JPS6193267A - Pressure boost device - Google Patents
Pressure boost deviceInfo
- Publication number
- JPS6193267A JPS6193267A JP21502284A JP21502284A JPS6193267A JP S6193267 A JPS6193267 A JP S6193267A JP 21502284 A JP21502284 A JP 21502284A JP 21502284 A JP21502284 A JP 21502284A JP S6193267 A JPS6193267 A JP S6193267A
- Authority
- JP
- Japan
- Prior art keywords
- diameter
- plunger
- piston
- small
- diameter bore
- 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
Links
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
- F02M57/00—Fuel-injectors combined or associated with other devices
- F02M57/02—Injectors structurally combined with fuel-injection pumps
- F02M57/022—Injectors structurally combined with fuel-injection pumps characterised by the pump drive
- F02M57/025—Injectors structurally combined with fuel-injection pumps characterised by the pump drive hydraulic, e.g. with pressure amplification
- F02M57/026—Construction details of pressure amplifiers, e.g. fuel passages or check valves arranged in the intensifier piston or head, particular diameter relationships, stop members, arrangement of ports or conduits
-
- 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
- F02M57/00—Fuel-injectors combined or associated with other devices
- F02M57/02—Injectors structurally combined with fuel-injection pumps
- F02M57/022—Injectors structurally combined with fuel-injection pumps characterised by the pump drive
- F02M57/025—Injectors structurally combined with fuel-injection pumps characterised by the pump drive hydraulic, e.g. with pressure amplification
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Fuel-Injection Apparatus (AREA)
Abstract
Description
【発明の詳細な説明】
（産業上の利用分野）
この発明は、増圧手段を持つ燃料噴射装置にあって、増
圧手段の改良に関するものである。DETAILED DESCRIPTION OF THE INVENTION (Field of Industrial Application) The present invention relates to a fuel injection device having a pressure increasing means, and relates to an improvement of the pressure increasing means.
（従来の技術）
従来、増圧手段を持つ燃料噴射装置は１例えば特開昭５
８−１４８２６６号公報に示すように、燃料を増圧する
増圧器９は、大径のボアＬＯａと、小径のボア１０ｂと
が連通して上下に形成され。(Prior art) Conventionally, a fuel injection device having a pressure increasing means is 1, for example, JP-A No. 5
As shown in Japanese Patent No. 8-148266, the pressure intensifier 9 for increasing the pressure of fuel is formed by vertically connecting a large-diameter bore LOa and a small-diameter bore 10b in communication with each other.
該ボア１０ａ、１０ｂ内に大径のピストンｌｌａと小径
のピストンｌｌｂとより成るサーボピストン１１が径に
対応して配され、上方部には大径ピストン室１３が設け
られ、該大径ピストン室１３は、圧油源に噴射期間制御
部３１を介して接続されている。サーボピストン１１の
小径のピストン１１ｂの下方には、嵌合のボア１０ｂと
により圧縮室１４が設けられ、該圧縮室Ｉ４は、燃料供
給源１５と燃料噴射ノズル２０に接続されている。A servo piston 11 consisting of a large-diameter piston lla and a small-diameter piston llb is arranged in the bores 10a and 10b in correspondence with the diameters, and a large-diameter piston chamber 13 is provided in the upper part. 13 is connected to a pressure oil source via an injection period control section 31. A compression chamber 14 is provided below the small-diameter piston 11b of the servo piston 11 by a fitting bore 10b, and the compression chamber I4 is connected to a fuel supply source 15 and a fuel injection nozzle 20.
