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EP0178505B1 - Fuel injection pump for combustion engines - Google Patents

Fuel injection pump for combustion engines Download PDF

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Publication number
EP0178505B1
EP0178505B1 EP85112161A EP85112161A EP0178505B1 EP 0178505 B1 EP0178505 B1 EP 0178505B1 EP 85112161 A EP85112161 A EP 85112161A EP 85112161 A EP85112161 A EP 85112161A EP 0178505 B1 EP0178505 B1 EP 0178505B1
Authority
EP
European Patent Office
Prior art keywords
control
control rod
driving members
fuel injection
pump
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
EP85112161A
Other languages
German (de)
French (fr)
Other versions
EP0178505A1 (en
Inventor
Josef Güntert
Walter Häfele
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.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
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 Robert Bosch GmbH filed Critical Robert Bosch GmbH
Priority to AT85112161T priority Critical patent/ATE40186T1/en
Publication of EP0178505A1 publication Critical patent/EP0178505A1/en
Application granted granted Critical
Publication of EP0178505B1 publication Critical patent/EP0178505B1/en
Expired legal-status Critical Current

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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
    • F02M59/24—Varying fuel delivery in quantity or timing with constant-length-stroke pistons having variable effective portion of stroke
    • F02M59/26—Varying fuel delivery in quantity or timing with constant-length-stroke pistons having variable effective portion of stroke caused by movements of pistons relative to their cylinders
    • F02M59/28—Mechanisms therefor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D17/00—Controlling engines by cutting out individual cylinders; Rendering engines inoperative or idling
    • F02D17/02—Cutting-out
    • 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
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/02—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively

Definitions

  • the invention is based on a fuel injection pump according to the preamble of claim 1.
  • the entrainment members are designed as clamps, which are adjustably clamped by tightening the free legs by means of a screw on the round control rod and have a pin which engages on the control slide in an annular groove provided for this purpose.
  • the individual entrainment members can be adjusted relative to one another with regard to their rotational position and thus the control slide with respect to their stroke position, but they cannot be actuated independently of one another. It is therefore also not possible to achieve the partial shutdown of the engine cylinders when the engine is idling (cylinder deactivation).
  • Such a cylinder deactivation is known per se in a fuel injection pump of another type (GB-A-2038934), in which the fuel delivery can be switched off from part of the pump work spaces to the internal combustion engine.
  • a fuel injection pump of another type GB-A-2038934
  • these measures can improve fuel consumption, exhaust gas and noise emissions, especially when the engine is idling and under partial load. In addition, less fuel gets into the engine lubricating oil while avoiding excessive thinning.
  • such a cylinder deactivation is also used in motor vehicles if only auxiliary units are to be driven by the engine of the vehicle for loading and unloading of silo or tank vehicles, for example.
  • these known in-line injection pumps in which the pump pistons of individual units of the pump can be rotated to shut off the delivery to zero delivery, this has not been known in the case of pumps controlled by a linear slide valve.
  • the aim of the invention is now to enable cylinder deactivation in a simple and space-saving manner even in the case of slide valve-controlled fuel injection pumps.
  • the first, two groups of entrainment members and the feature group consisting of two independently operable and arranged control rods comprising control rod from the characterizing part of claim 1 is known per se for fuel injection pumps of another type from GB-A-2038934 cited at the beginning.
  • the two control rods are arranged coaxially with one another, the second control rod being tubular, having radial openings with play in the direction of rotation for the entrainment members carried by the first control rod, and this first control rod guiding the rotary movement. Since the openings only have to be so large that the relative adjustment of the two control rods is possible, the stability of the rods is not impaired, so that even relatively high actuating forces can be transmitted without twisting the rods.
  • the two control rods are penetrated transversely to the longitudinal axis of the control rods by a driving pin that has play in the direction of rotation relative to one or the other control rod, the play being dimensioned such that when the second control rod is rotated in the direction constant opening of the relief bores (switching off the engine), the first control rod with the drive links carried by it is also turned into this opening position.
  • Such a driving pin penetrating both control rods can advantageously save an additional axial fixation of the two control rods against one another, and relatively narrow tolerances can be used, since no additional fastening means, for example the driving pin on the control rod, are required.
  • the combination of all the features specified in claim 1 allows the driving links, for. B. for their equality, independently of each other without affecting the overall function.
  • a particularly advantageous embodiment in terms of manufacture and assembly is that, according to claim 5, the entrainment members are designed as a rotating part having a threaded section and fastened to the respective control rod.
  • eccentrically offset pins can be arranged at one end of the driving members for engagement on the control slide, the driving members being secured against twisting by nuts running on the threaded section.
  • a plurality of cylinder liners 2 are embedded in series, in the pump cylinder 2a of which pump pistons 3 are guided and driven via a camshaft against the force of a spring 5 for their axial movement forming the working stroke.
  • the cylinder liner 2 there is a recess 6 which receives a control slide 7 which is axially displaceable on the pump piston 3.
  • the control slide 7 is actuated via a driving element 8, which is connected either to a first control rod 9 or to a second control rod 11 arranged in a tubular manner around it, so that a rotary movement of one of the control rods causes a corresponding displacement of the respective control slide 7.
  • a pump working chamber 12 is delimited by the pump piston 3 and the pump cylinder 2a, from which the pump piston 3 can deliver fuel to the internal combustion engine during its pressure stroke via a pressure valve 13 and a pressure line 14.
  • a relief bore 15 running in the pump piston 3 branches off from this pump work chamber 12 and is connected to an oblique groove 16 arranged on the lateral surface of the pump piston 3.
  • a control bore 17 is present in the control slide 7.
  • the oblique groove 16 interacts for the control of the relief bore 15 on the one hand with the control edge 18 formed by the lower end of the inner bore of the control slide 7 and on the other hand with the control bore 17 such that as long as the oblique groove 16 at least through the control bore 17 or the lower control edge 18 is partially open, fuel can flow out of the pump work chamber 12 via the relief bore 15 without pressure.
  • the pump piston 3 is rotated in a known manner by a speed controller by means of a third control rod 19, for which purpose this control rod 19 engages via a bushing 20 at a correspondingly flattened point 21 of the piston.
  • the first control rod 9 is of solid construction and is flattened in the area 22 opposite the control slides 7 such that the remaining cylinder segments 23 on the inner wall 24 of the tubular second control rod 11 for a relative rotational movement of the control rods to one another are led.
  • a first group of first driving links 26 is attached to the first control rod 9 (FIGS. 3 and 4), and a second group of second driving links 27 are mounted on the second control rod 11 (FIGS. 4 and 4).
  • the first and second driving members 26, 27 are bolt-shaped, each with a threaded section 28 at one end and an eccentrically offset to the longitudinal axis pin 29 with head 31, of which the latter engages in an annular groove 32 arranged on the control slide 7.
  • a nut 33 runs to fix the driving member on the control rod.
  • a slot 34 is provided on the end face of the driving member 26 facing away from the head 31 for the engagement of a turning tool (screwdriver), so that the individual heads 31 and the control slide 7 can be adjusted relative to one another by rotating the driving members 26 due to the eccentric arrangement of the pins 29 . The adjusted position can then be fixed by tightening the nuts 33.
  • a turning tool screwdriver
  • the first driving member 26 has a collar 35 as a counter-bearing to the nut 33, which is supported on a twist 36, which is located on one of the two flattened sides 37 of the first control rod 9.
  • the second control rod 11 there are radial openings 38 for the first driver links 26 in order to enable their relative pivoting in relation to the second driver links 27 or a relative rotation of the first control rod 9 in relation to the second control rod 11.
  • a sleeve 39 is provided for the power transmission, whereby on the one hand the opening 38 on this side is made only as large as is absolutely necessary and on the other hand the key 33 can be attacked by a key tool outside the second control rod 11.
  • the second driving member 27 has a conical collar 41 which bears against the inside of the tubular control rod 11 for tightening the driving member 27.
  • a recess 42 is provided for receiving a washer 43, via which the force is transmitted from the nut 33 to the control rod.
  • a collar 44 is provided which is guided in a bore 45 of the second control rod 11.
  • corresponding recesses 46 are provided in the first control rod 9 for the passage of the second driver links 27.
  • part of the control slide 7 can be axially related to the other part are displaced, whereby a part of the pump units of the fuel injection pump arranged in series can be switched off for the injection without influencing the injection function of the other part, as will be described in detail below.
  • the first control rod 9 with the first driver links 26 for “cylinder deactivation” can be rotated with respect to the second control rod 11 with the second driver links 27.
  • a pin 47 which is guided in a transverse bore 48 of the first control rods 9 and slides with its ends in circumferential grooves 49 of the second control rod 11, serves as a driving coupling between the two control rods 9 and 11.
  • These circumferential grooves 49 enable the first control rod 9 to rotate the associated control slide 7 in a position for cylinder deactivation, but if the second control rod 11 is rotated into such a position and the first control rod 9 is in the normal working position, the latter is for the shutdown of all cylinders is rotated.
  • a torsion spring 51 (FIG. 5) engaging with one end on the first control rod 9 and the other end on the second control rod 11, the first control rod 9 is held in a position in normal operation with respect to the second control rod 11 in which all Driving links 26, 27 or all control spools 7 assume the same working position.
  • a knurled head 52 of the first control rod this can then be adjusted in the manner described relative to the second control rod 11 into the switch-off position against the force of the spring 51.
  • a toothing 53 is provided at the end thereof, into which, as on the knurled head 52, corresponding adjustment means such as toothed rings or levers engage.
  • the second control rod 11 is in a position for normal operation with the second driving element 27.
  • this lower section of the oblique groove 16 dips into the control slide 7, so that the pressure required for the injection can then build up in the pump work chamber 12.
  • the injection is interrupted since the fuel can now flow out of the pump work chamber 12 via the relief bore 15 and the control bore 17 largely relieved of pressure.
  • the twist of the two control rods is used primarily to adjust the start of injection. If the control slide 7 is pushed up into the dashed position, the control bore 17 also moves upward accordingly.
  • the correspondingly articulated number of control slides 7 is shifted downward into the position shown in broken lines.
  • the oblique groove 16 overlaps with the control bore 17, and after the start of the stroke of the pump piston 3 upwards, the oblique groove 16 emerges from the control slide 7 before it is separated from the control bore 17, so that a connection is always made exists between the pump working space 12 and the recess 6. Accordingly, no injection pressure can build up and no injection can take place.
  • This cylinder deactivation is also carried out from a normal operating position of all control slides 7 when the second control rod 11 is rotated clockwise, takes the first control rod 9 and its group of articulated control slides with it via the pin 47, so that all control slides 7 are in a position for cylinder deactivation and thus Engine shutdown.
  • control slide controls the injection quantity by rotating or axially displacing it, and at least some of the control slides are displaceable in the cylinder deactivation position.

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  • 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)

Abstract

A fuel injection pump for internal combustion engines having in-line pumping elements, having pump pistons on which control slides are axially displaceable, in particular for adjusting the injection onset; in a relatively greatly displaced position, these control slides being arranged to interrupt the injection. The control slides are moved by first and second governor rods, each part of which carries one group of driver members of the control slides, and both governor rods are rotatable relative to one another. As a result, it is possible for normal operation to be controlled by the one governor rod, while at the same time an appropriate number of engine cylinders is shut off by the other governor rod, in that the associated control slides are displaced into respective corresponding positions.

