EP0288669B1 - Fuel injection pump for a diesel engine - Google Patents

Fuel injection pump for a diesel engine Download PDF

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Publication number
EP0288669B1
EP0288669B1 EP88101862A EP88101862A EP0288669B1 EP 0288669 B1 EP0288669 B1 EP 0288669B1 EP 88101862 A EP88101862 A EP 88101862A EP 88101862 A EP88101862 A EP 88101862A EP 0288669 B1 EP0288669 B1 EP 0288669B1
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EP
European Patent Office
Prior art keywords
pump
piston
pump piston
cylinder
adjusting sleeve
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 - Lifetime
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EP88101862A
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German (de)
French (fr)
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EP0288669A1 (en
Inventor
Hans Scherrer
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Sulzer AG
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Gebrueder Sulzer AG
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Publication of EP0288669A1 publication Critical patent/EP0288669A1/en
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/12—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by varying the length of stroke of the working members
    • F04B49/121—Lost-motion device in the driving mechanism
    • 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
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B3/00—Engines characterised by air compression and subsequent fuel addition
    • F02B3/06—Engines characterised by air compression and subsequent fuel addition with compression ignition
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/06—Control

Definitions

  • the invention relates to a fuel injection pump with the features of the preamble of claim 1.
  • the adjusting sleeve concentrically surrounds the pump piston and is connected to the pump piston in a rotationally fixed manner via a groove and a sliding wedge guided therein.
  • the adjusting sleeve has an external toothing which engages in a toothed rack on the regulating rod.
  • This swivel device consisting of regulating rod and adjusting sleeve serves to change the amount of fuel to be injected into the working cylinder of the reciprocating piston internal combustion engine depending on the load of the machine, by changing the position of the oblique control edges relative to the holes in the cylinder by the swiveling, so that the Shift start of delivery and / or end of delivery of the pump piston.
  • the size of the swivel range of the pump piston is limited due to the pump design and is approximately 60 °.
  • the course of the oblique control edges in the lateral surface of the pump piston thus extends over the range of 60 °.
  • the oblique control edges are relatively steep. Such a steep course results in an unfavorable reproducibility of the injected fuel quantity, i.e. there is a relatively large deviation of the delivery stroke of the pump piston, that is to say the injection quantity, from the position of the regulating rod.
  • Such deviations are e.g.
  • the invention has for its object to improve the injection pump of the type mentioned so that the disadvantages caused by the steep control edge course are avoided.
  • the larger swivel range of the pump piston now allows the course of the oblique control edges over a correspondingly larger circumference of the lateral surface of the To extend the pump piston so that - seen in the drawing - the control edges have a much smaller slope than before.
  • the disadvantages described in connection with the steep control edge profile of the known injection pumps are thus considerably reduced.
  • the deviations of the piston stroke due to the inaccuracies in the transmission path are therefore considerably smaller; the injection phase is ended more quickly because the piston stroke for the full opening of the overflow hole is reduced by the associated control edge.
  • a pump cylinder 2 is provided in a pump housing 1, which is fixed in the pump housing 1 by a pump housing cover 3.
  • a pump piston 4 is guided up and down, which is provided in its lateral surface near the upper piston end with control edges 5 which run obliquely to the longitudinal axis of the piston. These control edges cooperate in a known manner with two radial bores (not shown in FIG. 1) in the wall of the pump cylinder 2, as a result of which the start of delivery and the end of delivery of the pump piston 4 are determined.
  • the fuel to be injected is fed via an inlet line, also not shown in FIG.
  • the pump piston 4 has at its lower end protruding from the pump cylinder 2 a flange 9 with which it rests on a pump tappet 10 which is guided in the pump housing 1 so as to be axially movable.
  • the flange 9 is overlapped by a cap 11, which also surrounds part of the pump plunger 10 and on which the lower end of a compression spring 12 is supported.
  • the upper end of the compression spring 12 is supported on a spring plate 13 which is fixed in the pump housing 1.
  • a constant contact of the flange 9 on the pump tappet 10 is ensured by means of the compression spring 12.
  • a roller 14 is rotatably mounted therein, which rolls on a cam 15 of a camshaft that drives the pump piston 4 in time with the diesel engine.
  • the lower end of the pump cylinder 2 is surrounded by a sleeve 16, which at its lower end, which projects beyond the pump cylinder, is provided with two axial, diametrically opposite slots, into each of which a radial arm 17 of the pump piston 4 projects.
  • the axial length of the slots is at least the same as the maximum stroke of the pump piston 4.
  • the sleeve 16 has in its area above the slots an external toothing 18 which is in engagement with an internal toothing 19 which is provided in an adjusting sleeve 20 arranged eccentrically to the sleeve 16 and thus to the pump piston 4.
  • the Adjustment sleeve 20 is pivotally mounted in the pump housing 1 about its axis of rotation 21 (FIG. 3) and has a radially outwardly projecting stop tab 22 on its outer circumference. 1 is attached to the stop tab 22, which projects downward into a fork piece 24, which is adjustably fastened on a regulating rod 25 which can be moved back and forth transversely to the pump piston 4.
  • the regulating rod 25 By moving the regulating rod 25 by the amount "s" (FIG. 2), the adjusting sleeve 20 can thus be pivoted through an angle of approximately 60.degree of the driving pin 23 is shown in Fig. 2.
  • stop tab 22 is on a stop screw 26 which is attached to the pump housing 1.
  • the stop screw 26 is adjustable with the help of an adjusting nut 27.
  • the same arrangement of the stop screw and the adjusting nut is located on the opposite side of the swivel range of the adjusting sleeve 20 and interacts with the boundary surface 22 ⁇ of the stop tab 22.
  • the size of the path "s" and thus the size of the swivel range of the flap 22 is limited by the fact that the housing 1 cannot be weakened further in the area mentioned.
  • the pivoting movement of the adjusting sleeve 20 is translated into a larger adjusting movement of the sleeve 16 and thus of the pump piston 4.
  • the size of the pivoting movement of the sleeve 16 depends on the size of the eccentricity "e" (FIG. 3) between the longitudinal axis of the pump piston and the axis 21 of the adjusting sleeve 20. It can be reach maximum swivel range of approximately 120 ° of the sleeve 16 or the pump piston 4.
  • the lower half of the injection pump is inserted into an engine housing 30 in which the camshaft is also mounted. It is essential for the injection pump that the outer limit of the stop lug 22 lies within the diameter of the upper bore 31 in the engine housing that receives the pump housing 1, so that the injection pump can be easily installed and removed.
  • an injection pump is arranged in the engine housing in the manner described and there is an associated cam corresponding to cam 15 on the common camshaft.
  • the regulating rod 25 is also common to all working cylinders and has a fork piece 24 for each injection pump. By adjusting the fork pieces 24 relative to the regulating rod and adjusting the stop screws 26, the fuel quantities to be injected into the working cylinders can be made equal to one another.
  • the sleeve 16 In a departure from the exemplary embodiment described, it is also possible to omit the sleeve 16 and to provide its external toothing directly on the pump piston 4. In such a case, the outer toothing would have to be longer in the axial direction so that it remains in engagement with the inner toothing 19 of the adjusting sleeve 20 during the up and down movement of the pump piston.