従って、大径ピストン室１３に圧油が供給されると、サ
ーボピストン１１は下方へ動かされ、圧縮室１４内の燃
料油を圧縮し、増圧燃料は燃料噴射ノズル２０へ圧送さ
れる。圧送された燃料は、ニードル弁２２のプレッシャ
ステージを押圧し、該圧力がスプリング２３及び圧力室
２４内の圧力の合計の付勢力より勝ると、ニードル弁２
２がスプリング２３に抗してリフトされ噴孔２８が開き
、該噴孔２８から燃料が噴射され、圧力の降下に伴な・
つてニードル弁２２は閉じられる。Therefore, when pressure oil is supplied to the large-diameter piston chamber 13, the servo piston 11 is moved downward to compress the fuel oil in the compression chamber 14, and the pressurized fuel is fed to the fuel injection nozzle 20. The pressure fed fuel presses the pressure stage of the needle valve 22, and when the pressure exceeds the combined urging force of the spring 23 and the pressure inside the pressure chamber 24, the needle valve 2
2 is lifted against the spring 23 to open the nozzle hole 28, fuel is injected from the nozzle hole 28, and as the pressure decreases,
The needle valve 22 is then closed.
（９！明が解決しようとする問題点）
このような増圧器を有する燃料噴射装置にあって、燃料
噴射の特性は、増圧器からの燃料圧送特性に大きな影響
を受け、特に燃料噴射後に急激な圧力の降下が出来にく
く、燃料の噴射の切れが悪い欠点を有していた。また、
大径ピストンは圧縮ストローク最終段では、ボアを構成
する本体に衝突し、大きな音と振動が発生すると共に耐
久上の問題を有していた。(9!Problems to be solved by Ming) In a fuel injection device having such a pressure booster, the characteristics of fuel injection are greatly affected by the fuel pumping characteristics from the pressure booster, and especially when the fuel injection occurs rapidly after fuel injection. It had the disadvantage that it was difficult to achieve a sufficient pressure drop, and the fuel injection was poor. Also,
At the final stage of the compression stroke, the large-diameter piston collides with the main body that forms the bore, producing loud noise and vibration, and also poses durability problems.
このため、この発明では、燃料噴射弁からの燃料の噴射
の切れを良くするために、増圧器から燃料噴射弁へ送る
圧送燃料の立ち下がりを良好とすると共に、大径ピスト
ンが圧縮ストローク最終位置付近で本体に衝突する力を
弱める作用を加えることを目的とするものである。Therefore, in this invention, in order to improve the sharpness of the fuel injection from the fuel injection valve, the fall of the pressurized fuel sent from the pressure booster to the fuel injection valve is improved, and the large diameter piston is moved to the final position of the compression stroke. The purpose is to add an effect that weakens the force that collides with the main body in the vicinity.
（問題点を解決するための手段）
この発明の要旨は、まず第１に１本体に形成の小径の″
ボアと大径のボアとが連通して形成され、前記小径のボ
アに小径のプランジャを配し、このプランジャに当接す
るように前記大径のボアに１大径のピストンを配し、大
径のピストンに加えられる油圧でプランジャ側で高圧を
得るようにした増圧装置にあって、前記本体に前記小径
のボアに開口する戻し通路を形成すると共に、この戻し
通路に前記プランジャに該プランジャの加圧ストローク
最終位置付近で圧縮室と連通ずるカットオフボートを形
成したことにある。第２に、本体に形成の大径のボアと
小径のボアとを形成し、前記大径のボアに大径のピスト
ンを配し、この大径のピストンに当接するように前記小
径のボアに小径のプランジャを配し、大径のピストンに
加えられる油圧でプランジャ側で高圧を得るようにした
増圧装置にあって、前記本体に前記小径のボアに開口す
る戻し通路を形成すると共に、この戻し通路に前記プラ
ンジャに加圧ストローク最終位置付近で圧縮室と連通す
るカットオフボートを形成し、更に前記大径のピストン
の加圧ストローク最終位置付近で該加圧速度に抗するダ
ンパー部を形成したことにある。(Means for Solving the Problems) The gist of the present invention is, firstly, that a small diameter
A bore and a large-diameter bore are formed in communication, a small-diameter plunger is arranged in the small-diameter bore, a large-diameter piston is arranged in the large-diameter bore so as to come into contact with the plunger, and the large-diameter The pressure increase device is configured to obtain high pressure on the plunger side by using hydraulic pressure applied to the piston of the piston, and the main body is provided with a return passage that opens to the small diameter bore, and the return passage is provided with a return passage that is connected to the plunger. The reason is that a cut-off boat is formed that communicates with the compression chamber near the final position of the pressurization stroke. Second, a large-diameter bore and a small-diameter bore are formed in the main body, a large-diameter piston is disposed in the large-diameter bore, and a large-diameter piston is disposed in the small-diameter bore so as to come into contact with the large-diameter piston. A pressure increase device is provided with a small-diameter plunger and is configured to obtain high pressure on the plunger side by hydraulic pressure applied to a large-diameter piston. A cut-off boat that communicates with the compression chamber near the final position of the pressurizing stroke of the plunger is formed in the return passage, and a damper portion that resists the pressurizing speed is formed near the final position of the pressurizing stroke of the large diameter piston. It's what I did.
