JPS5874869A - Injection pump - Google Patents
Injection pumpInfo
- Publication number
- JPS5874869A JPS5874869A JP57171067A JP17106782A JPS5874869A JP S5874869 A JPS5874869 A JP S5874869A JP 57171067 A JP57171067 A JP 57171067A JP 17106782 A JP17106782 A JP 17106782A JP S5874869 A JPS5874869 A JP S5874869A
- Authority
- JP
- Japan
- Prior art keywords
- injection
- chamber
- pressure
- piston
- delivery
- 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
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
- F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
- F02M59/20—Varying fuel delivery in quantity or timing
- F02M59/32—Varying fuel delivery in quantity or timing fuel delivery being controlled by means of fuel-displaced auxiliary pistons, which effect injection
-
- 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
- F02M47/00—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
- F02M47/02—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure of accumulator-injector type, i.e. having fuel pressure of accumulator tending to open, and fuel pressure in other chamber tending to close, injection valves and having means for periodically releasing that closing pressure
- F02M47/027—Electrically actuated valves draining the chamber to release the closing pressure
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B75/00—Other engines
- F02B75/02—Engines characterised by their cycles, e.g. six-stroke
- F02B2075/022—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle
- F02B2075/025—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle two
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Fuel-Injection Apparatus (AREA)
Abstract
(57)【要約】本公報は電子出願前の出願データであるた
め要約のデータは記録されません。(57) [Abstract] This bulletin contains application data before electronic filing, so abstract data is not recorded.
Description
【発明の詳細な説明】
本発明は、特に低速及び軽負荷の作動点について、即ち
噴射される燃料の量が少ない場合に高噴射圧力を必要と
する噴射機関特に直接噴射式のディーゼル機関Ｋｌｌす
る・
線型又は回転聾の噴射ポンプは場合にょシ充分大きな圧
力を発生できない。仁の形式の従来の噴射ポンプはその
作動時に比較的大きな圧力を与えるが、その圧力は必ず
しも充分とは言えない。更に機械的な噴射ポンプは、噴
射の進行の調整についてもいろいろの不具合がある〇料
の噴射量が少ない場合に４′高圧が得られ、噴射開始時
点についての精度も高くなるようにした噴射装置を提供
することにある。DETAILED DESCRIPTION OF THE INVENTION The invention is particularly useful for injection engines, especially diesel engines with direct injection, which require high injection pressures, especially for low speed and light load operating points, i.e. when the quantity of injected fuel is small. - Linear or rotary injection pumps are often unable to generate sufficiently large pressures. Conventional injection pumps of the genus type provide relatively large pressures during their operation, but the pressures are not always sufficient. Furthermore, mechanical injection pumps have various problems when it comes to adjusting the progress of injection. An injection device that can obtain 4' high pressure when the injection amount of fuel is small and has high accuracy regarding the injection start point. Our goal is to provide the following.
本発明は基本的に１送出し室に燃料を送出すカム又は偏
心輪により機械的に作動する送出しビスシンを、送出し
圧力と対抗ばねめみによシ作動し噴射器と連通する噴射
室内の燃料を圧縮する噴射ピストンと−合し、そのほか
Ｋ、全送出し期間の間送出し室内の圧力を一定に一つ較
正された排出弁を配設し、全送出し期間の間送出しピス
トンの運動法則及び作動状態と無関係に、噴射室内の圧
力が一定になるようＫしたことにある。The present invention basically consists of a delivery screw that is mechanically actuated by a cam or an eccentric that delivers fuel to a delivery chamber, and an injection chamber that is actuated by a delivery pressure and a counter spring mechanism to communicate with an injector. K is connected to an injection piston for compressing fuel, and is also provided with a calibrated discharge valve to keep the pressure in the delivery chamber constant during the entire delivery period, and the delivery piston during the entire delivery period. The reason is that the pressure inside the injection chamber is kept constant regardless of the laws of motion and operating conditions.
上述の構成に、噴射ニードルの迅速な閉塞を一層にする
公知の形式の排出室と、噴射室内の燃料を予め一量決定
すると共に排出室に対する１
作用により噴射時点を制御する単一あ電動弁とを更−組
合せると一層好適である。In addition to the above-mentioned arrangement, there is provided an evacuation chamber of the known type, which furthermore facilitates rapid blocking of the injection needle, and a single motor-operated valve which predetermines the amount of fuel in the injection chamber and controls the injection time by means of an action on the evacuation chamber. It is even more preferable to combine the above.
