JPH0147609B2 - - Google Patents

Info

Publication number
JPH0147609B2
JPH0147609B2 JP56150842A JP15084281A JPH0147609B2 JP H0147609 B2 JPH0147609 B2 JP H0147609B2 JP 56150842 A JP56150842 A JP 56150842A JP 15084281 A JP15084281 A JP 15084281A JP H0147609 B2 JPH0147609 B2 JP H0147609B2
Authority
JP
Japan
Prior art keywords
fuel
valve
injection pump
pressure
electronic control
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
Application number
JP56150842A
Other languages
Japanese (ja)
Other versions
JPS5788228A (en
Inventor
Toomasu Jon Sukinaa Robaato
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
ZF International UK Ltd
Original Assignee
Lucas Industries Ltd
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Lucas Industries Ltd filed Critical Lucas Industries Ltd
Publication of JPS5788228A publication Critical patent/JPS5788228A/en
Publication of JPH0147609B2 publication Critical patent/JPH0147609B2/ja
Granted legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D1/00—Controlling fuel-injection pumps, e.g. of high pressure injection type
    • F02D1/02—Controlling fuel-injection pumps, e.g. of high pressure injection type not restricted to adjustment of injection timing, e.g. varying amount of fuel delivered
    • F02D1/08—Transmission of control impulse to pump control, e.g. with power drive or power assistance
    • F02D1/12—Transmission of control impulse to pump control, e.g. with power drive or power assistance non-mechanical, e.g. hydraulic
    • 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
    • F02M41/00—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor
    • F02M41/08—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined
    • F02M41/14—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined rotary distributor supporting pump pistons
    • F02M41/1405—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined rotary distributor supporting pump pistons pistons being disposed radially with respect to rotation axis
    • F02M41/1411—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined rotary distributor supporting pump pistons pistons being disposed radially with respect to rotation axis characterised by means for varying fuel delivery or injection timing
    • 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
    • F02M59/38—Pumps characterised by adaptations to special uses or conditions

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)
  • High-Pressure Fuel Injection Pump Control (AREA)
  • Electrical Control Of Air Or Fuel Supplied To Internal-Combustion Engine (AREA)

Description

【発明の詳細な説明】 この発明は内燃機関に液体燃料を供給する燃料
噴射ポンプ装置に関し、特に装着機関と調時関係
を保つて燃料を送出するように動作する噴射ポン
プと、噴射ポンプに燃料を供給する低圧供給ポン
プと、供給ポンプからの圧力流体が作用して噴射
ポンプの各噴射行程において供給される燃料量を
制御する表面をもつ分配部材と、前記燃料圧力を
制御する電気作動式弁装置の動作を制御するため
種々の機関運転因子に応答する電子制御システム
を含む種類の燃料噴射ポンプ装置を提供する。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a fuel injection pump device that supplies liquid fuel to an internal combustion engine, and more particularly to an injection pump that operates to deliver fuel while maintaining a timing relationship with the engine in which it is installed, and a fuel injection pump device that supplies liquid fuel to an internal combustion engine. a distribution member having a surface on which pressurized fluid from the feed pump acts to control the amount of fuel delivered on each injection stroke of the injection pump; and an electrically actuated valve to control the fuel pressure. A type of fuel injection pump device is provided that includes an electronic control system responsive to various engine operating factors to control operation of the device.

この種の既知の装置の例として英国特許第
2071874号明細書が挙げられるが、そこに示され
ている燃料噴射ポンプ装置が休止状態にあると
き、該装置に諸部品に対し装着機関を始動させよ
うとする場合この装置が直ちに最大燃料量を送出
するように配置することが通常の実施手段として
示されている。このために該分配部材は当初弾性
装置によつて偏倚されており、燃料圧力が増大す
ると該分配部材は弾性装置の作用に抗して移動さ
れて供給される燃料量を減少する。分配部材が最
小燃料位置に偏倚されている装置とは異るこの装
置の利点は、燃料の送出が始まるに先立つて発生
する燃料圧力を必要としないから実質的な燃料量
が遅滞なく送出されることである。 An example of a known device of this kind is British Patent No.
No. 2071874 is mentioned, but when the fuel injection pump device shown therein is in a rest state, when an attempt is made to start the engine equipped with various parts of the device, this device immediately reaches the maximum fuel amount. Arrangements for delivery are shown as common practice. For this purpose, the distribution member is initially biased by the elastic device, and as the fuel pressure increases, the distribution member is moved against the action of the elastic device, reducing the quantity of fuel supplied. The advantage of this system over systems in which the distribution member is biased to a minimum fuel position is that a substantial amount of fuel is delivered without delay since no fuel pressure is required to be developed before fuel delivery begins. That's true.

或る機関製造者にとつて望ましくかつ事実絶対
必要と見なされることは、電子制御システムの故
障の場合に機関を安全限界内で運転が可能ならし
める支援システムを提供することである。このよ
うな支援システムは、使用時に、電子制御システ
ムに先立つて機関運転者がこの支援システムを作
動させるかも知れないというような或る種の増進
された最大性能を発揮させてはならない。そのう
え、この支援システムは機関のアイドル運転速度
を制御できなければならない。 What is considered desirable, and indeed essential, by some engine manufacturers is to provide an assistance system that allows the engine to operate within safe limits in the event of a failure of the electronic control system. Such an assistance system must not, in use, provide some enhanced maximum performance such that the engine operator may activate the assistance system prior to the electronic control system. Moreover, this support system must be able to control the idle speed of the engine.