（作用）
したがって、プランジャの加圧ストローク最終位置付近
で、圧縮室と連通ずるカットオフボートが戻し通路に連
通ずるようになるため、圧縮室内の加圧燃料は急激に戻
し通路内に流出し、該圧縮室内の圧力が急激に降下する
ようになり、噴射弁からの燃料の噴射の切れを向上させ
る。(Function) Therefore, near the final position of the pressurization stroke of the plunger, the cut-off boat that communicates with the compression chamber comes to communicate with the return passage, so the pressurized fuel in the compression chamber suddenly flows out into the return passage. The pressure within the compression chamber will drop rapidly, improving the sharpness of fuel injection from the injector.
また、大径ピストンの加圧ストローク最終位置付近で．
ダンパー部により該大径ピストンの加圧行程速度が落さ
れ、本体への衝突を和らげることができ、耐久生の向上
がはかれる。Also, near the final position of the pressurizing stroke of the large diameter piston.
The damper section reduces the speed of the pressurizing stroke of the large diameter piston, making it possible to soften collisions with the main body, thereby improving durability.
（実施例） 以下、この発明の実施例を図面により説明する。(Example) Embodiments of the present invention will be described below with reference to the drawings.
第１図において１本体１には、小径のボア２ａと、これ
に連接して大径のボア２ｂとが形成され、該小径のボア
２ａには下記する小径のプランジャ６が、大径のボア２
ｂには下記する大径のピストン１４がそれぞれ配されて
いる。In FIG. 1, a small diameter bore 2a and a large diameter bore 2b are formed in a main body 1, and a small diameter plunger 6, which will be described below, is connected to the small diameter bore 2a. 2
A large-diameter piston 14, which will be described below, is arranged at each of the pistons b.
小径のボア２ａには、その反連接部分である開口端にね
じ３にて取付られたヘッド４が設けられ、該ヘッド４に
燃料噴射弁へ燃料を送り出す噴射管の接続口５及び下記
する圧縮室７に連通する通路８が形成されている。The small-diameter bore 2a is provided with a head 4 attached to its anti-connection open end with a screw 3, and a connection port 5 for an injection pipe that sends fuel to a fuel injection valve and a compression port described below. A passage 8 communicating with the chamber 7 is formed.
プランジャ６は、その一端では前記ピストン１４に当接
され５他端（ヘッド側）では、小径のボア２ａとヘッド
４とで圧縮室７が形成されている。The plunger 6 is in contact with the piston 14 at one end thereof, and at the other end (head side), a compression chamber 7 is formed by the small diameter bore 2a and the head 4.
この圧縮室７には、燃料供給源と連通ずる通路９が接続
され、該通路９の途中に逆止弁１０が設けられ、該逆止
弁１０は燃料供給源゛と接続するパイプとの接続用の継
手１１内に設けられている。また、プランジャ６には、
一端を圧縮室７に開口し、他端をプランジャ６の側面に
開口するカットオフボート１２が形成され、このカット
オフボート１２は、本体１に形成され、小径のボア２ａ
に開口の戻し通路１３に加圧ストローク最終位置付近で
連通ずるように構成されている。即ち、有効ストローク
は、第２図に示すように（Ａ）となる。A passage 9 communicating with a fuel supply source is connected to this compression chamber 7, and a check valve 10 is provided in the middle of the passage 9, and the check valve 10 is connected to a pipe connected to the fuel supply source. It is provided in the joint 11 for use. In addition, the plunger 6 has
A cut-off boat 12 is formed with one end opening into the compression chamber 7 and the other end opening into the side surface of the plunger 6. The cut-off boat 12 is formed in the main body 1 and has a small diameter bore 2a.
