JPS632599Y2 - - Google Patents
Info
- Publication number
- JPS632599Y2 JPS632599Y2 JP245680U JP245680U JPS632599Y2 JP S632599 Y2 JPS632599 Y2 JP S632599Y2 JP 245680 U JP245680 U JP 245680U JP 245680 U JP245680 U JP 245680U JP S632599 Y2 JPS632599 Y2 JP S632599Y2
- Authority
- JP
- Japan
- Prior art keywords
- hydraulic pressure
- pressure source
- fuel injection
- hydraulic
- pulsation
- 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
- 239000000446 fuel Substances 0.000 claims description 28
- 238000002347 injection Methods 0.000 claims description 23
- 239000007924 injection Substances 0.000 claims description 23
- 230000010349 pulsation Effects 0.000 claims description 16
- 238000002485 combustion reaction Methods 0.000 claims description 10
- 230000000116 mitigating effect Effects 0.000 claims description 9
- 239000003921 oil Substances 0.000 description 6
- 239000010720 hydraulic oil Substances 0.000 description 5
- 238000010586 diagram Methods 0.000 description 3
- 230000000694 effects Effects 0.000 description 3
- 239000012530 fluid Substances 0.000 description 2
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 2
- 238000009825 accumulation Methods 0.000 description 1
- 230000007547 defect Effects 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000002265 prevention Effects 0.000 description 1
Landscapes
- Fuel-Injection Apparatus (AREA)
Description
【考案の詳細な説明】
本考案は、内燃機関用燃料噴射装置において調
量精度の向上を図ることが可能な改良構造に関す
る。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to an improved structure capable of improving metering accuracy in a fuel injection device for an internal combustion engine.
内燃機関の燃料噴射装置では、油圧によつてプ
ランジヤを駆動しノズルからの燃料噴射を行う。
ノズルからの一サイクルの燃料噴射行程の終りは
切れの良いものであることが機関の良好な作動の
ために必要なので、プランジヤに弁機構を設けプ
ランジヤが所定ストローク時そのプランジヤの吐
出側をスピルさせ噴射の急速停止を図つている。
そして、従来技術では、このスピル燃料はインジ
エクタへの調量回路へ直接戻すように構成するの
が普通であつた。 In a fuel injection device for an internal combustion engine, a plunger is driven by hydraulic pressure to inject fuel from a nozzle.
Since it is necessary for the engine to operate properly that the end of one cycle of fuel injection stroke from the nozzle is sharp, a valve mechanism is provided in the plunger to prevent the discharge side of the plunger from spilling during a predetermined stroke. Efforts are being made to quickly stop injection.
In the prior art, this spilled fuel was typically configured to be returned directly to the metering circuit to the injector.
しかしながら、従来の構成ではスピルという衝
撃的な流体の流れを調量回路へ放出しているた
め、特にエンジンの高速での作動中に次の調量時
までに安定化できない程の圧力脈動が調量回路に
生ずる。その結果、調量のばらつきという燃料噴
射装置にとつて致命的欠陥を呈する。 However, the conventional configuration discharges an impulsive flow of fluid called spill into the metering circuit, which can cause pressure pulsations that cannot be stabilized before the next metering, especially when the engine is running at high speed. Occurs in the quantity circuit. As a result, the fuel injection system exhibits a fatal defect of metering variation.
かような欠点を解決する手段としてスピル回路
を大気圧に連通したリザーブタンクに接続したも
のが提案されている（特開昭54−121334号参照）。
ところが、この場合プランジヤが下死点に位置す
るとき調量回路からリザーバに油が無駄に流出す
ることになりエネルギ損失につながり、またスピ
ル時の油の大量流出により圧力源の圧力が変動し
易い。尚、この対策として別の弁機構を組み込む
ことが考えられるが、これは噴射装置全体の構成
を複雑化させるばかりか部品点数を増す結果とな
る。 As a means to solve these drawbacks, it has been proposed to connect a spill circuit to a reserve tank connected to atmospheric pressure (see Japanese Patent Laid-Open No. 121334/1983).
However, in this case, when the plunger is at the bottom dead center, oil wastefully flows out from the metering circuit to the reservoir, leading to energy loss, and the pressure of the pressure source tends to fluctuate due to a large amount of oil flowing out during spilling. . As a countermeasure to this problem, it may be possible to incorporate another valve mechanism, but this would not only complicate the overall configuration of the injection device but also increase the number of parts.
