JPS62350B2 - - Google Patents
Info
- Publication number
- JPS62350B2 JPS62350B2 JP13218381A JP13218381A JPS62350B2 JP S62350 B2 JPS62350 B2 JP S62350B2 JP 13218381 A JP13218381 A JP 13218381A JP 13218381 A JP13218381 A JP 13218381A JP S62350 B2 JPS62350 B2 JP S62350B2
- Authority
- JP
- Japan
- Prior art keywords
- valve
- piston
- injection
- needle valve
- 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.)
- Expired
Links
- 238000002347 injection Methods 0.000 claims description 74
- 239000007924 injection Substances 0.000 claims description 74
- 239000000446 fuel Substances 0.000 claims description 49
- 238000002485 combustion reaction Methods 0.000 claims description 7
- 239000003921 oil Substances 0.000 description 53
- 230000007423 decrease Effects 0.000 description 7
- 238000007599 discharging Methods 0.000 description 3
- 230000000694 effects Effects 0.000 description 3
- 239000000295 fuel oil Substances 0.000 description 3
- 238000000034 method Methods 0.000 description 3
- 238000010586 diagram Methods 0.000 description 2
- 239000000779 smoke Substances 0.000 description 2
- 230000003111 delayed effect Effects 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
- F02M45/00—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Fuel-Injection Apparatus (AREA)
Description
【発明の詳細な説明】
本発明は内燃機関の燃料噴射弁の改善に関す
る。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to improvements in fuel injection valves for internal combustion engines.
従来のこの種燃料噴射弁を第１図に示す。図に
おいて、０１は燃料噴射弁本体、０２は燃料噴射
弁内の油路、０３は針弁で、燃料噴射弁主体０１
内に滑動可能に挿入されている。０４は針弁押
棒、０５は針弁ばねで、ばね力は押棒０４を介し
針弁０３を弁座０１ｂへ押圧している。０６は開
弁圧調整ねじ、０７はばね室、０８は噴口、０９
は排出口、０１ａは油溜りである。 A conventional fuel injection valve of this type is shown in FIG. In the figure, 01 is the fuel injection valve main body, 02 is the oil passage inside the fuel injection valve, 03 is the needle valve, and the fuel injection valve main body 01
is slidably inserted within. 04 is a needle valve push rod, 05 is a needle valve spring, and the spring force presses the needle valve 03 toward the valve seat 01b via the push rod 04. 06 is the valve opening pressure adjustment screw, 07 is the spring chamber, 08 is the spout, 09
is a discharge port, and 01a is an oil reservoir.
燃料噴射ポンプ（図示しない）により燃料油は
圧縮され高圧になりながら噴射管（図示しない）
に送り込まれ、燃料噴射弁内の油路０２を経て油
溜り０１ａに至る。針弁０３はばね０５によつて
弁座０１ｂへ押し付けられ油溜り０１ａ内の燃料
油圧が一定圧力、即ち開弁圧力P0以上にならなけ
れば上昇しないように、開弁圧調整ねじ０６によ
つて初期ばね力が設定されている。従つて、燃料
噴射ポンプから送り込まれた高圧の圧力波が油溜
り０１ａにて開閉弁P0以上の圧力になると、針弁
０３は上昇し、油溜り０１ａ部の容積が増加し、
燃料噴射ポンプから送られた燃料の１部はこれに
費され、残りが噴口０８よりシリンダ内の燃焼室
（図示しない）へ燃料を噴出し、着火燃焼して出
力を出す。燃料噴射ポンプの吐出が終了すると、
油溜り０１ａ内の圧力が降下し、この圧力が閉弁
圧力以下になれば、ばね０５によつて針弁０３が
押し付けられ下降し、油溜り部の容積は減少し、
その一部は噴口０８より噴射され針弁０３が弁座
０１ｂへ着座すれば、噴射は終了する。なお、こ
の間の針弁０３の摺動部からの漏れはばね室０７
に至り、排出口０９を通つて排出される。 The fuel oil is compressed by the fuel injection pump (not shown) and becomes high pressure, while the injection pipe (not shown)
The oil is sent to the oil sump 01a via the oil passage 02 inside the fuel injection valve. The needle valve 03 is pressed against the valve seat 01b by a spring 05, and is adjusted by a valve opening pressure adjustment screw 06 so that it does not rise unless the fuel oil pressure in the oil reservoir 01a reaches a certain pressure, that is, the valve opening pressure P0 or higher. The initial spring force is set accordingly. Therefore, when the high pressure wave sent from the fuel injection pump reaches a pressure equal to or higher than the on-off valve P0 at the oil sump 01a, the needle valve 03 rises and the volume of the oil sump 01a increases.