Description

Die Erfindung betrifft eine Brennstoffeinspritzpumpe mit den Merkmalen des Oberbegriffs des Anspruchs 1.The invention relates to a fuel injection pump with the features of the preamble of claim 1.

Bei einer bekannten Einspritzpumpe dieser Art (DE-OS 1 910 170) umgibt die Verstellhülse den Pumpenkolben konzentrisch und ist über eine Nut und einem darin geführten Gleitkeil mit dem Pumpenkolben drehfest verbunden. Die Verstellhülse weist eine Aussenverzahnung auf, die in eine Zahnstange an der Regulierstange eingreift. Diese aus Regulierstange und Verstellhülse bestehende Schwenkvorrichtung dient dazu, die in den Arbeitszylinder der Hubkolbenbrennkraftmaschine einzuspritzende Brennstoffmenge in Abhängigkeit von der Last der Maschine zu verändern, indem durch das Verschwenken die Lage der schrägen Steuerkanten relativ zu den Löchern im Zylinder verändert wird, so dass sich der Förderbeginn und/oder das Förderende des Pumpenkolbens verschieben.In a known injection pump of this type (DE-OS 1 910 170), the adjusting sleeve concentrically surrounds the pump piston and is connected to the pump piston in a rotationally fixed manner via a groove and a sliding wedge guided therein. The adjusting sleeve has an external toothing which engages in a toothed rack on the regulating rod. This swivel device consisting of regulating rod and adjusting sleeve serves to change the amount of fuel to be injected into the working cylinder of the reciprocating piston internal combustion engine depending on the load of the machine, by changing the position of the oblique control edges relative to the holes in the cylinder by the swiveling, so that the Shift start of delivery and / or end of delivery of the pump piston.