本発明のその他の特徴は、沫発明の好適な実施例を示す
添付図面を参照している以下の実施例の説明により一層
明らかとなるであろう。Other features of the invention will become more apparent from the following description of the embodiments, which refers to the accompanying drawings showing preferred embodiments of the invention.
噴射ポンプの本体ｌは、第１図には図示しない複数の部
材から成り、これらの部材は適当な手段によ′り互いに
連結されている。本体ｌは押し棒コを有し、該押し棒−
はカム又は偏心輪３により上方から下方に付勢されてい
ると共に１それと反対の方向に対抗ばね亭によυ付勢さ
れ、上方死点と下方死点との間において移動するようＫ
なっている。この行程は必要に応じストッパーによシ制
限してもよい。押し棒ａは適当な切欠によシ送出しピス
トン！のピストンへ゛ラドに一体化されている大め、送
出しピストン３は同じ運動を行ない、下方運動の間は本
体ｌの中ぐり孔内において摺動し、燃料を送出し室１に
送出し、押し一層とピストン！との上方運動の間は、逆
止弁ｌを介して圧力供給管７かち供給される供給圧力に
よって燃料が送出し室４に供給される。The main body 1 of the injection pump consists of a number of parts, not shown in FIG. 1, which are connected to each other by suitable means. The main body l has a push rod.
K is biased downward from above by a cam or eccentric 3, and υ biased in the opposite direction by a counter spring, so that K moves between the upper dead center and the lower dead center.
It has become. This stroke may be limited by a stopper if necessary. Push rod a is a delivery piston with a suitable notch! A larger delivery piston 3, which is integrally integrated into the piston of , carries out the same movement, sliding in a borehole in the body l during the downward movement and delivering fuel into the delivery chamber 1; Push and piston! During the upward movement, fuel is supplied to the delivery chamber 4 by the supply pressure supplied by the pressure supply pipe 7 via the check valve l.
上記中ぐり孔と別の中ぐり孔又は好ましくは上記中ぐシ
孔の延長部分内に、噴射ピストンデがあり、噴射ピスト
ンデの行程は、上部ストンＡ −７０と、噴射室ｌコの
底面上に配設された下部ストッパー／／とＫよって制限
される０噴射＠／コには、噴射ピストンツを上部ストッ
パー７０の方に付勢する対抗復帰ばね／３も収容されて
いる。In a borehole separate from said borehole or preferably in an extension of said borehole, there is an injection piston whose stroke is connected to the upper stone A-70 and onto the bottom surface of the injection chamber l. The zero injection, which is limited by the arranged lower stops // and K, also accommodates a counter-return spring /3 which biases the injection piston towards the upper stop 70.
噴射室ｌコは、公知の噴射ニードル／ｌを備えた噴射器
／？Ｃ）容積室／６に、扁平な弁ｌｊを備え大配管／４
１１を介して連通している。The injection chamber is an injector equipped with a known injection needle. C) Volume chamber/6 is equipped with a flat valve lj and large piping/4
It communicates via 11.
また本発明によれば、送出し室６は、成る所定の高圧に
対して較正された排出弁／ｆから成る圧力制限装置を備
えている。送出しピストン！の直径は噴射ピストンデの
直径よりも成る所定の値だけ大きいため、偏心輪３によ
り規定される運動法則並びに機関運転状態の如何に係わ
らず、噴射ｉ［／Ｊと容積室１４との間の噴射圧力を、
噴射時の容積室／４ （送出し室）内の圧力に等しい一
定の値に保つことができる。換言すれば、送出しピスト
ン！の下方運動によって移動する燃料量が、噴射ピスト
ンｆＫよって移動する燃料量よりも常に多くなり、それ
により排出弁／？により調節される圧力が一定に保たれ
、それにより本発明の第１の課題がこうして解決され九
〇燃料の噴射量を予め定めることと、噴射時期の正確な
開始時点を定めることとが次に問題になる。Also according to the invention, the delivery chamber 6 is equipped with a pressure limiting device consisting of a discharge valve /f calibrated to a predetermined high pressure. Delivery piston! The diameter of the injection piston is larger than the diameter of the injection piston by a predetermined value, so that regardless of the laws of motion defined by the eccentric 3 and the operating state of the engine, the injection between the injection piston pressure,
It can be maintained at a constant value equal to the pressure in the volume chamber/4 (delivery chamber) during injection. In other words, the delivery piston! The quantity of fuel displaced by the downward movement of is always greater than the quantity of fuel displaced by the injection piston fK, so that the quantity of fuel displaced by the downward movement of the discharge valve /? The pressure regulated by is kept constant, so that the first problem of the invention is thus solved, and the next step is to predetermine the injection quantity of fuel and to determine the exact starting point of the injection timing. It becomes a problem.