Description

Stand der TechnikState of the art

Die Erfindung geht aus von einer Kraftstoffeinspritzpumpe nach der Gattung des Patentanspruchs 1. Bei einer bekannten Kraftstoffeinspritzpumpe dieser Art (DE-A-2146578) sind die Mitnahmeglieder als Klemmschellen ausgebildet, die durch Zusammenspannen der freien Schenkel mittels einer Schraube auf der runden Regelstange justierbar festgespannt sind und einen Zapfen aufweisen, der am Steuerschieber in eine hierfür vorgesehene Ringnut greift. Hierdurch können zwar die einzelnen Mitnahmeglieder bezüglich ih- rer Drehlage und damit die Steuerschieber bezüglich ihrer Hublage gegeneinander justiert werden, sie können aber nicht unabhängig voneinander betätigt werden. Es ist somit auch nicht möglich, die gerade bei grossen Motoren gewünschte teilweise Abstellung der Motorzylinder im Leerlauf zu erreichen (Zylinderabschaltung). Eine solche Zylinderabschaltung ist an sich bei einer Kraftstoffeinspritzpumpe anderer Bauart bekannt (GB-A-2038934), bei der die Kraftstofförderung von einem Teil der Pumpenarbeitsräume zur Brennkraftmaschine hin abschaltbar ist. Durch diese Massnahmen können vor allem im Leerlauf und Teillastbetrieb des Motors der Kraftstoffverbrauch und die Abgas- sowie Geräuschemissionswerte verbessert werden. Ausserdem gelangt auch weniger Kraftstoff in das Motorschmieröl unter Vermeidung eines zu starken Verdünnens desselben. Ausserdem wird eine derartige Zylinderabschaltung auch dann bei Kraftfahrzeugen verwendet, wenn zum Be- und Entladen beispielsweise von Silo- oder Tankfahrzeugen lediglich Nebenaggregate vom Motor des Fahrzeuges anzutreiben sind. Im Gegensatz zu diesen bekannten Reiheneinspritzpumpen, bei denen die Pumpenkolben einzelner Einheiten der Pumpe zur Abstellung der Förderung auf Nullförderung verdrehbar sind, ist dieses bei hubschiebergesteuerten Pumpen bisher nicht bekannt.The invention is based on a fuel injection pump according to the preamble of claim 1. In a known fuel injection pump of this type (DE-A-2146578), the entrainment members are designed as clamps, which are adjustably clamped by tightening the free legs by means of a screw on the round control rod and have a pin which engages on the control slide in an annular groove provided for this purpose. As a result, the individual entrainment members can be adjusted relative to one another with regard to their rotational position and thus the control slide with respect to their stroke position, but they cannot be actuated independently of one another. It is therefore also not possible to achieve the partial shutdown of the engine cylinders when the engine is idling (cylinder deactivation). Such a cylinder deactivation is known per se in a fuel injection pump of another type (GB-A-2038934), in which the fuel delivery can be switched off from part of the pump work spaces to the internal combustion engine. These measures can improve fuel consumption, exhaust gas and noise emissions, especially when the engine is idling and under partial load. In addition, less fuel gets into the engine lubricating oil while avoiding excessive thinning. In addition, such a cylinder deactivation is also used in motor vehicles if only auxiliary units are to be driven by the engine of the vehicle for loading and unloading of silo or tank vehicles, for example. In contrast to these known in-line injection pumps, in which the pump pistons of individual units of the pump can be rotated to shut off the delivery to zero delivery, this has not been known in the case of pumps controlled by a linear slide valve.

Ziel der Erfindung ist es nun, eine Zylinderabschaltung auch bei hubschiebergesteuerten Kraftstoffeinspritzpumpen auf eine einfache und bauraumsparende Weise zu ermöglichen.The aim of the invention is now to enable cylinder deactivation in a simple and space-saving manner even in the case of slide valve-controlled fuel injection pumps.

Vorteile der ErfindungAdvantages of the invention

Bei der erfindungsgemässen Kraftstoffeinspritzpumpe mit den kennzeichnenden Merkmalen des Patentanspruchs 1 wird mit verhältnismässig geringem Aufwand diese sogenannte Zylinderabschaltung auch bei hubschiebergesteuerten Einspritzpumpen erzielt. Dadurch ist ein Teil der Steuerschieber in eine Lage verschiebbar, in der sich im Pumpenarbeitsraum kein Einspritzdruck aufbauen kann, sondern der Kraftstoffdruck entlastet über die Entlastungsbohrung abströmt.In the fuel injection pump according to the invention with the characterizing features of patent claim 1, this so-called cylinder deactivation is achieved with relatively low effort even with lift-valve controlled injection pumps. As a result, part of the control slide can be displaced into a position in which no injection pressure can build up in the pump work space, but rather the fuel pressure is discharged via the relief bore.

