EP0624720B1 - Fuel injection pump for internal combustion engines - Google Patents

Fuel injection pump for internal combustion engines Download PDF

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Publication number
EP0624720B1
EP0624720B1 EP19940105646 EP94105646A EP0624720B1 EP 0624720 B1 EP0624720 B1 EP 0624720B1 EP 19940105646 EP19940105646 EP 19940105646 EP 94105646 A EP94105646 A EP 94105646A EP 0624720 B1 EP0624720 B1 EP 0624720B1
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EP
European Patent Office
Prior art keywords
lever
fuel injection
injection pump
adjusting
spring
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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EP19940105646
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German (de)
French (fr)
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EP0624720A1 (en
Inventor
Günter Dipl.-Ing. Bofinger
Claus Dipl.-Ing. Maier (Fh)
Willi Dipl.-Ing. Weippert (Fh)
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication date
Priority claimed from DE4332847A external-priority patent/DE4332847A1/en
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP0624720A1 publication Critical patent/EP0624720A1/en
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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
    • F02D1/045—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 characterised by arrangement of springs or weights
    • 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
    • F02D2001/0005—Details, component parts or accessories of centrifugal governors
    • F02D2001/002—Arrangement of governor springs
    • F02D2001/0025—Arrangement of governor springs having at least two springs, one of them being idling spring
    • 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
    • F02D2001/0005—Details, component parts or accessories of centrifugal governors
    • F02D2001/0045—Arrangement of means for influencing governor characteristics by operator

