JPS5951158A - Fuel injection valve - Google Patents
Fuel injection valveInfo
- Publication number
- JPS5951158A JPS5951158A JP15967582A JP15967582A JPS5951158A JP S5951158 A JPS5951158 A JP S5951158A JP 15967582 A JP15967582 A JP 15967582A JP 15967582 A JP15967582 A JP 15967582A JP S5951158 A JPS5951158 A JP S5951158A
- Authority
- JP
- Japan
- Prior art keywords
- injection
- valve
- suction
- fuel injection
- 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
- 238000002347 injection Methods 0.000 title claims abstract description 84
- 239000007924 injection Substances 0.000 title claims abstract description 84
- 239000000446 fuel Substances 0.000 title claims abstract description 60
- 238000002485 combustion reaction Methods 0.000 claims abstract description 13
- 239000000779 smoke Substances 0.000 abstract description 4
- 239000003921 oil Substances 0.000 description 32
- 230000007423 decrease Effects 0.000 description 6
- 239000000295 fuel oil Substances 0.000 description 4
- 230000000694 effects Effects 0.000 description 3
- XEEYBQQBJWHFJM-UHFFFAOYSA-N Iron Chemical group [Fe] XEEYBQQBJWHFJM-UHFFFAOYSA-N 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 238000007599 discharging Methods 0.000 description 2
- 238000006073 displacement reaction Methods 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 230000000630 rising effect Effects 0.000 description 1
- 239000004575 stone Substances 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
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】 木冗明は内燃機関の態別噴射弁に関する。[Detailed description of the invention] The present invention relates to type-specific injection valves for internal combustion engines.
従来のと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、Ｏ
ｘは針弁で、燃料噴射弁本体０１内に滑動可能に挿入さ
れている。０４は４弁押棒０５は針弁ばねで、ばね力は
押棒０４を介し針弁０３を噴口０８の内側に設けられた
弁座０１０２へ押圧している。０６は開弁圧調整ねし、
０７はばね室である。噴口０８は油溜りＯ］−０１とエ
ンノンのシリンダ内の燃焼室（図示しない）とを連通し
ている。０９は排出口である。A conventional fuel injection valve is shown in FIG. In the figure,
01 is the fuel injection valve body, 02 is the oil passage inside the fuel injection valve, O
Reference character x represents a needle valve, which is slidably inserted into the fuel injection valve main body 01. 04 is a four-valve push rod 05 is a needle valve spring, and the spring force presses the needle valve 03 to a valve seat 0102 provided inside the nozzle 08 via the push rod 04. 06 is the valve opening pressure adjustment,
07 is a spring chamber. The injection port 08 communicates the oil reservoir O]-01 with a combustion chamber (not shown) in the cylinder of the ennon. 09 is a discharge port.
態別噴射ポンプ（図示しない）により燃料油は圧縮され
高圧になｐながら噴射管（図示しない）を介して燃料噴
射弁内の油路０２を経て油溜り０１０１に至る。針弁０
３は、ばね０５によって弁１ｆｆｌＯ］０２へ押し付け
られ、油溜り０１０１内の燃料油圧が一定圧即ち開弁圧
Ｐ。以上にならなければ上昇しないように即ち開弁しな
いように。The fuel oil is compressed by a type injection pump (not shown) and reaches a high pressure while passing through an injection pipe (not shown), an oil passage 02 in the fuel injection valve, and reaches an oil sump 0101. Needle valve 0
3 is pressed against the valve 1fflO]02 by the spring 05, and the fuel oil pressure in the oil reservoir 0101 is at a constant pressure, that is, the valve opening pressure P. Do not raise the valve unless it exceeds this level, that is, do not open the valve.