Die erste, zwei Gruppen von Mitnahmegliedern und die aus zwei unabhängig betätigbaren und ineinander angeordneten Regelstangen bestehende Regelstange enthaltende Merkmalgruppe aus dem Kennzeichenteil des Patentanspruchs 1 ist für Kraftstoffeinspritzpumpen anderer Bauart an sich aus der eingangs zitierten GB-A-2038934 bekannt. Gemäss der zweiten Merkmalsgruppe sind die beiden Regelstangen koaxial zueinander angeordnet, wobei die zweite Regelstange rohrförmig ausgebildet ist, radiale Durchbrüche mit Spiel in Verdrehrichtung für die von der ersten Regelstange getragenen Mitnahmeglieder aufweist und diese erste Regelstange für die Drehbewegung führt. Da die Durchbrüche lediglich so gross sein müssen, dass die Relativverstellung der beiden Regelstangen möglich ist, wird die Stabilität der Stangen nicht beeinträchtigt, so dass auch verhältnismässig hohe Stellkräfte ohne Verwinden der Stangen übertragbar sind. Durch eine derartige Ausgestaltung wird erheblich Bauraum eingespart, was bei modernen Konstruktionen eine zunehmende Bedeutung gewinnt. Gemäss der dritten Merkmalsgruppe aus dem Kennzeichenteil des Patentanspruchs 1 sind die beiden Regelstangen von einem gegenüber der einen oder anderen Regelstange Spiel in Verdrehrichtung aufweisenden Mitnahmestift quer zur Längsachse der Regelstangen durchdrungen, wobei das Spiel so bemessen ist, dass bei einem Verdrehen der zweiten Regelstange in Richtung konstanter Aufsteuerung der Entlastungsbohrungen (Abstellung des Motors) auch die erste Regelstange mit den von ihr getragenen Mitnahmegliedern in diese Aufsteuerstellung mitgedreht wird. Durch einen derartigen, beide Regelstangen durchdringenden Mitnahmestift kann vorteilhafterweise eine zusätzliche Axialfixierung der beiden Regelstangen gegeneinander eingespart werden, und es kann mit verhältnismässig engen Toleranzen gearbeitet werden, da keine zusätzlichen Befestigungsmittel, beispielsweise des Mitnahmestiftes an der Regelstange, erforderlich sind. Die Kombination aller im Patentanspruch 1 angegebenen Merkmale erlaubt es, die Mitnahmeglieder, z. B. für deren Gleichstellung, unabhängig voneinander einzustellen, ohne dass die Gesamtfunktion beeinträchtigt wird.The first, two groups of entrainment members and the feature group consisting of two independently operable and arranged control rods comprising control rod from the characterizing part of claim 1 is known per se for fuel injection pumps of another type from GB-A-2038934 cited at the beginning. According to the second group of features, the two control rods are arranged coaxially with one another, the second control rod being tubular, having radial openings with play in the direction of rotation for the entrainment members carried by the first control rod, and this first control rod guiding the rotary movement. Since the openings only have to be so large that the relative adjustment of the two control rods is possible, the stability of the rods is not impaired, so that even relatively high actuating forces can be transmitted without twisting the rods. Such a configuration saves considerable installation space, which is becoming increasingly important in modern constructions. According to the third group of features from the characterizing part of claim 1, the two control rods are penetrated transversely to the longitudinal axis of the control rods by a driving pin that has play in the direction of rotation relative to one or the other control rod, the play being dimensioned such that when the second control rod is rotated in the direction constant opening of the relief bores (switching off the engine), the first control rod with the drive links carried by it is also turned into this opening position. Such a driving pin penetrating both control rods can advantageously save an additional axial fixation of the two control rods against one another, and relatively narrow tolerances can be used, since no additional fastening means, for example the driving pin on the control rod, are required. The combination of all the features specified in claim 1 allows the driving links, for. B. for their equality, independently of each other without affecting the overall function.

Eine besonders herstellungs- und montagegünstige Ausgestaltung der Erfindung besteht darin, dass gemäss Anspruch 5 die Mitnahmeglieder als einen Gewindeabschnitt aufweisende, an der jeweiligen Regelstange befestigten Drehteil ausgebildet sind. Hierbei können entsprechend dem Kennzeichenteil von Anspruch 6 an dem einen Ende der Mitnahmeglieder zum Eingriff am Steuerschieber exzentrisch versetzte Zapfen angeordnet sein, wobei die Mitnahmeglieder durch auf dem Gewindeabschnitt laufende Muttern gegen Sichverdrehen sicherbar sind. Hierdurch ist es möglich, Regelstangen und Mitnahmeglieder in einfacher spanabhebender Fertigung herzustellen. Ausserdem kann die Justierung aufgrund der Anordnung und Zugänglichkeit derartiger Mitnahmeglieder durch einen Einstellautomaten vorgenommen werden.A particularly advantageous embodiment in terms of manufacture and assembly is that, according to claim 5, the entrainment members are designed as a rotating part having a threaded section and fastened to the respective control rod. Here, according to the characterizing part of claim 6, eccentrically offset pins can be arranged at one end of the driving members for engagement on the control slide, the driving members being secured against twisting by nuts running on the threaded section. This makes it possible to manufacture control rods and drive links in a simple machining process. In addition, due to the arrangement and accessibility of such driving links, the adjustment can be carried out by an automatic setting machine.

Zeichnungdrawing

Ein Ausführungsbeispiel des Gegenstandes der Erfindung ist in der Zeichnung dargestellt und im folgenden näher beschrieben. Es zeigen:

  • Figur 1 einen Längsschnitt durch den oberen Teil einer Reihenkraftstoffeinspritzpumpe;
  • Figur 2 einen Ausschnitt aus Figur 1 in vergrössertem Massstab mit dem Steuerschieber in verschiedenen Stellungen und gemäss einem Schnitt 11-11 in Figur 4;
  • Figur 3 einen Schnitt durch die Regelstange nach 111-111 in Figur 4 und
  • Figur 5 einen Teilschnitt nach Linie V-V in Figur 1.
An embodiment of the object of the invention is shown in the drawing and described in more detail below. Show it:
  • 1 shows a longitudinal section through the upper part of an in-line fuel injection pump;
  • Figure 2 shows a detail of Figure 1 on an enlarged scale with the control slide in different positions and according to a section 11-11 in Figure 4;
  • 3 shows a section through the control rod according to 111-111 in Figure 4 and
  • 5 shows a partial section along line VV in Figure 1.