Definitions

  • the invention is based on a fuel injection pump for internal combustion engines according to the preamble of claim 1.
  • a fuel injection pump for internal combustion engines according to the preamble of claim 1.
  • Such a fuel injection pump known from EP-A-0 451 151, has a T-shaped adjusting lever on the outside of the pump housing, which has an adjusting lever for idling spring inside of the pump housing leading control shaft is connected and is pivotable about this as a pivot axis.
  • a Bowden cable is articulated at the base of the T-shaped adjusting lever and is actuated by a pneumatic servomotor depending on the operating states of the internal combustion engine.
  • the adjusting lever is provided in the known fuel injection pump on the outside of the housing of the fuel injection pump, which is adjustable between two stops and is actuated by a so-called accelerator cable to adjust the torque output of the internal combustion engine.
  • the adjusting lever is actuated by the servomotor in particular to raise the idle speed when additional units of the internal combustion engine are switched on.
  • the fuel injection pump according to the invention with the features of claim 1 has the advantage that, by coupling the adjusting lever with the adjusting lever, the idle speed can be set in certain operating ranges predetermined by the adjustment of the adjusting lever.
  • a desired fuel injection quantity or torque output can be achieved in particular in critical low speed ranges, as a result of which the running behavior of the internal combustion engine can be improved in such specific critical ranges.
  • the configuration according to claim 2 results in a favorable arrangement, which can also be retrofitted to an existing fuel injection pump, to achieve the idle setting according to claim 1.
  • the development of the invention according to claims 3 and 4 advantageously allows the degree of intervention in idling during the course vary the adjustment of the adjustment lever and adapt to the specific circumstances of the assigned internal combustion engine. Further adaptations are given by the configurations according to claim 5 and claim 6.
  • FIG. 1 shows a schematic arrangement of control spring, idle spring and control levers with a quantity adjusting element of a fuel injection pump
  • FIG. 2 shows the first exemplary embodiment of the invention with coupling of an adjusting lever with an adjusting lever of the fuel injection pump via a one-armed rocker arm
  • FIG. 3 shows the second exemplary embodiment of the invention with coupling via a two-armed rocker arm
  • Figure 4 shows a modified type of idle spring arrangement in the fuel injection pump.
  • a pump piston 1 In the interior of a fuel injection pump, as is known from EP-A-0 451 151, a pump piston 1 is arranged in a housing bore, which, but not shown here, delimits a pump work space in the housing bore, is driven to and fro as well as rotating and during its outward movement from the pump work space under injection pressure, the previously introduced fuel delivers to one of several injection lines determined by its rotational position.
  • the delivery stroke of the pump piston is ended under high pressure by opening a relief channel 2, which, starting from the pump working space in the pump piston 1, runs out via a radial bore 3 on the circumference of the pump piston and opens into the suction chamber surrounding the pump piston, which is filled with fuel brought to low pressure and out which the pump workspace is supplied with fuel during the suction stroke of the pump piston.
  • the relief of the relief channel 2 via the radial bore 3 takes place when the pump piston emerges in the form of a ring slide in the course of its delivery stroke, which goes to the right in the drawing, from the overlap of a quantity adjusting member 4 which can be displaced tightly on the pump piston 1.
  • the quantity adjustment element 4 is brought into its position determining the fuel injection quantity per pump piston stroke by means of a regulator lever 5 and is coupled to the latter via a coupling head 6.
  • the regulator lever 5 can be pivoted about an axis 7 against the force of an idle spring 8 attached to the end of the regulator lever 5, the other end of which is attached to an idle spring lever 9. This is via a shaft 10, which in no further leads out through the pump housing, connected to an adjusting lever 11, which is shown in more detail in Figure 2.
  • a centrifugal force adjuster 14 also acts on the control lever 5, by means of which the control lever is pivoted about the axis 7 with increasing speed and thus increasing force against the force of the idling spring 8.
  • the centrifugal force adjuster is a speed sensor that generates a speed-dependent force, and in addition to these mechanical speed sensors, other types of speed sensors can also be used, such as hydraulic or electromechanically operated sensors.
  • the governor lever is pivoted by the centrifugal force adjuster 14, possibly by overcoming an additional starting spring 15, which ensures that the quantity adjusting member 4 is in a starting position when the fuel injection pump is at a standstill and thus increases the fuel injection quantity, until the regulator lever 5 comes into contact with a tensioning lever 16. whose end position is determined by a stop 17 fixed to the housing.
  • This tensioning lever can also be pivoted about the axis 7 and a control spring 19 is articulated at its end, which in turn is attached to an adjusting lever 20.
  • the actuating lever 20 is actuated via an actuating shaft 21 which leads through the housing to the outside, an adjusting lever 22 being fastened to the outer end of the actuating shaft, which is also shown in greater detail in FIG.
  • the idle speed is determined with the aid of the centrifugal adjuster 14 for a given setting of the idle spring preload via the adjusting lever 11 and the idle spring actuating lever 9. If the preload of the idle spring 8 is overcome, the control lever 5 swings out and moves the ring slide 4, the quantity adjusting member, to the left (FIG. 1) and thus reduces the fuel injection quantity.
  • the control spring 19 is formed in the example shown as a compression spring with a matching spring, which are housed in a spring capsule, which is initially stable with a small applied force on the control spring unit as a fixed transmission member between the control lever 20 and rocker arm 16 such that with the adjustment of the control lever 20 different load positions can be set based on the full load position of the tensioning lever 16. Only when the final speed is reached is the force acting on the preloaded control spring 19 so great that the preload force of the clamped spring is overcome and the tensioning lever 16 can move independently of the position of the actuating lever 20.
  • the idle speed was initially fixed using the idle spring 8 and the adjusting lever 11, which was fixed by a stop 23, which is adjustable, the idle speed should now be variable by increasing the spring tension of the idle spring 8 within a predetermined range .
  • the adjusting lever 11 has a T-shaped configuration, the adjusting lever 11 in each case with one of the ends of the “T” crossbar 41 either at a first stop 23, which determines the lowest idling speed, or at a second stop 24, which determines the highest idling speed or the highest idling torque.
  • the T-shaped adjusting lever 11 is connected to the end of the shaft 10 in the region of its base point of the vertical T-line 42.
  • the adjusting lever 11 is acted on so that it strives to come to rest with its T-bar on the second stop 24.
  • This movement is controlled in that the adjusting lever 11 has in the middle of its T-bar a driving part in the form of a driving bolt 28 which projects transversely to the pivoting plane of the adjusting lever and engages in an elongated hole 29 of a drag lever 30.
  • the rocker arm 30 is provided at its end with a bearing 31 fixed to the housing and has an eye 32 at its outermost free end, through which an adjusting screw 33 lying in the pivoting plane of the rocker arm 30 is screwed and secured there with a nut.
  • the adjusting screw comes to rest on one arm 35 of an adjustment lever 22, which here has two arms and is fixedly connected in its center to the adjusting shaft 21.
  • the pivoting movement of the adjusting lever 22 is determined by a first adjusting lever stop 36 and a second adjusting lever stop 37, against which the adjusting lever 22 with its other lever arm 38 comes to rest when it is actuated with the aid of a Bowden cable 39 attached to the other lever arm 38 in accordance with an increasing torque request .
  • the second adjustment lever stop 37 is the full load stop.
  • the stops are adjustable in a known manner and fixable in their setting.
  • the rocker arm 30 follows the adjusting lever movement via the adjusting screw 33 under the influence of the force of the return spring 26 transmitted by means of the driving bolt 28 until the finger lever 30 pivots together with the adjusting lever 11 is that the adjusting lever with its left “T" bar as seen in the drawing comes to rest against the second stop 24.
  • This movement of the adjusting lever enables the coupling between rocker arm 30 and adjusting lever 11 by means of the driving bolt 28 and the elongated hole 29.
  • the additional Return spring 26 ensures that the adjusting screw 33 is constantly in contact with the adjusting lever 22 in this range of motion and guarantees the pivoting movement of the adjusting lever 11. This spring must overcome the force of the idle spring 8 with regard to FIG.
  • the frame can advantageously be determined by varying the idle injection quantity in the course of a load absorption caused by the adjustment of the adjusting lever 22.
  • the exact assignment of the rocker arm 30 to the adjusting lever 22 in the starting position is made possible by the adjusting screw 33.
  • the adjusting screw 33 when the adjusting screw 33 is actuated with the adjusting lever 22 resting on the first adjusting lever stop 36, the adjusting lever 11 can be brought to the first, the minimum stop 23 under the action of the return spring 26 is, the adjusting screw 33 can also serve directly as a stop for the minimum setting of the idle spring preload and replace the stop 23.
  • the driving pin 28 is inserted into another threaded bore in the adjusting lever 11, which additionally enables the elongated hole 29.
  • threaded bores in the adjusting lever 11 which are introduced at different distances from the shaft 10.
  • the entrainment parts, the entrainment pin 28 or the pin 40 were firmly connected to the adjusting lever 11 or 111 and the curve 39 or the elongated hole 29 realizing two parallel cam tracks was carried out on the drag lever 30, 131.
  • this can also be the other way round, also the guideways delimiting the elongated hole and coupling the driving pin 28 by positive locking can be one do not follow a straight curve.
  • FIG. 3 Another possibility of varying the idle speed by increasing the spring tension of the idle spring 8 within a predetermined range is the embodiment according to FIG. 3.
  • This two-armed rocker arm 130 in turn has at one end the eye 32 through which the adjusting screw 33 can be screwed, secured by a nut.
  • this adjusting screw can of course also be attached to the adjusting lever 22, which then acts on the end 32 of the two-armed rocker arm 130.
  • the other end of the two-armed rocker arm 130 has a cam track 39 on which a bolt 40 can slide, which projects vertically from the pivoting plane of the T-shaped adjusting lever 111.
  • this has a "T" crossbar 41, from which the arm 42 forming the vertical T-line of the T-shaped configuration protrudes at right angles.
  • the adjusting lever 111 is now firmly mounted on the shaft 10 at the transition from this arm 42 to the "T" crossbar 41.
  • the bolt 40 protrudes from the extreme end of the arm 42.
  • the adjusting lever 111 thus forms a three-armed lever, the shape of which can of course also be somewhat different from the T-shape.
  • a return spring 43 is attached to this one of its arms, which strives to pivot the rocker arm 130 about its axis 131 and to keep it in contact with the adjusting lever 22.
  • a return spring 126 also acts on the adjusting lever 111, which endeavors to pivot the adjusting lever 111 in such a way that the bolt 40 in Contact with cam track 39 remains.
  • the adjusting lever is again adjustable between the stops 23 and 24, so that with these stops the pretension of the idle spring 8 coupled to the locking lever 111 is determined.
  • the position of the adjusting screw 33 can be corrected accordingly so that the rocker arm 130 limited in its pivoting movement by its abutment on the bolt 40 is in abutment with the adjusting lever 22 via the adjusting screw 33 when the latter is on its first Adjustment lever stop is located according to its minimum setting. If the adjusting lever 22 is now adjusted in the direction of the excess quantity, the return spring 43, which acts on the rocker arm 130, causes the rocker arm 130 to follow the adjusting lever.
  • This return spring 43 overrides the return spring 126 and the adjusting lever 111 is now also pivoted in accordance with the pivoting movement of the rocker arm 130, namely until it comes into contact with the stop 24 with its “T” crossbar 41.
  • the adjusting lever 22 then lifts off the adjusting screw 33 and performs its other quantity-adjusting function.
  • the return spring 43 is thus designed so that it overcomes the force of the return spring 126, which serves to adjust the adjusting lever 111 and at the same time is stronger than the idle spring 8, which is subsequently biased.
  • FIG. 4 shows an embodiment variant of the arrangement of the idle spring in the regulator of the fuel injection pump.
  • the control spring is attached to the tensioning lever 16 so that it is acted upon by both the idle spring 8 and the control spring arrangement 19.
  • the control lever 5 serves only as a start lever for adjustment and subsequently to limit the excess starting quantity by the starting spring 15 being compressed by the centrifugal force adjuster 14 until the starting lever 5 comes to rest against the tensioning lever 16 and both levers can now be adjusted in combination by the centrifugal force adjuster.
  • the control spring arrangement 19 is set at the lowest load in accordance with the idling so that only the idling spring 8 is effective on the tensioning lever 16. Only after the idle speed has been exceeded does the tensioning lever 16 come into firm contact with the control spring arrangement 19, a further adjustment spring 44 being adjustable between the connection point of this control spring arrangement 19 and the tensioning lever.

