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EP0209681B1 - Speed governor for a fuel injection pump - Google Patents

Speed governor for a fuel injection pump Download PDF

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Publication number
EP0209681B1
EP0209681B1 EP86107316A EP86107316A EP0209681B1 EP 0209681 B1 EP0209681 B1 EP 0209681B1 EP 86107316 A EP86107316 A EP 86107316A EP 86107316 A EP86107316 A EP 86107316A EP 0209681 B1 EP0209681 B1 EP 0209681B1
Authority
EP
European Patent Office
Prior art keywords
governor
lever
shaft
fuel injection
spring arrangement
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
EP86107316A
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German (de)
French (fr)
Other versions
EP0209681A1 (en
Inventor
Franz Eheim
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
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Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP0209681A1 publication Critical patent/EP0209681A1/en
Application granted granted Critical
Publication of EP0209681B1 publication Critical patent/EP0209681B1/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
    • 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
    • F02D1/04—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 by mechanical means dependent on engine speed, e.g. using centrifugal governors

Definitions

  • the invention is based on a speed controller according to the preamble of the main claim.
  • a fuel injection pump has a control rod for adjusting the delivery rate, which is coupled to a centrifugal force adjuster via a two-armed lever.
  • One side of the adjusting sleeve of the centrifugal force adjuster is acted upon by a control spring, the pretension of which can be adjusted by a lever.
  • an additional spring acts on the control rod, the other end of which is attached to the end of a swivel arm which can be rotated about a point fixed to the housing with the aid of an adjusting lever.
  • This additional spring can be adjusted in terms of its direction of action with the help of the swivel arm, with it acting in the basic setting in support of the control spring.
  • the force component acting in the direction of the control rod can be changed, which results in a change in the overall characteristics of the control spring and additional spring.
  • This device is used to change the slew rate of the speed controller, but at the same time there is also a change in the load setting.
  • the setup is very complex.
  • a speed controller according to the preamble of claim 1 is known from FR-A 1 188 261.
  • the control spring arrangement, its connection to the control lever and the support arm are arranged outside the pump housing.
  • the tension of the regulating spring is changed on the one hand by changing the length between its fastening points, and on the other hand the position of the regulating spring changed to the shaft or their direction of force to the control lever.
  • the suspension point of the control spring can be set and fixed by adjusting an adjusting screw which is screwed on through the support arm.
  • An equally designed controller is known from DE-C 864 781.
  • the setting can advantageously be carried out with the housing of the fuel injection pump closed and during operation of the fuel injection pump.
  • only a single control spring is required to set the control characteristic and, due to the angular position of the control spring axis and the preload of the control spring, both the regulating steepness or the P-degree and the regulating speed can be easily set at a single point on the fuel injection pump will.
  • the device is therefore less complex and space-saving and can be used in particular in distributor injection pumps, which are characterized by a particularly small size.
  • a fuel injection pump that is equipped with such a controller is advantageously suitable for use in internal combustion engines with which, for example when generating electricity, exact speeds must be maintained with a precisely defined control behavior (P-degree).
  • the setting is made according to claim 1 for both the angular position and for the bias by adjusting movements that can be made during the operation of the fuel injection pump regardless of the adjustment of the support arm.
  • a further development of the object according to claim 1 is advantageously given by claim 2, whereby the bias of the spring can be changed in a particularly simple manner and with a large adjustment range.
  • FIG. 1 shows a partial section through a distributor fuel injection pump of known design with the essential parts of the speed controller
  • FIG. 2 shows a section through the longitudinal axis of the shaft of the swivel arm in the example according to FIG. 1
  • FIG. 3 shows a partial section through a distributor fuel injection pump for an exemplary embodiment
  • FIG. 4 shows a longitudinal section 3
  • FIG. 5 shows an embodiment as a partial section through the shaft of the swivel arm
  • FIG. 6 shows an embodiment with a section through the shaft of the swivel arm in a modification of the embodiment according to FIGS. 4 to 5
  • FIG. 7 shows a view of the swivel arm of the embodiment of Figure 6.
  • FIG. 1 shows part of a distributor fuel injection pump of a known type with a pump piston 1, which is set into a reciprocating and at the same time rotating movement by means not shown, and is guided in a bushing 3 inserted in the housing 2 of the fuel injection pump.
  • the housing includes a pump suction chamber 4 which is filled with fuel which is generally kept at a pressure which is controlled as a function of the speed in order to carry out control functions.
  • a ring slide 6 is arranged as a quantity adjusting member, which controls the mouth of a relief line 7 leading from the pump work chamber (not shown here) into the pump suction chamber.
  • the ring slide is displaceable on the pump piston, the fuel injection quantity delivered per pump stroke under high pressure being greater in the embodiment shown, the further the ring slide is displaced to the top dead center of the pump piston.
  • a speed controller which has a control lever 9 which can be pivoted about an adjustable housing 10 which is substantially fixed to the housing and is coupled via a head 11 at one end to the ring slide 6 and adjusts it.
  • This regulator lever can in principle be provided as the only regulator lever, but in the example shown a regulator lever arrangement with several levers is provided.
  • the control lever 9 is a start lever which is acted upon directly by an adjusting sleeve 13 of a centrifugal speed sensor 8, which is only indicated.
  • the start lever 9 Under the influence of the speed-dependent actuating forces of the adjusting sleeve 13, the start lever 9 can be brought into contact with the rocker arm 14. Between the start lever and the rocker arm, a leaf spring is arranged as a start spring 17, which is compressed during this process.
  • an idle control spring 18 designed as a compression spring is articulated, which is supported on an adjustable stop 19 fixed to the housing. This stop has a screw 20 screwed through the wall of the housing 2, which screw can be adjusted and fixed from the outside.