It is configured to communicate with a return passage 13 having an opening near the final position of the pressurizing stroke. That is, the effective stroke is (A) as shown in FIG.
大径のボア２ｂには、その反連接部分である開口端にね
じ１５にて取付られた蓋を兼ねるブラケット２１には、
大径のピストン１４を動かすための圧力が供給されるパ
イプが接続される継出１６が螺合している。この蓋を兼
ねるブラケット２１側に圧油供給室１７が形成されてい
る。The large-diameter bore 2b has a bracket 21 that also serves as a lid attached to the open end, which is the anti-connection part, with a screw 15.
A joint 16 to which a pipe to which pressure for moving the large-diameter piston 14 is supplied is connected is threaded. A pressure oil supply chamber 17 is formed on the side of the bracket 21 which also serves as a lid.
また、大径のボア２ｂの小径のボア側にあって、段部１
８より数ｍｍの適宜な寸法Ｂだけ加圧供給室側にリーク
油戻し通路１９が形成されている。Further, the stepped portion 1 is located on the small diameter bore side of the large diameter bore 2b.
A leak oil return passage 19 is formed on the pressure supply chamber side by an appropriate dimension B of several mm from 8.
リーク油戻し通路１９は、ピストン１４と大径のボア２
ｂとの間から漏れた油の回収と背圧の発生防止を目的に
設けられており、該通路１９は大気側に開放され、油で
充満されておらず空気が存在している。したがって、大
径のピストン１４の断部側室２０は空気が入っており、
大径のピストン１４がリーク戻し通路１９を閉塞すると
、該ピストン１４の断部側の室２０内の空気は逃げ場を
失ない、空気がダンパー作用を行なうダンパー部２２が
形成され、加圧ストローク最終位置付近で加圧速度に抗
する力が発生し減速させることができる。The leak oil return passage 19 connects the piston 14 and the large diameter bore 2.
The passage 19 is provided for the purpose of collecting oil leaking from between the passage 19 and the passage 19 and preventing the generation of back pressure, and the passage 19 is open to the atmosphere and is not filled with oil but is filled with air. Therefore, the section side chamber 20 of the large diameter piston 14 contains air,
When the large-diameter piston 14 closes the leak return passage 19, the air in the chamber 20 on the cut side of the piston 14 has no place to escape, and a damper section 22 is formed in which the air acts as a damper. A force that resists the pressurization speed is generated near the position, and it is possible to decelerate the pressurization speed.
上述の構成において、増圧装置は、第１の状態でＰ８料
油を加圧して燃料噴射弁に送出した状態を示している。In the above-described configuration, the pressure booster is shown in the first state in which the P8 fuel oil is pressurized and delivered to the fuel injection valve.
この状態から大径のピストン１４の圧油供給室１７内の
圧油が図示しない切換弁を切換えて戻されると、圧縮室
７内の圧力でプランジャ６を介してピストン１４が圧油
供給室１７方向へ戻されて第２図に示すような状態とな
る。When the pressure oil in the pressure oil supply chamber 17 of the large diameter piston 14 is returned from this state by switching the switching valve (not shown), the piston 14 is transferred to the pressure oil supply chamber 17 via the plunger 6 by the pressure in the compression chamber 7. It is returned to the direction shown in FIG. 2.
この状態で、圧縮室７内には、燃料供給源から逆止弁１
０を介して供給されているし、ピストン１４の断部側の
室２０内には空気が充満している。In this state, the check valve 1 is connected to the compression chamber 7 from the fuel supply source.