A portion of the fuel sent from the fuel injection pump is used for this purpose, and the remaining fuel is injected from the injection port 08 into a combustion chamber (not shown) in the cylinder, where it is ignited and combusted to produce output. When the fuel injection pump finishes discharging,
When the pressure inside the oil reservoir 01a decreases and this pressure becomes less than the valve closing pressure, the needle valve 03 is pressed down by the spring 05 and lowers, and the volume of the oil reservoir decreases.
A part of it is injected from the nozzle 08, and when the needle valve 03 is seated on the valve seat 01b, the injection ends. During this time, leakage from the sliding part of the needle valve 03 is caused by the spring chamber 07.
and is discharged through the discharge port 09.
しかし上記のものには次の欠点がある。 However, the above method has the following drawbacks.
デイーゼル機関の燃焼騒音を低下させるために
は、着火遅れ期間中の燃料量を少なくすることが
必要であり、これを燃料噴射の側から達成するた
めの手法の一つとして、噴射初期の噴射率を低く
抑制することが有効とされている。従来のもので
は、針弁の上昇により油溜りの容積が増加するの
で、燃料噴射ポンプより送油された燃料の一部が
これに費され、残りが噴口から噴射されるので、
噴射初期の噴射率が抑制されるが、一方圧力の低
下により針弁が下降する時には油溜りの容積が減
少し、その一部は噴口より噴射されるので、主噴
射終了後の噴射後期においても、第２図に示すよ
うに、低圧低噴射率の噴射がだらだらと続き、こ
のため排煙等が悪化する欠点がある。 In order to reduce the combustion noise of diesel engines, it is necessary to reduce the amount of fuel during the ignition delay period, and one method to achieve this from the fuel injection side is to reduce the injection rate at the initial stage of injection. It is said that it is effective to suppress the In conventional systems, the volume of the oil reservoir increases as the needle valve rises, so part of the fuel delivered from the fuel injection pump is used for this, and the rest is injected from the nozzle.
The injection rate at the initial stage of injection is suppressed, but on the other hand, when the needle valve descends due to a decrease in pressure, the volume of the oil reservoir decreases, and some of it is injected from the nozzle, so even in the latter stage of injection after the end of main injection. As shown in FIG. 2, the injection at low pressure and low injection rate continues sluggishly, which has the disadvantage of worsening smoke exhaust and the like.
本発明の目的は上記の点に着目し、噴射初期の
噴射率を抑制、即ち長期の低噴射率期間を確保
し、しかも主噴射終了後の後期の低圧低噴射率の
噴射を防止し、噴射の切れを良くすることのでき
る燃料噴射弁を提供することであり、その特徴と
するところは、内燃機関の燃料噴射弁において、
一端側が針弁の油溜りへの油路から分岐して形成
された分岐油路に臨むと共に他端側にばねを設け
たピストン、上記分岐油路に設けられた絞りと同
絞りと並列に設けられ上記ピストン側からの燃料
の流れを抑止する逆止弁を備えたことである。 The purpose of the present invention is to focus on the above-mentioned points, to suppress the injection rate at the initial stage of injection, that is, to ensure a long period of low injection rate, and to prevent low-pressure, low-injection-rate injection in the latter stage after the end of main injection. The purpose of the present invention is to provide a fuel injection valve that can improve the cutting performance of fuel injection valves for internal combustion engines.
A piston whose one end faces a branch oil passage formed by branching off from the oil passage to the oil reservoir of the needle valve, and whose other end is provided with a spring, is installed in parallel with the throttle provided in the branch oil passage. The present invention is equipped with a check valve that prevents the flow of fuel from the piston side.
この場合は、噴射初期にはピストンを針弁と同
期して上昇させ、圧力低下により降下する際には
針弁の降下、着座後にピストンが降下するように
ピストンの運動を制御できるので、問題点を解決
することができる。 In this case, the movement of the piston can be controlled so that the piston is raised in synchronization with the needle valve at the beginning of injection, the needle valve is lowered when it descends due to pressure drop, and the piston is lowered after seating. can be solved.