Beschreibung des AusführungsbeispielsDescription of the embodiment

In einem Gehäuse 1 einer Reihenkraftstoffeinspritzpumpe sind mehrere Zylinderbüchsen 2, von denen nur eine dargestellt ist, in Reihe eingelassen, in deren Pumpenzylinder 2a Pumpenkolben 3 geführt und über eine Nockenwelle entgegen der Kraft einer Feder 5 für ihre den Arbeitshub bildende axiale Bewegung angetrieben werden. In der Zylinderbüchse 2 ist eine Aussparung 6 vorhanden, die einen auf dem Pumpenkolben 3 axial verschiebbaren Steuerschieber 7 aufnimmt. Der Steuerschieber 7 wird über ein Mitnahmeglied 8 betätigt, das entweder mit einer ersten Regelstange 9 oder mit einer um diese rohrförmig angeordneten zweiten Regelstange 11 verbunden ist, so dass eine Drehbewegung einer der Regelstangen eine entsprechende Verschiebung des jeweiligen Steuerschiebers 7 bewirkt. Durch den Pumpenkolben 3 und den Pumpenzylinder 2a wird jeweils ein Pumpenarbeitsraum 12 begrenzt, aus dem der Pumpenkolben 3 während seines Druckhubes über ein Druckventil 13 und eine Druckleitung 14 Kraftstoff zur Brennkraftmaschine fördern kann. Ausserdem zweigt von diesem Pumpenarbeitsraum 12 eine im Pumpenkolben 3 verlaufende Entlastungsbohrung 15 ab, die mit einer auf der Mantelfläche des Pumpenkolbens 3 angeordneten Schrägnut 16 verbunden ist. Ausserdem ist im Steuerschieber 7 eine Steuerbohrung 17 vorhanden. Die Schrägnut 16 wirkt für die Steuerung der Entlastungsbohrung 15 einerseits mit der durch das untere Ende der Innenbohrung des Steuerschiebers 7 gebildeten Steuerkante 18 und andererseits mit der Steuerbohrung 17 derart zusammen, dass, solange die Schrägnut 16 durch die Steuerbohrung 17 oder die untere Steuerkante 18 mindestens teilweise aufgesteuert ist, Kraftstoff aus dem Pumpenarbeitsraum 12 über die Entlastungsbohrung 15 drucklos abströmen kann.In a housing 1 of a series fuel injection pump, a plurality of cylinder liners 2, only one of which is shown, are embedded in series, in the pump cylinder 2a of which pump pistons 3 are guided and driven via a camshaft against the force of a spring 5 for their axial movement forming the working stroke. In the cylinder liner 2 there is a recess 6 which receives a control slide 7 which is axially displaceable on the pump piston 3. The control slide 7 is actuated via a driving element 8, which is connected either to a first control rod 9 or to a second control rod 11 arranged in a tubular manner around it, so that a rotary movement of one of the control rods causes a corresponding displacement of the respective control slide 7. A pump working chamber 12 is delimited by the pump piston 3 and the pump cylinder 2a, from which the pump piston 3 can deliver fuel to the internal combustion engine during its pressure stroke via a pressure valve 13 and a pressure line 14. In addition, a relief bore 15 running in the pump piston 3 branches off from this pump work chamber 12 and is connected to an oblique groove 16 arranged on the lateral surface of the pump piston 3. In addition, a control bore 17 is present in the control slide 7. The oblique groove 16 interacts for the control of the relief bore 15 on the one hand with the control edge 18 formed by the lower end of the inner bore of the control slide 7 and on the other hand with the control bore 17 such that as long as the oblique groove 16 at least through the control bore 17 or the lower control edge 18 is partially open, fuel can flow out of the pump work chamber 12 via the relief bore 15 without pressure.

Je nach Drehlage des Pumpenkolbens 3 gelangt die Schrägnut 16 früher oder später in Überdekkung mit der Steuerbohrung 17, wodurch die Einspritzmenge bestimmt wird. Hierfür wird in bekannter Weise durch einen Drehzahlregler der Pumpenkolben 3 mittels einer dritten Regelstange 19 verdreht, wofür diese Regelstange 19 über eine Buchse 20 an einer entsprechend abgeflachten Stelle 21 des Kolbens angreift.Depending on the rotational position of the pump piston 3, the oblique groove 16 sooner or later coincides with the control bore 17, as a result of which the injection quantity is determined. For this purpose, the pump piston 3 is rotated in a known manner by a speed controller by means of a third control rod 19, for which purpose this control rod 19 engages via a bushing 20 at a correspondingly flattened point 21 of the piston.

Wie den Figuren 2-5 entnehmbar ist, ist die erste Regelstange 9 massiv ausgebildet und in dem den Steuerschiebern 7 gegenüberliegenden Bereich 22 so abgeflacht, dass die verbleibenden Zylindersegmente 23 auf der Innenwand 24 der rohrförmig ausgebildeten zweiten Regelstange 11 für eine relative Verdrehbewegung der Regelstangen zueinander geführt sind.As can be seen from FIGS. 2-5, the first control rod 9 is of solid construction and is flattened in the area 22 opposite the control slides 7 such that the remaining cylinder segments 23 on the inner wall 24 of the tubular second control rod 11 for a relative rotational movement of the control rods to one another are led.

An der ersten Regelstange 9 ist eine erste Gruppe von ersten Mitnahmegliedern 26 befestigt (Fig.3 und 4), und an die zweite Regelstange 11 sind eine zweite Gruppe von zweiten Mitnahmegliedern 27 montiert (Fig. und 4). Die ersten und zweiten Mitnahmeglieder 26, 27 sind bolzenförmig ausgebildet mit jeweils einem Gewindeabschnitt 28 am einen Ende und einem exzentrisch zur Längsachse versetzten Zapfen 29 mit Kopf 31, von denen letzterer in eine auf dem Steuerschieber 7 angeordnete Ringnut 32 greift. Auf dem Gewindeabschnitt 28 läuft eine Mutter 33 zur Festspannung des Mitnahmegliedes an der Regelstange. Ausserdem ist auf der dem Kopf 31 abgewandten Stirnseite des Mitnahmegliedes 26 ein Schlitz 34 für den Eingriff eines Verdrehwerkzeuges (Schraubenzieher) vorgesehen, so dass aufgrund der exzentrischen Anordnung der Zapfen 29 die einzelnen Köpfe 31 sowie die Steuerschieber 7 durch Verdrehen der Mitnahmeglieder 26 zueinander justierbar sind. Durch Anspannen der Muttern 33 kann dann die justierte Lage fixiert werden.A first group of first driving links 26 is attached to the first control rod 9 (FIGS. 3 and 4), and a second group of second driving links 27 are mounted on the second control rod 11 (FIGS. 4 and 4). The first and second driving members 26, 27 are bolt-shaped, each with a threaded section 28 at one end and an eccentrically offset to the longitudinal axis pin 29 with head 31, of which the latter engages in an annular groove 32 arranged on the control slide 7. On the threaded section 28, a nut 33 runs to fix the driving member on the control rod. In addition, a slot 34 is provided on the end face of the driving member 26 facing away from the head 31 for the engagement of a turning tool (screwdriver), so that the individual heads 31 and the control slide 7 can be adjusted relative to one another by rotating the driving members 26 due to the eccentric arrangement of the pins 29 . The adjusted position can then be fixed by tightening the nuts 33.