開弁圧調整ねじ０６によって初期ばね力が設定されてい
る。従って、燃料噴射ボンフ０から送り込まれた高圧の
圧力波が、油溜ｐｏ１０１にて開弁圧Ｉ）ｏ以−１の圧
力になると針弁０３は上昇し、油溜り０１０１部の容積
が増加し、燃れ１噴射ポンプから送られた燃料の一部は
これに費やされ、残りが噴Ｄ ０８より燃焼室へ噴出し
９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７留りＯＪ ０１内の圧力が降下し、この
圧力が閉弁圧以「になれは、ばね０５によって針弁０３
が押しつけられて下降し、油溜り０ ］ ０．１部の容
積は減少し、その一部は噴口０８より噴射され、企１弁
０；３が弁座０１０２−着座すれは噴射は終了する。The initial spring force is set by the valve opening pressure adjustment screw 06. Therefore, when the high pressure wave sent from the fuel injection bomb 0 reaches a pressure equal to or higher than the valve opening pressure I)o at the oil sump po101, the needle valve 03 rises and the volume of the oil sump 0101 increases. A part of the fuel sent from the injection pump is used for this, and the rest is injected from the injection D08 into the combustion chamber and ignited and burned to produce output. When the fuel injection pump finishes discharging, the pressure in the oil 7 reservoir OJ 01 decreases, and when this pressure becomes lower than the valve closing pressure, the needle valve 03 is closed by the spring 05.
is pressed and descends, the volume of the oil pool 0]0.1 part decreases, a part of which is injected from the nozzle 08, and when the valves 0 and 3 are seated on the valve seat 0102, the injection ends.
なお、この間の針弁０３の摺動部からの漏れははね室０
７に至り、排出口０９を通って排出される。In addition, leakage from the sliding part of needle valve 03 during this period is caused by splash chamber 0.
7 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.
ディーゼル機関の燃焼騒音を低下させるためには２着火
遅れ期間中の燃料量を少なくすることが心髄であり、こ
れを燃料噴射の側から達成させるだ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」二昇により油溜りの
容積か増加するので燃料噴射ポンプ０より送油された燃
料の一部がこれに費やされ、残りが噴口から噴射される
ので。In order to reduce the combustion noise of a diesel engine, it is essential to reduce the amount of fuel during the ignition delay period, and one way 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 the conventional system, the volume of the oil reservoir increases as the needle valve rises, so part of the fuel sent from the fuel injection pump 0 is used for this, and the rest is injected from the nozzle.
噴射初期の噴射率は抑制されるが、一方圧力の低下によ
り針弁が下降する時には油溜９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、このため排煙等か悪化する欠点がある。The injection rate in the early 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 9 decreases, and a part of it is injected from the nozzle, so in the latter stage of injection after the end of main injection. However, as shown in FIG. 2, the injection at low pressure and low injection rate continues lazily, which has the disadvantage of worsening smoke emissions.
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。The purpose of the present invention is to focus on the above points and to suppress the injection rate at the initial stage of injection, that is, to ensure a long period of low injection rate.
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
供することであシ、その特徴とするところは、燃料噴射
ポンプよりの燃料が導入される油溜りと、同油溜りと／
リングの燃焼室とを連通する噴口と、同噴口の内側に設
けられた弁座への着脱に上り同噴口を開閉する針弁とを
有する内燃機関の燃料噴射弁において、同燃料噴射弁の
内部に形成された空間に摺動可能に収容された吸戻しピ
ストン、同吸戻しピストンの頭部側空間と上記油溜りと
を連通ずる油路、°上記吸戻しピストンを上記針弁の閉
弁方向への変位開始とほぼ同期して上記頭部側空間の容
積を増大させる方向へ駆動する駆動装置を備えたことで
ある。Moreover, it is possible to provide a fuel injection valve that can prevent low-pressure, low-injection-rate injection in the latter period after the end of main injection and improve the sharpness of injection. The oil sump into which fuel is introduced and the same oil sump/
In a fuel injection valve for an internal combustion engine, which has a nozzle communicating with a combustion chamber of a ring, and a needle valve that opens and closes the nozzle by attaching to and removing from a valve seat provided inside the nozzle, a suction-return piston slidably housed in a space formed in the suction-return piston, an oil passage communicating the head side space of the suction-return piston with the oil reservoir; The present invention includes a drive device that drives in a direction to increase the volume of the head side space substantially in synchronization with the start of displacement.
この場合は、主噴射終了後に針弁が押し出す容積分の燃
料を吸戻しピストンによって吸戻して。In this case, after the main injection ends, the volume of fuel pushed out by the needle valve is sucked back by the suction piston.