この発明によれば、前記に規定された弁装置は
前記供給ポンプの吐出圧力を受ける表面をもち圧
力が増大すると変位されて前記表面に加えられる
圧力を増大する弁部材と、前記圧力による弁部材
の運動に抗するように前記弁部材を偏倚する弾性
装置と、前記弾性装置によつて作用される力を調
節するための手動操作装置を含む。 According to this invention, the valve device defined above has a surface that receives the discharge pressure of the supply pump, and a valve member that is displaced when the pressure increases to increase the pressure applied to the surface, and a valve member that is caused by the pressure. a resilient device for biasing the valve member against movement of the valve member, and a manual operating device for adjusting the force exerted by the resilient device.

この発明に係る燃料噴射ポンプ装置およびこれ
と組合わされる支援装置を図面を参照しつつ以下
に説明する。 DESCRIPTION OF THE PREFERRED EMBODIMENTS A fuel injection pump device and a support device combined therewith according to the present invention will be described below with reference to the drawings.

第１図において、この装置は２つの本体部分１
１，１２から成るハウジング１０を含み、部分１
１は孔あき突出部１３を備え、これによつて装着
機関に取付けられる。部分１１は回転駆動軸１４
を取付け、該駆動軸は使用時に装着機関と同期回
転するように該機関の駆動部材に結合される。こ
の駆動軸は一般に円筒形の室１５内に延び、かつ
この室内で大径のカツプ形部分１４ａをもつ。大
径部分には一対の直径上に配置された溝孔１６を
有し、かつ中空構造である。大径部分の開口端は
本体の部分１２に形成された差込１７まわりに配
置される。大径部分の内側面の残部は後述する目
的のためにテーパ形状に形成されている。 In FIG. 1, the device consists of two body parts 1
including a housing 10 consisting of parts 1 and 12;
1 is provided with a perforated projection 13 by which it is attached to the mounting engine. The portion 11 is a rotary drive shaft 14
and the drive shaft is coupled to a drive member of the mounted engine for rotation in synchronism with the engine in use. The drive shaft extends into a generally cylindrical chamber 15 and has a large diameter cup-shaped portion 14a within this chamber. The large diameter portion has a pair of diametrically arranged slot holes 16, and has a hollow structure. The open end of the large diameter section is arranged around a receptacle 17 formed in part 12 of the body. The remainder of the inner surface of the large diameter portion is tapered for the purpose described below.

駆動軸にはもみ下げ穴１８が形成され、かつオ
イルシール１９が駆動軸と係合するために本体部
分１１の外端に設けられている。駆動軸はスリー
ブ軸受２０によつて支持される。この駆動軸は、
軸の大径部分と末端表面と係合するスラスト表面
によつて軸方向の運動を抑止されている。或る場
合にはこのスラスト表面は本体部分１２に直接形
成されるが、他の場合には、駆動軸を取囲みかつ
低圧燃料供給ポンプ２２用の末端閉塞部として付
加的に使用される環状板２１によつて構成され
る。供給ポンプのロータ２２ａは駆動軸に担持さ
れかつ本体部分１１内に担持されたステータリン
グ２２ｂの偏心配置された表面と協働する羽根を
もつ。低圧ポンプは本体部分に取付けられたハウ
ジング内の燃料入口２３ａに接続された燃料入口
通路２３をもつ。低圧ポンプはまた出口２４をも
ち、圧力逃し弁２５が設けられて低圧ポンプの吐
出圧力が所望の制限値内に保たれることを保証す
る。 The drive shaft has a bulge hole 18 formed therein, and an oil seal 19 is provided at the outer end of the body portion 11 for engagement with the drive shaft. The drive shaft is supported by a sleeve bearing 20. This drive shaft is
Axial movement is restrained by a thrust surface that engages the large diameter portion of the shaft and the distal surface. In some cases this thrust surface is formed directly on the body portion 12, while in other cases it is an annular plate surrounding the drive shaft and additionally used as an end closure for the low pressure fuel supply pump 22. 21. The rotor 22a of the feed pump is carried on the drive shaft and has vanes that cooperate with an eccentrically arranged surface of a stator ring 22b carried within the body part 11. The low pressure pump has a fuel inlet passage 23 connected to a fuel inlet 23a in a housing attached to the body portion. The low pressure pump also has an outlet 24 and a pressure relief valve 25 is provided to ensure that the low pressure pump discharge pressure is maintained within desired limits.