Die Grösse des Schwenkbereichs des Pumpenkolbens ist - bedingt durch die Pumpenkonstruktion - begrenzt und beträgt etwa 60°. Ueber den Bereich von 60° erstreckt sich also der Verlauf der schrägen Steuerkanten in der Mantelfläche des Pumpenkolbens. In der zeichnerischen Abwicklung der Mantelfläche betrachtet, ergibt sich somit ein relativ steiler Verlauf der schrägen Steuerkanten. Ein solcher steiler Verlauf hat eine ungünstige Reproduzierbarkeit der eingespritzten Brennstoffmenge zur Folge, d.h. es ergibt sich eine verhältnismässig grosse Abweichung des Förderhubes des Pumpenkolbens, also der Einspritzmenge, von der Position der Regulierstange. Solche Abweichungen sind z.B. durch die Summe der Ungenauigkeiten im Uebertragungsweg vom an der Regulierstange angreifenden Regler bis zum Pumpenkolben (Spiele, Toleranzen, Montageungenaugigkeiten usw.) bedingt. Je steiler der Steuerkantenverlauf ist, desto grösser sind die Abweichungen des Kolbenhubes. Weitere Nachteile des steilen Steuerkantenverlaufs ergeben sich am Ende der Einspritzphase, indem der Kolbenhub ziemlich gross wird, der notwendig ist, um das Ueberströmloch im Zylinder durch die zugehörige Steuerkante voll zu öffnen. Dies bedeutet, dass die Einspritzung nicht rasch beendet wird, sondern "schleichend", wodurch die Verbrennung des Brennstoffs verschlechtert wird. Einspritzpumpen der eingangs genannten Art werden ausserdem nur für konstanten Einspritzbeginn verwendet. Ein Vorverlegen des Einspritzbeginns vor den Zünd-OT lässt sich wegen des steilen Steuerkantenverlaufs praktisch nicht realisieren.The size of the swivel range of the pump piston is limited due to the pump design and is approximately 60 °. The course of the oblique control edges in the lateral surface of the pump piston thus extends over the range of 60 °. Considered in the graphic development of the lateral surface, the oblique control edges are relatively steep. Such a steep course results in an unfavorable reproducibility of the injected fuel quantity, i.e. there is a relatively large deviation of the delivery stroke of the pump piston, that is to say the injection quantity, from the position of the regulating rod. Such deviations are e.g. due to the sum of the inaccuracies in the transmission path from the controller acting on the regulating rod to the pump piston (clearances, tolerances, inaccuracies in assembly, etc.). The steeper the control edge, the greater the deviations in the piston stroke. Further disadvantages of the steep control edge course arise at the end of the injection phase in that the piston stroke becomes quite large, which is necessary in order to fully open the overflow hole in the cylinder through the associated control edge. This means that the injection is not stopped quickly, but "creepingly", which deteriorates the combustion of the fuel. Injection pumps of the type mentioned are also only used for constant injection start. It is practically impossible to advance the start of injection before the ignition TDC due to the steep control edge course.

Der Erfindung liegt die Aufgabe zugrunde, die Einspritzpumpe der eingangs genannten Art so zu verbessern, dass die durch den steilen Steuerkantenverlauf bedingten Nachteile vermieden werden.The invention has for its object to improve the injection pump of the type mentioned so that the disadvantages caused by the steep control edge course are avoided.

Diese Aufgabe wird erfindungsgemäss durch die Merkmale des Kennzeichens des Anspruchs 1 gelöst.According to the invention, this object is achieved by the features of the characterizing part of claim 1.

