EP0232393B1 - Centrifugal-force rpm regulator for fuel injection pumps - Google Patents

Centrifugal-force rpm regulator for fuel injection pumps Download PDF

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Publication number
EP0232393B1
EP0232393B1 EP86905192A EP86905192A EP0232393B1 EP 0232393 B1 EP0232393 B1 EP 0232393B1 EP 86905192 A EP86905192 A EP 86905192A EP 86905192 A EP86905192 A EP 86905192A EP 0232393 B1 EP0232393 B1 EP 0232393B1
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EP
European Patent Office
Prior art keywords
brackets
regulating
centrifugal
spindle
guide lever
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Expired
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EP86905192A
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German (de)
French (fr)
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EP0232393A1 (en
Inventor
Werner BRÜHMANN
Ernst Ritter
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication of EP0232393A1 publication Critical patent/EP0232393A1/en
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    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D1/00—Controlling fuel-injection pumps, e.g. of high pressure injection type
    • F02D1/02—Controlling fuel-injection pumps, e.g. of high pressure injection type not restricted to adjustment of injection timing, e.g. varying amount of fuel delivered
    • F02D1/08—Transmission of control impulse to pump control, e.g. with power drive or power assistance
    • F02D1/10—Transmission of control impulse to pump control, e.g. with power drive or power assistance mechanical