Das erste Mitnahmeglied 26 weist als Gegenlager zur Mutter 33 einen Bund 35 auf, der sich an einer Abdrehung 36 abstützt, die sich an einer der beiden abgeflachten Seiten 37 der ersten Regelstange 9 befindet.The first driving member 26 has a collar 35 as a counter-bearing to the nut 33, which is supported on a twist 36, which is located on one of the two flattened sides 37 of the first control rod 9.

In der zweiten Regelstange 11 sind radiale Durchbrüche 38 für die ersten Mitnahmeglieder 26 vorhanden, um deren Relativschwenken in bezug auf die zweiten Mitnahmeglieder 27 bzw. ein Relatiwerdrehen der ersten Regelstange 9 in bezug zur zweiten Regelstange 11 zu ermöglichen. Zwischen Mutter 33 und Regelstange 9 ist eine Hülse 39 für die Kraftübertragung vorgesehen, wodurch einerseits der Durchbruch 38 auf dieser Seite nur so gross wie unbedingt nötig gestaltet wird und andererseits der Angriff an die Mutter 33 durch ein Schlüsselwerkzeug ausserhalb der zweiten Regelstange 11 erfolgen kann.In the second control rod 11 there are radial openings 38 for the first driver links 26 in order to enable their relative pivoting in relation to the second driver links 27 or a relative rotation of the first control rod 9 in relation to the second control rod 11. Between nut 33 and control rod 9, a sleeve 39 is provided for the power transmission, whereby on the one hand the opening 38 on this side is made only as large as is absolutely necessary and on the other hand the key 33 can be attacked by a key tool outside the second control rod 11.

Das zweite Mitnahmeglied 27 weist am Abschluss des Gewindeabschnittes 28 einen kegligen Bund 41 auf, der zum Festspannen des Mitnahmegliedes 27 an der Innenseite der rohrförmigen Regelstange 11 anliegt. In der äusseren Mantelfläche dieser zweiten Regelstange 11 ist eine Eindrehung 42 zur Aufnahme einer Unterlegscheibe 43 vorgesehen, über die die Kraft von der Mutter 33 auf die Regelstange übertragen wird. Auf der dem Gewindeabschnitt 28 abgewandten Seite dieses zweiten Mitnahmegliedes 27 ist ein Bund 44 vorgesehen, der in einer Bohrung 45 der zweiten Regelstange 11 geführt ist. Um die Relativbewegung der ersten und zweiten Mitnahmeglieder 26, 27 bzw. die relative Verdrehbewegung der Regelstangen 9 und 11 zueinander zu ermöglichen, sind für den Durchgang der zweiten Mitnahmeglieder 27 in der ersten Regelstange 9 entsprechende Ausnehmungen 46 vorhanden.At the end of the threaded section 28, the second driving member 27 has a conical collar 41 which bears against the inside of the tubular control rod 11 for tightening the driving member 27. In the outer lateral surface of this second control rod 11, a recess 42 is provided for receiving a washer 43, via which the force is transmitted from the nut 33 to the control rod. On the side of this second driving member 27 facing away from the threaded section 28, a collar 44 is provided which is guided in a bore 45 of the second control rod 11. In order to enable the relative movement of the first and second driver links 26, 27 or the relative rotational movement of the control rods 9 and 11 relative to one another, corresponding recesses 46 are provided in the first control rod 9 for the passage of the second driver links 27.

Aufgrund dieser Relativverdrehung der beiden Regelstangen zueinander kann ein Teil der Steuerschieber 7 in bezug auf den anderen Teil axial verschoben werden, wodurch ein Teil der in Reihe angeordneten Pumpeinheiten der Kraftstoffeinspritzpumpe für die Einspritzung abschaltbar ist, ohne dass die Einspritzfunktion des anderen Teils, wie weiter unten noch im einzelnen beschrieben, beeinflusst wird. Bei diesem Ausführungsbeispiel ist die erste Regelstange 9 mit den ersten Mitnahmegliedern 26 für die «Zylinderabschaltung» gegenüber der zweiten Regelstange 11 mit den zweiten Mitnahmegliedern 27 verdrehbar.Due to this relative rotation of the two control rods to one another, part of the control slide 7 can be axially related to the other part are displaced, whereby a part of the pump units of the fuel injection pump arranged in series can be switched off for the injection without influencing the injection function of the other part, as will be described in detail below. In this exemplary embodiment, the first control rod 9 with the first driver links 26 for “cylinder deactivation” can be rotated with respect to the second control rod 11 with the second driver links 27.

Als Mitnahmekopplung zwischen den beiden Regelstangen 9 und 11 dient, wie in Fig. 4 dargestellt, ein Stift 47, der in einer Querbohrung 48 der ersten Regelstangen 9 geführt ist und mit seinen Enden in Umfangsnuten 49 der zweiten Regelstange 11 gleitet. Diese Umfangsnuten 49 ermöglichen der ersten Regelstange 9 eine entsprechende Verdrehung zur Verschiebung der zugeordneten Steuerschieber 7 in eine Stellung für Zylinderabschaltung, bewirkt aber, wenn die zweite Regelstange 11 in eine derartige Stellung verdreht wird und die erste Regelstange 9 in normaler Arbeitsstellung war, dass letztere für das Abstellen aller Zylinder mitverdreht wird.4, a pin 47, which is guided in a transverse bore 48 of the first control rods 9 and slides with its ends in circumferential grooves 49 of the second control rod 11, serves as a driving coupling between the two control rods 9 and 11. These circumferential grooves 49 enable the first control rod 9 to rotate the associated control slide 7 in a position for cylinder deactivation, but if the second control rod 11 is rotated into such a position and the first control rod 9 is in the normal working position, the latter is for the shutdown of all cylinders is rotated.