Description

Stand der TechnikState of the art

Die Erfindung geht aus von einer Kraftstoffeinspritzpumpe für Brennkraftmaschinen nach der Gattung des Patentanspruchs 1. Eine solche durch die EP-A-0 451 151 bekannte Kraftstoffeinspritzpumpe weist auf der Außenseite des Pumpengehäuses einen T-förmig gestalteten Einstellhebel auf, der mit einer zum Leerlauffederstellhebel im Innern des Pumpengehäuses führenden Stellwelle verbunden ist und um diese als Schwenkachse schwenkbar ist. Dabei ist am Fußpunkt des T-förmigen Einstellhebels ein Bowdenzug angelenkt, der von einem pneumatischen Stellmotor in Abhängigkeit von Betriebszuständen der Brennkraftmaschine betätigt wird. Unabhängig von diesem Einstellhebel ist bei der bekannten Kraftstoffeinspritzpumpe außen am Gehäuse der Kraftstoffeinspritzpumpe der Verstellhebel vorgesehen, der zwischen zwei Anschlägen verstellbar ist und durch einen sogenannten Gaszug zur Einstellung der Drehmomentabgabe der Brennkraftmaschine betätigt wird.The invention is based on a fuel injection pump for internal combustion engines according to the preamble of claim 1. Such a fuel injection pump, known from EP-A-0 451 151, has a T-shaped adjusting lever on the outside of the pump housing, which has an adjusting lever for idling spring inside of the pump housing leading control shaft is connected and is pivotable about this as a pivot axis. A Bowden cable is articulated at the base of the T-shaped adjusting lever and is actuated by a pneumatic servomotor depending on the operating states of the internal combustion engine. Regardless of this setting lever, the adjusting lever is provided in the known fuel injection pump on the outside of the housing of the fuel injection pump, which is adjustable between two stops and is actuated by a so-called accelerator cable to adjust the torque output of the internal combustion engine.

Der Einstellhebel wird dabei durch den Stellmotor insbesondere zur Anhebung der Leerlaufdrehzahl bei Zuschalten von Zusatzaggregaten der Brennkraftmaschine betätigt.The adjusting lever is actuated by the servomotor in particular to raise the idle speed when additional units of the internal combustion engine are switched on.

Vorteile der ErfindungAdvantages of the invention

Die erfindungsgemäße Kraftstoffeinspritzpumpe mit den Merkmalen des Patentanspruchs 1 hat demgegenüber den Vorteil, daß durch die Koppelung des Einstellhebels mit dem Verstellhebel der Leerlauf in bestimmten, durch die Einstellung des Verstellhebels vorgegebenen Betriebsbereichen eingestellt werden kann. Dabei kann insbesondere in kritischen geringen Drehzahlbereichen eine gewünschte Kraftstoffeinspritzmenge bzw. Drehmomentabgabe erzielt werden, wodurch das Laufverhalten der Brennkraftmaschine in solchen bestimmten kritischen Bereichen verbessert werden kann.The fuel injection pump according to the invention with the features of claim 1 has the advantage that, by coupling the adjusting lever with the adjusting lever, the idle speed can be set in certain operating ranges predetermined by the adjustment of the adjusting lever. A desired fuel injection quantity or torque output can be achieved in particular in critical low speed ranges, as a result of which the running behavior of the internal combustion engine can be improved in such specific critical ranges.

Durch die Ausgestaltung gemäß Patentanspruch 2 ergibt sich eine günstige, ggf. auch bei einer vorhandenen Kraftstoffeinspritzpumpe nachrüstbare Anordnung zur Erzielung der Leerlaufeinstellung gemäß Patentanspruch 1. Durch die Weiterbildung der Erfindung gemäß Patentanspruch 3 und 4 läßt sich vorteilhaft der Grad des Eingriffes auf den Leerlauf im Laufe der Verstellung des Verstellhebels variieren und speziellen Gegebenheiten der zugeordneten Brennkraftmaschine anpassen. Weitere Anpassungsmöglichkeiten sind durch die Ausgestaltungen gemäß Patentanspruch 5 und Patentanspruch 6 gegeben.The configuration according to claim 2 results in a favorable arrangement, which can also be retrofitted to an existing fuel injection pump, to achieve the idle setting according to claim 1. The development of the invention according to claims 3 and 4 advantageously allows the degree of intervention in idling during the course vary the adjustment of the adjustment lever and adapt to the specific circumstances of the assigned internal combustion engine. Further adaptations are given by the configurations according to claim 5 and claim 6.

Zeichnungdrawing

Zwei Ausführungsbeispiele des Gegenstands der Erfindung sind in der Zeichnung dargestellt, und werden im nachstehenden näher erläutert. Es zeigen Figur 1 eine schematische Anordnung von Regelfeder, Leerlauffeder und Regelhebeln mit Mengenverstellorgan einer Kraftstoffeinspritzpumpe, Figur 2 das erste Ausführungsbeispiel der Erfindung mit Kopplung eines Einstellhebels mit einem Verstellhebel der Kraftstoffeinspritzpumpe über einen einarmigen Schlepphebel, Figur 3 das zweite Ausführungsbeispiel der Erfindung mit Koppelung über einen zweiarmigen Schlepphebel und Figur 4 eine abgewandelte Art der Leerlauffederanordnung bei der Kraftstoffeinspritzpumpe.Two embodiments of the object of the invention are shown in the drawing and are explained in more detail below. FIG. 1 shows a schematic arrangement of control spring, idle spring and control levers with a quantity adjusting element of a fuel injection pump, FIG. 2 shows the first exemplary embodiment of the invention with coupling of an adjusting lever with an adjusting lever of the fuel injection pump via a one-armed rocker arm, FIG. 3 shows the second exemplary embodiment of the invention with coupling via a two-armed rocker arm and Figure 4 shows a modified type of idle spring arrangement in the fuel injection pump.