Definitions

  • the invention relates to a centrifugal speed controller of fuel injection pumps according to the preamble of the main claim.
  • Such speed controllers are on the market as variable speed controllers or idle speed controllers from Bosch under the names EP / RSV. And EP / RSF (see also Basch, Technical Instruction VDT-UBP 210/1 De. P. 29, (1975)).
  • EP / RSV variable speed controllers
  • EP / RSF see also Basch, Technical Instruction VDT-UBP 210/1 De. P. 29, (1975)
  • the theoretically very precisely defined bearing and application points deviate from the intended positions as a result of manufacturing errors. These deviations can either be corrected by subsequent and thus expensive processing of the parts concerned or they have to be compensated for by appropriate training of the control parts.
  • the controller also works with an adjustment device which, like these EP / RS controllers, achieves a "fuel adjustment" by the joint head with its side facing away from the centrifugal adjuster hitting an adjustment bolt loaded by an adjustment spring, there is a risk that whenever the joint head is inclined due to the torsion of the guide lever to the surface of the adjustment bolt, a point of displacement and thereby undesired change. the proposed «alignment» takes place.
  • Deviations from the adjustment direction can result, for example, in an off-center force attack by the centrifugal forces of the centrifugal force adjuster. These one-sided loads in certain speed ranges can lead to the parts that can be displaced relative to one another becoming caught. These undesired transverse forces also cause a deterioration in the controller quality because the actual power transmission lines deviate from the originally aligned lines.
  • the adjusting piece designed as an adjusting sleeve is guided on a stub shaft of the centrifugal weight adjuster and engages axially on a rolling bearing in which the joint head is inserted with a corresponding pin .
  • the joint head has stub axles running transversely to the direction of adjustment, on which the tabs of the guide lever engage via elongated holes which are open at the bottom.
  • a cross pin is present as a cross bearing, which at least partially penetrates the joint head and is penetrated by the axis, as a result of which a simpler construction for assembly can be achieved.
  • there is play between the joint head and the tabs which allows the joint head to be moved slightly sideways with respect to the guide lever and with respect to the central line of force; if, for example, there is a production-related lateral offset from the guide lever to the flyweight adjuster. This displacement of the joint head can take place on the axle or by moving the axle ends in the tabs of the guide lever.
  • axle ends are firmly connected to the tabs of the guide lever in order to improve its rigidity.
  • a spacer bolt for example riveted, is provided on both sides between the tabs as one of the transverse connections near the pivot bearing of the guide lever.
  • FIG. 1 shows a perspective view of the essential parts of the regulator with schematically illustrated supplementary parts of the regulator; 2 shows a longitudinal section through the area of the flyweight adjuster and joint head of the first embodiment; Fig. 3 shows a section through the joint head along line III-III in Fig. 2 and Fig. 4 to 6, the second embodiment in three sections or views.
  • 1 denotes a flyweight adjuster. which acts on an adjusting piece which acts via a lever system 3 on a quantity control element 4 which is only shown schematically.
  • An interventional lever 5 can be used to intervene arbitrarily in the lever system 3.
  • centrifugal weights 6 act on the adjusting piece 2 via angled lever 7, the adjusting forces corresponding to the centrifugal forces and thus the rotational speed.
  • the flyweight adjuster 1 is driven via a shaft 8, the end 9 of which is guided in an inner bore 10 of the adjusting piece 2.
  • the flyweights 6 with levers 7 are mounted on crossbars 11 which rotate with the shaft 8.
  • the adjusting piece 2 is shown in different partial sections.
  • the adjustment piece 2 has a collar 12 which is rotationally symmetrical and on the side facing the centrifugal weight adjuster 1, with the interposition of a roller bearing 13, the levers 7 of the centrifugal weight adjuster 1 engage.
  • a roller bearing 13 Arranged within the roller bearing 13 is a sleeve part 14 of the adjusting piece 2, in the inner bore 10 of which the end of the shaft 8 projects, on which the adjusting piece 2 is axially displaceable.
  • an articulated head 15 is provided, which in this first exemplary embodiment is formed in one piece with the adjusting piece 2 and which has a cross bearing with a transverse bore 16 of elongated cross section (elongated hole) through which an axis 17 projects.
  • the joint head 15 and the axis 17 are fixed to one another by a bolt 18 which traverses both, so that the axis 17 can be pivoted about the bolt 18 by a certain angle limited by the cross section of the transverse bore 16 (FIG. 3).
  • the ends of tabs 20 of a double-arm guide lever 21 and the ends of a likewise double-arm deflection lever 22 are supported on the free axle ends 19 of the axis 17.
  • the pair of deflection levers 22 is connected to one another by a pin 23.
  • a crank 24 engages, which is only shown schematically, the adjusting lever 5.
  • a pivot axis 25 for a control lever 26 is arranged, which is mounted at one end 27 in the controller housing and at the other end 28 the quantity control member 4, in particular a control rod, articulates.
  • the ends of the guide lever 21 facing away from the axis 17 are pivotably arranged in the controller housing via a fixed pivot bearing 29, on which the end of a power lever 30 is also mounted.
  • On the motor lever engages a counteracting the centrifugal force f Regier Eder 31 at.
  • the power lever 30 is supported with its end 32 on a stop 33 of the housing.
  • an adjustment device 34 with an adjustment spring 35, which only yields from a certain centrifugal force or speed and thus influences the characteristic curve of the controller determined up to that point by the control spring 31.
  • the injection quantity is thus "adjusted to the quantity that can be burned by the engine without soot.”
  • Centrifugal speed controller formed works as follows: If the final control speed is exceeded at a certain setting of the adjusting lever 5, a force is exerted on the adjusting element 2 by the centrifugal force of the centrifugal weights 6 via the angle lever 7, which displaces it against the force of the spring 31 or 35 .
  • the pair of guide levers 21 is displaced via the axis 17 and thereby takes the control lever 26 and power lever 30 with it.
  • the quantity control element 4 is shifted into a position for a smaller injection quantity, and by driving the power lever 30, the spring 31 or 35 must be overcome until a new equilibrium position is reached.
  • the injection quantity for accelerating and braking the engine can be set arbitrarily via the adjusting lever 5.
  • the bell crank 22 is adjusted by the crank 24, whereby the control lever 26 is also pivoted into a desired position via the pivot axis 25.
  • the regulation of the idle speed works in principle like that of the final speed with the difference that as soon as the engine falls below a certain speed, the speed controller brings the quantity control element 4 into a position for larger injection quantities until a balance is again achieved here.
  • variable speed controllers all-speed controllers
  • the intermediate speed is also regulated in these all-speed controllers, which can be set arbitrarily in the latter, so that the lever arrangement deviates somewhat from that shown in FIG. 1.
  • the bellcrank 22 is not required and the control wheels act on the power lever on the one hand, but on the other hand, in contrast to the idle speed controller, on a swivel lever which can be adjusted by the arbitrarily adjustable adjusting lever, the pretension of the control spring changing depending on the swivel position.
  • the second exemplary embodiment shown in FIGS. 4 to 6 is used in the case of adjustment regulators, just as the first exemplary embodiment can be used with these regulators. Since the invention can be used with both types of controller, a detailed description of an adjustment controller is dispensed with in detail.
  • FIG. 4 is shown in its box-like shape and the joint head 115, specifically in FIG. 4 as a longitudinal section, in FIG. 5 as a partial section and view along line VV in FIG. 4 and in FIG. 6 as a section along line VI-VI in Fig. 4.
  • the guide lever 121 also has its two tabs 120 here, which are firmly connected to one another by the axis 117 of the joint head 115 and by a spacer bolt 37 at the other end of the lever.
  • the connection is made here by riveting the axle ends 119 or the ends of the spacer bolt 37.
  • An additional stiffening is achieved by a bushing 38, which is clamped between the two tabs 120 and in which a bearing pin 39 with axial clamping is guided, on which the control lever 126 is mounted. In this way, a relatively torsionally rigid system is created, in which the arrangement of the fixed pivot bearing 129 contributes to the stiffening.
  • the joint head 115 is formed separately from the adjusting piece 2 and has a plug 40 towards the centrifugal force adjuster.
  • the axis 117 penetrates a cross bolt 36, which, however, also traverses the joint head 115.
  • a play 41 is present between the joint head 115 and the tabs 120, so that there is also a possible displacement of the joint head 115 on the axis 117 transversely to the direction of adjustment indicated by the double arrow I.