円筒形内孔２６が本体部分１２に形成され該孔
内にスリーブ２７が嵌装されている。スリーブ２
７は、室１５内に突出しかつ該室内に位置する大
径頭部分をもつ回転方向および軸方向に可動な分
配部材２８を収容する。次に噴射ポンプについて
説明すると、横向きに延びる内孔２９が頭部分に
形成され、該内孔内に一対の往復運動可能なポン
ププランジヤ３０が配置された構成となつてお
り、後述するカムリング４１も含まれる。内孔２
９は分配部材に形成されためくら通路３１と連通
しかつ頭部分内のその末端において栓によつて密
閉されている。この通路は分配部材の周辺に形成
されかつ直径上で配置された一対の縦方向溝孔３
２、および分配部材の周辺に形成された単一の縦
方向溝孔３３と連通する。溝孔３３は、スリーブ
に形成された複数の出口ポート３４と連通し、該
出口ポートは使用時に装着機関の各噴射ノズルに
接続される出口３５と連通する。溝孔３２はスリ
ーブに形成された入口ポート３７と整合し、かつ
該ポートはソレノイド装置４０によつて制御され
るオン・オフ弁を用いて低圧ポンプの出口２４と
連通する円周溝３８から内向きに延びる。 A cylindrical bore 26 is formed in the body portion 12 and a sleeve 27 is fitted within the bore. sleeve 2
7 houses a rotationally and axially movable distribution member 28 with a large diameter head portion projecting into and located within the chamber 15 . Next, the injection pump will be described. An inner hole 29 extending laterally is formed in the head portion, and a pair of pump plungers 30 that can reciprocate are disposed within the inner hole. A cam ring 41, which will be described later, is also provided. included. Inner hole 2
9 communicates with a blind passage 31 formed in the dispensing member and is sealed at its end in the head part by a plug. The passageway is formed in the periphery of the distribution member by a pair of diametrically disposed longitudinal slots 3.
2, and a single longitudinal slot 33 formed around the periphery of the distribution member. The slots 33 communicate with a plurality of outlet ports 34 formed in the sleeve, which in use communicate with outlets 35 that are connected to respective injection nozzles of the mounting engine. Slot 32 is aligned with an inlet port 37 formed in the sleeve, and the port is injected from a circumferential groove 38 in communication with the outlet 24 of the low pressure pump using an on-off valve controlled by a solenoid device 40. Extends in the direction.

環状カムリング４１が分配部材２８の頭部分を
囲み、このカムリングの内周辺の表面に直径上で
対になつて配置されたカム山が形成されている。
特別の実例においては、装置が６気筒機関に燃料
を供給するものであるから３組のカム山を有して
いる。カムリング４１は、全体を４２で示されか
つ半径方向に配設された栓４３によつてカムリン
グに結合された燃料圧力作動装置により分配部材
の回転軸線まわりに角運動可能である。 An annular cam ring 41 surrounds the head portion of the distribution member 28 and has diametrically arranged cam ridges formed on its inner peripheral surface.
In a particular example, the system is for supplying fuel to a six cylinder engine, so it has three sets of cam lobes. The cam ring 41 is angularly movable about the axis of rotation of the distribution member by a fuel pressure actuator, generally indicated at 42 and coupled to the cam ring by a radially disposed plug 43.

一対の従動子がプランジヤの外端に配置され、
従動子はそれぞれシユー４５に担持されたローラ
４４を含む。従動子は、分配部材の頭部分の側面
に取付けられた一対の側板４６，４７によつて分
配部材に対し軸方向に保持されている。側板は環
状形態で、かつ駆動軸に形成された溝孔１６内に
位置する外向きに延びる部分をもつ。シユーの円
周方向側面には円周方向に延びる突起４９が設け
られ、その半径方向外側表面はテーパが形成され
て駆動軸の大径部分の内側表面に形成されたテー
パ付き表面と協働する。 a pair of followers positioned at the outer ends of the plunger;
The followers each include a roller 44 carried by a shoe 45. The follower is held axially relative to the distribution member by a pair of side plates 46, 47 attached to the sides of the head portion of the distribution member. The side plate is of annular configuration and has an outwardly extending portion located within a slot 16 formed in the drive shaft. The circumferential side of the shoe is provided with a circumferentially extending protrusion 49 whose radially outer surface is tapered to cooperate with a tapered surface formed on the inner surface of the large diameter portion of the drive shaft. .

使用時に、入口ポート３７と溝孔３２とが合致
して燃料がめくら通路３１を介して内孔２９に供
給されると、プランジヤ３０が燃料の圧力によつ
て外向きに移動され、これによりシユー４５およ
びローラ４４に外向き運動を与える。この外向き
運動は、シユーのテーパ付き表面との当接によつ
て制限され、かつ分配部材を軸方向に移動するこ
とによつて、プランジヤの外向き運動距離が変化
される。よつて、内孔２９に供給される燃料の量
が制御され、これによりプランジヤ３０が一対の
カム山によつて内向きに動かされるとき出口３５
を通つて送出される燃料の量を定める。 In use, when inlet port 37 and slot 32 mate and fuel is supplied to bore 29 through blind passage 31, plunger 30 is moved outwardly by the pressure of the fuel, thereby 45 and rollers 44 in an outward motion. This outward movement is limited by abutment with the tapered surface of the shoe, and by axially moving the distribution member, the distance of outward movement of the plunger is varied. Thus, the amount of fuel supplied to the bore 29 is controlled such that when the plunger 30 is moved inwardly by the pair of cam lobes, the outlet 35
determines the amount of fuel delivered through.