従つて、本考案の目的は上述した従来技術の欠
点を解決しスピルによる調量変動防止を簡単な構
成によつて達成することにある。そして、この目
的を達成するべく本考案にあつてはスピルをアキ
ユムレータ又はサージタンク等の脈動緩和装置を
有し、調量回路内における圧力以上の圧力をもつ
油圧圧力源の供給側高圧部に独立の管路で戻すと
いう構成としている。 Therefore, an object of the present invention is to solve the above-mentioned drawbacks of the prior art and to achieve prevention of metering fluctuations due to spill with a simple structure. In order to achieve this purpose, the present invention has a pulsation mitigation device such as an accumulator or a surge tank, and separates the spill from the high pressure part on the supply side of the hydraulic pressure source having a pressure higher than the pressure in the metering circuit. The structure is such that the water is returned through a pipe.
アキユムレータ又はサージタンク等は大きな容
量を有しているので、スピルによる圧力上昇がも
たらされた時において、スピルによる圧力上昇が
直接にアキユムレータ又はサージタンク等の脈動
緩和装置に導かれる構成とすることによつてアキ
ユムレータ内の空気圧などによる蓄圧、又は通常
ΔP＝Ｅ・ΔV／Ｖで表わされる燃料の圧縮性による
蓄圧効果（サージタンクの大容量によりＶの値は
大きく、サージタンク内の圧力上昇ΔPは小さい）
により圧力脈動は緩和される。 Since the accumulator or surge tank has a large capacity, when a pressure increase due to spill occurs, the configuration should be such that the pressure increase due to spill is directly guided to the pulsation mitigation device such as the accumulator or surge tank. The effect of pressure accumulation due to the air pressure in the accumulator, or the compressibility of the fuel, which is usually expressed as ΔP=E・ΔV/V (the value of V is large due to the large capacity of the surge tank, and the pressure increase in the surge tank ΔP) (is small), the pressure pulsations are alleviated.
この結果油圧圧力源はスピルによる圧力変動お
よび無効エネルギーを効率的に吸収でき、結果と
して調量回路の圧力は安定化し、調量精度の向上
が達成できると共に、エネルギー損失を大幅に低
減できるのである。 As a result, the hydraulic pressure source can efficiently absorb pressure fluctuations and reactive energy due to spills, and as a result, the pressure in the metering circuit is stabilized, improving metering accuracy and significantly reducing energy loss. .
以下添付図面によつて本考案の実施例を説明す
れば、燃料噴射装置は大きく分けてインジエクタ
１、ピストン作動用の高油圧圧力源２、調量用の
低油圧圧力源３から成る。これらの圧力源２，３
はその構成を第３図に示すように、アキユムレー
タ又はサージタンク等の脈動緩和装置１０１や、
リリーフ弁１０２、ポンプ１０３、フイルタ１０
４、タンク１０５等より成る通常の定圧圧力源で
ある。インジエクタ１はノズル４、ボア内を油密
状態で摺動するプランジヤ５、それより径の大き
な作動上一体であるピストン６、油圧の切替弁と
して働くスプール弁８、噴射制御用電磁弁９，１
０、バランス用絞り１１、及び逆止弁１２を備え
る。スプール弁８の一側のボア１３内に作動油室
１４が形成され、他側のばね１５はスプール弁８
を作動油室１４が小さくなるよう付勢している。
ピストン６の上側におけるボア１６内にピストン
作動油室１７が形成され、一方プランジヤ５の下
側におけるそのボア１８内にポンプ室１９が形成
される。ボア１８はリング状溝２０を有し、一方
プランジヤ５はたて孔２１及びこれに連通するリ
ング状溝２２を有している。プランジヤ５はその
下死点直前まで達すると双方のリング状溝２０と
２２とが連通し、ポンプ室１９の燃料がボア１８
のリング状溝２０に流出しスピルが行われる。 An embodiment of the present invention will be described below with reference to the accompanying drawings. The fuel injection device is broadly divided into an injector 1, a high hydraulic pressure source 2 for actuating the piston, and a low hydraulic pressure source 3 for metering. These pressure sources 2, 3
As shown in FIG. 3, it includes a pulsation mitigation device 101 such as an accumulator or surge tank,
Relief valve 102, pump 103, filter 10
4. It is a normal constant pressure source consisting of a tank 105 and the like. The injector 1 includes a nozzle 4, a plunger 5 that slides inside the bore in an oil-tight state, a piston 6 that has a larger diameter and is operationally integrated, a spool valve 8 that functions as a hydraulic pressure switching valve, and an injection control solenoid valve 9, 1.