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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)

Abstract

Centrifugal-force rpm regulator for fuel injection pumps of interal combustion engines with a centrifugal weight adjuster (1) which by the action of its centrifugal weights (6) operates an articulated head (2) which by means of a pin (17) couples a twin-armed guide lever (21), in the form of a stiff frame, with a strip (20). The pin (17) is supported via a cross-bearing (18) in the articulation head (15) where it is inserted in an aperture (16) which is provided, in the direction of displacement, with a longitudinally-shaped cross-section, so that the pin (17) can effect a limited pivoting movement in the aperture (16) around the cross-bearing (18).

Description

Stand der TechnikState of the art

Die Erfindung geht aus von einem Fliehkraftdrehzahlregler von Kraftstoffeinspritzpumpen nach der Gattung des Hauptanspruchs. Derartige Drehzahlregler sind als Verstellregler oder Leerlaufenddrehzahlregler von der Firma Bosch unter der Bezeichnung EP/RSV .und EP/RSF auf dem Markt (vergleiche auch Basch, Technische Unterrichtung VDT-UBP 210/1 De. S. 29, (1975)). Bei diesen in Großserie hergestellten Drehzahlreglern weichen die theoretisch sehr genau festgelegten Lager - und Angriffspunkte infolge Fertigungsfehlern von den vorgesehenen Stellen ab. Diese Abweichungen können entweder durch nachträgliche und damit teure Bearbeitung der betroffenen Teile korrigiert werden oder sie müssen durch entsprechende Ausbildung der Regierteile kompensiert werden. Eine solche Kompensation ist beispielsweise beim doppelarmigen Führungshebel mit seiner kastenförmigen Konstruktion erreicht, indem dieser torsionsweich ausgeführt ist. Die Torsionsweichheit hat jedoch den Nachteil, daß dadurch die Regelung im Ganzen ungenau wird und zu großen Streuungen neigt und daß dadurch die Einstellbarkeit des Reglers wesentlich erschwert wird.The invention relates to a centrifugal speed controller of fuel injection pumps according to the preamble of the main claim. Such speed controllers are on the market as variable speed controllers or idle speed controllers from Bosch under the names EP / RSV. And EP / RSF (see also Basch, Technical Instruction VDT-UBP 210/1 De. P. 29, (1975)). In the case of these speed controllers manufactured in large series, the theoretically very precisely defined bearing and application points deviate from the intended positions as a result of manufacturing errors. These deviations can either be corrected by subsequent and thus expensive processing of the parts concerned or they have to be compensated for by appropriate training of the control parts. Such compensation is achieved, for example, in the case of the double-arm guide lever with its box-shaped construction in that it is designed to be torsionally soft. However, the torsional softness has the disadvantage that the control as a whole is inaccurate and tends to be very scattered and that the adjustability of the controller is thereby made considerably more difficult.