そのために、排出室−〇を備えた゛公知の形式の噴射器
１７が用いられ、排出室−〇内に摺動自在に配設された
排出ピストンλｌは、ニードルばねコＪを備えた押し棒
−一を介してニードルｔｇを閉塞方向に付勢する。排出
室コ０の盲孔内にあるストッパーコ亭はニードルｉｔｒ
の上方運動を確実に制限するが ＝、ドルばね２Ｊは、
容積室／６内の噴射圧力が充分高く、また排出室−〇内
の高圧にょシェードルｌｚの上方運動が妨げられる場合
にのみ、ニードル／ｌの上方運動を制御する０ピストン
コ／の下面、押し棒ココ、ニードル／ｌの頂部及びニー
ドルばねコ３を含む容積全体は、供給圧力と同じに統一
されている。 ゛
本発明によれば、排出ｍコ０は、別Ｏ逆止弁Ｊｊ）Ｃよ
シ配管ツから供給圧力を受け、電動三方弁１４Ｆ１次の
１つの位置を取ることができる。For this purpose, an injector 17 of known type is used, which is provided with a discharge chamber 〇, in which the discharge piston λl, which is slidably arranged, is a push rod equipped with a needle spring J. The needle tg is biased in the closing direction through one. The stopper in the blind hole of the discharge chamber is the needle itr.
Although it reliably limits the upward movement of =, the dollar spring 2J is
Only when the injection pressure in the volume chamber /6 is sufficiently high and the upward movement of the high pressure shader lz in the discharge chamber -○ is prevented, the lower surface of the 0 piston co/, the push rod, which controls the upward movement of the needle /l. The entire volume including the top of the needle/l and the needle spring 3 is unified to the same supply pressure. According to the present invention, the discharge mco0 receives supply pressure from the separate O check valve Jj)C and can take one position of the electric three-way valve 14F1.
即ち電動三方弁Ｊ４は、第１位置においては、噴射室ｌ
コを配管１γ、Ｊｊによシ排出室２０に連通させ、三方
弁一番の励磁位置に対応し得る第２位置では排出室ＪＯ
を配管Ｊ９を介して配管りに連通させ、噴射室ｌコの配
管コアを閉塞する。That is, in the first position, the electric three-way valve J4
The pipes 1γ and Jj are connected to the discharge chamber 20, and the discharge chamber JO is connected to the discharge chamber 20 at the second position, which corresponds to the first excitation position of the three-way valve.
is communicated with the piping via piping J9, and the piping core of the injection chamber l is closed.
その九め噴射の制御と燃料量を予め定めることが同一の
三方弁コ４により同時に確保される。Control of the ninth injection and predetermining the fuel amount are simultaneously ensured by the same three-way valve 4.
用量決定は送出しピストン！の上方運動の間に行なわれ
、噴射ピストンデは、供給圧力ないし給送圧力の下で燃
料を噴射ｉｉ［／コに送る第１位置に電動三方弁−６が
ある時にのみ上方運動する。この場合即ち三方弁Ｊ４が
第１位置にある時には、送出し室４、噴射室／コは、逆
止弁ｔ。Dose determination is done by the delivery piston! During the upward movement of the injection piston, the injection piston moves upward only when the electrically operated three-way valve 6 is in the first position delivering fuel to the injection ii[/co] under the supply pressure. In this case, that is, when the three-way valve J4 is in the first position, the delivery chamber 4 and the injection chamber are connected to the check valve t.