0, a balance throttle 11, and a check valve 12. A hydraulic oil chamber 14 is formed in the bore 13 on one side of the spool valve 8, and a spring 15 on the other side is connected to the spool valve 8.
is biased so that the hydraulic oil chamber 14 becomes smaller.
A piston hydraulic fluid chamber 17 is formed in the bore 16 on the upper side of the piston 6, while a pump chamber 19 is formed in its bore 18 on the underside of the plunger 5. The bore 18 has a ring-shaped groove 20, while the plunger 5 has a vertical hole 21 and a ring-shaped groove 22 communicating therewith. When the plunger 5 reaches just before its bottom dead center, both ring-shaped grooves 20 and 22 communicate with each other, and the fuel in the pump chamber 19 is transferred to the bore 18.
The water flows out into the ring-shaped groove 20 and is spilled.
前記の二系統の圧力源のうち高圧源２はスプー
ル弁８によつて切替られる第一のポート２３に配
管２４によつて導通される。第二のポート２８は
配管２９を介しリザーブタンク２７に戻される。
前記の絞り１１はこの通路２９上に設けられる。
更に低圧源３は配管２５により逆止弁１２を介し
ポンプ室１９に接続され調量燃料の供給を行う。
更に低圧源３は配管３１により前記の電磁弁９を
介しスプール弁作動油室１４と通じ、スプール弁
８の切替を行う。尚、この室１４は前記の電磁弁
１０によつてリザーブタンク２７と接続され、油
の戻しを行う。 Of the two pressure sources mentioned above, the high pressure source 2 is connected to a first port 23 which is switched by a spool valve 8 through a pipe 24 . The second port 28 is returned to the reserve tank 27 via piping 29.
The aforesaid throttle 11 is provided on this passage 29.
Further, the low pressure source 3 is connected to the pump chamber 19 via the check valve 12 by a pipe 25 to supply metered fuel.
Further, the low pressure source 3 communicates with the spool valve operating oil chamber 14 via the above-mentioned solenoid valve 9 through a pipe 31, and switches the spool valve 8. Incidentally, this chamber 14 is connected to the reserve tank 27 by the above-mentioned solenoid valve 10, and oil is returned thereto.
本考案によれば低圧源３は更に配管２６によつ
てスピル用のリング状溝２０に連通し、これによ
つてスピル油を低圧源３に戻す構成としている。 According to the present invention, the low pressure source 3 is further communicated with the spill ring groove 20 through a pipe 26, whereby spilled oil is returned to the low pressure source 3.
以上述べた本考案の作動を述べると、図示の状
態では電磁弁９は閉でありスプール弁作動油室１
４は圧力源３と切離される一方電磁弁１０は開で
あり室１４はリザーブタンク２７と通じ、その結
果ばね１５によつてスプール弁８は図の左方に動
き第一のポート２３を閉第二のポート２８を開と
している。かくしてピストン作動油室１７は配管
２９によつてリザーブタンク２７と連通する。そ
の結果、プランジヤ５は、低圧源３から逆止弁１
２を介しポンプ室１９内へ導入される油圧で上昇
するのが許される。このとき、室１９内に所定量
の燃料が充填され燃料噴射作動に備える。 To describe the operation of the present invention described above, in the state shown, the solenoid valve 9 is closed and the spool valve hydraulic oil chamber 1 is closed.
4 is disconnected from the pressure source 3, while the solenoid valve 10 is open and the chamber 14 communicates with the reserve tank 27, so that the spring 15 moves the spool valve 8 to the left in the figure and closes the first port 23. The second port 28 is open. Thus, the piston hydraulic oil chamber 17 communicates with the reserve tank 27 via the piping 29. As a result, the plunger 5 receives the check valve 1 from the low pressure source 3.
2 is allowed to rise due to the hydraulic pressure introduced into the pump chamber 19. At this time, a predetermined amount of fuel is filled into the chamber 19 to prepare for the fuel injection operation.