分配部材の軸方向位置は液圧的に変化される
が、これは本体部分１２の円筒形内孔２６の末端
に形成された室５０内の分配部材の端面２８Ａに
加わる圧力を変化させることによつて、実施され
る。円筒形内孔２６の末端は閉塞部材によつて閉
鎖され、圧力燃料は第２図に示す弁を用いて室５
０に供給される。燃料は制限オリフイス５２を通
つて室から流出し、燃料はこの装置の内部に流動
する。第２図に示された如く、弁５１は開き位置
に偏倚されておりかつこの弁と組合わされたソレ
ノイドに電流を供給することによつて閉じられ
る。ソレノイドへの電流の供給は電子制御システ
ム５５の作用を受けて行われ、該システムの構造
はこの発明の部分を構成するものではなく、例え
ばイギリス特許明細書第1429293号に記載のもの
がある。分配部材はもみ下げ穴１８内に配設され
た圧縮コイルばね５３によつて偏倚され、該ばね
は駆動軸１４と分配部材２８との間で作用し、か
つ室５０内の圧力を受けた燃料の作用に抗して分
配部材２８を押動するように作用する。室５０内
には変換器５４が配設され、該変換器は、分配部
材の回転速度および分配部材の軸方向設定位置の
標示を電子制御システム５５に提供するのに用い
られる。 The axial position of the distribution member is hydraulically varied, which changes the pressure exerted on the end surface 28A of the distribution member within the chamber 50 formed at the distal end of the cylindrical bore 26 of the body portion 12. Therefore, it will be implemented. The distal end of the cylindrical bore 26 is closed by a closure member, and the pressurized fuel is discharged into the chamber 5 using the valve shown in FIG.
0. Fuel exits the chamber through the restriction orifice 52 and fuel flows into the interior of the device. As shown in FIG. 2, valve 51 is biased to the open position and is closed by applying current to the solenoid associated with the valve. The supply of current to the solenoid takes place under the action of an electronic control system 55, the structure of which does not form part of this invention and is described, for example, in British Patent Specification No. 1429293. The distribution member is biased by a helical compression spring 53 disposed within the kneading hole 18, which spring acts between the drive shaft 14 and the distribution member 28 and which compresses the pressurized fuel in the chamber 50. act to push the distribution member 28 against the action of. A transducer 54 is disposed within the chamber 50 and is used to provide an indication of the rotational speed of the dispensing member and the axial set position of the dispensing member to an electronic control system 55.

特に第２図において、圧力燃料が５６で示す二
方弁によつて供給ポンプの出口から供給され、通
常の運転状態においては、燃料は弁５６によつて
室５０に流動し、室５０内の圧力は弁５１の有効
サイズを調節することによつて制御される。前述
の如く、この制御は通常の電子制御システム５５
によつて実施される。この制御システムが故障す
ると、安全状態を考えると、弁が開き位置をと
る。この状態になると、室５０内の圧力は、増大
し、分配部材はばね５３の作用に抗して最大範囲
まで移動されて機関へ流入する燃料量を減ずる。
これによつて機関の停止を起すおそれがある。別
の故障状態としては、弁５１が閉じ位置になる場
合で、この場合は室５０内の圧力を低下させ、機
関への供給燃料量は増大する。この例において、
電子制御システムが故障するとこれを機関の運転
者に警告し、このような警告を受けると運転者が
弁５６を手動操作して弁を別の位置に動作させる
ように配置されている。この別の位置において、
弁５１は回路から除外されて、燃料は手動操作弁
５７によつて室５０に供給される。この弁は第２
図に線図によつて示されるが、該弁がばね５７Ｂ
によつて弁座上に着座したボール５７Ａを含むこ
とが判るであろう。ばねによつて作用される力は
変化させることができる。このばねとの当接は、
５８で示す回動レバーによつて機関のスロツトル
ペダルに結合される。スロツトルペダルが押圧さ
れると、弁部材に作用するばねによつて加えられ
る力は増大し、これによつて弁部材をその弁座に
押動し室５０への燃料の流動を減少する。この結
果、室５０内の圧力は減少するから機関に供給さ
れる燃料の量を増大させる。しかし、機関の速度
が増大すると、ポンプ２２の吐出圧力が増大し、
ボールの表面に作用するこの圧力増大はボール５
７Ａをその座からもち上げて、室５０内の圧力を
増大させる。この結果、分配部材はばねの作用に
抗して移動して、機関に供給される燃料の量を減
少し、このようにして調整作用が得られる。 In particular, in FIG. 2, pressurized fuel is supplied from the outlet of the supply pump by a two-way valve indicated at 56; under normal operating conditions, fuel flows to chamber 50 by valve 56; Pressure is controlled by adjusting the effective size of valve 51. As mentioned above, this control is performed by a conventional electronic control system 55.
Implemented by. If this control system fails, the valve assumes the open position, considering the safety condition. In this condition, the pressure in chamber 50 increases and the distribution member is moved to its maximum extent against the action of spring 53 to reduce the amount of fuel entering the engine.
This may cause the engine to stop. Another failure condition is when valve 51 is in the closed position, which reduces the pressure within chamber 50 and increases the amount of fuel supplied to the engine. In this example,
If the electronic control system malfunctions, it is arranged to alert the operator of the engine, and upon receiving such warning, the operator manually operates the valve 56 to operate the valve to another position. In this other position,
Valve 51 is removed from the circuit and fuel is supplied to chamber 50 by manually operated valve 57. This valve is the second
It is shown diagrammatically in the figure that the valve is connected to spring 57B.
It will be seen that this includes a ball 57A seated on the valve seat. The force exerted by the spring can be varied. The contact with this spring is
It is connected to the engine throttle pedal by a pivot lever shown at 58. When the throttle pedal is depressed, the force applied by the spring acting on the valve member increases, thereby forcing the valve member into its seat and reducing the flow of fuel into chamber 50. As a result, the pressure within chamber 50 decreases, thereby increasing the amount of fuel supplied to the engine. However, as the engine speed increases, the pump 22 discharge pressure increases;
This increased pressure acting on the surface of the ball causes the ball 5
7A is lifted from its seat to increase the pressure within chamber 50. As a result, the distribution member moves against the action of the spring and reduces the amount of fuel supplied to the engine, thus providing a regulating effect.