なお、本発明のように針弁とピストンを別個に
並列して設ければ、各々は従来の針弁と同様な作
動をするので、信頼性、耐久性に関しても良い。 In addition, if the needle valve and the piston are provided separately and in parallel as in the present invention, each operates in the same manner as a conventional needle valve, so reliability and durability are improved.
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３図は本発明による１実施例の燃料噴射弁を
示す断面図である。 FIG. 3 is a sectional view showing one embodiment of a fuel injection valve according to the present invention.
図において、１は燃料噴射弁本体、２は油路、
３は針弁で、燃料噴射弁本体１内に滑動可能に挿
入されている。４は針弁押棒、５は針弁ばねで、
針弁３を押し付けている。６は針弁開弁圧調整ね
じ、７は針弁ばね室、８は噴口、９は排出口、１
０１は針弁の油溜り、１０２は針弁の弁座であ
る。１０は逆止弁、１１は逆止弁ばね、１２は絞
り、１３はピストン、１４はピストン用押棒、１
５はピストン用ばね、１６はピストン開弁圧調整
ねじ兼ピストンストツパ、１７はピストン用ばね
室、１９は排出口、１１１はピストンの油溜り、
１１２は環状部油路である。 In the figure, 1 is the fuel injection valve body, 2 is the oil passage,
A needle valve 3 is slidably inserted into the fuel injection valve main body 1. 4 is the needle valve push rod, 5 is the needle valve spring,
The needle valve 3 is pressed. 6 is a needle valve opening pressure adjustment screw, 7 is a needle valve spring chamber, 8 is a spout, 9 is a discharge port, 1
01 is the oil reservoir of the needle valve, and 102 is the valve seat of the needle valve. 10 is a check valve, 11 is a check valve spring, 12 is a throttle, 13 is a piston, 14 is a push rod for the piston, 1
5 is a spring for the piston, 16 is a piston valve opening pressure adjustment screw and piston stopper, 17 is a spring chamber for the piston, 19 is a discharge port, 111 is an oil reservoir for the piston,
112 is an annular oil passage.
ピストンの一端側は油路２より分岐して形成さ
れた分岐油路３１に臨む。即ち、分岐油路３１は
油路２より分岐した環状部油路１１２と、並列に
設けられた絞り１２と逆止弁１０と、油溜り１１
１とを介してピストン１３の一端側に開口してい
る。これによつて、ピストン１３は針弁３と並列
に設けられている。 One end side of the piston faces a branch oil passage 31 formed by branching from the oil passage 2. That is, the branch oil passage 31 includes an annular oil passage 112 branched from the oil passage 2, a throttle 12 and a check valve 10 provided in parallel, and an oil sump 11.
1 and is open to one end side of the piston 13. Thereby, the piston 13 is provided in parallel with the needle valve 3.
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.
燃料噴射ポンプ（図示しない）により燃料油は
圧縮され高圧になりながら噴射管（図示しない）
に送り込まれ、燃料噴射弁内の油路２を経て油溜
り１０１と、環状部油路１１２を経て油溜り１１
１に至る。針弁３はばね５によつて、またピスト
ン１３はばね１５によつて押し付けられ、一定圧
力即ち開弁圧P0以上にならなければ上昇しない。
従つて、燃料噴射ポンプから送り込まれた高圧の
圧力波が油溜り１０１にて開弁圧P0以上になると
針弁３は上昇し、またこの時に逆止弁１０が開く
ので絞り１２はきかず、油溜り１０１の圧力が開
弁圧P0になる時には、油溜り１１１の圧力も開弁
圧P0になつており、針弁３とほぼ同時にピストン
１３も上昇する。従つて、針弁３上昇時の容積増
加は油溜り１０１と１１１での増加の和となり、
大きくなる。針弁３の上昇により燃料は噴口８よ
りシリンダ内の燃焼室（図示しない）へ噴出さ
れ、着火燃焼して出力を出す。 The fuel oil is compressed by the fuel injection pump (not shown) and becomes high pressure, while the injection pipe (not shown)
The oil is sent to the oil sump 101 via the oil passage 2 in the fuel injection valve, and the oil sump 11 via the annular oil passage 112.