Durch eine mit ihrem einen Ende an der ersten Regelstange 9 und ihrem anderen Ende an der zweiten Regelstange 11 angreifenden Drehfeder 51 (Fig.5) wird die erste Regelstange 9 bei Normalbetrieb in bezug auf die zweite Regelstange 11 in einer Stellung gehalten, bei der alle Mitnahmeglieder 26, 27 bzw. alle Steuerschieber 7 die gleiche Arbeitsstellung einnehmen. Durch Eingriff an einem Rändelkopf 52 der ersten Regelstange kann diese dann in der beschriebenen Art gegenüber der zweiten Regelstange 11 in die Abschaltstellung entgegen der Kraft der Feder 51 verstellt werden. Zur Verstellung bzw. auch zum Festhalten der zweiten Regelstange 11 dient eine an deren Ende vorhandene Verzahnung 53, in die, wie auch am Rändelkopf 52 entsprechende Verstellmittel wie Zahnkränze oder Hebel angreifen.By means of a torsion spring 51 (FIG. 5) engaging with one end on the first control rod 9 and the other end on the second control rod 11, the first control rod 9 is held in a position in normal operation with respect to the second control rod 11 in which all Driving links 26, 27 or all control spools 7 assume the same working position. By engaging a knurled head 52 of the first control rod, this can then be adjusted in the manner described relative to the second control rod 11 into the switch-off position against the force of the spring 51. To adjust or also hold the second control rod 11, a toothing 53 is provided at the end thereof, into which, as on the knurled head 52, corresponding adjustment means such as toothed rings or levers engage.

Anhand Fig. 2 wird die Funktion näher erläutert: Die zweite Regelstange 11 nimmt mit dem zweiten Mitnahmeglied 27 gerade eine Stellung für Normalbetrieb ein. Gleiches gilt für den Steuerschieber 7, der mit seiner unteren Steuerkante 18 das untere Ende der Schrägnut 16 so weit freilegt, dass eine Verbindung zwischen Pumpenarbeitsraum 12 und der Aussparung 6 besteht. Sobald nun der Pumpenkolben mit seinem Druckhub beginnt, taucht dieser untere Abschnitt der Schrägnut 16 in den Steuerschieber 7, so dass sich danach im Pumpenarbeitsraum 12 der für die Einspritzung erforderliche Druck aufbauen kann. Sobald dann während des weiteren Druckhubes des Pumpenkolbens 3 die Schrägnut 16 in Überdekkung mit der im Steuerschieber 7 angeordneten Steuerbohrung 17 gelangt, wird die Einspritzung unterbrochen, da der Kraftstoff aus dem Pumpenarbeitsraum 12 nunmehr über die Entlastungsbohrung 15 und die Steuerbohrung 17 weitgehend druckentlastet abströmen kann. Bei diesem Ausführungsbeispiel dient die Verdrehung der beiden Regelstangen vor allem dazu, den Spritzbeginn zu verstellen. Wenn der Steuerschieber 7 in die gestrichelte Stellung nach oben geschoben wird, gelangt auch die Steuerbohrung 17 entsprechend weiter nach oben. Da die Schrägnut 16 auf dem Pumpenkolben 3 angeordnet dieser Bewegung nicht folgt, ist der Vorhub des Pumpenkolbens 3, bevor die Schrägnut 16 in den Ringschieber 7 taucht, entsprechend länger, und der Spritzbeginn ist entsprechend für die Drehlage der Nokkenwelle der Einspritzpumpe auf später geschoben.The function is explained in more detail with reference to FIG. 2: the second control rod 11 is in a position for normal operation with the second driving element 27. The same applies to the control slide 7, which exposes the lower end of the oblique groove 16 with its lower control edge 18 to such an extent that there is a connection between the pump work chamber 12 and the recess 6. As soon as the pump piston begins its pressure stroke, this lower section of the oblique groove 16 dips into the control slide 7, so that the pressure required for the injection can then build up in the pump work chamber 12. As soon as the oblique groove 16 then overlaps with the control bore 17 arranged in the control slide 7 during the further pressure stroke of the pump piston 3, the injection is interrupted since the fuel can now flow out of the pump work chamber 12 via the relief bore 15 and the control bore 17 largely relieved of pressure. In this embodiment, the twist of the two control rods is used primarily to adjust the start of injection. If the control slide 7 is pushed up into the dashed position, the control bore 17 also moves upward accordingly. Since the oblique groove 16 arranged on the pump piston 3 does not follow this movement, the forward stroke of the pump piston 3 before the oblique groove 16 plunges into the ring slide 7 is correspondingly longer, and the start of injection is accordingly postponed for the rotational position of the camshaft of the injection pump.

Wenn die erste Regelstange 9 gemäss der Darstellung von Fig.2 im Uhrzeigersinn verdreht wird, wird die entsprechend angelenkte Anzahl von Steuerschiebern 7 in die strichpunktiert dargelegte Lage nach unten verschoben. Wie ersichtlich steht in dieser Lage die Schrägnut 16 in Überdeckung mit der Steuerbohrung 17, und nach Beginn des Hubes des Pumpenkolbens 3 nach oben taucht die Schrägnut 16 aus dem Steuerschieber 7 aus, bevor sie von der Steuerbohrung 17 getrennt wird, so dass stets eine Verbindung zwischen dem Pumpenarbeitsraum 12 und der Aussparung 6 besteht. Entsprechend kann sich kein Einspritzdruck aufbauen, und es kann keine Einspritzung stattfinden. Diese Zylinderabschaltung wird auch aus einer Normalbetriebstellung aller Steuerschieber 7 dann durchgeführt, wenn die zweite Regelstange 11 im Uhrzeigersinn verdreht wird, über den Stift 47 die erste Regelstange 9 sowie deren Gruppe angelenkter Steuerschieber mitnimmt, so dass alle Steuerschieber 7 in eine Stellung für Zylinderabschaltung und damit Abstellung des Motors gestellt werden.If the first control rod 9 is rotated clockwise as shown in FIG. 2, the correspondingly articulated number of control slides 7 is shifted downward into the position shown in broken lines. As can be seen in this position, the oblique groove 16 overlaps with the control bore 17, and after the start of the stroke of the pump piston 3 upwards, the oblique groove 16 emerges from the control slide 7 before it is separated from the control bore 17, so that a connection is always made exists between the pump working space 12 and the recess 6. Accordingly, no injection pressure can build up and no injection can take place. This cylinder deactivation is also carried out from a normal operating position of all control slides 7 when the second control rod 11 is rotated clockwise, takes the first control rod 9 and its group of articulated control slides with it via the pin 47, so that all control slides 7 are in a position for cylinder deactivation and thus Engine shutdown.