第２図は２つのグラフを示し、上方のものは横
軸の機関速度に対するポンプ２２の吐出圧力をプ
ロツトしたグラフ、下方のものは縦軸を燃料量と
し、横軸を回転速度とした調速機特性を示すグラ
フである。実線は電子制御システムを用いて得ら
れた特性で、線５９はアイドリング特性を、また
線６０は最大燃料特性を示し、後者の場合冷間時
始動の際の過剰燃料特性を含む。線５９と６０と
の間に見られる破線は弁５７を用いて得られた調
速機特性であり、このグラフから言えることは弁
５７を用いた機関から直接得られる性能は、通常
の電子制御システムが作動状態にあるときに得ら
れる性能より劣ることが判る。即ち、最大燃料特
性に関しては電子制御システムの場合より効率が
悪く、アイドリング回転数が高いと言うことであ
る。第３図において、、構成要素は第２図とは異
つて配置され、ただ基本的な相違は、弁５６は電
磁作動弁６１によつて置き換えられている。その
うえ、弁５７の構造はわずかに異る。弁６１はこ
の場合も二方弁で、この弁は燃料が弁５７によつ
て室５０に供給される位置に、ばね６３によつて
偏倚される弁部材６２を含む。弁と組合わされた
ソレノイドが付勢されると、電機子６４は弁部材
をそのばねの作用に抗して移動して弁５７に接続
する通路を閉じる。ゆえに電子制御システムによ
つて作動される弁５１によつて室５０に燃料が流
入する。このシステムが故障した場合は弁６１と
組合わされたソレノイドは除勢され、弁５７を用
いる機関の制御は自動的に実施される。 Figure 2 shows two graphs; the upper one plots the discharge pressure of the pump 22 against the engine speed on the horizontal axis, and the lower one plots the fuel amount on the vertical axis and the rotational speed on the horizontal axis. 2 is a graph showing machine characteristics. The solid lines are the characteristics obtained using the electronic control system, line 59 showing the idling characteristic and line 60 the maximum fuel characteristic, in the latter case including the excess fuel characteristic during cold start. The dashed line between lines 59 and 60 is the governor characteristic obtained using valve 57, and what can be said from this graph is that the performance directly obtained from the engine using valve 57 is higher than that of normal electronic control. It can be seen that the performance is inferior to that obtained when the system is in operation. That is, they are less efficient with respect to maximum fuel characteristics than electronic control systems and have higher idling speeds. In FIG. 3, the components are arranged differently than in FIG. 2, the only fundamental difference being that valve 56 is replaced by an electromagnetically actuated valve 61. Moreover, the structure of valve 57 is slightly different. Valve 61 is again a two-way valve and includes a valve member 62 biased by a spring 63 into a position where fuel is supplied to chamber 50 by valve 57 . When the solenoid associated with the valve is energized, armature 64 moves the valve member against the action of its spring to close the passageway connecting valve 57. Fuel therefore enters the chamber 50 by means of a valve 51 actuated by the electronic control system. In the event of a failure of this system, the solenoid associated with valve 61 is deenergized and control of the engine using valve 57 is automatically implemented.