噴口より噴出するのを防止できる。It can prevent spouting from the nozzle.
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。In the figure, 1 is the fuel injection valve body, and 2 is the oil passage.
３は針弁で、燃料噴射弁本体０１内に滑動可能に挿入さ
れている。４は針弁押棒、５は針弁ばねでばね力は押棒
４を介し針弁３を噴口８の内側に設けられた弁座１０２
へ押圧している。６は開弁圧調整ねじ、７はばね室であ
る。噴口８は油溜シ１０１とエンノンのンリング内の燃
焼室（図示しない）とを連通している。９は排出口であ
る。A needle valve 3 is slidably inserted into the fuel injection valve main body 01. 4 is a needle valve push rod, 5 is a needle valve spring, and the spring force is applied to the needle valve 3 via the push rod 4 to a valve seat 102 provided inside the nozzle 8.
It's being pushed to. 6 is a valve opening pressure adjustment screw, and 7 is a spring chamber. The nozzle 8 communicates the oil sump 101 with a combustion chamber (not shown) in the ennon ring. 9 is a discharge port.
１０ｔま吸戻しピストンで、燃料噴身−１弁の内部に形
成された空間内に摺動可能に収容されている。A 10 ton suction/return piston is slidably accommodated in a space formed inside the fuel injection valve 1.
１１は吸戻しピストンばね、１２は吸戻しピストン駆動
棒、１３は吸戻しピストン駆動カムである。11 is a suction and return piston spring, 12 is a suction and return piston driving rod, and 13 is a suction and return piston drive cam.
１４は吸戻ピストンの油溜りで、吸戻しピスト４ぐ゛
ンｌ−０Ｋ収容されている空間の吸戻しピストン１４の
ピストン駆動カムち頭部側の空間である。Reference numeral 14 denotes an oil reservoir of the suction piston, which is a space on the head side of the piston drive cam of the suction piston 14 in the space in which the suction piston 4 gun 1-0K is accommodated.
１５は吸戻しピストン用の油路で、油溜、！ｌ；ｌ １
０１と上記吸戻しピストン１４の頭部側の空間とを連通
している。15 is the oil passage for the suction and return piston, and the oil sump! l；l 1
01 and the space on the head side of the suction/return piston 14 are communicated with each other.
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）を介して燃料噴
射弁内の油路２を経て油溜り１０１に至る。針弁３はば
ね５によって弁座１０２へ押し付けられ、油溜り１０．
１内の燃料油圧が一定圧即ち開弁圧Ｐ。以上にならなけ
れば上昇しない。従って、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Ｐ。以上に
なれば。The fuel oil is compressed by a fuel injection pump (not shown) to a high pressure and reaches an oil reservoir 101 via an injection pipe (not shown), an oil passage 2 in a fuel injection valve. The needle valve 3 is pressed against the valve seat 102 by the spring 5, and the oil sump 10.
The fuel oil pressure within 1 is constant pressure, that is, the valve opening pressure P. It will not rise unless it exceeds this level. Therefore, the high pressure wave sent from the fuel injection pump reaches the valve opening pressure P in the oil reservoir 101. If it becomes more than that.
針弁３は上昇し油溜り１０１の容積が増加し、燃料噴射
ポンプから送られた燃料の一部はこれに費やされ、残り
が噴口８よシ燃焼室へ噴射され１着火燃焼して出力を出
す。燃料噴射ポンプの吐出が終了ずれば、油溜り１０１
の圧力が低下し、この圧力が閉弁圧以下になれば、ばね
５によって針弁３が押し伺けられ降下し始める。The needle valve 3 rises and the volume of the oil reservoir 101 increases, and a part of the fuel sent from the fuel injection pump is used for this, and the rest is injected into the combustion chamber through the nozzle 8 and ignited to produce output. issue. If the fuel injection pump stops discharging, the oil sump 101
When the pressure decreases and becomes below the valve closing pressure, the needle valve 3 is pushed by the spring 5 and begins to descend.