Im Innern einer Kraftstoffeinspritzpumpe, wie sie durch die EP-A-0 451 151 bekannt ist, ist in einer Gehäusebohrung ein Pumpenkolben 1 angeordnet, der, hier aber nicht dargestellt, in der Gehäusebohrung einen Pumpenarbeitsraum begrenzt, hin- und hergehend sowie rotierend angetrieben ist und bei seiner Hinbewegung aus dem Pumpenarbeitsraum unter Einspritzdruck den zuvor eingebrachten Kraftstoff zu einer von mehreren, durch seine Drehstellung bestimmten Einspritzleitung fördert. Die Beendigung des Förderhubs des Pumpenkolbens unter Hochdruck erfolgt durch Aufsteuern eines Entlastungskanals 2, der ausgehend vom Pumpenarbeitsraum im Pumpenkolben 1 verlaufend über eine Radialbohrung 3 am Pumpenkolbenumfang austritt und in den den Pumpenkolben dort umgebenden Saugraum mündet, der mit auf Niederdruck gebrachtem Kraftstoff gefüllt ist und aus dem der Pumpenarbeitsraum beim Saughub des Pumpenkolbens mit Kraftstoff versorgt wird. Die Entlastung des Entlastungskanals 2 über die Radialbohrung 3 erfolgt dann, wenn der Pumpenkolben im Laufe seines, in der Zeichnung nach rechts gehenden, Förderhubs aus der Überdeckung eines dicht auf dem Pumpenkolben 1 verschiebbaren Mengenverstellorgans 4 in Form eines Ringschiebers austritt.In the interior of a fuel injection pump, as is known from EP-A-0 451 151, a pump piston 1 is arranged in a housing bore, which, but not shown here, delimits a pump work space in the housing bore, is driven to and fro as well as rotating and during its outward movement from the pump work space under injection pressure, the previously introduced fuel delivers to one of several injection lines determined by its rotational position. The delivery stroke of the pump piston is ended under high pressure by opening a relief channel 2, which, starting from the pump working space in the pump piston 1, runs out via a radial bore 3 on the circumference of the pump piston and opens into the suction chamber surrounding the pump piston, which is filled with fuel brought to low pressure and out which the pump workspace is supplied with fuel during the suction stroke of the pump piston. The relief of the relief channel 2 via the radial bore 3 takes place when the pump piston emerges in the form of a ring slide in the course of its delivery stroke, which goes to the right in the drawing, from the overlap of a quantity adjusting member 4 which can be displaced tightly on the pump piston 1.

Das Mengenverstellorgan 4 wird mittels eines Reglerhebels 5 in seine die Kraftstoffeinspritzmenge pro Pumpenkolbenhub bestimmende Stellung gebracht und ist über einen Kupplungskopf 6 mit diesem gekoppelt. Der Reglerhebel 5 ist um eine Achse 7 schwenkbar und zwar gegen die Kraft einer am Ende des Reglerhebels 5 angehängten Leerlauffeder 8, deren anderes Ende an einem Leerlauffederstellhebel 9 befestigt ist. Dieser ist über eine Welle 10, die in nicht weiter dargestellter Weise durch das Pumpengehäuse nach außen führt, mit einem Verstellhebel 11 verbunden, der in Figur 2 näher dargestellt ist. Am Reglerhebel 5 greift ferner ein Fliehkraftversteller 14 an, durch den der Reglerhebel mit zunehmender Drehzahl und somit zunehmender Kraft entgegen der Kraft der Leerlauffeder 8 um die Achse 7 geschwenkt wird. Der Fliehkraftversteller stellt einen Drehzahlgeber dar, der eine drehzahlabhängige Kraft erzeugt, wobei außer diesen mechanischen Drehzahlgebern auch andere Arten von Drehzahlgebern Anwendung finden können, wie hydraulische oder elektromechanisch betriebene Geber. Durch den Fliehkraftversteller 14 wird der Reglerhebel ggf. unter Überwindung einer zusätzlichen Startfeder 15, die für eine Startstellung des Mengenverstellorgans 4 beim Stillstand für die Kraftstoffeinspritzpumpe sorgt und somit für eine erhöhte Kraftstoffeinspritzmenge, geschwenkt, bis der Reglerhebel 5 zur Anlage an einen Spannhebel 16 kommt, dessen Endlage durch einen gehäusefesten Anschlag 17 bestimmt ist. Dieser Spannhebel ist ebenfalls um die Achse 7 schwenkbar und es ist an seinem Ende eine Regelfeder 19 angelenkt, die andererseits wiederum an einem Stellhebel 20 befestigt ist. Der Stellhebel 20 wird über eine Stellwelle 21, die durch das Gehäuse nach außen führt, betätigt, wobei am außenliegenden Ende der Stellwelle ein Verstellhebel 22 befestigt ist, der ebenfalls in Figur 2 näher dargestellt ist.The quantity adjustment element 4 is brought into its position determining the fuel injection quantity per pump piston stroke by means of a regulator lever 5 and is coupled to the latter via a coupling head 6. The regulator lever 5 can be pivoted about an axis 7 against the force of an idle spring 8 attached to the end of the regulator lever 5, the other end of which is attached to an idle spring lever 9. This is via a shaft 10, which in no further leads out through the pump housing, connected to an adjusting lever 11, which is shown in more detail in Figure 2. A centrifugal force adjuster 14 also acts on the control lever 5, by means of which the control lever is pivoted about the axis 7 with increasing speed and thus increasing force against the force of the idling spring 8. The centrifugal force adjuster is a speed sensor that generates a speed-dependent force, and in addition to these mechanical speed sensors, other types of speed sensors can also be used, such as hydraulic or electromechanically operated sensors. The governor lever is pivoted by the centrifugal force adjuster 14, possibly by overcoming an additional starting spring 15, which ensures that the quantity adjusting member 4 is in a starting position when the fuel injection pump is at a standstill and thus increases the fuel injection quantity, until the regulator lever 5 comes into contact with a tensioning lever 16. whose end position is determined by a stop 17 fixed to the housing. This tensioning lever can also be pivoted about the axis 7 and a control spring 19 is articulated at its end, which in turn is attached to an adjusting lever 20. The actuating lever 20 is actuated via an actuating shaft 21 which leads through the housing to the outside, an adjusting lever 22 being fastened to the outer end of the actuating shaft, which is also shown in greater detail in FIG.