  • the axis 10 common to the start lever and rocker arm is mounted on an adjusting lever 23 which, in a manner not shown here, e.g. is pivotable against spring force around a fixed point of the housing for adjusting the axis.
  • the setting is also carried out by a screw 66 screwed through the housing wall, which engages at the end of the adjusting lever.
  • the control spring arrangement 15 consists of a helical spring 21 loaded under tension, one end of which is hooked into an eyelet 22 on the rocker arm 14 and the other end of which is hooked onto a pin 24. As can be seen in FIG. 2, this is located at the end of a support or swivel arm 25 which is mounted on a shaft 26. This penetrates the housing 2 within an eccentric bushing 28 and has an adjusting lever 29 at the outwardly projecting end. The shaft 26 is tightly guided in the eccentric bushing and sits eccentrically to the axis of the bushing, which in turn is guided through the housing and has an adjusting lever 30 at the outer end.
  • the controller shown here is an all-speed controller, in which the speed is set by adjusting the bias of the control spring 21, when it is exceeded, the rocker arm 14 is deflected together with the start lever 9 and the ring slide 6 is displaced downward.
  • the controller can also work with just one lever, which the centrifugal speed sensor and the control springs then engage. In this position of the ring slide, a lower fuel injection quantity is injected, which in turn reduces the previously reached speed. The actuating force on the adjusting sleeve 13 is then correspondingly lower, so that the rocker arm 14 again comes into a pivoting position which corresponds to a higher fuel injection quantity. Depending on the size of the preload, this control process occurs at lower or higher speeds.
  • the bias is set by the position of the shaft 26, which is adjustable by means of the eccentric bushing 28.
  • the regulating speed can also be changed, that is to say the steepness of the fuel injection quantity characteristic curve between full-load operation and idling.
  • the angular position of the axis of the helical control spring 21 relative to the rocker arm 14 can be changed, which is brought about by turning the adjusting lever 29.
  • individual positions of the pivot position of the pivot arm 25 are shown. If one then forms in each case the extension of the axis of the coil spring 21, it can be seen that with increasing deflection the effective lever arm with respect to the axis 10 decreases in connection with the passage of the prestress of the coil spring 21 on the regulating process.
  • the effective spring characteristic which is expressed in the steepness of the regulating process when the set speed is reached, can be varied.
  • a desired regulating steepness (P degree) can be set very precisely.
  • the axis of the helical spring 21 advantageously lies in the swivel plane which describes the eyelet 22 when the rocker arm 14 is deflected.
  • FIG. 3 shows an embodiment variant of the embodiment according to FIG. 1 and, except for the configuration of the swivel arm and its actuation, corresponds to the embodiment according to FIG. 1. Reference is therefore made to the description of this figure with regard to these parts.
  • a pivot arm 35 is provided in FIG. 3, which can be pivoted about a shaft 36 which is fixed to the housing, as can be seen in FIG.
  • the swivel arm 35 is made in two parts in the present case and consists of a support arm 37 and a slidable part 38 on which the pin 24 is fastened at the extreme end, in which the end of the coil spring 21 is suspended.
  • the displaceable part has the shape of a sheet metal strip and has a first slot 39 and a second slot 40. These elongated holes are penetrated by a rivet 41 and 42, respectively, via which the displaceable part 38 is coupled to the support arm 37.
  • the displaceable part 38 At the axis of the shaft 36, to which the support arm 37 is fixedly connected, the displaceable part 38 has a recess 44 with a shoulder 45 pointing in the direction of displacement along the support arm 37.
  • the shaft 36 has a stepped bore 46, 47, in the part of the larger diameter 46 adjoining the suction chamber, an actuating pin 49 is coaxially guided and has a surface 50 in the form of a wedge on its end that projects into the pump suction chamber 4 , which protrudes into the recess 44 and works there with the shoulder 45.
  • the part 38 is displaced more or less far along the support arm 37 and thus the coil spring 21 is more or less pretensioned.
  • a pin 52 is guided through the stepped bore part 47, which is smaller in diameter, which presses on the end face of the actuating pin 49 and is screwed into a thread 53 in the shaft 36 from the outside.
  • the screw-in position is fixed with the aid of a lock nut 54, which is screwed onto the end of the pin 52.
  • the adjusting pin 49 is thus also adjusted.
  • the characteristic of the helical spring 21 can be influenced by adjusting the swivel position of the swivel arm 35.
  • the pretension is varied in a simple manner via the pin 52 and the adjusting pin 52, regardless of the pivot position.
  • This type of intervention can also be used to set a desired preload in the finest steps.
  • a very precisely adjustable controller is obtained which is suitable for the operation of unit engines.
  • FIG. 6 shows a further embodiment variant, in which, as in the exemplary embodiment according to FIGS. 3 and 4, the swivel arm 35 'is mounted on a shaft 36 designed in the same way as in FIG.
  • the swivel arm 35 ' consists of a support arm 37 and a part 38' which can be moved thereon and which has a first elongated hole 39 and a second elongated hole 40.
  • the displaceable part 38 is connected to the support arm 37 via rivets 41 and 42 which extend through the elongated holes 39 and 40.
  • the displaceable part 38 ' has a laterally open recess 44', into which a pin 57 now engages, which is mounted eccentrically on the end face of an actuator 59.
  • the actuator 59 consists of a bolt which is mounted tightly in an axial bore 60 in the shaft 36.
  • a threaded bore 61 adjoins the bore 60 to the outside, through which the threaded part 62 of the bolt 59 is screwed.
  • the threaded part 62 has a form-fitting surface 63, via which the bolt 59 can be rotated.
  • a lock nut 64 is screwed onto the threaded part 62.
  • the shaft 36 can be rotated via the adjusting lever 29, whereby the swivel position of the helical spring 21 can be adjusted.
  • the displacement position of the displaceable part 38' is determined.
  • the advantage here is that the displaceable part 38 'can be moved back and forth independently of the restoring force of the spring 21 via the recess which is adapted to the width of the pin diameter of the pin 57. If a washer 66 is also placed on the end face of the bolt, on which the pin 57 is then seated, the adjustment range of the displaceable part can be increased compared to the embodiment according to FIG.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • High-Pressure Fuel Injection Pump Control (AREA)
  • Fuel-Injection Apparatus (AREA)