次に、図示しないコントローラは電磁弁９を開
に切替えて低圧源３をスプール弁作動油室１４に
連通すると共に、電磁弁１０を閉に切替えて室１
４をリザーブタンク２７から切離し、かくしてス
プール弁８は右側に動き、第二のポート２８を塞
ぐと共に第一のポート２３を開放する。かくして
圧力源２からの高圧が配管２４を介しピストン作
動油室１７に導入され、その結果、ピストン６及
びプランジヤ５は下降を開始し、圧力源２の圧力
をP2、ピストン６の断面積とプランジヤ５の断
面積の比を
ｍ＝ピストン断面積／プランジヤ断面積としたとき、ポ
ンプ室１
９内の圧力ｐを理論上はｐ＝p2×ｍで表わされる
超高圧にする。この圧力がノズル４に所定にセツ
トしてある開弁圧を超えるとこれは開弁し、図示
しない内燃機関燃焼室への燃料噴射が行われる。 Next, the controller (not shown) switches the solenoid valve 9 to open to communicate the low pressure source 3 to the spool valve operating oil chamber 14, and switches the solenoid valve 10 to close to connect the low pressure source 3 to the chamber 14.
4 from the reserve tank 27, and the spool valve 8 thus moves to the right, closing the second port 28 and opening the first port 23. In this way, the high pressure from the pressure source 2 is introduced into the piston hydraulic oil chamber 17 via the piping 24, and as a result, the piston 6 and the plunger 5 start descending, and the pressure of the pressure source 2 is reduced to P 2 and the cross-sectional area of the piston 6 is When the ratio of the cross-sectional areas of the plunger 5 is m=piston cross-sectional area/plunger cross-sectional area, the pressure p in the pump chamber 19 is theoretically set to an extremely high pressure expressed as p=p 2 ×m. When this pressure exceeds a predetermined valve opening pressure set in the nozzle 4, the nozzle 4 opens and fuel is injected into a combustion chamber (not shown) of the internal combustion engine.
プランジヤ５が下死点近くに達すると、プラン
ジヤ５のリング状溝２２がボア１８のリング状溝
２０と導通し、スピルが行われてポンプ室１９内
の圧力が急降下し、ノズル４は急閉弁し噴射が終
了する。このスピルに基づく放出燃料は、本考案
によれば、独立の配管２６を介し油圧源３に直接
戻している。したがつて、スピル時におけるポン
プ室１９内の圧力は、ここから発生したスピル脈
動が直接に油圧源３に大きな容量又はアキユムレ
ータ、さらに油圧源３の中に具備した圧力リリー
フ弁等によつて、吸収されることでその反射波に
よる脈動を受けることがない。さらに調量回路と
はこのスピルの通路が独立しているために、調量
回路自体の圧力変動もない。 When the plunger 5 reaches near the bottom dead center, the ring-shaped groove 22 of the plunger 5 communicates with the ring-shaped groove 20 of the bore 18, a spill occurs, the pressure in the pump chamber 19 suddenly drops, and the nozzle 4 suddenly closes. Valve injection ends. According to the invention, this spilled fuel is returned directly to the hydraulic source 3 via a separate pipe 26. Therefore, the pressure inside the pump chamber 19 at the time of spill is determined by the spill pulsation generated therefrom being directly applied to the hydraulic power source 3 by a large capacity or an accumulator, and also by a pressure relief valve provided in the hydraulic power source 3. By being absorbed, there is no pulsation caused by the reflected waves. Furthermore, since this spill path is independent of the metering circuit, there is no pressure fluctuation in the metering circuit itself.
かくして、次の噴射の開始までにポンプ室１９
内及び調量配管２５内の圧力は安定化されてお
り、正確な調量が行われることになる。 Thus, by the start of the next injection, the pump chamber 19
The pressure within the metering pipe 25 is stabilized, and accurate metering will be performed.
また、スピルに基づく放出燃料の有するエネル
ギーは油圧源３において有効に再利用されると共
に、スピル時において圧力源３から燃料がむだに
流出することもないのでエネルギー損失を大幅に
低減することができる。 Furthermore, the energy possessed by the discharged fuel due to the spill is effectively reused in the hydraulic source 3, and the fuel does not wastefully flow out from the pressure source 3 during the spill, so energy loss can be significantly reduced. .