Bei Niedriglastbetrieb wird mit Hilfe des Fliehkraftverstellers 14 bei gegebener Einstellung der Leerlauf federvorspannung über den Einstellhebel 11 und den Leerlauffederstellhebel 9 die Leerlaufdrehzahl bestimmt. Wird die Vorspannung der Leerlauffeder 8 überwunden, schwenkt der Reglerhebel 5 aus und verschiebt den Ringschieber 4, das Mengenverstellorgan, nach links (Figur 1) und reduziert somit die Kraftstoffeinspritzmenge. Unter Lastbetrieb liegt der Reglerhebel 5 voll am Schlepphebel 16 an, wobei insbesondere bei Vollastbetrieb der Spannhebel 16 durch die Einstellung der Regelfeder 19 am Vollastanschlag 17 gehalten wird, bis die Endabregeldrehzahl erreicht wird, bei der die vorgespannte Regelfeder 19 komprimiert wird und der Spannhebel 16 zusammen mit dem Reglerhebel 5 im Uhrzeigersinn, bezogen auf die Zeichnung, ausgelenkt wird. Damit wird wiederum die Kraftstoffeinspritzmenge reduziert.In low-load operation, the idle speed is determined with the aid of the centrifugal adjuster 14 for a given setting of the idle spring preload via the adjusting lever 11 and the idle spring actuating lever 9. If the preload of the idle spring 8 is overcome, the control lever 5 swings out and moves the ring slide 4, the quantity adjusting member, to the left (FIG. 1) and thus reduces the fuel injection quantity. Under load operation, the control lever 5 is in full contact with the rocker arm 16, the tensioning lever 16 being in particular at full load operation due to the setting of the control spring 19 Full load stop 17 is held until the final control speed is reached, at which the prestressed control spring 19 is compressed and the tensioning lever 16 is deflected together with the control lever 5 in a clockwise direction, based on the drawing. This in turn reduces the fuel injection quantity.

Die Regelfeder 19 ist im ausgeführten Beispiel als Druckfeder ausgebildet mit einer Angleichfeder, die in einer Federkapsel untergebracht sind, wobei diese zunächst bei geringer aufgebrachter Kraft auf die Regelfedereinheit stabil als festes Übertragungsglied zwischen Stellhebel 20 und Schlepphebel 16 liegt derart, daß mit dem Verstellen des Stellhebels 20 ausgehend von der Vollastlage des Spannhebels 16 verschiedene Laststellungen eingestellt werden können. Erst bei Erreichen der Enddrehzahl ist die Kraft, die auf die vorgespannte Regelfeder 19 wirkt, so groß, daß die Vorspannkraft der eingespannten Feder überwunden wird und sich der Spannhebel 16 unabhängig von der Stellung des Stellhebels 20 bewegen kann.The control spring 19 is formed in the example shown as a compression spring with a matching spring, which are housed in a spring capsule, which is initially stable with a small applied force on the control spring unit as a fixed transmission member between the control lever 20 and rocker arm 16 such that with the adjustment of the control lever 20 different load positions can be set based on the full load position of the tensioning lever 16. Only when the final speed is reached is the force acting on the preloaded control spring 19 so great that the preload force of the clamped spring is overcome and the tensioning lever 16 can move independently of the position of the actuating lever 20.

Während bei bisherigen Pumpen zunächst die Leerlaufdrehzahl mit Hilfe der Leerlauffeder 8 und des Einstellhebels 11 fest eingestellt war, indem dieser durch einen Anschlag 23, der einstellbar ist fixiert wurde, soll nun die Leerlaufdrehzahl durch Erhöhung der Federspannung der Leerlauffeder 8 in einem vorgegebenen Rahmen variabel sein. Gemäß der Figur 2 weist der Einstellhebel 11 eine T-förmige Konfiguration auf, wobei der Einstellhebel 11 jeweils mit einem der Enden des "T"-Querbalkens 41 entweder an einem ersten Anschlag 23, der die kleinste Leerlaufdrehzahl bestimmt oder an einem zweiten Anschlag 24, der die höchste Leerlaufdrehzahl oder das höchste Leerlaufdrehmoment bestimmt, zur Anlage kommt. Der T-förmige Einstellhebel 11 ist dabei im Bereich seines Fußpunktes des senkrechten T-Striches 42 mit dem Ende der Welle 10 verbunden.While in previous pumps, the idle speed was initially fixed using the idle spring 8 and the adjusting lever 11, which was fixed by a stop 23, which is adjustable, the idle speed should now be variable by increasing the spring tension of the idle spring 8 within a predetermined range . According to FIG. 2, the adjusting lever 11 has a T-shaped configuration, the adjusting lever 11 in each case with one of the ends of the “T” crossbar 41 either at a first stop 23, which determines the lowest idling speed, or at a second stop 24, which determines the highest idling speed or the highest idling torque. The T-shaped adjusting lever 11 is connected to the end of the shaft 10 in the region of its base point of the vertical T-line 42.

Durch eine außenliegende zusätzliche Rückstellfeder 26 wird der Einstellhebel 11 so beaufschlagt, daß er bestrebt ist mit seinem T-Balken am zweiten Anschlag 24 zur Anlage zu kommen. Diese Bewegung wird dadurch kontrolliert, daß der Einstellhebel 11 in der Mitte seines T-Balkens ein Mitnahmeteil in Form eines Mitnahmebolzens 28 aufweist, der quer zur Schwenkebene des Einstellhebels absteht und in ein Langloch 29 eines Schlepphebels 30 eingreift. Der Schlepphebel 30 ist an seinem Ende mit einer gehäusefesten Lagerung 31 versehen und weist an seinem äußersten freien Ende ein Auge 32 auf, durch das eine in der Schwenkebene des Schlepphebels 30 liegende Einstellschraube 33 geschraubt ist und dort mit einer Mutter gesichert ist. Die Einstellschraube kommt zur Anlage an den einen Arm 35 eines hier zweiarmig ausgebildeten Verstellhebels 22, der in seiner Mitte mit der Stellwelle 21 fest verbunden ist. Die Schwenkbewegung des Verstellhebels 22 wird bestimmt durch einen ersten Verstellhebelanschlag 36 und einem zweiten Verstellhebelanschlag 37, an den der Verstellhebel 22 mit seinem anderen Hebelarm 38 zur Anlage kommt, wenn er mit Hilfe eines am anderen Hebelarm 38 eingehängten Bowdenzugs 39 entsprechend einem zunehmenden Drehmomentwunsch betätigt wird. Der zweite Verstellhebelanschlag 37 ist dabei der Vollastanschlag. Die Anschläge sind in bekannter Weise einstellbar und in ihrer Einstellung fixierbar. Ausgehend von einer Stellung des Verstellhebels 22 von seinem die Minimaleinspritzmenge bestimmenden ersten Anschlag 36 folgt der Schlepphebel 30 der Verstellhebelbewegung über die Einstellschraube 33 unter Einwirkung der mittels des Mitnahmebolzens 28 übertragenen Kraft der Rückstellfeder 26 solange, bis der Schlepphebel 30 zusammen mit dem Einstellhebel 11 so verschwenkt ist, daß der Einstellhebel mit seinem in der Zeichnung gesehen linken "T"-Balken zur Anlage an den zweiten Anschlag 24 gelangt. Diese Bewegung des Einstellhebels ermöglicht die Kupplung zwischen Schlepphebel 30 und Einstellhebel 11 mittels des Mitnahmebolzens 28 und dem Langloch 29. Die zusätzliche Rückstellfeder 26 sorgt dabei dafür, daß die Einstellschraube 33 in diesem Bewegungsbereich ständig in Anlage an dem Verstellhebel 22 ist und garantiert die Schwenkbewegung des Einstellhebels 11. Dabei muß diese Feder im Hinblick auf die Figur 1 die Kraft der Leerlauffeder 8 überwinden.By an external return spring 26, the adjusting lever 11 is acted on so that it strives to come to rest with its T-bar on the second stop 24. This movement is controlled in that the adjusting lever 11 has in the middle of its T-bar a driving part in the form of a driving bolt 28 which projects transversely to the pivoting plane of the adjusting lever and engages in an elongated hole 29 of a drag lever 30. The rocker arm 30 is provided at its end with a bearing 31 fixed to the housing and has an eye 32 at its outermost free end, through which an adjusting screw 33 lying in the pivoting plane of the rocker arm 30 is screwed and secured there with a nut. The adjusting screw comes to rest on one arm 35 of an adjustment lever 22, which here has two arms and is fixedly connected in its center to the adjusting shaft 21. The pivoting movement of the adjusting lever 22 is determined by a first adjusting lever stop 36 and a second adjusting lever stop 37, against which the adjusting lever 22 with its other lever arm 38 comes to rest when it is actuated with the aid of a Bowden cable 39 attached to the other lever arm 38 in accordance with an increasing torque request . The second adjustment lever stop 37 is the full load stop. The stops are adjustable in a known manner and fixable in their setting. Starting from a position of the adjusting lever 22 from its first stop 36 which determines the minimum injection quantity, the rocker arm 30 follows the adjusting lever movement via the adjusting screw 33 under the influence of the force of the return spring 26 transmitted by means of the driving bolt 28 until the finger lever 30 pivots together with the adjusting lever 11 is that the adjusting lever with its left "T" bar as seen in the drawing comes to rest against the second stop 24. This movement of the adjusting lever enables the coupling between rocker arm 30 and adjusting lever 11 by means of the driving bolt 28 and the elongated hole 29. The additional Return spring 26 ensures that the adjusting screw 33 is constantly in contact with the adjusting lever 22 in this range of motion and guarantees the pivoting movement of the adjusting lever 11. This spring must overcome the force of the idle spring 8 with regard to FIG.