Description

Stand der TechnikState of the art

Die Erfindung geht von einem Drehzahlregler nach der Gattung des Hauptanspruchs aus. Bei einem durch das DE-GM 1 784 561 bekannten Drehzahlregler weist eine Kraftstoffeinspritzpumpe zur Verstellung der Fördermenge eine Regelstange auf, die über einen zweiarmigen Hebel mit einem Fliehkraftversteller gekoppelt ist. Die eine Seite der Stellmuffe des Fliehkraftverstellers wird von einer Regelfeder beaufschlagt, deren Vorspannung durch einen Hebel verstellbar ist. Ferner greift an der Regelstange eine Zusatzfeder an, deren anderes Ende am Ende eines Schwenkarmes befestigt ist, der um einen gehäusefesten Punkt mit Hilfe eines Stellhebels verdrehbar ist. Diese Zusatzfeder kann hinsichtlich ihrer Wirkrichtung mit Hilfe des Schwenkarmes verstellt werden, wobei sie in der Grundeinstellung in Unterstützung der Regelfeder wirkt. Durch Veränderung der Winkellage der Achse der Zusatzfeder zur Regelstange läßt sich die in Richtung Regelstange wirkende Kraftkomponente verändern, was eine Änderung der Gesamtcharakteristik von Regelfeder und Zusatzfeder ergibt. Wegen der Abweichung der Drehachse des Schwenkhebels vom Befestigungspunkt der Zusatzfeder an der Regelstange ergibt sich bei der Veränderung der Winkellage der Zusatzfeder auch eine Änderung der Vorspannung derselben. Diese Einrichtung dient zur Veränderung der Abregelsteilheit des Drehzahlreglers, wobei sich jedoch zugleich auch eine Änderung der Lasteinstellung ergibt. Die Einrichtung ist dabei sehr aufwendig.The invention is based on a speed controller according to the preamble of the main claim. In a speed controller known from DE-GM 1 784 561, a fuel injection pump has a control rod for adjusting the delivery rate, which is coupled to a centrifugal force adjuster via a two-armed lever. One side of the adjusting sleeve of the centrifugal force adjuster is acted upon by a control spring, the pretension of which can be adjusted by a lever. Furthermore, an additional spring acts on the control rod, the other end of which is attached to the end of a swivel arm which can be rotated about a point fixed to the housing with the aid of an adjusting lever. This additional spring can be adjusted in terms of its direction of action with the help of the swivel arm, with it acting in the basic setting in support of the control spring. By changing the angular position of the axis of the additional spring relative to the control rod, the force component acting in the direction of the control rod can be changed, which results in a change in the overall characteristics of the control spring and additional spring. Because of the deviation of the axis of rotation of the pivot lever from the point of attachment of the additional spring to the control rod, when the angular position of the additional spring changes, there is also a change in the pretensioning thereof. This device is used to change the slew rate of the speed controller, but at the same time there is also a change in the load setting. The setup is very complex.

Ein Drehzahlregler gemäß der Gattung des Patentanspruchs 1 ist durch die FR-A 1 188 261 bekannt. Hier sind jedoch die Regelfederanordnung, deren Verbindung zum Regelhebel sowie der Trägerarm außerhalb des Pumpengehäuses angeordnet. Durch Schwenken des Verstellhebels, der auf einer parallel zu einer den Reglerhebel tragenden Welle liegenden zweiten Welle befestigt ist, auf der ferner der Trägerarm angebracht ist, wird die Regelfeder zum einen in ihrer Spannung durch Längenänderung zwischen ihren Befestigungspunkten verändert, zum anderen die Lage der Regelfeder zur Welle bzw. ihre Kraftrichtung zum Reglerhebel verändert.A speed controller according to the preamble of claim 1 is known from FR-A 1 188 261. Here, however, the control spring arrangement, its connection to the control lever and the support arm are arranged outside the pump housing. By pivoting the adjusting lever, which is fastened on a second shaft lying parallel to a shaft carrying the regulator lever and on which the support arm is also attached, the tension of the regulating spring is changed on the one hand by changing the length between its fastening points, and on the other hand the position of the regulating spring changed to the shaft or their direction of force to the control lever.

Zur Modifikation der Ausgangsspannung der Regelfederanordnung kann der Aufhängepunkt der Regelfeder durch Verstellen einer Stellschraube, die durch den Trägerarm angeschraubt ist, eingestellt und fixiert werden. Ein gleichermaßen konzipierter Regler ist durch die DE-C 864 781 bekannt.To modify the output voltage of the control spring arrangement, the suspension point of the control spring can be set and fixed by adjusting an adjusting screw which is screwed on through the support arm. An equally designed controller is known from DE-C 864 781.

Liegt die Regelfederanordnung aber innerhalb der Kraftstoffeinspritzpumpe, so ist eine solche Einstellung der Vorspannung mittels einer Stellschraube, wie auch in der US-A 4 100 890 gezeigt, ohne Öffnung des Reglergehäuses nicht möglich. Dies gilt auch für den Drehzahlregler nach DE-A 11 576 338, wo die Federspannung durch Einhaken der Feder an verschiedenen Einhakösen am innerhalb des Pumpengehäuses liegenden Spannhebel variiert werden kann.However, if the control spring arrangement lies within the fuel injection pump, then such an adjustment of the preload by means of an adjusting screw, as also shown in US Pat. No. 4,100,890, is not possible without opening the regulator housing. This also applies to the speed controller according to DE-A 11 576 338, where the spring tension can be varied by hooking the spring onto different hooking eyelets on the tension lever located inside the pump housing.

Demgegenüber kann beim erfindungsgemäßen Drehzahlregler mit den kennzeichnenden Merkmalen des Patentanspruchs 1 in vorteilhafter Weise die Einstlelung bei geschlossenem Gehäuse der Kraftstoffeinspritzpumpe und während des Betriebs der Kraftstoffeinspritzpumpe vorgenommen werden. Zur Einstellung der Regelcharakteristik ist abweichend vom eingangs genannten Stand der Technik nur eine einzige Regelfeder notwendig und es kann durch die Winkellage der Regelfederachse und die Vorspannung der Regelfeder sowohl die Abregelsteilheit bzw. der P-Grad auch die Abregeldrehzahl einfach an einer einzigen Stelle der Kraftstoffeinspritzpumpe eingestellt werden.In contrast, in the speed controller according to the invention with the characterizing features of claim 1, the setting can advantageously be carried out with the housing of the fuel injection pump closed and during operation of the fuel injection pump. In contrast to the prior art mentioned at the outset, only a single control spring is required to set the control characteristic and, due to the angular position of the control spring axis and the preload of the control spring, both the regulating steepness or the P-degree and the regulating speed can be easily set at a single point on the fuel injection pump will.