Wenn der Regler zudem mit einer Angleichvorrichtung arbeitet, bei der, wie bei diesen EP/RS-Reglern, eine « Kraftstoffangleichung » erzielt wird, indem der Gelenkkopf mit seiner dem Fliehkraftversteller abgewandten Seite auf einen durch eine Angleichfeder belasteten Angleichbolzen stößt, so besteht die Gefahr, daß immer dann, wenn aufgrund der Torsion des Führungshebels der Gelenkkopf schräg zur Angriffsfläche des Angleichbolzens steht, eine Angriffspunktverschiebung und dadurch ungewünschte Änderung. der vorgesehenen « Angleichung » stattfindet.If the controller also works with an adjustment device which, like these EP / RS controllers, achieves a "fuel adjustment" by the joint head with its side facing away from the centrifugal adjuster hitting an adjustment bolt loaded by an adjustment spring, there is a risk that whenever the joint head is inclined due to the torsion of the guide lever to the surface of the adjustment bolt, a point of displacement and thereby undesired change. the proposed «alignment» takes place.

Hinzu kommen Regelungsfehler, die auf Reibungsverluste des Reglers zurückzuführen sind, welche beispielsweise bei der Übertragung der Fliehgewichtsverstellkräfte auf den Führungshebel und von dort auf das Fördermengenverstellglied auftreten. Diese Reibungsverluste nehmen naturgemäß zu, wenn aufgrund von Torsionsweichheit oder sonstigen Verwindungen im Regiergestänge Verspannungen auftreten. Reibungsverluste und Verwindungen entstehen besonders bei Fluchtungsfehlern, das heißt, wenn die Kraftübertragung nicht in der durch die Fliehkraftverstellerachse bestimmten Verstellrichtung erfolgt, so daß Kippmomente entstehen, was sich besonders nachteilig an den Stellen auswirkt, an denen die Kraftübertragung über Formschlußflächen statt über Punkte oder Linien erfolgt. Abweichungen von der Verstellrichtung können beispielsweise einen außermittigen Kraftangriff der Fliehkräfte des Fliehkraftverstellers zur Folge haben. wobei-diese einseitigen Belastungen in bestimmten Drehzahlbereichen zu einer Verhakung der relativ zueinander verschiebbaren Teile führen kann. Diese ungewünschten Querkräfte bewirken auch deshalb eine Verschlechterung der Reglerqualität, weil die tatsächlichen Kraftübertragungslinien von den ursprünglich vorgesehenen fluchtenden Linien abweichen.In addition there are control errors which can be attributed to friction losses of the controller which occur, for example, when the centrifugal weight adjustment forces are transmitted to the guide lever and from there to the delivery quantity adjustment element. These frictional losses naturally increase when tension occurs in the control linkage due to torsional softness or other twisting. Frictional losses and torsion occur particularly in the case of misalignments, i.e. if the force is not transmitted in the direction of adjustment determined by the centrifugal force adjustment axis, so that tilting moments arise, which has a particularly disadvantageous effect at the points where the force is transmitted via positive locking surfaces instead of points or lines . Deviations from the adjustment direction can result, for example, in an off-center force attack by the centrifugal forces of the centrifugal force adjuster. these one-sided loads in certain speed ranges can lead to the parts that can be displaced relative to one another becoming caught. These undesired transverse forces also cause a deterioration in the controller quality because the actual power transmission lines deviate from the originally aligned lines.

In Bezug auf die jedem Regler zugrundeliegende Reglerkurve wirken sich diese beschriebenen Mängel einerseits darin aus, daß diese Reglerkurve eine verhältnismäßig große Streuung aufweist und daß außerdem beim Übergang zur Abregelung ein weicher Übergang statt eines scharfen Knickes vorhanden ist. Zur Definition einer exakten Reglerkurve ist es aber erforderlich, daß Rastpunkte für die Einstellung gegeben sind. beispielsweise beim Übergang zur Abregelung. Diese Nachteile wirken sich besonders beim Leerlaufenddrehzahlregler aus, bei dem die Abregelung zur Vermeidung von insbesondere Motorschäden dadurch erst ab einer bestimmten Drehzahl beginnen darf, die durch einen nicht vorhandenen Rastpunkt nicht einstellbar ist. Nur wenn die Höchstdrehzahl des Motors über die Kraftstoffeinspritzpumpe sehr präzise eingeregelt werden kann, ist die volle Ausnutzung dieser Enddrehzahl des Motors möglich.With regard to the controller curve on which each controller is based, these deficiencies described have the effect, on the one hand, that this controller curve has a relatively large spread and that, in addition, a smooth transition instead of a sharp bend is present during the transition to reduction. To define an exact controller curve, it is necessary that there are locking points for the setting. for example during the transition to curtailment. These disadvantages have a particular effect on the idle speed governor, in which the limitation to avoid engine damage, in particular, may therefore only begin at a certain engine speed that cannot be set by a non-existing stop point. Only when the maximum speed of the engine can be adjusted very precisely via the fuel injection pump is it possible to fully utilize this final speed of the engine.