Durch das exzentrische Anbringen der mit der Innenverzahnung versehenen Verstellhülse und das Anbringen einer dazu passenden Aussenverzahnung am Pumpenkolben wird die Schwenkbewegung der Verstellhülse in eine grössere Verschwenkbewegung des Pumpenkolbens übersetzt, wobei sich etwa eine Verdoppelung des bisherigen Schwenkbereichs des Pumpenkolbens erzielen lässt, d.h. etwa 120°. Diese Vergrösserung des Schwenkbereichs des Pumpenkolbens wird dabei mit einem geradlinigen Verstellweg der Regulierstange erreicht, der gleich gross bleibt wie bei den Einspritzpumpen der eingangs genannten Art. Der grössere Schwenkbereich des Pumpenkolbens erlaubt nunmehr, den Verlauf der schrägen Steuerkanten über einen entsprechend grösseren Umfang der Mantelfläche des Pumpenkolbens zu erstrecken, so dass - in der zeichnerischen Abwicklung gesehen - die Steuerkanten eine wesentlich geringere Steigung als bisher aufweisen. Damit sind die im Zusammenhang mit dem steilen Steuerkantenverlauf der bekannten Einspritzpumpen beschriebenen Nachteile erheblich verringert. Die Abweichungen des Kolbenhubes infolge der Ungenauigkeiten im Uebertragungsweg sind also wesentlich kleiner; die Einspritzphase wird rascher beendet, weil auch der Kolbenhub zum vollen Oeffnen des Ueberströmloches durch die zugehörige Steuerkante kleiner wird. Schliesslich wird es möglich, mit der neuen Einspritzpumpe einen variablen Förderbeginn zu fahren, d.h. den Einspritzbeginn vor den Zünd-OT zu verlegen.Due to the eccentric attachment of the adjusting sleeve provided with the internal toothing and the attachment of a matching external toothing on the pump piston, the pivoting movement of the adjusting sleeve is translated into a larger pivoting movement of the pump piston, whereby approximately a doubling of the previous pivoting range of the pump piston can be achieved, ie approximately 120 °. This enlargement of the swivel range of the pump piston is achieved with a rectilinear adjustment path of the regulating rod, which remains the same size as in the injection pumps of the type mentioned at the outset. The larger swivel range of the pump piston now allows the course of the oblique control edges over a correspondingly larger circumference of the lateral surface of the To extend the pump piston so that - seen in the drawing - the control edges have a much smaller slope than before. The disadvantages described in connection with the steep control edge profile of the known injection pumps are thus considerably reduced. The deviations of the piston stroke due to the inaccuracies in the transmission path are therefore considerably smaller; the injection phase is ended more quickly because the piston stroke for the full opening of the overflow hole is reduced by the associated control edge. Eventually it becomes possible with the new one To drive the injection pump a variable start of delivery, ie to postpone the start of injection before the ignition TDC.

Ein Ausführungsbeispiel der Erfindung wird in der folgenden Beschreibung anhand der Zeichnung näher erläutert. Es zeigen:

  • Fig. 1 einen Axialschnitt durch eine Brennstoffeinspritzpumpe, die im Motorengehäuse montiert ist,
  • Fig. 2 einen Querschnitt durch die Pumpe entsprechend den Schnittlinien A-B und C-D in Fig. 1 und
  • Fig. 3 einen Querschnitt durch einen Teil der Pumpe im Bereich der Verzahnungen.
An embodiment of the invention is explained in more detail in the following description with reference to the drawing. Show it:
  • 1 is an axial section through a fuel injection pump which is mounted in the engine housing,
  • Fig. 2 shows a cross section through the pump according to the section lines AB and CD in Fig. 1 and
  • Fig. 3 shows a cross section through part of the pump in the region of the teeth.