It reaches 1. The needle valve 3 is pressed by the spring 5, and the piston 13 is pressed by the spring 15, and will not rise unless the pressure exceeds a certain pressure, that is, the valve opening pressure P0 .
Therefore, when the high pressure wave sent from the fuel injection pump reaches the valve opening pressure P0 or higher in the oil sump 101, the needle valve 3 rises, and at this time, the check valve 10 opens, so the throttle 12 is not activated. When the pressure in the oil reservoir 101 reaches the valve opening pressure P 0 , the pressure in the oil reservoir 111 also reaches the valve opening pressure P 0 , and the piston 13 also rises almost simultaneously with the needle valve 3. Therefore, the increase in volume when the needle valve 3 rises is the sum of the increases in the oil reservoirs 101 and 111,
growing. As the needle valve 3 rises, fuel is injected from the nozzle 8 into a combustion chamber (not shown) in the cylinder, where it is ignited and combusted to produce output.
燃料噴射ポンプの吐出が終了すると、針弁側の
油溜り１０１内の圧力が低下し、この圧力が閉弁
圧力以下になれば、ばね５によつてまず針弁３が
押し付けられ、降下し着座する。一方、ビストン
側では、燃料噴射ポンプの吐出が終了し、油路内
の圧力が低下すると逆止弁１０が逆止弁ばね１１
によつて閉じられ、燃料は絞り１２により絞り作
用を受ける。このため、油溜り１１１内の圧力降
下はゆるやかになり、絞りの方法、形状の適当な
選択によりその圧力降下の速度は制御され、針弁
３の着座後に油溜り１１１内の圧力を閉弁圧以下
にすれば、針弁の着座後にピスト１３が降下す
る。従つて、ピストン１３が降下する際の容積変
化分の燃料は噴口８より噴射されない。なお、こ
の間の針弁３及びピストン１３の摺動部からの漏
れはそれぞればね室７及び１７に至り、排出口９
及び１９を通つて排出される。また、ピストン１
３の形状を下部が円錐状にし、そのコーン部で着
座するようにすれば、ピストン１３の閉弁圧力を
開弁圧力に比べて小さくすることができ、ピスト
ンの降下開始を遅くできるので一層効果がある。
上記構成の作用を噴射現象の初期及び後期に分け
て説明する。 When the fuel injection pump finishes discharging, the pressure in the oil reservoir 101 on the needle valve side decreases, and when this pressure falls below the valve closing pressure, the needle valve 3 is first pressed by the spring 5 and lowered to a seated position. do. On the other hand, on the piston side, when the discharge of the fuel injection pump ends and the pressure in the oil passage decreases, the check valve 10 is activated by the check valve spring 11.
The fuel is throttled by the throttle 12. Therefore, the pressure drop in the oil sump 111 becomes gradual, and the speed of the pressure drop is controlled by appropriate selection of the method and shape of the throttle, and after the needle valve 3 is seated, the pressure in the oil sump 111 is reduced to the valve closing pressure. If the following is done, the piston 13 will descend after the needle valve is seated. Therefore, the fuel corresponding to the change in volume when the piston 13 descends is not injected from the injection port 8. During this time, leakage from the sliding parts of the needle valve 3 and piston 13 reaches the spring chambers 7 and 17, respectively, and the discharge port 9.
and 19. Also, piston 1
If the shape of the piston 13 is made into a conical shape at the bottom and the piston 13 is seated at the cone, the valve closing pressure of the piston 13 can be made smaller than the valve opening pressure, and the start of descent of the piston can be delayed, making it even more effective. There is.
The operation of the above configuration will be explained separately for the early stage and the latter stage of the injection phenomenon.
(1) 噴射初期
燃料噴射ポンプからの圧力が伝播してきて、油
溜り１０１の圧力が開弁圧以上になれば針弁３が
上昇して噴射が始まる。この時分岐された環状部
油路１１２も同一の圧力となり、逆止弁１０が開
くために絞り１２は影響せず、従つて油溜り１１
１も油溜り１０１と同一の圧力となる。このた
め、ピストン１３は針弁３と同時に上昇する（ピ
ストン１３に作用するばね１５のばね力をそのよ
うに設定しておく）。(1) Initial stage of injection When the pressure from the fuel injection pump propagates and the pressure in the oil reservoir 101 exceeds the valve opening pressure, the needle valve 3 rises and injection begins. At this time, the branched annular oil passage 112 also has the same pressure, and the check valve 10 opens, so the throttle 12 does not affect the oil sump 11.