0, and the chamber 20 on the cut side of the piston 14 is filled with air.
この状態から圧油供給室１７内に圧油が供給されると、
大径のピストン７はプランジャ側へストロークし、プラ
ンジャ６を押圧し、圧縮室７内の燃料油を圧縮し、カッ
トオフボート１２が戻し通路１３に連通するまで圧縮が
行なわれ、該圧縮室７内の圧力は燃料噴射弁へ接続口５
から送り出される。カットオフボート１２が戻し通路１
３と連通ずると、圧縮室７内の圧力は急激に低下して燃
料噴射弁への送出を停止する。このカットオフボート１
２により燃料送出時にあって、圧力の立ち下りを急激に
できるために、燃料噴射弁の噴射切れが良好となるもの
である。When pressure oil is supplied into the pressure oil supply chamber 17 from this state,
The large diameter piston 7 strokes toward the plunger side, presses the plunger 6, compresses the fuel oil in the compression chamber 7, and compression is performed until the cutoff boat 12 communicates with the return passage 13, and the compression chamber 7 The pressure inside is connected to the fuel injection valve at connection port 5.
sent from. Cut-off boat 12 returns passage 1
3, the pressure within the compression chamber 7 drops rapidly and stops delivering fuel to the injector. This cut-off boat 1
2, when the fuel is delivered, the pressure can fall rapidly, so that the injection of the fuel injection valve can be cut off smoothly.
また、大径のピストン１４は、加圧ストローク最終位置
付近で該ピストン１４がリーク戻し通路１９を閉塞する
ために、ピストン１４に対してダンパー効果が発生し、
断部１８に当るストロークの速度を遅くすることができ
、断部１８との音や振動を小さくすると共に耐久性を向
上させることができた。In addition, since the piston 14 having a large diameter closes the leak return passage 19 near the final position of the pressurizing stroke, a damper effect is generated on the piston 14.
It was possible to slow down the speed of the stroke that hits the cut portion 18, reduce noise and vibration with the cut portion 18, and improve durability.
（発明の効果）
以上のように、この発明によれば、プランジャに設けた
カットオフボートと本体に設けた戻し通路とで燃料油の
圧力の立ち下がりを急激に己未るようになり、この結果
として、燃料噴射弁から燃料噴射切れを良好にすること
ができるものである。(Effects of the Invention) As described above, according to the present invention, the cut-off boat provided in the plunger and the return passage provided in the main body prevent the pressure of fuel oil from dropping rapidly. As a result, it is possible to improve fuel injection cut-off from the fuel injection valve.
また、リーク戻し通路をピストンの加圧ストローク最終
位置で当接する断部より適宜な寸法だけ加圧油供給室側
に形成したので、該ピストンの加圧ストローク最終位置
付近でダンパー効果が得られ、本体に衝突する速度を弱
めることができ、音、振動の発生を低下させ、合わせて
耐久性を向上させることができるものである。In addition, since the leak return passage is formed on the side of the pressurized oil supply chamber by an appropriate dimension from the section that comes into contact with the piston at the final position of the pressurizing stroke, a damper effect can be obtained near the final position of the pressurizing stroke of the piston. It is possible to reduce the speed of collision with the main body, reduce the generation of noise and vibration, and improve durability.
第１図はこの発明の実施例を示す断面図、第２図は同上
の作動状態を説明する要部の断面図である。
１・・・本体、２ａ・・・小径のボア、２ｂ・・・大径
のボア、６・・・プランジャ、７・・・圧縮室、大径の
ピストン、１２・・・カットオフボート、１３・・・戻
し通路、１４・・・大径のピストン、２２・・・ダンパ
ー部。FIG. 1 is a cross-sectional view showing an embodiment of the present invention, and FIG. 2 is a cross-sectional view of essential parts explaining the operating state of the same. DESCRIPTION OF SYMBOLS 1... Main body, 2a... Small diameter bore, 2b... Large diameter bore, 6... Plunger, 7... Compression chamber, large diameter piston, 12... Cut-off boat, 13 ... Return passage, 14... Large diameter piston, 22... Damper section.