一方、吸戻しピストン１０は針弁３が上昇している間は
吸戻しピストン駆動カム１３により、駆動棒１２を介し
て押し下げられ、一定位置にある′が。On the other hand, while the needle valve 3 is rising, the suction piston 10 is pushed down by the suction piston drive cam 13 via the drive rod 12, and remains at a constant position.
、駆動カム１３の形状、セツティングにより針弁３の降
下し始めるとき、即ち閉弁方向への変位開始とほぼ同期
して上方、即ちピストン頭部側空間の容積を増大させる
方向へ動き始めるように設定されている。このため、針
弁３が降下する際の容積変化分の燃料のほとんどは油路
１５を経て吸戻しぎストン１０によって吸戻し作用を受
け、噴口８より噴射されない。また、針弁３の着座後次
の噴射が開始するまでの期間中に、吸戻しピストン１０
は駆動カム１３によりゆっくシと降下し、吸戻した分の
燃料はゆっくり押し戻され、燃料噴射には関係しない。Due to the shape and setting of the drive cam 13, the needle valve 3 starts to move upward, that is, in the direction of increasing the volume of the piston head side space, almost synchronously with the movement of the needle valve 3 in the valve closing direction. is set to . Therefore, most of the fuel corresponding to the change in volume when the needle valve 3 descends passes through the oil passage 15 and is sucked back by the sucking back stone 10, and is not injected from the injection port 8. In addition, during the period after the needle valve 3 is seated until the next injection starts, the suction piston 10
is slowly lowered by the drive cam 13, and the sucked back fuel is slowly pushed back and is not related to fuel injection.
なお、この間の針弁３の摺動部からの漏れはばね室７に
至り、排出口９を通って排出以上の作用を燃料噴射率に
着目してまとめれば。Note that the leakage from the sliding part of the needle valve 3 during this period reaches the spring chamber 7, passes through the discharge port 9, and the effects beyond the discharge can be summarized by focusing on the fuel injection rate.
次のようになる。It will look like this:
（１）噴射初期においては、吸戻しピストンの作用を受
けず従来の燃料噴射弁と同様に、針弁の」二昇による容
積増加が大きく燃料噴射ポンプより送られてきた燃料の
内、これに費やされる分が多い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 volume increase due to the needle valve's second rise is large, and the fuel sent from the fuel injection pump is not affected by the action of the suction piston, just like a conventional fuel injection valve. Since a large amount of fuel is consumed, the injection rate at the initial stage of injection is suppressed to a low level.
（２）噴射後期においては、針弁の降下による容積汲化
分の燃料のほとんどは吸戻しピストンによって吸戻され
、噴口より噴射されない。このため。(2) In the latter stage of injection, most of the fuel pumped in volume due to the descent of the needle valve is sucked back by the suction piston and is not injected from the nozzle port. For this reason.
主噴射終了後の低圧低噴射率の噴射がだらだら続くのを
防止でき、噴射の切れが良くなる。It is possible to prevent low-pressure, low-injection-rate injection from continuing sluggishly after the end of main injection, resulting in better injection sharpness.
従って、噴射率モードは第４図のようになる。Therefore, the injection rate mode is as shown in FIG.
なお２以上のことはホール型燃料噴射弁においても適用
できる。Note that the above two points can also be applied to a hall type fuel 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のを防止で
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５図は本発明による他の実施例の燃料噴射弁の要部を
断面にて示す側面図である。FIG. 5 is a side view showing a main part of a fuel injection valve according to another embodiment of the present invention in cross section.
図において、符号１より９まで及び１０１゜１０２は前
記した実施例を示す第３図と同一のものである。In the figure, numerals 1 to 9 and 101 to 102 are the same as in FIG. 3 showing the above-described embodiment.
２０は吸戻しピストン、２１は吸戻しピストンばね、２
２は固定鉄芯、２３はコイル、２４はターミナル、２５
は針弁リフトセンサ、２６は吸戻シヒストン用油路であ
る。20 is a suction piston, 21 is a suction piston spring, 2
2 is a fixed iron core, 23 is a coil, 24 is a terminal, 25
2 is a needle valve lift sensor, and 26 is an oil passage for a suction cylinder.