1 also has the same pressure as the oil sump 101. Therefore, the piston 13 rises at the same time as the needle valve 3 (the spring force of the spring 15 acting on the piston 13 is set in such a manner).
この結果、噴射初期において運動部材の上昇に
伴なう容積増加は
針弁３上昇時の油溜り１０１の容積増加
ピストン１３上昇時の油溜り１１１の容積増
加
の両者の和となり、これにより初期噴射率が抑制
される。従つて、従来燃料噴射弁と同等に初期噴
射率を抑制しようとする時、ピストン１３の容積
増加分を大きくすることによつて、針弁３の容積
増加分を減少することが可能となる（即ち、針弁
３の径を小さくできる）。 As a result, the increase in volume due to the rise of the moving member at the beginning of injection is the sum of the increase in volume of oil sump 101 when needle valve 3 rises and the increase in volume of oil sump 111 when piston 13 rises. rate is suppressed. Therefore, when trying to suppress the initial injection rate to the same level as the conventional fuel injection valve, by increasing the volume increase of the piston 13, it is possible to reduce the volume increase of the needle valve 3 ( In other words, the diameter of the needle valve 3 can be made smaller).
(2) 噴射後期
燃料噴射ポンプの吐出が終了すれば、油溜り１
０１及び油溜り１１１の圧力が低下する。(2) Late injection After the fuel injection pump finishes discharging, oil sump 1
01 and the pressure in the oil reservoir 111 decreases.
この圧力が閉弁圧以下になれば、針弁３はばね
５によつて押付けられ、降下し着座する。 When this pressure becomes lower than the valve closing pressure, the needle valve 3 is pressed by the spring 5 and lowers to a seated position.
一方、ピストン１３について言えば、圧力低下
によつて逆止弁１０が逆止弁ばね１１によつて閉
じられ、絞り１２により絞り作用を受ける。この
ため、油溜り１１１の圧力降下は油溜り１０１の
それに比べてゆるやかになる。この結果針弁３の
着座後にピストン１３が降下するようにできる。 On the other hand, regarding the piston 13, due to the pressure drop, the check valve 10 is closed by the check valve spring 11, and the piston 13 is subjected to a throttle action by the throttle 12. Therefore, the pressure drop in the oil reservoir 111 is slower than that in the oil reservoir 101. As a result, the piston 13 can be made to descend after the needle valve 3 is seated.
従つて、噴射後期において運動部材の降下に伴
なう容積の内、
針弁３の降下時の容積変化分の燃料は噴口８
より噴射されるが、
ピストン１３の降下時の容積変化分の燃料は
噴口８より噴射されない。 Therefore, in the latter half of injection, out of the volume caused by the descent of the moving member, the fuel corresponding to the volume change when the needle valve 3 descends is transferred to the nozzle 8.
However, the fuel corresponding to the change in volume when the piston 13 descends is not injected from the nozzle 8.
ここで、ピストン１３を設けることによつて針
弁３の運動に伴なう容積変化分を小さくすること
ができ（小さくしても初期噴射率の抑制に対して
悪影響を及ぼさない）、この結果噴射の切れが良
くなる。 By providing the piston 13, it is possible to reduce the volume change due to the movement of the needle valve 3 (even if the change is made smaller, it does not have a negative effect on suppressing the initial injection rate), and as a result, The sharpness of the jet becomes better.
以上の作用を噴射率に着目してまとめれば、以
下のようになる。 The above effects can be summarized with a focus on the injection rate as follows.
(1) 噴射初期においては、針弁とピストンとがほ
ぼ同時に上昇することによつて、その容積増加
が大きく、ポンプより送られてきた燃料の内こ
れに費される分が多くなるため、噴射初期での
噴射率が低く抑制される。(1) At the beginning of injection, the needle valve and piston rise almost simultaneously, resulting in a large increase in volume, and a large portion of the fuel sent from the pump is spent on this, resulting in the injection The initial injection rate is suppressed to a low level.