Gemäss Fig. 1 ist in einem Pumpengehäuse 1 ein Pumpenzylinder 2 vorgesehen, der durch einen Pumpengehäusedeckel 3 im Pumpengehäuse 1 fixiert wird. Im Pumpenzylinder 2 ist ein Pumpenkolben 4 auf- und abbeweglich geführt, der in seiner Mantelfläche nahe dem oberen Kolbenende mit schräg zur Kolbenlängsachse verlaufenden Steuerkanten 5 versehen ist. Diese Steuerkanten wirken in bekannter Weise mit zwei in Fig. 1 nicht dargestellten radialen Bohrungen in der Wand des Pumpenzylinders 2 zusammen, wodurch der Förderbeginn und das Förderende des Pumpenkolbens 4 bestimmt wird. Der einzuspritzende Brennstoff wird über eine in Fig. 1 ebenfalls nicht dargestellte Zuführleitung einem Ringraum 6 zwischen Pumpengehäuse 1 und Pumpenzylinder 2 zugeführt, aus dem er über die eben erwähnte, den Förderbeginn bestimmende Bohrung in den Förderraum 7 der Pumpe gelangt. Ueber eine zentrale Bohrung 8 im Pumpengehäusedeckel 3 gelangt die einzuspritzende Brennstoffmenge während des Förderhubes des Pumpenkolbens 4 zum nicht dargestellten Einspritzventil im Zylinderdeckel des Dieselmotors.1, a pump cylinder 2 is provided in a pump housing 1, which is fixed in the pump housing 1 by a pump housing cover 3. In the pump cylinder 2, a pump piston 4 is guided up and down, which is provided in its lateral surface near the upper piston end with control edges 5 which run obliquely to the longitudinal axis of the piston. These control edges cooperate in a known manner with two radial bores (not shown in FIG. 1) in the wall of the pump cylinder 2, as a result of which the start of delivery and the end of delivery of the pump piston 4 are determined. The fuel to be injected is fed via an inlet line, also not shown in FIG. 1, to an annular space 6 between the pump housing 1 and the pump cylinder 2, from which it reaches the delivery chamber 7 of the pump via the aforementioned bore, which determines the start of delivery. Via a central Bore 8 in the pump housing cover 3 reaches the amount of fuel to be injected during the delivery stroke of the pump piston 4 to the injection valve (not shown) in the cylinder cover of the diesel engine.

Der Pumpenkolben 4 weist an seinem unteren, aus dem Pumpenzylinder 2 herausragenden Ende einen Flansch 9 auf, mit dem er an einem Pumpenstössel 10 anliegt, der im Pumpengehäuse 1 axial beweglich geführt ist. Der Flansch 9 ist von einer Kappe 11 übergriffen, die auch einen Teil des Pumpenstössels 10 umgibt und auf der sich das untere Ende einer Druckfeder 12 abstützt. Das obere Ende der Druckfeder 12 stützt sich an einem Federteller 13 ab, der im Pumpengehäuse 1 fixiert ist. Mittels der Druckfeder 12 wird ein ständiges Anliegen des Flansches 9 am Pumpenstössel 10 gewährleistet. Am unteren Ende des Pumpenstössels 10 ist in diesem eine Rolle 14 drehbar gelagert, die auf einer Nocke 15 einer Nockenwelle abrollt, die den Pumpenkolben 4 im Takt des Dieselmotors antreibt.The pump piston 4 has at its lower end protruding from the pump cylinder 2 a flange 9 with which it rests on a pump tappet 10 which is guided in the pump housing 1 so as to be axially movable. The flange 9 is overlapped by a cap 11, which also surrounds part of the pump plunger 10 and on which the lower end of a compression spring 12 is supported. The upper end of the compression spring 12 is supported on a spring plate 13 which is fixed in the pump housing 1. A constant contact of the flange 9 on the pump tappet 10 is ensured by means of the compression spring 12. At the lower end of the pump plunger 10, a roller 14 is rotatably mounted therein, which rolls on a cam 15 of a camshaft that drives the pump piston 4 in time with the diesel engine.