第４図においては、僅かに相違する配置が示さ
れ、この配置において、第３図に示す弁５１，６
１および５７の役目は複合されている。この複合
弁は６５で示され、燃料入口７４が中央部に開口
した弁座６７上に押圧される板状の弁座材６６を
含み室５０への圧力燃料の流動を防止する。弁部
材６６は磁性材料で造られかつ押し棒６８によつ
て接触され、その他端は、圧縮コイルばね７０に
よつて偏倚された電機子６９と係合し、このばね
によつて作用される力は、使用時に装着機関のス
ロツトルペダルに結合されたレバー７１によつて
変動される。ばね７０は弁部材６６を弁座と接触
させて、弁の部分を構成する２つのソレノイドを
この時点で無能化し、構成諸部品は前述の第３図
に示した弁５７の機能を果す。換言すれば、ポン
プの吐出圧力が増大すると、弁部材６６は弁座か
ら離座して室５０内の圧力を増大させ、これによ
りばねの作用に抗して分配部材２８を移動して機
関に供給される燃料量を減少する。 In FIG. 4 a slightly different arrangement is shown, in which the valves 51, 6 shown in FIG.
The roles of 1 and 57 are combined. The compound valve is indicated at 65 and includes a plate-shaped valve seat 66 pressed onto a valve seat 67 with a fuel inlet 74 opening in the center to prevent flow of pressurized fuel into the chamber 50. The valve member 66 is made of magnetic material and is contacted by a push rod 68, the other end of which engages an armature 69 biased by a helical compression spring 70 to absorb the force exerted by this spring. is varied in use by a lever 71 connected to the throttle pedal of the installed engine. Spring 70 brings valve member 66 into contact with the valve seat, disabling the two solenoids forming part of the valve at this point, and the components performing the function of valve 57 shown in FIG. 3 above. In other words, as the pump discharge pressure increases, the valve member 66 unseats and increases the pressure within the chamber 50, thereby displacing the distribution member 28 against the action of the spring and forcing it into the engine. Reduce the amount of fuel supplied.

２つのソレノイド巻線７２，７３が弁部材６６
および電機子６９それぞれに磁力を作用して吸引
するために設けられる。これらの巻線は電子制御
システムに接続され、巻線７２はアイドリング運
転燃料特性を制御するのに用いられ、巻線７３は
最大燃料特性を制御するのに用いられる。もし巻
線７３および通常の電子制御システムの組合わさ
れた部分が故障すると、アイドリング特性は依然
として電子制御システムにより決定される。これ
に反し、もし巻線７２が通常の電子制御システム
と共に故障すると、アイドリング特性は弁部材６
６に作用する圧力とばね７０によつて作用される
抵抗力とによつて決められる。 The two solenoid windings 72 and 73 are connected to the valve member 66.
and the armature 69 to apply magnetic force to each of them to attract them. These windings are connected to an electronic control system, with winding 72 used to control idle fuel characteristics and winding 73 used to control maximum fuel characteristics. If winding 73 and the associated portions of the conventional electronic control system fail, the idle characteristics will still be determined by the electronic control system. On the other hand, if winding 72 fails along with the normal electronic control system, the idling characteristics of valve member 6
6 and the resistance force exerted by spring 70.

弁部材６６はひつかかり現象を起す危険が極め
て少いように構成される。押し棒６８は適正な間
隙をもつが、押し棒の両端が同一の燃料圧力を受
けて燃料内の塵埃粒子がここに設けられた間隙内
に滞留する危険を少くすることを保証するために
平衝通路が設けられている。以上の実施例から理
解されるように本発明による燃料噴射ポンプ装置
は電子制御による燃料量制御系が不意に故障をし
ても即座に手動操作に切り替わり、安全且つ確実
な機関の速度制御が可能となり、また、二方向弁
或いは複合型の弁により形成された切換弁自体も
その構成が簡素であり、製造が極めて容易である
点もまた見逃せない一つの大きな利点である。 The valve member 66 is constructed in such a way that there is very little risk of binding phenomena. The push rod 68 has a suitable clearance, but is flat to ensure that both ends of the push rod receive the same fuel pressure to reduce the risk of dust particles in the fuel becoming lodged within the gap provided here. A passageway is provided. As can be understood from the above embodiments, the fuel injection pump device according to the present invention can immediately switch to manual operation even if the electronically controlled fuel quantity control system unexpectedly breaks down, making it possible to safely and reliably control the speed of the engine. Another major advantage that cannot be overlooked is that the switching valve itself, which is formed by a two-way valve or a composite valve, has a simple structure and is extremely easy to manufacture.

【図面の簡単な説明】[Brief explanation of drawings]