(2) 噴射後期においては、針弁の着座後にピスト
ンが降下するので、ピストン１３の容積変化分
は燃料噴射に関係しない。このため、主噴射終
了後の低圧低噴射率の噴射がだらだらと続くの
を防止でき、噴射の切れが良くなる。従つて、
噴射率モードは第４図のようになる。(2) In the latter stage of injection, the piston descends after the needle valve is seated, so the change in volume of the piston 13 has no bearing on fuel injection. Therefore, it is possible to prevent the low-pressure, low-injection-rate injection from continuing sluggishly after the end of the main injection, and the sharpness of the injection is improved. Therefore,
The injection rate mode is as shown in FIG.
なお、以上のことはホール型噴射弁においても
適用できる。 Note that the above can also be applied to a hall type injection valve.
上述の場合には次の効果がある。 The above case has the following effects.
(1) 着火遅れ期間中の燃料量を少なくすることが
でき、燃焼騒音を低減できる。(1) The amount of fuel during the ignition delay period can be reduced, and combustion noise can be reduced.
(2) 低圧低噴射率の噴射がだらだらと続くことが
防止でき、排煙、燃費等を低減できる。(2) It is possible to prevent low-pressure, low-injection-rate injection from continuing sluggishly, reducing smoke emissions, fuel consumption, etc.
第１図は従来の燃料噴射弁を示す断面図、第２
図は第１図の燃料噴射弁の燃料噴射率を示す線
図、第３図は本発明による１実施例の燃料噴射弁
を示す断面図、第４図は第３図の燃料噴射弁の燃
料噴射率を示す線図である。
１……燃料噴射弁本体、２……油路、３……針
弁、８……噴口、１０……逆止弁、１２……絞
り、１３……ピストン、１５……ピストン用ば
ね、１０１……針弁の油溜り、１１１……ピスト
ンの油溜り、１１２……環状部油路。
Figure 1 is a sectional view showing a conventional fuel injection valve, Figure 2 is a sectional view showing a conventional fuel injection valve.
3 is a diagram showing the fuel injection rate of the fuel injection valve of FIG. 1, FIG. 3 is a sectional view showing a fuel injection valve of an embodiment of the present invention, and FIG. It is a diagram showing an injection rate. DESCRIPTION OF SYMBOLS 1... Fuel injection valve body, 2... Oil path, 3... Needle valve, 8... Nozzle port, 10... Check valve, 12... Throttle, 13... Piston, 15... Spring for piston, 101 ... Oil reservoir of needle valve, 111 ... Oil reservoir of piston, 112 ... Annular part oil passage.
Claims (1)
りべの油路から分岐して形成された分岐油路、一
端側が該分岐油路に臨み他端側がばねに当接され
たピストン、上記分岐油路中に設けられた絞り、
上記分岐油路に並列に設けられ上記ピストン側か
ら上記油溜りへの油路に向かう燃料の流れを抑止
する逆止弁を備えたことを特徴とする燃料噴射
弁。1. In a fuel injection valve for an internal combustion engine, a branch oil passage formed by branching from an oil passage in an oil reservoir of a needle valve, a piston with one end facing the branch oil passage and the other end abutting a spring, and the branch as described above. A throttle installed in the oil passage,
A fuel injection valve characterized in that the fuel injection valve is provided with a check valve that is provided in parallel with the branch oil passage and prevents the flow of fuel from the piston side toward the oil passage to the oil reservoir.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP13218381A JPS5835261A (en) | 1981-08-25 | 1981-08-25 | Fuel injection valve |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP13218381A JPS5835261A (en) | 1981-08-25 | 1981-08-25 | Fuel injection valve |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS5835261A JPS5835261A (en) | 1983-03-01 |
| JPS62350B2 true JPS62350B2 (en) | 1987-01-07 |
Family
ID=15075323
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP13218381A Granted JPS5835261A (en) | 1981-08-25 | 1981-08-25 | Fuel injection valve |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS5835261A (en) |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS60116076U (en) * | 1984-01-13 | 1985-08-06 | 株式会社ボッシュオートモーティブ システム | fuel injection nozzle unit |
| JPS60234967A (en) * | 1984-05-04 | 1985-11-21 | Ulvac Corp | Target for sputtering |
-
1981
- 1981-08-25 JP JP13218381A patent/JPS5835261A/en active Granted
Also Published As
| Publication number | Publication date |
|---|---|
| JPS5835261A (en) | 1983-03-01 |
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