Durch Einstellung der Anschläge 23 und 24 kann in vorteilhafter Weise der Rahmen bestimmt werden indem die Leerlaufeinspritzmenge variiert wird im Laufe einer durch die Verstellung des Verstellhebels 22 bewirkten Lastaufnahme. Die exakte Zuordnung des Schlepphebels 30 zum Verstellhebel 22 in Ausgangslage ermöglicht die Einstellschraube 33. Da beispielsweise mit der Betätigung der Einstellschraube 33 bei am ersten Verstellhebelanschlag 36 anliegenden Verstellhebel 22 der Einstellhebel 11 unter Einwirkung der Rückstellfeder 26 an den ersten, den Minimal-Anschlag 23 bringbar ist, kann die Einstellschraube 33 auch direkt als Anschlag für die Minimaleinstellung der Leerlauffedervorspannung dient und den Anschlag 23 ersetzen. Weiterhin besteht die Möglichkeit das Übersetzungsverhältnis zwischen Verstellbewegung des Einstellhebels 11 und Verstellbewegung des Verstellhebels 22 zu verändern, indem die Lage des Mitnahmebolzens 28 zur Welle 10 verändert wird. Der Mitnahmebolzen 28 wird dabei in eine andere Gewindebohrung im Einstellhebel 11 eingesetzt, was das Langloch 29 zusätzlich ermöglicht. Im Einstellhebel 11 befinden sich hierzu Gewindebohrungen die in unterschiedlichem Abstand zur Welle 10 eingebracht sind. Bei den beschriebenen Ausführungsbeispielen waren die Mitnahmeteile, der Mitnahmebolzen 28 oder der Bolzen 40 fest mit dem Einstellhebel 11 bzw. 111 verbunden und die Kurve 39 oder das zwei parallele Kurvenbahn verwirklichende Langloch 29 auf dem Schlepphebel 30, 131 ausgeführt. Natürlich kann das auch umgekehrt sein, auch können die das Langloch begrenzenden, den Mitnahmebolzen 28 durch Formschluß koppelnden Führungsbahnen einer nicht geradlinigen Kurve folgen.By adjusting the stops 23 and 24, the frame can advantageously be determined by varying the idle injection quantity in the course of a load absorption caused by the adjustment of the adjusting lever 22. The exact assignment of the rocker arm 30 to the adjusting lever 22 in the starting position is made possible by the adjusting screw 33. For example, when the adjusting screw 33 is actuated with the adjusting lever 22 resting on the first adjusting lever stop 36, the adjusting lever 11 can be brought to the first, the minimum stop 23 under the action of the return spring 26 is, the adjusting screw 33 can also serve directly as a stop for the minimum setting of the idle spring preload and replace the stop 23. Furthermore, there is the possibility of changing the transmission ratio between the adjusting movement of the adjusting lever 11 and the adjusting movement of the adjusting lever 22 by changing the position of the driving bolt 28 relative to the shaft 10. The driving pin 28 is inserted into another threaded bore in the adjusting lever 11, which additionally enables the elongated hole 29. For this purpose there are threaded bores in the adjusting lever 11 which are introduced at different distances from the shaft 10. In the exemplary embodiments described, the entrainment parts, the entrainment pin 28 or the pin 40 were firmly connected to the adjusting lever 11 or 111 and the curve 39 or the elongated hole 29 realizing two parallel cam tracks was carried out on the drag lever 30, 131. Of course, this can also be the other way round, also the guideways delimiting the elongated hole and coupling the driving pin 28 by positive locking can be one do not follow a straight curve.