Die Einrichtung ist demzufolge wenig aufwendig und raumsparend und kann insbesondere bei Verteilereinspritzpumpen, die sich durch besonders kleine Baugröße auszeichnen, zum Einsatz gebracht werden. Insbesondere ist eine Kraftstofeinspritzpumpe, die mit einem solchen Regler ausgestattet ist, vorteilhaft für den Einsatz bei Brennkraftmaschinen geeignet, mit denen wie zum Beispiel bei der Stromerzeugung exakte Drehzahlen eingehalten werden müssen mit einem genau festgelegten Abregelverhalten (P-Grad).The device is therefore less complex and space-saving and can be used in particular in distributor injection pumps, which are characterized by a particularly small size. In particular, a fuel injection pump that is equipped with such a controller is advantageously suitable for use in internal combustion engines with which, for example when generating electricity, exact speeds must be maintained with a precisely defined control behavior (P-degree).

Die Einstellung erfolgt gemäß Patentanspruch 1 sowohl für die Winkellage als auch für die Vorspannung durch Stellbewegungen, die während des Betriebs der Kraftstoffeinspritzpumpe unabhängig von der Verstellung des Trägerarms vorgenommen werden können. Eine Weiterbildung des Gegenstands nach Patentanspruch 1 ist vorteilhaft durch den Patentanspruch 2 gegeben, womit in besonders einfacher Weise und mit einem großen Verstellbereich die Vorspannung der Feder verändert werden kann.The setting is made according to claim 1 for both the angular position and for the bias by adjusting movements that can be made during the operation of the fuel injection pump regardless of the adjustment of the support arm. A further development of the object according to claim 1 is advantageously given by claim 2, whereby the bias of the spring can be changed in a particularly simple manner and with a large adjustment range.

Weitere Ausgestaltungen der Erfindung sind den übrigen Unteransprüchen zu entnehmen, sie werden mit ihren Vorteilen in der nachfolgenden Beschreibung näher erläutert.Further refinements of the invention can be found in the remaining subclaims, and their advantages are explained in more detail in the description below.

Zeichnungdrawing

Vergleichs- und Ausführungsbeispiele der Erfindung sind in der Zeichnung dargestellt. Es zeigen Figur 1 einen Teilschnitt durch eine Verteilerkraftstoffeinspritzpumpe bekannter Bauart mit den wesentlichen Teilen des Drehzahlreglers, Figur 2 einen Schnitt durch die Längsachse der Welle des Schwenkarmes beim Beispiel nach Figur 1, Figur 3 einen Teilschnitt durch eine Verteilerkraftstoffeinspritzpumpe für ein Ausführungsbeispiel, Figur 4 einen Längsschnitt durch die Welle des Schwenkarmes beim Ausführungsbeispiel nach Figur 3, Figur 5 ein Ausführungsbeispiel als Teilschnitt durch die Welle des Schwenkarmes, Figur 6 ein Ausführungsbeispiel mit einem Schnitt durch die Welle des Schwenkarmes in Abwandlung zum Ausführungsbeispiel nach Figur 4 bis 5 und Figur 7 eine Aussicht auf den Schwenkarm des Ausführungsbeispiels nach Figur 6.Comparative and exemplary embodiments of the invention are shown in the drawing. 1 shows a partial section through a distributor fuel injection pump of known design with the essential parts of the speed controller, FIG. 2 shows a section through the longitudinal axis of the shaft of the swivel arm in the example according to FIG. 1, FIG. 3 shows a partial section through a distributor fuel injection pump for an exemplary embodiment, and FIG. 4 shows a longitudinal section 3, FIG. 5 shows an embodiment as a partial section through the shaft of the swivel arm, FIG. 6 shows an embodiment with a section through the shaft of the swivel arm in a modification of the embodiment according to FIGS. 4 to 5 and FIG. 7 shows a view of the swivel arm of the embodiment of Figure 6.

Beschreibung der AusführungsbeispieleDescription of the embodiments

In der Zeichnung Figur 1 ist ein Teil einer Verteilerkraftstoffeinspritzpumpe bekannter Bauart wiedergegeben mit einem Pumpenkolben 1, der durch nicht weiter gezeigte Mittel in eine hin- und hergehende und zugleich drehende Bewegung versetzt wird und in einer im Gehäuse 2 der Kraftstoffeinspritzpumpe eingesetzten Buchse 3 geführt wird. Das Gehäuse schließt einen Pumpensaugraum 4 ein, der mit Kraftstoff gefüllt ist, welcher in der Regel zur Durchführung von Steuerfunktionen auf einem drehzahlabhängig gesteuerten Druck gehalten wird. Auf dem Pumpenkolben ist als Mengenverstellorgan ein Ringschieber 6 angeordnet, der die Mündung einer vom hier nicht dargestellten Pumpenarbeitsraum herführenden Entlastungsleitung 7 in den Pumpensaugraum steuert. Der Ringschieber ist dazu auf dem Pumpenkolben verschiebbar, wobei in der gezeigten Ausgestaltung die pro Pumpenhub unter Hochdruck geförderte Kraftstoffeinspritzmenge um so größer ist, je weiter zum oberen Totpunkt des Pumpenkolbens der Ringschieber verschoben ist.FIG. 1 shows part of a distributor fuel injection pump of a known type with a pump piston 1, which is set into a reciprocating and at the same time rotating movement by means not shown, and is guided in a bushing 3 inserted in the housing 2 of the fuel injection pump. The housing includes a pump suction chamber 4 which is filled with fuel which is generally kept at a pressure which is controlled as a function of the speed in order to carry out control functions. On the pump piston, a ring slide 6 is arranged as a quantity adjusting member, which controls the mouth of a relief line 7 leading from the pump work chamber (not shown here) into the pump suction chamber. For this purpose, the ring slide is displaceable on the pump piston, the fuel injection quantity delivered per pump stroke under high pressure being greater in the embodiment shown, the further the ring slide is displaced to the top dead center of the pump piston.