第１図はこの発明に係る装置の切断側面図で、
該装置は他の図面において図式に示され、第２，
３，４図は第１図に示す装置に種々の支援システ
ムを取付けた場合を示す。 図中の符号 １０…ハウジング、１１…部分、
１２…部分、１３…孔あき突出部、１４…駆動
軸、１５…円筒形室、１６…溝孔、１７…差込部
分、１８…内孔、１９…オイルシール、２０…ス
リーブ軸受、２１…環状板、２２…燃料供給ポン
プ、２２ａ…ロータ、２２ｂ…ステータリング、
２３…燃料入口、２３ａ…燃料入口、２４…燃料
出口、２５…逃し弁、２６…内孔、２７…スリー
ブ、２８…分配部材、２８Ａ…端面、２９…内
孔、３０…プランジヤー、３１…めくら通路、３
２…溝孔、３３…溝孔、３４…出口ポート、３５
…出口、３７…入口ポート、３８…円周溝、３９
…オン・オフ弁、４０…ソレノイド装置、４１…
環状カムリング、４２…燃料圧力作動装置、４３
…栓、４４…ローラ、４５…シユー、４６，４７
…側板、４９…突起、５０…室、５１…弁、５２
…オリフイス、５３…圧縮ばね、５４…変換器、
５５…電子制御システム、５６…二方向弁、５７
…手動操作弁、５８…回動レバー、５９，６０…
ライン、６１…弁、６２…弁部材、６３…ばね、
６４…電機子、６５…弁、６６…弁部材、６７…
座、６８…押し棒、６９…電機子、７０…圧縮ば
ね、７１…レバー、７２，７３…ソレノイド巻線
を示す。 FIG. 1 is a cutaway side view of the device according to the invention;
The apparatus is shown diagrammatically in the other figures, the second,
Figures 3 and 4 show the apparatus shown in Figure 1 with various support systems attached. Symbols in the figure 10...housing, 11...part,
12... portion, 13... perforated protrusion, 14... drive shaft, 15... cylindrical chamber, 16... slot, 17... insertion part, 18... inner hole, 19... oil seal, 20... sleeve bearing, 21... Annular plate, 22... fuel supply pump, 22a... rotor, 22b... stator ring,
23...Fuel inlet, 23a...Fuel inlet, 24...Fuel outlet, 25...Relief valve, 26...Inner hole, 27...Sleeve, 28...Distribution member, 28A...End face, 29...Inner hole, 30...Plunger, 31...Blind aisle, 3
2...Slot hole, 33...Slot hole, 34...Outlet port, 35
...Outlet, 37...Inlet port, 38...Circumferential groove, 39
...On/off valve, 40...Solenoid device, 41...
Annular cam ring, 42...Fuel pressure actuation device, 43
...Plug, 44...Roller, 45...Show, 46,47
...Side plate, 49...Protrusion, 50...Chamber, 51...Valve, 52
... Orifice, 53 ... Compression spring, 54 ... Converter,
55...Electronic control system, 56...Two-way valve, 57
...Manual operation valve, 58...Rotary lever, 59,60...
line, 61...valve, 62...valve member, 63...spring,
64... Armature, 65... Valve, 66... Valve member, 67...
Seat, 68... push rod, 69... armature, 70... compression spring, 71... lever, 72, 73... solenoid winding.

Claims (1)

【特許請求の範囲】 １ 装着機関と調時関係をもつて燃料を送出する
ように動作する噴射ポンプ２９，３０，４１と、
噴射ポンプに燃料を供給する低圧燃料供給ポンプ
２２と、噴射ポンプの各噴射行程において供給さ
れる燃料量を制御するように低圧燃料供給ポンプ
２２からの加圧燃料が作用する端面２８Ａをもつ
分配部材２８と、前記端面に作用する燃料圧力を
制御するための電子制御弁５１と、前記電子制御
弁の動作を制御する種々の機関運転因子に応答す
る電子制御システム５５と、前記電子制御弁ある
いは電子制御システムが故障した際に作動して手
動制御弁５７を介して燃料を前記端面２８Ａと本
体部分１２に依つて画成される室５０へ導く通路
に切換えるところの二方向弁５６，６１とを含
み、さらに前記手動制御弁５７が前記低圧燃料供
給ポンプ２２の吐出圧力を受けて移動可能な弾性
装置５７Ｂに依り偏倚された弁部材５７Ａと、前
記弾性装置に依つて作用される力を調節する手動
操作装置５８とから成る事を特徴とする燃料噴射
ポンプ装置。 ２ 前記二方向弁５６が手動操作可能である事を
特徴とする前記特許請求の範囲第１項に記載の燃
料噴射ポンプ装置。 ３ 前記二方向弁６１が前記電子制御システム５
５に依り電気的に制御される事を特徴とする前記
特許請求の範囲第１項に記載の燃料噴射ポンプ装
置。 ４ 装着機関と調時関係をもつて燃料を送出する
ように動作する噴射ポンプ２９，３０，４１と、
噴射ポンプに燃料を供給する低圧燃料供給ポンプ
２２と、噴射ポンプの各噴射行程において供給さ
れる燃料量を制御するように低圧燃料供給ポンプ
２２からの加圧燃料が作用する端面２８Ａをもつ
分配部材２８と、前記端面に作用する圧力を制御
する複合型の弁６５とから成り、前記複合型の弁
６５が中央部に燃料入口７４が開口した弁座６７
に係合する方向に押し棒６８を介して弾性装置７
０により偏倚された板状の弁部材６６と、前記弾
性装置７０の端部に係合して弾性力を調節する手
動レバー７１と、種々の機関運転因子に応答する
電子制御システム５５と、該システムに依つて制
御されると共に前記押し棒６８を囲繞している一
対のソレノイド巻線７２，７３とを備え、更に前
記弁部材６６が低圧燃料供給ポンプ２２からの燃
料圧力を本体部分１２と前記端面２８Ａとに依つ
て画成された室５０に作用する圧力を制御するた
めに、燃料圧力に抗する前記弾性装置の偏倚力に
抗して前記弁座６７との離間距離を増加するべく
前記ソレノイド巻線により発生される電磁力によ
り制御されるように成した事を特徴とする燃料噴
射ポンプ装置。[Claims] 1. Injection pumps 29, 30, 41 that operate to deliver fuel in a timing relationship with the installed engine;
A distribution member having a low pressure fuel supply pump 22 for supplying fuel to the injection pump and an end face 28A on which pressurized fuel from the low pressure fuel supply pump 22 acts to control the amount of fuel delivered on each injection stroke of the injection pump. 28, an electronic control valve 51 for controlling the fuel pressure acting on the end face, an electronic control system 55 responsive to various engine operating factors to control the operation of the electronic control valve, and an electronic control valve 51 for controlling the fuel pressure acting on the end face. two-way valves 56, 61 which are actuated in the event of a failure of the control system to divert fuel via manual control valve 57 to a passageway leading to chamber 50 defined by end face 28A and body portion 12; The manual control valve 57 further includes a valve member 57A biased by an elastic device 57B movable in response to the discharge pressure of the low-pressure fuel supply pump 22, and adjusting the force exerted by the elastic device. A fuel injection pump device characterized by comprising a manual operation device 58. 2. The fuel injection pump device according to claim 1, wherein the two-way valve 56 is manually operable. 3 The two-way valve 61 is connected to the electronic control system 5
5. The fuel injection pump device according to claim 1, wherein the fuel injection pump device is electrically controlled by the fuel injection pump device according to claim 1. 4 injection pumps 29, 30, 41 that operate to deliver fuel in a timed relationship with the installed engine;
A distribution member having a low pressure fuel supply pump 22 for supplying fuel to the injection pump and an end face 28A on which pressurized fuel from the low pressure fuel supply pump 22 acts to control the amount of fuel delivered on each injection stroke of the injection pump. 28 and a composite type valve 65 for controlling the pressure acting on the end face, and the composite type valve 65 has a valve seat 67 with a fuel inlet 74 opened in the center thereof.
the elastic device 7 via the push rod 68 in the direction of engagement with the
a plate-shaped valve member 66 biased by 0; a manual lever 71 that engages the end of the elastic device 70 to adjust the elastic force; and an electronic control system 55 that is responsive to various engine operating factors. a pair of solenoid windings 72, 73 controlled by the system and surrounding the push rod 68, and the valve member 66 directing fuel pressure from the low pressure fuel supply pump 22 to the body portion 12 and the push rod 68; In order to control the pressure acting on the chamber 50 defined by the end face 28A, the separation distance from the valve seat 67 is increased against the biasing force of the elastic device against the fuel pressure. A fuel injection pump device characterized in that it is controlled by electromagnetic force generated by a solenoid winding.
JP56150842A 1980-10-29 1981-09-25 Fuel injection pump device Granted JPS5788228A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
GB8034742 1980-10-29