尚、周知のことではあるが、電磁弁９を閉→開
とし、電磁弁１０を開→閉とする切替タイミング
によつて噴射タイミングが設定され、このタイミ
ングからある時間逆のぼつて電磁弁９を開→閉と
し、電磁弁１０を閉→開とする。この状態で前述
の調量作動が行われ、噴射タイミングでの電磁弁
切替時まで続く。 As is well known, the injection timing is set by switching the solenoid valve 9 from closed to open and the solenoid valve 10 from open to closed. is changed from open to closed, and the solenoid valve 10 is changed from closed to open. In this state, the aforementioned metering operation is performed and continues until the solenoid valve is switched at the injection timing.
従つてこの逆のぼつた時間が調量時間となり、
この間に上昇したプランジヤのストロークにより
次回噴射する噴射量を決定する。尚、絞り１１は
プランジヤがこのストロークを行う際の作動速度
を規制し調量が制御された速度で達成されるよう
にする。 Therefore, this inverse drop-off time becomes the metering time,
The amount of injection to be injected next time is determined by the stroke of the plunger that has risen during this time. Note that the throttle 11 regulates the operating speed at which the plunger makes this stroke so that metering is achieved at a controlled rate.
第２図に示す部分変形例では、リング状溝２０
と圧力源３とを結ぶ独立のスピル配管２６中に逆
止弁３０を設けた点が第１図と相異する。この逆
止弁はスピル中におけるポンプ室１９内の高周波
成分の乱れを遮断し、ポンプ室１９内の圧力脈動
をより一層押える効果を奏する。この構成によれ
ばスピル用の配管２６をより高圧の圧力源例えば
第１図の圧力源２に連通することが可能となる。
その結果、調量用の低圧圧力源内のスピルによる
圧力変動は完全に押えられる。 In the partial modification shown in FIG.
This differs from FIG. 1 in that a check valve 30 is provided in an independent spill pipe 26 connecting the pressure source 3 and the pressure source 3. This check valve blocks disturbances in high frequency components within the pump chamber 19 during spilling, and has the effect of further suppressing pressure pulsations within the pump chamber 19. With this configuration, it is possible to connect the spill pipe 26 to a higher pressure source, for example, the pressure source 2 in FIG. 1.
As a result, pressure fluctuations due to spills in the low-pressure metering pressure source are completely suppressed.
尚、第１図、第２図の実施例で、油圧圧力源が
高圧と低圧とで二つ具備したものを説明したが、
油圧圧力源は１つでも３つ以上でも、本考案の効
果は奏される。また、油圧の切替弁として働く電
磁弁、スプール弁の構成は他の型のものであつて
も良い。 In the embodiments shown in FIGS. 1 and 2, the hydraulic pressure sources are provided with two high-pressure and low-pressure sources.
The effects of the present invention can be achieved regardless of whether there is one hydraulic pressure source or three or more hydraulic pressure sources. Furthermore, the configuration of the electromagnetic valve and spool valve that function as hydraulic switching valves may be of other types.
以上説明したように、本考案の内燃機関用燃料
噴射装置は、
油圧によつてプランジヤを駆動しノズルから燃
料噴射を行うと共に、ノズルからの一サイクルの
燃料噴射行程の終期がプランジヤに設けた弁機構
によつて行われるスピルで決定される内燃機関の
燃料噴射装置において、脈動緩和装置を有する油
圧圧力源を設けると共に、該油圧圧力源にスピル
の通路を他の油圧回路とは独立して接続している
ので、スピルよる圧力変動および無効エネルギー
を効率的に吸収でき、調量回路の圧力を安定化し
調量精度の向上を達成できると共に、エネルギー
損失を大幅に低減できるという優れた効果を奏す
る。 As explained above, in the fuel injection device for an internal combustion engine of the present invention, the plunger is driven by hydraulic pressure and fuel is injected from the nozzle. In a fuel injection system for an internal combustion engine that is determined by a spill performed by a mechanism, a hydraulic pressure source having a pulsation mitigation device is provided, and a spill passage is connected to the hydraulic pressure source independently from other hydraulic circuits. This makes it possible to efficiently absorb pressure fluctuations and reactive energy caused by spills, stabilize the pressure in the metering circuit, improve metering accuracy, and significantly reduce energy loss. .