Natürlich ist auch denkbar, dass die Erfindung an einer Einspritzmengensteuerung angewendet wird, bei der der Steuerschieber durch Verdrehen oder axiales Verschieben die Einspritzmenge steuert und wobei mindestens ein Teil der Steuerschieber in Zylinderabschaltstellung verschiebbar sind.Of course, it is also conceivable that the invention is applied to an injection quantity control in which the control slide controls the injection quantity by rotating or axially displacing it, and at least some of the control slides are displaceable in the cylinder deactivation position.

Claims (6)

1. Fuel injection pump for combustion engines having pump plungers (3) arranged in line, guided in pump cylinders (2a), delimiting with these a pump working space (12) and driven so as to produce a reciprocating working stroke, having in each case one at least axially displaceable control slide (7) on each pump plunger (3) for controlling at least one relief bore (15) of the pump working space (12), said relief bore extending in the pump plunger (3), and having driving members (8) arranged on a control rod (9, 11), which can be rotated for the purpose of moving the control slides (7), and engaging on the control slides (7), characterized in that two groups of driving members (8) are present, of which a first group of driving members (26) can be moved arbitrarily into a position of constant opening of the relief bores (15) of some of the pump working spaces (12) independently of a second group of driving members (27) simultaneously controlling the normal operation, and the control rod comprises two control rods which are independently actuable and are arranged one within the other, a first control rod (9) carrying the first group of driving members (26) and a second control rod (11) carrying the second group of driving members (27), in that the two control rods (9, 11) are arranged coaxially to one another, the second control rod (11) being of tubular design, having radial openings (38) with play in the direction of rotation for the driving members (26) carried by the first control rod (9), and guiding this first control rod (9) for the rotary movement, and in that the two control rods (9, 11) are penetrated transversely to the longitudinal axis of the control rods (9, 11) by a driving pin (47) having play with respect to one or other of the control rods in the direction of rotation, the play being dimensioned so that when the second control rod (11) is rotated in the direction of constant opening of the relief bores (15) the first control rod (9) together with the driving members (26) carried by it is also turned into this opening position.
2. Fuel injection pump according to claim 1, characterized in that the driving members (27) carried by the second control rod (11) pass through the tube of this control rod as well as slots (46) in the first, guided control rod (9), said slots being provided with play in the direction of rotation.
3. Fuel injection pump according to claim 1 or 2, characterized in that the first control rod (9) is flattened and guided on the inside wall (24) of the tubular control rod (11) by cylinder segments (23) provided at the narrow sides.
4. Fuel injection pump according to one of the preceding claims 1 to 3, characterized in that a torsionally elastic member (51) which restores the control rods to an identical position with respect to the driving members (8) engages on at least one of the control rods (9, 11).
5. Fuel injection pump according to one of the preceding claims, characterized in that the driving members (8, 26, 27) are designed as pivoted parts which have a threaded section (28) and are fixed on the respective control rod (9, 11).
6. Fuel injection pump according to claim 5, characterized in that pegs (29) are arranged eccentrically offset at one end of the driving members (8,26,27) for engaging in the control slides (7) and in that the driving members (8, 26, 27) can be secured against rotation by nuts (33) which travel on the threaded section (28).
EP85112161A 1984-10-01 1985-09-25 Fuel injection pump for combustion engines Expired EP0178505B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT85112161T ATE40186T1 (en) 1984-10-01 1985-09-25 FUEL INJECTION PUMP FOR COMBUSTION ENGINES.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3435987 1984-10-01
DE19843435987 DE3435987A1 (en) 1984-10-01 1984-10-01 FUEL INJECTION PUMP FOR INTERNAL COMBUSTION ENGINES

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EP0178505A1 EP0178505A1 (en) 1986-04-23
EP0178505B1 true EP0178505B1 (en) 1989-01-18

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US (1) US4706626A (en)
EP (1) EP0178505B1 (en)
JP (1) JPH0681938B2 (en)
AT (1) ATE40186T1 (en)
DE (2) DE3435987A1 (en)

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WO1987005665A1 (en) * 1986-03-22 1987-09-24 Robert Bosch Gmbh Fuel injection pump for internal combustion engines
DE3707646A1 (en) * 1986-03-24 1987-10-08 Bosch Gmbh Robert FUEL INJECTION PUMP FOR INTERNAL COMBUSTION ENGINES
DE3633899A1 (en) * 1986-10-04 1988-04-07 Bosch Gmbh Robert FUEL INJECTION PUMP FOR INTERNAL COMBUSTION ENGINES
DE3724409A1 (en) * 1986-10-31 1988-05-19 Bosch Gmbh Robert FUEL INJECTION PUMP FOR INTERNAL COMBUSTION ENGINES
DE3870748D1 (en) * 1987-07-25 1992-06-11 Bosch Gmbh Robert FUEL INJECTION PUMP FOR INTERNAL COMBUSTION ENGINES.
DE3736091A1 (en) * 1987-10-24 1989-05-03 Bosch Gmbh Robert FUEL INJECTION PUMP FOR INTERNAL COMBUSTION ENGINES
US5080564A (en) * 1989-02-08 1992-01-14 Diesel Kiki Co., Ltd. Prestroke control device for fuel injection pumps
DE4041656A1 (en) * 1990-12-22 1992-07-02 Bosch Gmbh Robert FUEL INJECTION PUMP FOR INTERNAL COMBUSTION ENGINES
DE4100093A1 (en) * 1991-01-04 1992-07-09 Bosch Gmbh Robert FUEL INJECTION PUMP FOR INTERNAL COMBUSTION ENGINES WITH LOAD AND / OR SPEED-RELATED INJECTION HISTORY
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Also Published As

Publication number Publication date
ATE40186T1 (en) 1989-02-15
DE3435987A1 (en) 1986-04-10
JPS61182458A (en) 1986-08-15
US4706626A (en) 1987-11-17
DE3567701D1 (en) 1989-02-23
JPH0681938B2 (en) 1994-10-19
EP0178505A1 (en) 1986-04-23

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