Publications (2)

Publication Number Publication Date
JPS5788228A JPS5788228A (en) 1982-06-02
JPH0147609B2 true JPH0147609B2 (en) 1989-10-16

Family

ID=10516943

Family Applications (1)

Application Number Title Priority Date Filing Date
JP56150842A Granted JPS5788228A (en) 1980-10-29 1981-09-25 Fuel injection pump device

Country Status (10)

Country Link
JP (1) JPS5788228A (en)
AR (1) AR228374A1 (en)
BR (1) BR8106966A (en)
DE (1) DE3142980A1 (en)
ES (1) ES505632A0 (en)
FR (1) FR2492887A1 (en)
GB (1) GB2108727B (en)
IT (1) IT1138667B (en)
MX (1) MX153898A (en)
ZA (1) ZA816220B (en)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3243348A1 (en) * 1982-11-24 1984-05-24 Robert Bosch Gmbh, 7000 Stuttgart FUEL INJECTION PUMP
FR2567577B1 (en) * 1984-07-12 1989-03-03 Cav Roto Diesel IMPROVEMENTS ON FUEL INJECTION PUMPS FOR INTERNAL COMBUSTION ENGINES
DE3719807A1 (en) * 1987-06-13 1988-12-22 Bosch Gmbh Robert RADIAL PISTON FUEL INJECTION PUMP
DE3929932C1 (en) * 1989-09-08 1991-03-21 Mercedes-Benz Aktiengesellschaft, 7000 Stuttgart, De
DE3937962C1 (en) * 1989-11-15 1991-05-02 Mercedes-Benz Aktiengesellschaft, 7000 Stuttgart, De

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5730260U (en) * 1980-07-25 1982-02-17

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1209357B (en) * 1961-09-21 1966-01-20 Cav Ltd Hydraulic regulator for internal combustion engines
GB2037365B (en) * 1978-11-25 1982-12-08 Lucas Industries Ltd Liquid fuel injection pumping apparatus

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5730260U (en) * 1980-07-25 1982-02-17

Also Published As

Publication number Publication date
BR8106966A (en) 1982-07-13
AR228374A1 (en) 1983-02-28
ES8206755A1 (en) 1982-08-16
DE3142980C2 (en) 1990-12-13
GB2108727B (en) 1985-02-06
IT8124207A0 (en) 1981-09-29
JPS5788228A (en) 1982-06-02
ES505632A0 (en) 1982-08-16
DE3142980A1 (en) 1982-06-16
ZA816220B (en) 1982-09-29
MX153898A (en) 1987-02-11
FR2492887A1 (en) 1982-04-30
FR2492887B1 (en) 1984-10-26
IT1138667B (en) 1986-09-17
GB2108727A (en) 1983-05-18

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