Das untere Ende des Pumpenzylinders 2 ist von einer Hülse 16 umgeben, die an ihrem unteren, über den Pumpenzylinder hinausragenden Ende mit zwei axialen, einander diametral gegenüberliegenden Schlitzen versehen ist, in die je ein radialer Arm 17 des Pumpenkolbens 4 hineinragt. Die axiale Länge der Schlitze ist mindestens gleich gross wie der maximale Hub des Pumpenkolbens 4. Auf diese Weise ist eine drehfeste Verbindung zwischen dem Pumpenkolben 4 und der Hülse 16 hergestellt, die auf dem Zylinder 2 drehbar gleitet. Die Hülse 16 weist in ihrem Bereich oberhalb der Schlitze eine Aussenverzahnung 18 auf, die mit einer Innenverzahnung 19 im Eingriff steht, die in einer exzentrisch zur Hülse 16 und damit zum Pumpenkolben 4 angeordneten Verstellhülse 20 vorgesehen ist. Die Verstellhülse 20 ist im Pumpengehäuse 1 um ihre Drehachse 21 (Fig. 3) schwenkbar gelagert und weist an ihrem äusseren Umfang einen radial nach aussen ragenden Anschlaglappen 22 auf. Am Anschlaglappen 22 ist ein in Fig. 1 nach unten ragender Mitnehnmerstift 23 befestigt, der in ein Gabelstück 24 ragt, das auf einer quer zum Pumpenkolben 4 hin- und her beweglichen Regulierstange 25 einstellbar befestigt ist. Durch Bewegen der Regulierstange 25 um den Betrag "s" (Fig. 2) lässt sich also über das Gabelstück 24 und den Mitnehnmerstift 23 die Verstellhülse 20 um einen Winkel von ca. 60° verschwenken, wie dies durch die strichpunktierte Darstellung des Gabelstücks 24 und des Mitnehmerstiftes 23 in Fig. 2 dargestellt ist. In der in Fig. 2 oberen strichpunktiert dargestellten Stellung liegt die seitliche Begrenzungsfläche 22′ (Fig. 3) des Anschlaglappens 22 an einer Anschlagschraube 26, die am Pumpengehäuse 1 angebracht ist. Die Anschlagschraube 26 ist mit Hilfe einer Stellmutter 27 einstellbar. Eine gleiche Anordnung von Anschlagschraube und Stellmutter befindet sich auf der entgegengesetzten Seite des Schwenkbereichs der Verstellhülse 20 und wirkt mit der Begrenzungsfläche 22˝ des Anschlaglappens 22 zusammen. Die Grösse des Weges "s" und damit die Grösse des Schwenkbereiches des Lappens 22 ist dadurch begrenzt, dass das Gehäuse 1 in dem genannten Bereich nicht weiter geschwächt werden kann. Mit Hilfe der Innenverzahnung 19 und der Aussenverzahnung 18 wird die Schwenkbewegung der Verstellhülse 20 in eine grössere Verstellbewegung der Hülse 16 und damit des Pumpenkolbens 4 übersetzt. Die Grösse der Schwenkbewegung der Hülse 16 ist abhängig von der Grösse der Exzentrizität "e" (Fig. 3) zwischen der Längsachse des Pumpenkolbens und der Achse 21 der Verstellhülse 20. Es lässt sich ein maximaler Schwenkbereich von ungefähr 120° der Hülse 16 bzw. des Pumpenkolbens 4 erreichen.The lower end of the pump cylinder 2 is surrounded by a sleeve 16, which at its lower end, which projects beyond the pump cylinder, is provided with two axial, diametrically opposite slots, into each of which a radial arm 17 of the pump piston 4 projects. The axial length of the slots is at least the same as the maximum stroke of the pump piston 4. In this way, a rotationally fixed connection between the pump piston 4 and the sleeve 16 is made, which slides on the cylinder 2 rotatably. The sleeve 16 has in its area above the slots an external toothing 18 which is in engagement with an internal toothing 19 which is provided in an adjusting sleeve 20 arranged eccentrically to the sleeve 16 and thus to the pump piston 4. The Adjustment sleeve 20 is pivotally mounted in the pump housing 1 about its axis of rotation 21 (FIG. 3) and has a radially outwardly projecting stop tab 22 on its outer circumference. 1 is attached to the stop tab 22, which projects downward into a fork piece 24, which is adjustably fastened on a regulating rod 25 which can be moved back and forth transversely to the pump piston 4. By moving the regulating rod 25 by the amount "s" (FIG. 2), the adjusting sleeve 20 can thus be pivoted through an angle of approximately 60.degree of the driving pin 23 is shown in Fig. 2. In the upper dash-dotted position in Fig. 2, the lateral boundary surface 22 '(Fig. 3) of the stop tab 22 is on a stop screw 26 which is attached to the pump housing 1. The stop screw 26 is adjustable with the help of an adjusting nut 27. The same arrangement of the stop screw and the adjusting nut is located on the opposite side of the swivel range of the adjusting sleeve 20 and interacts with the boundary surface 22˝ of the stop tab 22. The size of the path "s" and thus the size of the swivel range of the flap 22 is limited by the fact that the housing 1 cannot be weakened further in the area mentioned. With the help of the internal toothing 19 and the external toothing 18, the pivoting movement of the adjusting sleeve 20 is translated into a larger adjusting movement of the sleeve 16 and thus of the pump piston 4. The size of the pivoting movement of the sleeve 16 depends on the size of the eccentricity "e" (FIG. 3) between the longitudinal axis of the pump piston and the axis 21 of the adjusting sleeve 20. It can be reach maximum swivel range of approximately 120 ° of the sleeve 16 or the pump piston 4.