Zur Einstellung des Ringschiebers 6 ist ein Drehzahlregler vorgesehen, der einen Reglerhebel 9 aufweist, der um eine im wesentlichen gehäusefeste, einstellbare Achse 10 schwenkbar ist und dabei über einen Kopf 11 an seinem einen Ende mit dem Ringschieber 6 gekoppelt ist und diesen verstellt. Dieser Reglerhebel kann grundsätzlich als einziger Reglerhebel vorgesehen werden, im ausgeführten Beispiel ist jedoch eine Reglerhebelanordnung mit mehreren Hebeln vorgesehen. Dabei handelt es sich bei dem Reglerhebel 9 um einen Starthebel, der unmittelbar von einer Verstellmuffe 13 eines nur angedeuteten Fliehkraftdrehzahlgebers 8 beaufschlagt wird. Auf der Achse 10 ist ferner ein einarmiger Schlepphebel 14 angeordnet, an dessen äu- βerstem Ende eine Regelfederanordnung 15 angreift. Diese wirkt der Kraftwirkung der Verstellmuffe 13 entgegen. Unter Einwirkung der drehzahlabhängigen Stellkräfte der Verstellmuffe 13 kann der Starthebel 9 zur Anlage an den Schlepphebel 14 gebracht werden. Zwischen Starthebel und Schlepphebel ist eine Blattfeder als Startfeder 17 angeordnet, die bei diesem Vorgang komprimiert wird. Am Ende des verstellmuffenseitigen Hebelarms des Reglerhebels 9 ist eine als Druckfeder ausgebildete Leerlaufregelfeder 18 angelenkt, die sich an einem verstellbaren gehäusefesten Anschlag 19 abstützt. Dieser Anschlag weist eine durch die Wand des Gehäuses 2 geschraubte Schraube 20 auf, die von außen einstellbar und fixierbar ist. Die dem Starthebel und Schlepphebel gemeinsame Achse 10 ist auf einem Justierhebel 23 gelagert, der in hier nicht weiter gezeigter Weise z.B. entgegen Federkraft um einen Gehäusefestpunkt zur Einstellung der Achse schwenkbar ist. Die Einstellung erfolgt ebenfalls durch eine durch die Gehäusewand geschraubte Schraube 66, die am Ende des Einstellhebels angreift.To set the ring slide 6, a speed controller is provided which has a control lever 9 which can be pivoted about an adjustable housing 10 which is substantially fixed to the housing and is coupled via a head 11 at one end to the ring slide 6 and adjusts it. This regulator lever can in principle be provided as the only regulator lever, but in the example shown a regulator lever arrangement with several levers is provided. The control lever 9 is a start lever which is acted upon directly by an adjusting sleeve 13 of a centrifugal speed sensor 8, which is only indicated. On the axle 10 there is also a one-armed rocker arm 14, at the extreme end of which a control spring arrangement 15 engages. This counteracts the force of the adjusting sleeve 13. Under the influence of the speed-dependent actuating forces of the adjusting sleeve 13, the start lever 9 can be brought into contact with the rocker arm 14. Between the start lever and the rocker arm, a leaf spring is arranged as a start spring 17, which is compressed during this process. At the end of the lever arm of the control lever 9 on the adjusting sleeve side, an idle control spring 18 designed as a compression spring is articulated, which is supported on an adjustable stop 19 fixed to the housing. This stop has a screw 20 screwed through the wall of the housing 2, which screw can be adjusted and fixed from the outside. The axis 10 common to the start lever and rocker arm is mounted on an adjusting lever 23 which, in a manner not shown here, e.g. is pivotable against spring force around a fixed point of the housing for adjusting the axis. The setting is also carried out by a screw 66 screwed through the housing wall, which engages at the end of the adjusting lever.

Die Regelfederanordnung 15 besteht im gezeigten Ausführungsbeispiel aus einer auf Zug belasteten Schraubenfeder 21, deren eines Ende in eine Öse 22 am Schlepphebel 14 eingehängt ist und deren anderes Ende an einen Zapfen 24 eingehängt ist. Dieser befindet sich, wie der Figur 2 entnehmbar ist, am Ende eines Träger- oder Schwenkarmes 25, der auf einer Welle 26 gelagert ist. Diese durchdringt das Gehäuse 2 innerhalb einer Exzenterbuchse 28 und weist am nach außen ragenden Ende einen Verstellhebel 29 auf. Die Welle 26 ist in der Exzenterbuchse dicht geführt und sitzt außermittig zur Achse der Buchse, die ihrerseits wiederum durch das Gehäuse geführt ist und am außen liegenden Ende einen Stellhebel 30 aufweist. Mit diesem kann die Drehlage der Exzenterbuchse und damit die Lage der Welle 26 verändert werden, wobei die Winkellage der Exzenterbuchse mittels einer Schraube 31 fixierbar ist, die durch ein Langloch 32 im Stellhebel 30 geführt in das Pumpengehäuse eingeschraubt ist.In the exemplary embodiment shown, the control spring arrangement 15 consists of a helical spring 21 loaded under tension, one end of which is hooked into an eyelet 22 on the rocker arm 14 and the other end of which is hooked onto a pin 24. As can be seen in FIG. 2, this is located at the end of a support or swivel arm 25 which is mounted on a shaft 26. This penetrates the housing 2 within an eccentric bushing 28 and has an adjusting lever 29 at the outwardly projecting end. The shaft 26 is tightly guided in the eccentric bushing and sits eccentrically to the axis of the bushing, which in turn is guided through the housing and has an adjusting lever 30 at the outer end. This can be used to change the rotational position of the eccentric bushing and thus the position of the shaft 26, the angular position of the eccentric bushing being fixable by means of a screw 31 which is screwed into the pump housing through an elongated hole 32 in the adjusting lever 30.

Der hier dargestellte Regler ist ein Alldrehzahlregler, bei dem durch die Verstellung der Vorspannung der Regelfeder 21 die Drehzahl eingestellt wird, bei deren Überschreiten der Schlepphebel 14 zusammen mit dem Starthebel 9 ausgelenkt und der Ringschieber 6 nach unten verschoben wird. Im Prinzip kann der Regler auch mit nur einem Hebel arbeiten, an dem dann der Fliehkraftdrehzahlgeber und die Regelfedern angreifen. In dieser Stellung des Ringschiebers kommt eine geringere Kraftstoffeinspritzmenge zur Einspritzung, was wiederum die zuvor erreichte Drehzahl reduziert. Entsprechend geringer ist dann wiederum die Stellkraft an der Verstellmuffe 13, so daß der Schlepphebel 14 wieder in eine Schwenklage kommt, die einer höheren Kraftstoffeinspritzmenge entspricht. Je nach Größe der Vorspannung tritt dieser Regelvorgang bei niedrigeren oder höheren Drehzahlen auf. Die Vorspannung wird dabei durch die Lage der Welle 26 eingestellt, die mittels der Exzenterbuchse 28 verstellbar ist.The controller shown here is an all-speed controller, in which the speed is set by adjusting the bias of the control spring 21, when it is exceeded, the rocker arm 14 is deflected together with the start lever 9 and the ring slide 6 is displaced downward. In principle, the controller can also work with just one lever, which the centrifugal speed sensor and the control springs then engage. In this position of the ring slide, a lower fuel injection quantity is injected, which in turn reduces the previously reached speed. The actuating force on the adjusting sleeve 13 is then correspondingly lower, so that the rocker arm 14 again comes into a pivoting position which corresponds to a higher fuel injection quantity. Depending on the size of the preload, this control process occurs at lower or higher speeds. The bias is set by the position of the shaft 26, which is adjustable by means of the eccentric bushing 28.