Ｊｊによって供給圧力を受ける。しかし復帰ばね／Ｊの
ため、送出し室６内の圧力は噴射室／Ｊ内の圧力よりも
大となるので、対抗ばねダにより送出しピストンＩが上
方運動する時（偏心輪Ｊがその下方死点から上方死点の
方に移動する時）Ｋは燃料が逆止弁ｔを介して送出し室
≦に入ることはでき壕くなる。従って用量決定された燃
料は、管径を決める横断面積及び三方弁−基が第１位置
に戻っ走時と押し棒コが上方死点に到達した時との間の
経過時間のみに依存する。従２て機関運転速度に留意し
て電子装置によりこの時間を正確に制御で暑得る・その
反対に１送出しピストン３の下方運動の間に三方弁−１
がその第１位置ＫＴｏると、排出室コ０は、噴射ｉ［／
コと同様、逆止弁／ｆにょヤ制御される高圧の作用を受
けるため、三方弁−４がその第一位置に移動するように
付勢されない限シ噴射は行なわれない０この移動の後は
、排出室−〇内の圧力が降下し、用量決定され要所定量
の燃料が流れるのに要する時間の間上述し九ように一定
の圧力下で配管ｌヂを介して噴射が行なわれる。It receives supply pressure from Jj. However, due to the return spring /J, the pressure in the delivery chamber 6 is greater than the pressure in the injection chamber /J, so when the delivery piston I moves upward due to the opposing spring (the eccentric wheel J is When moving from the dead center to the upper dead center), the fuel cannot enter the delivery chamber ≦ through the check valve t, and becomes a trench. The dosed fuel therefore depends only on the cross-sectional area, which determines the tube diameter, and on the elapsed time between when the three-way valve base returns to the first position and when the push rod reaches top dead center. Therefore, this time can be precisely controlled by means of an electronic device, keeping in mind the engine operating speed.Conversely, during the downward movement of the delivery piston 3, the three-way valve-1
is in its first position KTo, the discharge chamber Ko0 is injected i[/
Similar to check valve/f, injection will not take place unless the three-way valve-4 is energized to move to its first position due to the action of the controlled high pressure. During the time required for the pressure in the discharge chamber 0 to fall and for the required dosed amount of fuel to flow, injection is carried out through the pipe 12 under constant pressure as described above.
更に噴射ピストンｔの下方行程の終了時に送出しｍｉを
排出１ｉｉ Ｊ ａ Ｋ ｓま六噴射室／−を圧力供給
管にそれぞれ連通させるため、噴射ピストンデに管路Ｊ
Ｏ，Ｊ／が、また、本体ｌ中に配管３Ｊ、３３がそれぞ
れ形成されてあり、その結果噴射器Ｉりの容積室１４の
圧力が完全に排除されると共に、＝−ドルｉｔが確実に
下方移動され、迅速な閉塞が確実に行なわれる。Furthermore, at the end of the downward stroke of the injection piston t, the discharge mi is discharged.
O, J/ are also formed in the main body 1 with piping 3J, 33, respectively, so that the pressure in the volume chamber 14 of the injector I is completely eliminated, and it is ensured that = - dollar it. is moved downward to ensure rapid occlusion.
第一〜７図には、噴射装置の作用がいろいろの変更例と
共に図示されている。第２図は押し棒コの上方運動開始
時を示し、電動三方弁コ４に電圧が印加され、それによ
り送出し室６が充填されるが、噴射室／Ｊには未だ充填
されず、ピストンナは不動である◎
第３図は、電動三方弁−４の消磁に対応する定量開始時
を示し、ピストンデはばね圧の下で上方移動し、燃料量
が予め定量測定される。1 to 7 illustrate the operation of the injection device together with various modifications. FIG. 2 shows the push rod starting to move upward, and voltage is applied to the electric three-way valve 4, thereby filling the delivery chamber 6, but the injection chamber /J is not yet filled, and the piston is stationary. ◎ Figure 3 shows the start of metering corresponding to the demagnetization of the electric three-way valve-4, the piston moves upward under spring pressure, and the amount of fuel is pre-metered.
第亭図は送出し開始と、゛送出し室６及び噴射室ｌコに
対する同時圧力供給とを示している。The diagram in FIG. 1 shows the start of delivery and the simultaneous supply of pressure to the delivery chamber 6 and the injection chamber 1.
この圧力は圧力制限装置である排出弁／ｆＫより調節さ
れる◎この状態では、排出ｉ１−〇の圧力と容積ｇ／４
の圧力とが同一であるため、ニードル／１は上方移動で
きない・
第３図は、電動三方弁コ１の励磁により噴射が開始され
る正確゛な時点を示している。排出室−〇の燃料は吐出
され、ニードル／Ｉが上方移動し、噴射室／Ｊ内にある
所定量の燃料が、排出弁／？によシ調節された一定の圧
力の下で噴射される。This pressure is regulated by the discharge valve/fK, which is a pressure limiting device.◎In this state, the pressure and volume of discharge i1-〇 are g/4
Since the pressures are the same, the needle 1 cannot move upwards. FIG. The fuel in the discharge chamber -○ is discharged, the needle /I moves upward, and a predetermined amount of fuel in the injection chamber /J is discharged from the discharge valve /? It is injected under a controlled constant pressure.