Eine andere Möglichkeit, die Leerlaufdrehzahl durch Erhöhung der Federspannung der Leerlauffeder 8 in einem vorgegebenen Rahmen zu variieren besteht in der Ausgestaltung gemäß Figur 3. Diese unterscheidet sich von der Ausgestaltung nach Figur 2 dadurch, daß statt eines einarmigen Schlepphebels 30 nun ein zweiarmiger Schlepphebel 130 vorgesehen ist, der um eine mittlere Achse 131 schwenkbar ist. Dieser zweiarmige Schlepphebel 130 weist an seinem einen Ende wiederum das Auge 32 auf, durch das die Einstellschraube 33 geschraubt werden kann mit Sicherung durch eine Mutter. In technischer Äquivalenz ist natürlich diese Einstellschraube auch auf dem Verstellhebel 22 anbringbar, die dann auf das Ende 32 des zweiarmigen Schlepphebels 130 wirkt. Das andere Ende des zweiarmigen Schlepphebels 130 weist eine Kurvenbahn 39 auf, auf der ein Bolzen 40 gleiten kann, der senkrecht aus der Schwenkebene des T-förmigen Einstellhebels 111 herausragt. Dieser weist wie auch beim ersten Ausführungsbeispiel nach Figur 2 einen "T"-Querbalken 41 auf, von dem rechtwinklig der den senkrechten T-Strich der T-förmigen Konfiguration bildende Arm 42 absteht. Der Einstellhebel 111 ist nun am Übergang dieses Armes 42 zum "T"-Querbalken 41 fest auf der Welle 10 gelagert. Der Bolzen 40 steht dabei am äußersten Ende des Armes 42 ab. Der Einstellhebel 111 bildet somit einen dreiarmigen Hebel, der in seiner Form natürlich auch etwas von der T-Form abweichend gestaltet sein kann.Another possibility of varying the idle speed by increasing the spring tension of the idle spring 8 within a predetermined range is the embodiment according to FIG. 3. This differs from the embodiment according to FIG. 2 in that a two-armed rocker arm 130 is now provided instead of a one-armed rocker arm 30 which is pivotable about a central axis 131. This two-armed rocker arm 130 in turn has at one end the eye 32 through which the adjusting screw 33 can be screwed, secured by a nut. In technical equivalence, this adjusting screw can of course also be attached to the adjusting lever 22, which then acts on the end 32 of the two-armed rocker arm 130. The other end of the two-armed rocker arm 130 has a cam track 39 on which a bolt 40 can slide, which projects vertically from the pivoting plane of the T-shaped adjusting lever 111. As in the first exemplary embodiment according to FIG. 2, this has a "T" crossbar 41, from which the arm 42 forming the vertical T-line of the T-shaped configuration protrudes at right angles. The adjusting lever 111 is now firmly mounted on the shaft 10 at the transition from this arm 42 to the "T" crossbar 41. The bolt 40 protrudes from the extreme end of the arm 42. The adjusting lever 111 thus forms a three-armed lever, the shape of which can of course also be somewhat different from the T-shape.

Zur Nachführung des zweiarmigen Schlepphebels 130 ist an diesem einem seiner Arme eine Rückstellfeder 43 befestigt, die bestrebt ist, den Schlepphebel 130 um seine Achse 131 zu schwenken und in Kontakt mit dem Verstellhebel 22 zu halten. Auch am Einstellhebel 111 greift wiederum eine Rückstellfeder 126 an, die bestrebt ist, den Einstellhebel 111 so zu verschwenken, daß der Bolzen 40 in Kontakt mit der Kurvenbahn 39 bleibt.To track the two-armed rocker arm 130, a return spring 43 is attached to this one of its arms, which strives to pivot the rocker arm 130 about its axis 131 and to keep it in contact with the adjusting lever 22. A return spring 126 also acts on the adjusting lever 111, which endeavors to pivot the adjusting lever 111 in such a way that the bolt 40 in Contact with cam track 39 remains.

Wie im vorstehenden Ausführungsbeispiel nach Figur 2 ist der Einstellhebel wiederum zwischen den Anschlägen 23 und 24 verstellbar, so daß mit diesen Anschlägen die Vorspannung der mit dem Feststellhebel 111 gekoppelten Leerlauffeder 8 bestimmt wird. Bei einer Verstellung des Anschlags 23 kann entsprechend die Lage der Einstellschraube 33 so korrigiert werden, daß der in seiner Schwenkbewegung durch seine Anlage an den Bolzen 40 begrenzte Schlepphebel 130 über die Einstellschraube 33 in Anlage an dem Verstellhebel 22 ist, wenn dieser sich an seinem ersten Verstellhebelanschlag entsprechend seiner Minimaleinstellung befindet. Wird der Verstellhebel 22 nun in Richtung Mehrmenge verstellt, so bewirkt die Rückstellfeder 43, die am Schlepphebel 130 angreift, daß der Schlepphebel 130 dem Verstellhebel folgt. Diese Rückstellfeder 43 überspielt die Rückstellfeder 126 und es wird entsprechend der Schwenkbewegung des Schlepphebels 130 nun auch der Einstellhebel 111 geschwenkt und zwar solange, bis dieser mit seinem "T"-Querbalken 41 in Anlage an den Anschlag 24 kommt. Danach hebt der Verstellhebel 22 von der Einstellschraube 33 ab und führt seine sonstige mengenverstellende Funktion durch. Die Rückstellfeder 43 ist dabei also so ausgebildet, daß sie die Kraft der Rückstellfeder 126, die zur Nachführung des Verstellhebels 111 dient überwindet und zugleich auch stärker ist als die Leerlauffeder 8, die in der Folge vorgespannt wird.As in the previous exemplary embodiment according to FIG. 2, the adjusting lever is again adjustable between the stops 23 and 24, so that with these stops the pretension of the idle spring 8 coupled to the locking lever 111 is determined. When the stop 23 is adjusted, the position of the adjusting screw 33 can be corrected accordingly so that the rocker arm 130 limited in its pivoting movement by its abutment on the bolt 40 is in abutment with the adjusting lever 22 via the adjusting screw 33 when the latter is on its first Adjustment lever stop is located according to its minimum setting. If the adjusting lever 22 is now adjusted in the direction of the excess quantity, the return spring 43, which acts on the rocker arm 130, causes the rocker arm 130 to follow the adjusting lever. This return spring 43 overrides the return spring 126 and the adjusting lever 111 is now also pivoted in accordance with the pivoting movement of the rocker arm 130, namely until it comes into contact with the stop 24 with its “T” crossbar 41. The adjusting lever 22 then lifts off the adjusting screw 33 and performs its other quantity-adjusting function. The return spring 43 is thus designed so that it overcomes the force of the return spring 126, which serves to adjust the adjusting lever 111 and at the same time is stronger than the idle spring 8, which is subsequently biased.