Weiterhin ist aber auch zusätzlich noch die Abregelgeschwindigkeit veränderbar, das heißt die Steilheit des Kraftstoffeinspritzmengen-Kennlinienverlaufes zwischen Vollastbetrieb und Leerlauf. Zu diesem Zweck ist die Winkellage der Achse der Schraubenregelfeder 21 zum Schlepphebel 14 veränderbar, was durch Drehen des Verstellhebels 29 bewirkt wird. In Figur 1 sind einzelne Stellungen der Schwenklage des Schwenkarmes 25 eingezeichnet. Wenn man dann jeweils die Verlängerung der Achse der Schraubenfeder 21 bildet, erkennt man, daß sich mit zunehmender Auslenkung der wirksame Hebelarm bezüglich der Achse 10 verringert verbunden mit dem Durchgriff der Vorspannung der Schraubenfeder 21 auf den Abregelvorgang. Auf diese Art und Weise kann die wirksame Federcharakteristik, die in der Steilheit des Abregelvorgangs bei Erreichen der eingestellten Drehzahl zum Ausdruck kommt, variiert werden. Mit der mit dem Ausführungsbeispiel nach Figur 1 möglichen Verschwenkung der Winkellage der Schraubenfeder 21 zum Reglerhebel 14 läßt sich sehr genau eine gewünschte Abregelsteilheit (P-Grad) einstellen. Vorteilhaft liegt die Achse der Schraubenfeder 21 dabei in der Schwenkebene, die die Öse 22 bei Auslenkung des Schlepphebels 14 beschreibt.Furthermore, however, the regulating speed can also be changed, that is to say the steepness of the fuel injection quantity characteristic curve between full-load operation and idling. For this purpose, the angular position of the axis of the helical control spring 21 relative to the rocker arm 14 can be changed, which is brought about by turning the adjusting lever 29. In Figure 1, individual positions of the pivot position of the pivot arm 25 are shown. If one then forms in each case the extension of the axis of the coil spring 21, it can be seen that with increasing deflection the effective lever arm with respect to the axis 10 decreases in connection with the passage of the prestress of the coil spring 21 on the regulating process. In this way, the effective spring characteristic, which is expressed in the steepness of the regulating process when the set speed is reached, can be varied. With the pivoting of the angular position of the helical spring 21 relative to the control lever 14, which is possible with the exemplary embodiment according to FIG. 1, a desired regulating steepness (P degree) can be set very precisely. The axis of the helical spring 21 advantageously lies in the swivel plane which describes the eyelet 22 when the rocker arm 14 is deflected.

Figur 3 zeigt eine Ausführungsvariante zum Ausführungsbeispiel nach Figur 1 und stimmt bis auf die Ausgestaltung des Schwenkarmes und seiner Betätigung mit der Ausführung gemäß Figur 1 überein. Es wird deshalb bezüglich dieser Teile auf die Beschreibung dieser Figur Bezug genommen.FIG. 3 shows an embodiment variant of the embodiment according to FIG. 1 and, except for the configuration of the swivel arm and its actuation, corresponds to the embodiment according to FIG. 1. Reference is therefore made to the description of this figure with regard to these parts.

Abweichend vom Beispiel nach Figur 1 ist bei Figur 3 ein Schwenkarm 35 vorgesehen, der um eine gehäusefest gelagerte Welle 36 schwenkbar ist, wie der Figur 4 entnehmbar ist. Der Schwenkarm 35 ist im vorliegenden Fall zweiteilig ausgeführt und besteht aus einem Trägerarm 37 und einem auf diesem verschiebbaren Teil 38, auf dem am äußersten Ende der Zapfen 24 befestigt ist, in dem das Ende der Schraubenfeder 21 eingehängt ist. Der verschiebbare Teil hat die Form eines Blechstreifens und weist ein erstes Langloch 39 und ein zweites Langloch 40 auf. Diese Langlöcher werden von jeweils einem Niet 41 und 42 durchdrungen, über die der verschiebbare Teil 38 mit dem Trägerarm 37 gekoppelt ist. In Höhe der Achse der Welle 36, mit der der Trägerarm 37 fest verbunden ist, weist der verschiebbare Teil 38 eine Ausnehmung 44 auf mit einer in Verschieberichtung längs des Trägerarms 37 weisenden Schulter 45.In a departure from the example according to FIG. 1, a pivot arm 35 is provided in FIG. 3, which can be pivoted about a shaft 36 which is fixed to the housing, as can be seen in FIG. The swivel arm 35 is made in two parts in the present case and consists of a support arm 37 and a slidable part 38 on which the pin 24 is fastened at the extreme end, in which the end of the coil spring 21 is suspended. The displaceable part has the shape of a sheet metal strip and has a first slot 39 and a second slot 40. These elongated holes are penetrated by a rivet 41 and 42, respectively, via which the displaceable part 38 is coupled to the support arm 37. At the axis of the shaft 36, to which the support arm 37 is fixedly connected, the displaceable part 38 has a recess 44 with a shoulder 45 pointing in the direction of displacement along the support arm 37.