第６図は、送出しピストンｊの行程終了前の噴射ピスト
ンデの行程終了状態を示し、この状態では噴射室ｌコと
噴射器ｌりの容積室１１及びこれに対応する配管から燃
料が完全に排出されるが、排出室−〇は、送出し室６内
のピストンｊの送出し終了によって部分的に再充填され
る。従ってこれによシニードル／１が急速に再閉塞する
。FIG. 6 shows the end of stroke of the injection piston before the end of the stroke of the delivery piston j. In this state, the fuel is completely drained from the injection chamber l, the volume chamber 11 of the injector l, and the corresponding piping. Although it is evacuated, the evacuation chamber -0 is partially refilled by the end of the delivery of the piston j in the delivery chamber 6. This therefore causes the needle/1 to rapidly reocclude.
第７．を図に押し棒コ及び送出しピストン！の速度−行
程曲線を示す０この場合には偏心輪３により正弦波状の
運動法則を与えるが、その他の運動法則を用いてもよい
。館を図には電動三方弁−１の制御信号をカム軸の回転
サイクルの関数として示す・電動三方弁コロの給電方形
波の立上り縁Ｊ亭は、もちろん噴射進行に伜なつ九噴射
開始を正確に定め、立下り縁３ｊは、送出し開始におい
て終了する燃料の所定量に対応している◇このように電
動三方弁２番は、１つの機能を充たすとしても、！サイ
クルについて／）４ルスのみを受け、そのａつの縁即ち
立上り縁及び立下シ縁は機関の作動条件即ち噴射の進行
−・・速度及び負荷に従って別々に電子工学的に定めら
れる。7th. The figure shows the push rod and delivery piston! In this case, the eccentric wheel 3 provides a sinusoidal law of motion, but other laws of motion may be used. The figure shows the control signal of the electric three-way valve-1 as a function of the rotation cycle of the camshaft.The rising edge of the square wave of the power supply to the electric three-way valve roller is of course accurate to the injection start. , and the falling edge 3j corresponds to the predetermined amount of fuel that ends at the start of delivery.◇In this way, even if electric three-way valve No. 2 fulfills one function,! For a cycle/) only four pulses are received, the two edges of which are electronically defined separately according to the operating conditions of the engine, i.e. the progress of the injection, the speed and the load.
本発明は噴射ポンプに係るものであるが、多気筒機関に
ついて、−例としてダ気筒機関に応用する場合について
は第１Ｏ図に示すようＫ。Although the present invention relates to an injection pump, the present invention is applied to a multi-cylinder engine, for example, as shown in FIG. 1O.
全部の構成要素即ち偏心輪３、対抗はね亭及び送出し室
！を同一の本体Ｉ内で、気筒数を＊ｇして配列変えをす
ることもできる。All components: eccentric wheel 3, counterspring bow and delivery chamber! It is also possible to change the arrangement within the same main body I by increasing the number of cylinders *g.
機関の運転サイクルに依って設定したカム又は偏心輪Ｊ
を支持する軸！ｌは、ダサイクル機関の場合には半分の
速度で、またコサイクル機関の場合には同じ速度でそれ
ぞれ回転される・送出しピストン！は噴射ピストンｔに
高圧配管１Ｊ）（よシ連結されてらる■送出しポンプＳ
の送出しｍＡは一つの１ｉＡａ、Ａｂに分割され、室Ａ
ｍ、４ｂは配管ｊＪＫよシ連結されている。Cam or eccentric wheel J set depending on the operating cycle of the engine
The axis that supports! l is rotated at half the speed in the case of a da-cycle engine, and at the same speed in the case of a co-cycle engine.・Delivery piston! is the high pressure pipe 1J) (connected to the injection piston t) ■Delivery pump S
The delivered mA is divided into one 1iAa, Ab, and the chamber A
m and 4b are connected to piping jJK.