Figur 4 zeigt eine Ausführungsvariante der Anordnung der Leerlauffeder im Regler der Kraftstoffeinspritzpumpe. Abweichend vom Ausführungsbeispiel nach Figur 1 ist hier die Regelfeder am Spannhebel 16 befestigt, so daß dieser sowohl von der Leerlauffeder 8 als auch von der Regelfederanordnung 19 beaufschlagt wird. Der Reglerhebel 5 dient in diesem Zusammenhang als Starthebel lediglich zur Einstellung und in der Folge zur Abregelung der Startübermenge, indem durch den Fliehkraftversteller 14 die Startfeder 15 zusammengedrückt wird, bis der Starthebel 5 zur Anlage an dem Spannhebel 16 gelangt und beide Hebel nun im Verbund durch den Fliehkraftversteller verstellbar sind. Bei diesem Regler ist bei Niedrigstlast entsprechend dem Leerlauf die Regelfederanordnung 19 so eingestellt, daß lediglich die Leerlauffeder 8 auf den Spannhebel 16 wirksam ist. Erst nach Überschreiten der Leerlaufdrehzahl gelangt der Spannhebel 16 in festen Kontakt mit der Regelfederanordnung 19, wobei zwischen dem Verbindungspunkt dieser Regelfederanordnung 19 und dem Spannhebel noch eine weitere Angleichfeder 44 einstellbar ist.FIG. 4 shows an embodiment variant of the arrangement of the idle spring in the regulator of the fuel injection pump. In a departure from the exemplary embodiment according to FIG. 1, the control spring is attached to the tensioning lever 16 so that it is acted upon by both the idle spring 8 and the control spring arrangement 19. In this context, the control lever 5 serves only as a start lever for adjustment and subsequently to limit the excess starting quantity by the starting spring 15 being compressed by the centrifugal force adjuster 14 until the starting lever 5 comes to rest against the tensioning lever 16 and both levers can now be adjusted in combination by the centrifugal force adjuster. In this controller, the control spring arrangement 19 is set at the lowest load in accordance with the idling so that only the idling spring 8 is effective on the tensioning lever 16. Only after the idle speed has been exceeded does the tensioning lever 16 come into firm contact with the control spring arrangement 19, a further adjustment spring 44 being adjustable between the connection point of this control spring arrangement 19 and the tensioning lever.

Claims (10)

  1. Fuel injection pump for internal combustion engines, with a fuel injection quantity adjusting member (4) actuated by a governor lever (5, 16) which is adjustable counter to the force of a regulating spring (19) in dependence of a force formed in dependence on the engine speed, the regulating spring (19) being arranged between the governor lever (5, 16) and an operating lever (20) which is adjustable by means of a pivotable adjusting lever (22) and which is mounted fixedly relative to the housing, and with an idling spring (8) which, in addition to the regulating spring (19), is coupled to the governor lever (5, 16) and which is clamped between the latter and an idling spring operating lever (9) which is mounted fixedly relative to the housing on a shaft (10) and which is adjustable by means of a setting lever (11, 111) which is connected to the shaft (10) and is pivotable between two adjustable stops (23, 24, 33, 36) and which can be set in dependence on operating parameters of the internal combustion engine by means of an actuating device, characterized in that the actuating device consists of a return spring (26, 126) engaging on the setting lever (11, 111) and of a coupling arrangement, by means of which the setting lever (11, 111) is coupled non-positively to the adjusting lever (22), in such a way that, in the pivoting range between the two stops (23, 24, 33, 36), the setting lever (11, 111) follows the adjustment of the adjusting lever (22).
  2. Fuel injection pump according to Claim 1, characterized in that the coupling arrangement consists of a drag lever (30, 130) which is pivotable about a fixed axis (31, 131) and which is coupled to the setting lever (11, 111) via a take-up part (28, 40) provided eccentrically to the pivot axis of the setting lever (11, 111) formed by the axis of the shaft (10) and can be brought to bear against the adjusting lever (22) under the effect of a return force.
  3. Fuel injection pump according to Claim 2, characterized in that the take-up part (28, 40) is fixedly connected to one of the parts, namely the drag lever (30, 130) or setting lever (11, 111), and is guided on a cam (29, 39) on the other of the parts, namely the setting lever (11, 111) or drag lever (30, 130).
  4. Fuel injection pump according to Claim 3, characterized in that the cam (29) has two mutually parallel guide tracks, between which the take-up part (28) is guided.
  5. Fuel injection pump according to Claim 3, characterized in that the take-up part (28, 40) is held under the effect of a return spring (26, 126) in bearing contact against the cam consisting of a cam track (29, 39).
  6. Fuel injection pump according to Claim 4 or 5, characterized in that the cam has a rectilinear path.
  7. Fuel injection pump according to one of Claims 3 to 6, characterized in that the distance between the take-up parts (28, 40) and the pivot axis of the setting lever (11, 111) can be changed in order to change the transmission ratio between the adjustment of the adjusting lever and the adjustment of the setting lever.
  8. Fuel injection pump according to Claim 4, characterized in that the guide tracks are formed by a long hole (29) which is arranged in the drag lever (30) in the region between the pivot axis of the setting lever (11) and the axis (31) of the one-armed drag lever (30).
  9. Fuel injection pump according to Claim 5, characterized in that the drag lever (131) is a two-armed lever and by a return spring (43) can be brought with one arm into bearing contact against the adjusting lever (22), and the take-up part (40) is arranged on the setting lever (111) and, by the force of the return spring (126) engaging on the setting lever (111), can be held in bearing contact against the cam (39) arranged on the other lever arm of the drag lever (131).
  10. Fuel injection pump according to one of the preceding claims, characterized in that there is arranged between the drag lever (30, 130) and adjusting lever (22) a setscrew (33), by means of which the pivoting position of the drag lever (30, 130) relative to the initial position of the adjusting lever (22) at one of its adjusting lever stops (36) can be set.
EP19940105646 1993-05-14 1994-04-13 Fuel injection pump for internal combustion engines Expired - Lifetime EP0624720B1 (en)

Applications Claiming Priority (4)

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DE4316243 1993-05-14
DE4316243 1993-05-14
DE4332847A DE4332847A1 (en) 1993-05-14 1993-09-27 Fuel injection pump for IC engine - has actuator of return spring and coupling arrangement, to couple setting and adjusting levers
DE4332847 1993-09-27

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EP0624720A1 EP0624720A1 (en) 1994-11-17
EP0624720B1 true EP0624720B1 (en) 1996-03-06

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DE4443114A1 (en) * 1994-12-03 1996-06-05 Bosch Gmbh Robert Fuel injection pump for internal combustion engines

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3027671A1 (en) * 1980-07-22 1982-02-18 Daimler-Benz Ag, 7000 Stuttgart Centrifugal fuel injection pump regulator - has idling leaf spring coupled to further spring with engine parameter-dependent spring force
DE3239696A1 (en) * 1982-10-27 1984-03-01 Daimler-Benz Ag, 7000 Stuttgart Device for adjustment of the idling speed
DE3322214A1 (en) * 1983-06-21 1985-01-10 Robert Bosch Gmbh, 7000 Stuttgart Injection pump for internal-combustion engines
DE3743060A1 (en) * 1987-12-18 1989-06-29 Bosch Gmbh Robert SPEED REGULATOR FOR FUEL INJECTION PUMPS
DE3844452A1 (en) * 1988-12-31 1990-07-05 Bosch Gmbh Robert DISTRIBUTION FUEL INJECTION PUMP FOR INTERNAL COMBUSTION ENGINES

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Publication number Publication date
JPH074270A (en) 1995-01-10
EP0624720A1 (en) 1994-11-17

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