Wie aus Fig. 1 ersichtlich, ist die Einspritzpumpe mit ihrer unteren Hälfte in ein Motorengehäuse 30 eingesteckt, in dem auch die Nockenwelle gelagert ist. Wesentlich für die Einspritzpumpe ist, dass die äussere Begrenzung des Anschlaglappens 22 innerhalb des Durchmessers der oberen, das Pumpengehäuse 1 aufnehmenden Bohrung 31 im Motorengehäuse liegt, so dass sich die Einspritzpumpe ohne weiteres ein- und ausbauen lässt. Je Arbeitszylinder des Dieselmotors ist eine Einspritzpumpe in der beschriebenen Weise im Motorengehäuse angeordnet und ist auf der gemeinsamen Nockenwelle eine zugehörige, der Nocke 15 entsprechende Nocke vorhanden. Auch die Regulierstange 25 ist für alle Arbeitszylinder gemeinsam und hat für jede Einspritzpumpe ein Gabelstück 24. Durch Einstellen der Gabelstücke 24 relativ zur Regulierstange und Einstellen der Anschlagschrauben 26 lassen sich die in die Arbeitszylinder einzuspritzenden Brennstoffmengen untereinander gleich gross machen.As can be seen from FIG. 1, the lower half of the injection pump is inserted into an engine housing 30 in which the camshaft is also mounted. It is essential for the injection pump that the outer limit of the stop lug 22 lies within the diameter of the upper bore 31 in the engine housing that receives the pump housing 1, so that the injection pump can be easily installed and removed. For each working cylinder of the diesel engine, an injection pump is arranged in the engine housing in the manner described and there is an associated cam corresponding to cam 15 on the common camshaft. The regulating rod 25 is also common to all working cylinders and has a fork piece 24 for each injection pump. By adjusting the fork pieces 24 relative to the regulating rod and adjusting the stop screws 26, the fuel quantities to be injected into the working cylinders can be made equal to one another.

Abweichend von dem beschriebenen Ausführungsbeispiel ist es auch möglich, die Hülse 16 wegzulassen und deren Aussenverzahnung direkt am Pumpenkolben 4 vorzusehen. In einem solchen Falle müsste die Aussenverzahnung in axialer Richtung länger ausgebildet sein, damit sie während der Auf- und Abbewegung des Pumpenkolbens mit der Innenverzahnung 19 der Verstellhülse 20 im Eingriff bleibt.In a departure from the exemplary embodiment described, it is also possible to omit the sleeve 16 and to provide its external toothing directly on the pump piston 4. In such a case, the outer toothing would have to be longer in the axial direction so that it remains in engagement with the inner toothing 19 of the adjusting sleeve 20 during the up and down movement of the pump piston.

Claims (6)