この実施例の作用原理は噴射ポンプの作用原理と同じで
あるが、高圧の制御についてのみ相違しており、この相
違によシ、多気筒について複数の噴射ポンプを用い九場
合と比較して利点が得られる。実際には噴射ポンプの場
合には排出弁１９は噴射器支持体に合体されているので
、一定の噴射圧力が全て同一となるように、複数の噴射
ポンプ支持体について非常に正確で細密な較正を行なう
ことが必１！になる。この実施例によれば、複数の噴射
器支持体について１個の排出弁ｉｔしか存在しない。室
６１は、配管ｊ４１及び逆止弁ｊ０を介して起部ｊＪに
連結してあシ、配管Ｓコの先端には単一の排出弁ｉｔが
配設してあシ、逆止弁ｊｏは、７つの＠４ａ内の圧力が
他の＠ ４ ａ内の圧力と干渉せずに調節できるように
取付けられている。The working principle of this embodiment is the same as that of the injection pump, but only the control of the high pressure is different, and this difference provides advantages compared to the case of using multiple injection pumps for multiple cylinders. is obtained. In practice, in the case of injection pumps, the discharge valve 19 is integrated into the injector support, so that a very accurate and detailed calibration for several injection pump supports is required, so that the constant injection pressure is all the same. It is essential to do this! become. According to this embodiment, there is only one discharge valve it for a plurality of injector supports. The chamber 61 is connected to the starting part jJ via a pipe j41 and a check valve j0, and a single discharge valve it is disposed at the tip of the pipe S, and the check valve jo is , are installed so that the pressure in the seven @4a can be adjusted without interfering with the pressure in the other @4a.
第１図は噴射ポンプ全体の略配列図、第一図から＃Ｉ４
図はその作用説明図、第７図から第を図は作動サイクル
を示す線図、第ｉｏ図は多気筒機関に応用した本発明の
噴射ポンプを示す略配列図である。
！・・送出しピストン、１・・送出し室、？・會噴射ビ
スＦン、／Ｊａ・噴射室、／Ｊ＠一対抗復帰ばね、／り
・・噴射器、／Ｉ・・二〜ドル、／？・・排出弁（圧力
制限装置）、 −〇・ｅ排出室、−Ｉ・・排出ピストン
。Figure 1 is a schematic arrangement diagram of the entire injection pump, #I4 from Figure 1
FIG. 7 is an explanatory diagram of its operation, FIGS. 7 to 7 are diagrams showing operating cycles, and FIG. io is a schematic arrangement diagram showing the injection pump of the present invention applied to a multi-cylinder engine. ! ...Delivery piston, 1...Delivery chamber, ?・Injection screw Fn, /Ja・Injection chamber, /J@one counter return spring, /ri・・Injector, /I・・2~$, /?・・Discharge valve (pressure limiting device), −〇・e discharge chamber, −I・・discharge piston.
Claims (1)
え大形式の品−ドル（／Ｉ）付き噴射１） （／ ？）
に、予め用量決定され大量の燃料を供給するための噴射
ポンプであって、任意の運動法則に従りてカム叉は偏心
輪によ）機械的に制御され、送出しｉｌ−に燃料を送出
すようｋした送出しピストン（四と、送出しｉｉ！（＠
内の圧力のみによシ作動され、噴射ＩＩ（／デ）に供給
するための噴射室（ノコ）Ｋ燃料を送出すようＫした対
抗復帰ばね（ｌめ付き噴射ピストン（９）と、機関の作
動状態及びその負荷、と無関係な予め調節され九高圧値
に送出し型棒）内の圧力を制−する圧力制限偏置（）９
）とを備え九ことを特徴とする噴射ポンプ０ １） 噴射室（／Ｊ）内の所定の圧力が噴射器（ｌり）
に伝達されると同時に排出室（−〇）にも伝達さｊ５排
出室（−〇）への上記圧力が電動三方弁（Ｊ Ａ）によ