第１図は本考案の燃料噴射装置の一実施例を示
す全体構成図、第２図は第２の実施例を示す部分
図、第３図は油圧圧力源の一実施例を示す模式構
成図である。
１……インジエクタ、２，３……油圧圧力源、
５……プランジヤ、６……ピストン、８……スプ
ール弁、９，１０……電磁弁、２５……調量配
管、２６……スピルの通路をなす配管。
Fig. 1 is an overall configuration diagram showing one embodiment of the fuel injection device of the present invention, Fig. 2 is a partial diagram showing the second embodiment, and Fig. 3 is a schematic diagram showing an embodiment of the hydraulic pressure source. It is. 1...Injector, 2, 3...Hydraulic pressure source,
5... Plunger, 6... Piston, 8... Spool valve, 9, 10... Solenoid valve, 25... Metering pipe, 26... Piping forming a spill passage.
Claims (1)
を油圧の切替弁の切替えによりピストンが受け
ることによつてプランジヤを駆動しノズルから
燃料噴射を行うと共に、 ノズルからの一サイクルの燃料噴射行程の終期
がプランジヤに形成したリング状溝、プランジ
ヤに形成したリング状溝とポンプ室との連通路
およびボアに形成したリング状溝から成る弁機
構を用いて燃料をスピルさせることにより決定
され、 また油圧圧力源と前記ポンプ室とを逆止弁を介
して接続した調量配管とを備える内燃機関の燃
料噴射装置において、 脈動緩和装置を有する油圧圧力源を設けると共
に、該油圧圧力源の脈動緩和装置を備えた油圧
供給側の高圧部にスピルの通路を他の油圧回路
とは独立して接続し、スピルによる脈動が他の
油圧回路に影響することなく、直接に油圧圧力
源の脈動緩和装置によつて吸収されるようにし
たことを特徴とする内燃機関用燃料噴射装置。 (2) 前記脈動緩和装置はアキユムレータを有する
実用新案登録請求の範囲第１項に記載の内燃機
関用燃料噴射装置。 (3) 前記脈動緩和装置はサージタンクを有する実
用新案登録請求の範囲第１項に記載の内燃機関
用燃料噴射装置。[Scope of Claim for Utility Model Registration] (1) A piston receives hydraulic pressure supplied from a hydraulic pressure source through piping by switching a hydraulic pressure switching valve, thereby driving a plunger and injecting fuel from a nozzle, The end of one cycle of fuel injection stroke from the nozzle injects fuel using a valve mechanism consisting of a ring-shaped groove formed in the plunger, a communication path between the ring-shaped groove formed in the plunger and the pump chamber, and a ring-shaped groove formed in the bore. In the fuel injection device for an internal combustion engine, the fuel injection device is determined by spilling the oil and has a metering pipe connecting the hydraulic pressure source and the pump chamber via a check valve, wherein the hydraulic pressure source has a pulsation mitigation device. At the same time, the spill passage is connected to a high pressure part on the hydraulic supply side equipped with a pulsation mitigation device of the hydraulic pressure source independently of other hydraulic circuits, so that pulsation due to spill does not affect other hydraulic circuits. 1. A fuel injection device for an internal combustion engine, characterized in that the pulsation is absorbed directly by a pulsation mitigation device of a hydraulic pressure source. (2) The fuel injection device for an internal combustion engine according to claim 1, wherein the pulsation mitigation device includes an accumulator. (3) The fuel injection device for an internal combustion engine according to claim 1, wherein the pulsation mitigation device includes a surge tank.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP245680U JPS632599Y2 (en) | 1980-01-16 | 1980-01-16 |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP245680U JPS632599Y2 (en) | 1980-01-16 | 1980-01-16 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS56105658U JPS56105658U (en) | 1981-08-18 |
| JPS632599Y2 true JPS632599Y2 (en) | 1988-01-22 |
Family
ID=29599291
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP245680U Expired JPS632599Y2 (en) | 1980-01-16 | 1980-01-16 |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS632599Y2 (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP1744052A3 (en) * | 2000-08-02 | 2007-02-14 | Mikuni Corporation | Electronically controlled fuel injection device |
-
1980
- 1980-01-16 JP JP245680U patent/JPS632599Y2/ja not_active Expired
Also Published As
| Publication number | Publication date |
|---|---|
| JPS56105658U (en) | 1981-08-18 |
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