噴射の前半、即ち針弁３が上昇し、その後降下を始める
寸での期間中の作用は前記した実施例と同じであるので
、噴射の後半について述べる。Since the operation during the first half of the injection, that is, the period when the needle valve 3 rises and then begins to descend, is the same as in the embodiment described above, the second half of the injection will be described.
油溜り１０１の圧力が低下し、この圧力が閉弁圧以下に
なれば、ばね５によって針弁３が押しつけられ降下し着
座する。この時、針弁リフトセ、ンサ２５により針弁３
の運動を検知しておき、針弁３が降下し始める時期に信
号を発生するようにして・おき、この信号はコントロー
ルユニット（図示しない）へ人力される。コイル２３は
ターミナル２４によりコントロールユニ、トに接続され
ており、前述の信号によってコイル２３に通電されると
吸戻しピストン２０は固定鉄芯２２に吸引されて上方へ
動くようになっている。即ち、ピストン頭部側の空間の
容積が増大する。When the pressure in the oil reservoir 101 decreases and becomes equal to or less than the valve closing pressure, the needle valve 3 is pressed by the spring 5 and descends to be seated. At this time, the needle valve 3 is lifted by the needle valve lift sensor 25.
The movement of the needle valve 3 is detected and a signal is generated when the needle valve 3 starts to descend, and this signal is manually input to a control unit (not shown). The coil 23 is connected to the control unit through a terminal 24, and when the coil 23 is energized by the above-mentioned signal, the suction/return piston 20 is attracted to the fixed iron core 22 and moves upward. That is, the volume of the space on the piston head side increases.
このため、針弁３が降下する際の容積変化分の燃料のほ
とんどは油路２６を通じて吸戻しピストン２０によって
吸戻し作用を受け、噴口８より噴射されない。寸だ、針
弁３の着座後、リフトセッザ２５により着座信号を検知
し９次の噴射が開始するまでの期間中に吸戻しピストン
２０ばゆっくりと降下し、吸戻した分の燃料はゆっくり
押し戻され燃料噴射には関係しない。Therefore, most of the fuel corresponding to the change in volume when the needle valve 3 descends is sucked back by the suction piston 20 through the oil passage 26, and is not injected from the injection port 8. After the needle valve 3 is seated, the suction piston 20 slowly descends during the period from when the lift sezza 25 detects the seating signal to when the ninth injection starts, and the sucked back fuel is slowly pushed back. It has nothing to do with fuel injection.
従って、噴射率モードは前述した第４図と同様になる。Therefore, the injection rate mode is similar to that shown in FIG. 4 described above.
効果は前記の実施例と同じである。The effect is the same as in the previous embodiment.
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図の燃ネ」噴射弁の燃料噴射率を示す
線図、第５図は本発明による他の実施例の燃料噴射弁の
要部を断面にて示す側面図である。
３・・・針弁、８・・・噴口、１０１・・・油溜シ、１
０２・・・弁座、 ］、 ０ 、２０・・・吸戻しピス
トン、１４・・・吸戻しピストン頭部側空間、１５．２
６・・・油路。
牙ＩＶ
クランク負（ｄｅｑ ）
牙２Ｖ
片３７Figure 1 is a sectional view showing a conventional fuel injection valve, and Figure 2 is a cross-sectional view of a conventional fuel injection valve.