って排除されない＠）噴射が阻止され、それにより、電
気的に定まりえ正確な噴射時点において一定の予め調節
され大圧力が直ちに生ずるようＫしたことを特徴とする
特許請求の範囲第１項記載の噴射ポンプ。 Ｊ） 噴射ｍ（／Ｊ）を圧力供給管（ηと遅弧して連通
させることによ〉燃料を予め用量決定すると共に、噴射
器（ｌツ）の排出１１ムＯ）内の過圧によシ噴射時点を
定めるえめの、単一の電動三方弁（コ４）鮪し、電動三
方弁（コ番）の共通の第１経路（Ｊ ｔ）は排出室（Ｊ
→に電動三方弁（Ｊｌ）を連通させる経路であり、他の
一つの経路（コツ）。 （コツ）は噴射室（／萄及び圧力供給管ｆｆ）Ｋそれぞ
れ連結され、電動三方弁（Ｊ６）の励磁はｌサイクルに
ついて唯／＠０方形パルスによ〉制御され、この方形パ
ルスの１つの縁即ち立上りＩＩ（Ｊｌ）及び立下〉縁（
ｓｓ）は、噴射の進行と予め用量決定された所定量の燃
料とを別々に規制する電子装置によ）定めることを特徴
とする特許請求の範囲第一項記載の噴射ポンプ。 亭） 噴射ピストン（９）内に管路（３１）を、また本
体（１）内に配管（，７Ｊ）をそれぞれ形成し、これら
の管路及び配管は、ニードル（／ｌ）の迅速な閉塞のた
め噴射器（ｌり）の容積室（ｚｉ）の圧力を排除するよ
うに、ピストン行程終了の直前に噴射室（／Ｊ）を圧力
供給管（７）に連通させるように配設されていることを
特徴とする特許請求の範囲第１−７項のいずれか／）Ｋ
記載の噴射ポンプＯ Ｉ） 送出しピストン（５）の行程終了に先行する噴射
ピストン（９）の行程終了の直前に送出し室（６）を排
出１ｉ！（コ０）に連通させる別の管路（３０）及び配
管（Ｊコ）を噴射ポンプ（９）及び本体ｆｌ） Ｋそれ
ぞれ形成し、それＫよシ、ニードル（／ｌ）の閉島を加
速する丸めに排出室（コＯ）を再充填させるようにした
ことを特徴とする特許請求の範囲第事項記載の噴射ポン
プ。 １） 多気筒機関に供給を行なうように多重型とし喪特
許請求の範囲第１−７項のいずれか１つに記載の噴射ポ
ンプであって、各々の気筒に対応する各々の送出し皇が
、配管ＩＪＫより互に連結され九゛２つの部分（４＆
、 ４ ｂ） Ｋ分割されており、一方の部分（ロ）及
びこれに対応する部材（１−１）は、噴射器（／ ？）
から隔置された共通カム軸（２／）を備えたｌっの組立
体Ｋまとめられ、単一の圧力制限装置（ｌデ）が逆止弁
（ｊｏ）によりそれぞれの室（４ａ）ＩＩ続され九こと
を特徴とする噴射ポンプ。[Claims] l) Large type product with piston (S /) and discharge 31 (Jt7) - injection with dollar (/I) 1) (/?)
an injection pump for supplying a pre-dosed quantity of fuel to a delivery il- The delivery piston (4 and delivery ii! (@
The injection piston (9) with a counter-return spring (injection piston (9)) is actuated only by the internal pressure and is designed to deliver fuel to the injection chamber (saw) K for supplying the injection II (/D), and Pressure limiting eccentricity (9) to limit the pressure in the delivery type rod to a pre-adjusted high pressure value (9) independent of the operating state and its load
) and an injection pump characterized in that: 1) the predetermined pressure in the injection chamber (/J) is
The above pressure to the discharge chamber (-〇) is not eliminated by the electric three-way valve (J A) at the same time as it is transmitted to the discharge chamber (-〇). 2. An injection pump as claimed in claim 1, characterized in that a constant preset high pressure is generated immediately at a precise injection point determined by . J) Pre-dosing the fuel by connecting the injection m (/J) with the pressure supply pipe (η) in a delayed arc and also overpressure in the injector discharge 11 m O). The common first path (Jt) of the electric three-way valve (No. 4) is the single electric three-way valve (No. 4) that determines the injection point.
