20 2016-01-18 三菱重工業株式会社 Fuel injection valve and fuel injection device

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2016008505A (en) * 2014-06-20 2016-01-18 三菱重工業株式会社 Fuel injection valve and fuel injection device

Similar Documents

Publication Publication Date Title
US4266727A (en) Double-needle injection-valve
US5170751A (en) Water-injection diesel engine
JPH0216360A (en) Fuel injection device of internal combustion engine
EP0365130B1 (en) Fuel injection nozzle
JPS5950848B2 (en) Fuel injection valve for internal combustion engine with pre-chamber
CN111120166A (en) Integrated direct-injection dual-fuel injector with check valve
US5651346A (en) Accumulator-type injection system
JPH10141185A (en) Fuel injection valve for internal combustion engine
US4410141A (en) Fuel injection nozzle for internal combustion engines
JPH04259662A (en) Multi-jet type two-step injecting automatic fuel injector of diesel engine
JPS61201880A (en) Fuel jet nozzle for internal combustion engine
US2605141A (en) Fuel injection apparatus
HU176993B (en) Fuel injection system for internal combustion engines of air compression
JP3748116B2 (en) Fuel injection device
JPH0754730A (en) Fuel injection device for internal combustion engine
JP2782896B2 (en) Fuel injection valve for direct injection diesel engine
JP2582195Y2 (en) Fuel injection device for internal combustion engine
WO2002031350A3 (en) Fuel injection valve
JPH04237868A (en) Pressure valve for fuel injection pump
KR200161086Y1 (en) Pilot fuel injection valve for a diesel engine
JP2007255291A (en) Fuel injector of internal combustion engine
JPH07224739A (en) Fuel injection nozzle
JPH0412165A (en) Fuel injection device
JPH0861189A (en) Fuel injection valve
JPH021487Y2 (en)