FIG. 3 is a diagram showing the fuel injection rate of the fuel injection valve shown in the figure. FIG. 3 is a sectional view showing a fuel injection valve according to one embodiment of the present invention, FIG. 4 is a diagram showing the fuel injection rate of the fuel injection valve of FIG. 3, and FIG. FIG. 2 is a side view showing a main part of the fuel injection valve of the example in cross section. 3... needle valve, 8... nozzle, 101... oil sump, 1
02... Valve seat, ], 0, 20... Suction/return piston, 14... Suction/return piston head side space, 15.2
6...Oil road. Fang IV crank negative (deq) Fang 2V piece 37
Claims (1)
と、同油溜りと７リングの燃焼室とを連通する噴口と、
同噴口の内側に設けられた弁座への着脱により同噴口を
開閉する針弁とを有する内燃機関の燃料噴射弁において
、同燃刺噴射弁の内部に形成された空間に摺動可能に収
容された吸戻しピストン、同吸戻しピストンの頭部側空
間と上記油溜りとを連通ずる油路、上記吸戻しピストン
を上記針弁の閉弁方向への変位開始とほぼ同期して上記
頭部１国字間の容積をｊＮｑ大させる方向へ駆動するｊ
（バ動装置を（ｉｉｉｉえたことを特徴とする燃料噴射
弁内1. An oil reservoir into which fuel from 2nd fuel injection pump 0 is introduced, and a nozzle that communicates the oil reservoir with the 7-ring combustion chamber;
A fuel injection valve for an internal combustion engine having a needle valve that opens and closes the nozzle by attaching to and removing from a valve seat provided inside the nozzle, which is slidably housed in a space formed inside the fuel injection valve. a suction-return piston, an oil passage that communicates the head side space of the suction-return piston with the oil reservoir; Drive in the direction of increasing the volume between 1 national characters by jNq
(Inside a fuel injection valve characterized by having a valve movement device (iii)
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP15967582A JPS5951158A (en) | 1982-09-16 | 1982-09-16 | Fuel injection valve |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP15967582A JPS5951158A (en) | 1982-09-16 | 1982-09-16 | Fuel injection valve |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS5951158A true JPS5951158A (en) | 1984-03-24 |
| JPH0373755B2 JPH0373755B2 (en) | 1991-11-22 |
Family
ID=15698871
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP15967582A Granted JPS5951158A (en) | 1982-09-16 | 1982-09-16 | Fuel injection valve |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS5951158A (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS62223454A (en) * | 1986-03-22 | 1987-10-01 | Mazda Motor Corp | Fuel injection nozzle for diesel engine |
Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5349625A (en) * | 1976-10-15 | 1978-05-06 | Kouzou Yamane | Method for after leakage prevention in diesel engine |
-
1982
- 1982-09-16 JP JP15967582A patent/JPS5951158A/en active Granted
Patent Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5349625A (en) * | 1976-10-15 | 1978-05-06 | Kouzou Yamane | Method for after leakage prevention in diesel engine |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS62223454A (en) * | 1986-03-22 | 1987-10-01 | Mazda Motor Corp | Fuel injection nozzle for diesel engine |
Also Published As
| Publication number | Publication date |
|---|---|
| JPH0373755B2 (en) | 1991-11-22 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| JPH0654106B2 (en) | Engine fuel injector | |
| JPS61272461A (en) | Fuel injection valve for internal-combustion engine | |
| EP0778412B1 (en) | Fuel injection pump | |
| JPS5951158A (en) | Fuel injection valve | |
| JP3235286B2 (en) | Fuel injection device for internal combustion engine | |
| JPH08261092A (en) | Injector | |
| JP2002031018A (en) | High pressure fuel pump | |
| JPH0422058Y2 (en) | ||
| JPS62350B2 (en) | ||
| JPS6036779Y2 (en) | Suction-back piston device | |
| JP2553011B2 (en) | Fuel injection pump | |
| JP2563796Y2 (en) | Hydraulic valve gear for internal combustion engine | |
| JP2578012Y2 (en) | Fuel injection device | |
| JP2001153001A (en) | Fuel injection device for internal combustion engine | |
| JPS5856376Y2 (en) | Fuel injection pump delivery valve | |
| JPS63230958A (en) | Unit type fuel injection device | |
| JPH04113782U (en) | diesel engine fuel injection system | |
| JP2964135B2 (en) | Fuel injection device | |
| JP2597157B2 (en) | Relief type fuel injection pump for diesel engine | |
| JPH07189701A (en) | Piston for internal combustion engine | |
| JP2573652Y2 (en) | Pre-stroke control device for fuel injection pump | |
| JPH06221243A (en) | Electromagnetic spill valve control unit injector | |
| JPS647244Y2 (en) | ||
| JPS59221455A (en) | Fuel injection pump | |
| JPS56148641A (en) | Knocking suppressor for internal combustion engine |