1. Fuel injection pump for reciprocating-piston internal combustion engines of the diesel type, with at least one pump piston (4), which can move up and down in a cylinder (2) and comprises control edges (5), which extend obliquely to its longitudinal axis, in its surface area, which control edges determine with holes provided in the cylinder (2) the beginning and end of delivery of the pump piston (4), and with an adjusting sleeve (20), which surrounds the pump piston (4) and co-operates with a control rod (25), which is mounted outside the cylinder (2) and can reciprocate in a straight line, in order to swivel the pump piston (4), characterised in that the adjusting sleeve (20) surrounds the pump piston (4) eccentrically and is provided with an internal tooth system (19), that an external tooth system (18), which engages with this internal tooth system, is mounted on the pump piston (4), and that the adjusting sleeve (20) is hinged to the control rod (25).
2. Pump according to claim 1, with a pump casing (1) which accommodates the cylinder (2), surrounds with its lower end the tappet (10), which transmits the up-and-down movement of the pump piston (4), and is inserted in an engine casing (30) containing a camshaft drive, characterised in that the connection point between the adjusting sleeve (20) and the control rod (25) is disposed inside the contour, which is accommodated by the engine casing (30), of the pump casing (1).
3. Pump according to claim 2, characterised in that the adjusting sleeve (20) comprises on its outside a stop lug (22), which co-operates via its two lateral end surfaces (22′, 22˝) with stops (26) which are disposed on the pump casing (1) and limit the swivelling range of the adjusting sleeve (20).
4. Pump according to claim 3, characterised in that the stops (26) disposed on the pump casing (1) are adjustable.
5. Pump according to claim 3, characterised in that a driving pin (23) is secured to the stop lug (22) and projects into a fork (24) which in turn is secured in an adjustable manner to the control rod (25).
6. Pump according to one of claims 1 to 5, characterised in that the pump piston (4) is connected to an axially fixed coupling sleeve (16), which is rotatably mounted on the cylinder (2) and the outside of which is provided with the external tooth system (18).
EP88101862A 1987-04-30 1988-02-09 Fuel injection pump for a diesel engine Expired - Lifetime EP0288669B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH1652/87 1987-04-30
CH1652/87A CH672005A5 (en) 1987-04-30 1987-04-30

Publications (2)

Publication Number Publication Date
EP0288669A1 EP0288669A1 (en) 1988-11-02
EP0288669B1 true EP0288669B1 (en) 1991-03-20

Family

ID=4215469

Family Applications (1)

Application Number Title Priority Date Filing Date
EP88101862A Expired - Lifetime EP0288669B1 (en) 1987-04-30 1988-02-09 Fuel injection pump for a diesel engine

Country Status (8)

Country Link
EP (1) EP0288669B1 (en)
JP (1) JPS63272959A (en)
CH (1) CH672005A5 (en)
DE (1) DE3862056D1 (en)
DK (1) DK164827C (en)
ES (1) ES2022482B3 (en)
FI (1) FI96535C (en)
NO (1) NO168725C (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103267012A (en) * 2013-05-29 2013-08-28 宁波合力机泵有限公司 Flow adjusting device capable of changing plunger volume

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5730104A (en) * 1997-02-19 1998-03-24 Caterpillar Inc. Injection rate shaping device for a fill metered hydraulically-actuated fuel injection system
JP7022380B2 (en) * 2018-01-31 2022-02-18 いすゞ自動車株式会社 Fuel pump assembly structure

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1054199A (en) * 1950-12-08 1954-02-09 Daimler Benz Ag Fuel injection device, in particular with injection pump and injection nozzle combined in a single unit
US3498229A (en) * 1967-11-01 1970-03-03 Dake Corp Hydraulic pump assembly
US3566702A (en) * 1968-03-01 1971-03-02 Bryce Berger Ltd Liquid fuel injection pumps
AT381148B (en) * 1980-12-18 1986-08-25 Friedmann & Maier Ag INJECTION DEVICE FOR INJECTION INTERNAL COMBUSTION ENGINES
DE3501287A1 (en) * 1984-01-18 1985-07-25 Friedmann & Maier AG, Hallein, Salzburg Injection pump for injection internal combustion engines

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103267012A (en) * 2013-05-29 2013-08-28 宁波合力机泵有限公司 Flow adjusting device capable of changing plunger volume
CN103267012B (en) * 2013-05-29 2015-10-07 宁波合力机泵有限公司 A kind of flow regulator changing plunger volume

Also Published As

Publication number Publication date
NO168725B (en) 1991-12-16
FI96535B (en) 1996-03-29
FI880655A0 (en) 1988-02-12
NO881890L (en) 1988-10-31
JPS63272959A (en) 1988-11-10
FI96535C (en) 1996-07-10
DE3862056D1 (en) 1991-04-25
FI880655A (en) 1988-10-31
NO881890D0 (en) 1988-04-29
CH672005A5 (en) 1989-10-13
ES2022482B3 (en) 1991-12-01
EP0288669A1 (en) 1988-11-02
DK134188A (en) 1988-10-31
DK164827C (en) 1993-01-11
DK134188D0 (en) 1988-03-11
DK164827B (en) 1992-08-24
NO168725C (en) 1992-03-25

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