Die Welle 36 weist eine Stufenbohrung 46, 47 auf, in deren zum Saugraum angrenzenden Teil mit größerem Durchmesser 46 koaxial ein Stellstift 49 dicht geführt ist, der an seiner in den Pumpensaugraum 4 ragenden Stirnseite eine zu seiner Achse geneigte Fläche 50 in Form eines Keils hat, die in die Ausnehmung 44 ragt und dort mit der Schulter 45 zusammenarbeitet. Je nach Eintauchtiefe der geneigten Fläche 50 in die Ausnehmung 44 wird der Teil 38 mehr oder weniger weit längs des Trägerarms 37 verschoben und damit die Schraubenfeder 21 mehr oder weniger stark vorgespannt. Zur Verstellung des Stellstiftes 49 wird durch den im Durchmesser kleineren Stufenbohrungsteii 47 ein Stift 52 geführt, der auf die Stirnseite des Stellstiftes 49 drückt und von außen in ein Gewinde 53 in der Welle 36 eingeschraubt ist. Die Einschraubstellung wird mit Hilfe einer Kontermutter 54, die auf das Ende des Stiftes 52 geschraubt wird, fixiert. Je nach Einschraubtiefe des Stiftes 42 wird damit auch der Stellstift 49 verstellt.The shaft 36 has a stepped bore 46, 47, in the part of the larger diameter 46 adjoining the suction chamber, an actuating pin 49 is coaxially guided and has a surface 50 in the form of a wedge on its end that projects into the pump suction chamber 4 , which protrudes into the recess 44 and works there with the shoulder 45. Depending on the immersion depth of the inclined surface 50 in the recess 44, the part 38 is displaced more or less far along the support arm 37 and thus the coil spring 21 is more or less pretensioned. To adjust the actuating pin 49, a pin 52 is guided through the stepped bore part 47, which is smaller in diameter, which presses on the end face of the actuating pin 49 and is screwed into a thread 53 in the shaft 36 from the outside. The screw-in position is fixed with the aid of a lock nut 54, which is screwed onto the end of the pin 52. Depending on the screw-in depth of the pin 42, the adjusting pin 49 is thus also adjusted.

Auch mit dieser Ausgestaltung läßt sich durch Einstellung der Schwenklage des Schwenkarmes 35 die Charakteristik der Schraubenfeder 21 im Regelsinne beeinflussen. Die Vorspannung wird unabhängig von der Schwenklage in einfacher Weise über den Stift 52 und den Stellstift 52 variiert. Auch durch diese Art des Eingriffs läßt sich in feinsten Schritten eine gewünschte Vorspannung einstellen. Man erhält einen sehr genau einstellbaren Regler, der für den Betrieb von Aggregatstriebwerken geeignet ist.With this configuration, too, the characteristic of the helical spring 21 can be influenced by adjusting the swivel position of the swivel arm 35. The pretension is varied in a simple manner via the pin 52 and the adjusting pin 52, regardless of the pivot position. This type of intervention can also be used to set a desired preload in the finest steps. A very precisely adjustable controller is obtained which is suitable for the operation of unit engines.

Statt einer keilförmig ausgebildeten Spitze des Stellstiftes 49 kann dieser auch eine kegelige Spitze 56 aufweisen, wie das in Figur 5 gezeigt ist. In diesem Falle spielt es keine Rolle, welche Drehlage der Stellstift 49 einnimmt und es kann anstelle der einzelnen Stifte 49 und 52 ein einziger Stellstift 49' verwendet werden, der zur Änderung der Einschraubtiefe verdreht und ebenfalls mit einer Kontermutter 54 gesichert wird.Instead of a wedge-shaped tip of the actuating pin 49, this can also have a conical tip 56, as shown in FIG. 5. In this case it does not matter which rotational position the adjusting pin 49 takes and instead of the individual pins 49 and 52 a single adjusting pin 49 'can be used, which is rotated to change the screw-in depth and is also secured with a lock nut 54.

Figur 6 zeigt eine weitere Ausführungsvariante, bei der wie beim Ausführungsbeispiel nach Figuren 3 und 4 der Schwenkarm 35' auf einer gleichermaßen wie bei Figur 3 ausgebildeten Welle 36 gelagert ist. Der Schwenkarm 35' besteht auch hier aus einem Trägerarm 37 und einem darauf verschiebbaren Teil 38', das ein erstes Langloch 39 und ein zweites Langloch 40 aufweist. Wie bei Figur 3 wird der verschiebbare Teil 38 über durch die Langlöcher 39 und 40 greifende Niete 41 und 42 mit dem Trägerarm 37 verbunden. Abweichend vom Ausführungsbeispiel nach Figur 3 hat jedoch der verschiebbare Teil 38' eine seitlich offene Ausnehmung 44', in die nun ein Zapfen 57 eingreift, der exzentrisch auf der Stirnseite eines Stellorgans 59 gelagert ist. Das Stellorgan 59 besteht aus einem Bolzen, der dicht in einer axialen Bohrung 60 in der Welle 36 gelagert ist. An die Bohrung 60 schließt sich nach außen eine Gewindebohrung 61 an, durch die der Gewindeteil 62 des Bolzens 59 geschraubt ist. Am nach außen die Welle 36 überragenden Ende des Gewindeteils 62 weist dieser eine Formschlußfläche 63 auf, über die der Bolzen 59 verdrehbar ist. Zur Sicherung der Drehstellung des Bolzens ist auf das Gewindeteil 62 eine Kontermutter 64 geschraubt. Auch bei deisem Ausführungsbeispiel ist die Welle 36 über den Verstellhebel 29 verdrehbar, womit die Schwenklage der Schraubenfeder 21 einstellbar ist. Durch Verstellung des Bolzens 59 und des Zapfens 57, der auf eine Schulter 65 an der Ausnehmung 44' greift, wird die Verschiebestellung des verschiebbaren Teils 38' bestimmt. Dabei ist von Vorteil, daß über die in der Breite dem Zapfendurchmesser des Zapfens 57 angepaßte Ausnehmung unabhängig von der Rückstellkraft der Feder 21 der verschiebbare Teil 38' sowohl hin- als auch herverstellbar ist. Wenn an der Stirnseite des Bolzens weiterhin auch noch eine Scheibe 66 aufgesetzt ist, auf der dann der Zapfen 57 sitzt, kann der Verstellbereich des verschiebbaren Teils gegenüber der Ausgestaltung nach Figur 4 noch vergrößert werden.FIG. 6 shows a further embodiment variant, in which, as in the exemplary embodiment according to FIGS. 3 and 4, the swivel arm 35 'is mounted on a shaft 36 designed in the same way as in FIG. Here, too, the swivel arm 35 'consists of a support arm 37 and a part 38' which can be moved thereon and which has a first elongated hole 39 and a second elongated hole 40. As in FIG. 3, the displaceable part 38 is connected to the support arm 37 via rivets 41 and 42 which extend through the elongated holes 39 and 40. In a departure from the exemplary embodiment according to FIG. 3, however, the displaceable part 38 'has a laterally open recess 44', into which a pin 57 now engages, which is mounted eccentrically on the end face of an actuator 59. The actuator 59 consists of a bolt which is mounted tightly in an axial bore 60 in the shaft 36. A threaded bore 61 adjoins the bore 60 to the outside, through which the threaded part 62 of the bolt 59 is screwed. At the end of the threaded part 62 projecting outwards from the shaft 36, the threaded part 62 has a form-fitting surface 63, via which the bolt 59 can be rotated. To secure the rotational position of the bolt, a lock nut 64 is screwed onto the threaded part 62. In this embodiment too, the shaft 36 can be rotated via the adjusting lever 29, whereby the swivel position of the helical spring 21 can be adjusted. By adjusting the bolt 59 and the pin 57, which engages on a shoulder 65 on the recess 44 ', the displacement position of the displaceable part 38' is determined. The advantage here is that the displaceable part 38 'can be moved back and forth independently of the restoring force of the spring 21 via the recess which is adapted to the width of the pin diameter of the pin 57. If a washer 66 is also placed on the end face of the bolt, on which the pin 57 is then seated, the adjustment range of the displaceable part can be increased compared to the embodiment according to FIG.