Claims (3)
て形成され、前記小径のボアに小径のプランジヤを配し
、この小径のプランジヤに当接するように前記大径のボ
アに大径のピストンを配し、大径のピストンに加えられ
る油圧でプランジヤ側で高圧を得るようにした増圧装置
にあって、前記本体に前記小径のボアに開口する戻し通
路を形成すると共に、この戻し通路に前記プランジヤに
該プランジヤの加圧ストローク最終位置付近で圧縮室と
連通するカットオフポートを形成したことを特徴とする
増圧装置。1. A small-diameter bore and a large-diameter bore formed in the main body are formed in communication with each other, a small-diameter plunger is arranged in the small-diameter bore, and a large-diameter plunger is arranged in the large-diameter bore so as to abut on the small-diameter plunger. A pressure increase device is provided with a piston and is configured to obtain high pressure on the plunger side by hydraulic pressure applied to a large diameter piston, wherein a return passage opening to the small diameter bore is formed in the main body, and the return passage A pressure increase device characterized in that the plunger is provided with a cut-off port that communicates with a compression chamber near the final position of the pressurization stroke of the plunger.
、前記大径のボアに大径のピストンを配し、この大径の
ピストンに当接するように前記小径のボアに小径のプラ
ンジヤを配し、大径のピストンに加えられる油圧でプラ
ンジヤ側で高圧を得るようにした増圧装置にあって、前
記本体に前記小径のボアに開口する戻し通路を形成する
と共に、この戻し通路に前記プランジヤに加圧ストロー
ク最終位置付近で圧縮室と連通するカットオフポートを
形成し、更に前記大径のピストンの加圧ストローク最終
位置付近で該加圧速度に抗するダンパー部を形成したこ
とを特徴とする増圧装置。2. A large-diameter bore and a small-diameter bore are formed in the main body, a large-diameter piston is arranged in the large-diameter bore, and a small-diameter plunger is arranged in the small-diameter bore so as to come into contact with the large-diameter piston. A pressure increase device is provided in which a high pressure is obtained on the plunger side by hydraulic pressure applied to a large diameter piston. The plunger is characterized by forming a cut-off port that communicates with the compression chamber near the final position of the pressurizing stroke, and further forming a damper portion that resists the pressurizing speed near the final position of the pressurizing stroke of the large-diameter piston. Pressure booster.
ストンが加圧ストローク最終位置で当接する断部より適
宜な寸法だけ加圧油供給室側に形成したことを特徴とす
る特許請求の範囲第２項記載の増圧装置。3. Claim 2, characterized in that the damper part has a large diameter bore with a leakage oil return passage formed on the side of the pressurized oil supply chamber by an appropriate dimension from the section where the piston comes into contact at the final position of the pressurizing stroke. Pressure booster described in section.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP21502284A JPS6193267A (en) | 1984-10-13 | 1984-10-13 | Pressure boost device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP21502284A JPS6193267A (en) | 1984-10-13 | 1984-10-13 | Pressure boost device |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPS6193267A true JPS6193267A (en) | 1986-05-12 |
Family
ID=16665436
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP21502284A Pending JPS6193267A (en) | 1984-10-13 | 1984-10-13 | Pressure boost device |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS6193267A (en) |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS54112418A (en) * | 1978-01-25 | 1979-09-03 | Bosch Gmbh Robert | Pump nozzle for internal combustion engine |
| JPS5726261A (en) * | 1980-07-24 | 1982-02-12 | Diesel Kiki Co Ltd | Fuel injector of internal combustion engine |
-
1984
- 1984-10-13 JP JP21502284A patent/JPS6193267A/en active Pending
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS54112418A (en) * | 1978-01-25 | 1979-09-03 | Bosch Gmbh Robert | Pump nozzle for internal combustion engine |
| JPS5726261A (en) * | 1980-07-24 | 1982-02-12 | Diesel Kiki Co Ltd | Fuel injector of internal combustion engine |
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