This is the route that connects the electric three-way valve (Jl) to →, and is another route (trick). (Tips) are connected to the injection chamber (/socket and pressure supply pipe ff) K, and the excitation of the electric three-way valve (J6) is controlled by only /@0 square pulse for l cycle, and one of this square pulse Edge, that is, rising II (Jl) and falling〉edge (
2. Injection pump according to claim 1, characterized in that ss) is determined by an electronic device that separately regulates the progress of injection and the predetermined amount of fuel. A conduit (31) is formed in the injection piston (9) and a pipe (, 7J) is formed in the main body (1), and these pipes and pipes are designed to quickly close the needle (/l). Therefore, the injection chamber (/J) is arranged to communicate with the pressure supply pipe (7) just before the end of the piston stroke so as to eliminate the pressure in the volume chamber (zi) of the injector (1). Any one of claims 1 to 7, characterized in that /)K
The described injection pump O I) discharges the delivery chamber (6) immediately before the end of the stroke of the injection piston (9), which precedes the end of the stroke of the delivery piston (5) 1i! Another conduit (30) and piping (J) are formed to communicate with the injection pump (9) and the main body (fl), respectively, and this accelerates the closure of the needle (/l). The injection pump according to claim 1, characterized in that the discharge chamber (CO) is refilled in a rounded manner. 1) An injection pump according to any one of Claims 1 to 7, which is of a multiple type so as to supply a supply to a multi-cylinder engine, wherein each delivery pump corresponding to each cylinder is , 92 parts (4&
, 4 b) It is divided into K parts, and one part (b) and the corresponding member (1-1) are the injector (/?)
A single pressure limiting device (lde) is connected to each chamber (4a) by a check valve (jo), with a common camshaft (2/) spaced apart from each other. An injection pump characterized by:
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| FR8118558 | 1981-10-01 | ||
| FR8118558A FR2514075A1 (en) | 1981-10-01 | 1981-10-01 | PUMP INJECTOR WITH CONSTANT INJECTION PRESSURE AND PREDOSAGE AND DERIVATIVE SYSTEM |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS5874869A true JPS5874869A (en) | 1983-05-06 |
| JPH0454064B2 JPH0454064B2 (en) | 1992-08-28 |
Family
ID=9262668
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP57171067A Granted JPS5874869A (en) | 1981-10-01 | 1982-10-01 | Injection pump |
Country Status (4)
| Country | Link |
|---|---|
| EP (1) | EP0077235B1 (en) |
| JP (1) | JPS5874869A (en) |
| DE (1) | DE3265437D1 (en) |
| FR (1) | FR2514075A1 (en) |
Families Citing this family (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0759919B2 (en) * | 1986-04-04 | 1995-06-28 | 日本電装株式会社 | Fuel injection controller for diesel engine |
| US5333786A (en) * | 1993-06-03 | 1994-08-02 | Cummins Engine Company, Inc. | Fuel injection device for an internal combustion engine |
| US5438968A (en) * | 1993-10-06 | 1995-08-08 | Bkm, Inc. | Two-cycle utility internal combustion engine |
| EP0962649A1 (en) * | 1998-06-04 | 1999-12-08 | Wolfgang Dr. Heimberg | Fuel injection apparatus |
| AU4506799A (en) * | 1998-06-04 | 1999-12-20 | Wolfgang Heimberg | Pumping device |
Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5696154A (en) * | 1979-12-28 | 1981-08-04 | Nippon Denso Co Ltd | Fuel injection device |
Family Cites Families (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE1103685B (en) * | 1956-12-13 | 1961-03-30 | Pierre Etienne Bessiere | Self-regulating piston pump for fuel injection in internal combustion engines |
| DE2558789A1 (en) * | 1975-12-24 | 1977-07-14 | Bosch Gmbh Robert | HIGH PRESSURE FUEL INJECTION DEVICE FOR DIESEL ENGINES |
| US4250857A (en) * | 1978-09-13 | 1981-02-17 | The Bendix Corporation | Fuel injector for producing shaped injection pulses |
-
1981
- 1981-10-01 FR FR8118558A patent/FR2514075A1/en active Granted
-
1982
- 1982-09-27 EP EP82401738A patent/EP0077235B1/en not_active Expired
- 1982-09-27 DE DE8282401738T patent/DE3265437D1/en not_active Expired
- 1982-10-01 JP JP57171067A patent/JPS5874869A/en active Granted
Patent Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5696154A (en) * | 1979-12-28 | 1981-08-04 | Nippon Denso Co Ltd | Fuel injection device |
Also Published As
| Publication number | Publication date |
|---|---|
| JPH0454064B2 (en) | 1992-08-28 |
| FR2514075A1 (en) | 1983-04-08 |
| EP0077235B1 (en) | 1985-08-14 |
| FR2514075B1 (en) | 1983-12-23 |
| EP0077235A1 (en) | 1983-04-20 |
| DE3265437D1 (en) | 1985-09-19 |
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