Claims (5)

1. Speed governor for fuel injection pumps having at least one governor lever (9, 14) to adjust the fuel quantity which is injected per pump piston stroke of the fuel injection pump, having a force as a function of the speed which engages the governor lever at least indirectly and having a governor spring arrangement (15), coupled on the one hand to a point on the governor lever, which is adjustable by a pivotable support arm (37) arranged on a shaft (26, 36) which is mounted in the housing of the fuel injection pump and passed out through a wall of the housing and exhibits an adjusting lever (29) there, which support arm (37) is coupled to a second part (38) adjustable thereon in the direction of the governor spring arrangement, to one end of which the governor spring arrangement is fastened and by the pivoting of which the angular position of the axis of the governor spring arrangement (25) to the initial position of the governor lever (14) and the pretension of the governor spring arrangement are variable, characterized in that the support arm (35, 35') is arranged inside the housing of the fuel injection pump and the second part is slidable on the support arm, is coupled to the support arm (37) by two slot and pin joints (39, 40, 41, 42) and is adjustable by an adjusting member (49, 52; 59) passed coaxially through the shaft (36).
2. Speed governor according to Claim 1, characterized in that the adjusting member is mounted slidably in the shaft and exhibits a surface (50, 56) inclined to the sliding direction of adjusting member (49) and slidable part (38) which engages a shoulder (45) on the slidable part (38), and an axial sliding position of the adjusting member (49, 52) to the shaft (36) is secured.
3. Speed governor according to Claim 1, characterized in that the adjusting member (59) is mounted rotatably in the shaft (36) and engages by an eccen- tricallly movable abutment surface (57) a shoulder (65, 44') on the slidable part (38') and the rotary po- sifion of the adjusting member (59) to the shaft is to be secured.
4. Speed governor according to either Claim 2 or 3, characterized in that the shoulder (45, 65) is a boundary edge of a recess (44, 44') in the slidable part (38, 38').
5. Speed governor according to one of the previous claims, characterized in that the point where the governor spring arrangement (15) is fastened to the bracing part (25, 35, 35') is located in the pivotal plane of the coupling point (22) of the governor spring arrangement on the governor lever (14).
EP86107316A 1985-06-22 1986-05-30 Speed governor for a fuel injection pump Expired EP0209681B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19853522434 DE3522434A1 (en) 1985-06-22 1985-06-22 SPEED REGULATOR FOR FUEL INJECTION PUMPS
DE3522434 1985-06-22

Publications (2)

Publication Number Publication Date
EP0209681A1 EP0209681A1 (en) 1987-01-28
EP0209681B1 true EP0209681B1 (en) 1989-09-20

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EP86107316A Expired EP0209681B1 (en) 1985-06-22 1986-05-30 Speed governor for a fuel injection pump

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EP (1) EP0209681B1 (en)
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DE (2) DE3522434A1 (en)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3744275A1 (en) * 1987-12-24 1989-07-13 Kloeckner Humboldt Deutz Ag Mechanical speed governor for an internal-combustion engine having an adjustable degree of irregularity
DE3829798A1 (en) * 1988-09-02 1990-03-08 Bosch Gmbh Robert FUEL INJECTION PUMP FOR INTERNAL COMBUSTION ENGINES
JPH02221646A (en) * 1989-02-21 1990-09-04 Yanmar Diesel Engine Co Ltd Governor device of engine

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE864781C (en) * 1948-05-15 1953-01-29 Porsche Konstruktionen G M B H Centrifugal governors for internal combustion engines, especially for motor vehicles
FR1188261A (en) * 1957-12-12 1959-09-21 Universal all-speed ball regulator, particularly for injection pumps
DE1120849B (en) * 1960-05-12 1961-12-28 Ammann A G U Vibrating mill
DE2342107A1 (en) * 1973-08-21 1975-02-27 Bosch Gmbh Robert SPEED REGULATOR FOR FUEL INJECTION PUMPS
JPS544583Y2 (en) * 1975-06-13 1979-02-27
DE3004035A1 (en) * 1980-02-05 1981-08-13 Robert Bosch Gmbh, 7000 Stuttgart CONTROL DEVICE FOR A FUEL INJECTION PUMP
DE3141518A1 (en) * 1981-10-20 1983-04-28 Robert Bosch Gmbh, 7000 Stuttgart Device for controlling the air-fuel ratio of the operating mixture to be introduced into the combustion chambers of a self-igniting internal combustion engine
JPS59184331U (en) * 1983-05-26 1984-12-07 株式会社ボッシュオートモーティブ　システム Fuel injection pump control lever shaft

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DE3522434A1 (en) 1987-01-02
JPS61294142A (en) 1986-12-24
DE3665752D1 (en) 1989-10-26
EP0209681A1 (en) 1987-01-28
JP2672296B2 (en) 1997-11-05

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