Bei einem anderen bekannten Fliehkraftdrehzahlregler der eingangs genannten Art (DE-PS 1 011 223) ist das als Verstellmuffe ausgebildete Verstellstück auf einem Wellenstummel des Fliehgewichtsverstellers geführt und greift über ein Wälzlager, in das der Gelenkkopf mit einem entsprechenden Zapfen gesteckt ist, axial an diesem an. Der Gelenkkopf weist quer zur Verstellrichtung verlaufende Achsstummel auf, an denen die Laschen des Führungshebels über nach unten offene Langlöcher angreifen. Diese Ausführung hat den Nachteil, daß konstruktive Ungenauigkeiten der Hebellager sowie Fluchtungsfehler der Stellbewegungen entweder nicht ausgeglichen werden oder durch Torsionsnachgiebigkeit des Führungshebels ausgeglichen werden, was beides entweder zu hoher Reibung oder den obengenannten Reglerfehlern führt.In another known centrifugal speed controller of the type mentioned (DE-PS 1 011 223), the adjusting piece designed as an adjusting sleeve is guided on a stub shaft of the centrifugal weight adjuster and engages axially on a rolling bearing in which the joint head is inserted with a corresponding pin . The joint head has stub axles running transversely to the direction of adjustment, on which the tabs of the guide lever engage via elongated holes which are open at the bottom. This design has the disadvantage that structural inaccuracies of the lever bearings and misalignment of the actuating movements are either not compensated for or are compensated for by torsional flexibility of the guide lever, both of which either lead to high friction or the above-mentioned control errors.

Vorteile der ErfindungAdvantages of the invention

Der erfindungsgemäße Fliehkraftdrehzahlregler mit den kennzeichnenden Merkmalen des Hauptanspruches hat demgegenüber verschiedene Vorteile :

  • - Der Führungshebel kann weitgehend torsionsstarr ausgebildet werden, um mit einem derartigen steifen Führungshebel eine nahezu fehlerfreie Übertragung der einseitig angreifenden Regelhebelkraft zu erzielen und außerdem auch eine Verringerung der Nacharbeit am Führungshebel zu erhalten ;
  • - Fertigungsbedingte Ungenauigkeiten, die vor allem zu Fluchtungsfehlern führen, können vollständig und ohne Verwindungsproblem der Hebel bzw. ohne Kraftaufwand ausgeglichen werden ;
  • - Die Kraftübertragung vom Gelenkkopf auf den Führungshebel erfolgt über Linienberührung innerhalb des Kreuzlagers anstatt über Punktberührung, wie beispielsweise beim Kugelkopf, so daß erstens ein geringerer Verschleiß auftritt und zweitens eine höhere Belastung möglich ist ;
  • - Die Kraftübertragung der Verstellkräfte beispielsweise vom Verstellstück auf den Gelenkkopf kann querkraftfrei erfolgen, da sich die Achse aufgrund der Ovalität der die Achse aufnehmenden Bohrung in dem erforderlichen Maß um das Kreuzlager schwenken läßt, so daß vor allem auch der Kraftangriff weitgehend in der Mitte der Achse und somit in der gewünschten Kraftlinie erfolgt. Der doppelarmige Führungshebel kann sich dann auch noch bei einseitigem größeren Widerstand leicht verwinden, ohne daß deshalb der Kraftangriffspunkt aus dieser Kraftlinie verschoben wird, beispielsweise zu einem der beiden Laschen hin. Nach einer vorteilhaften Ausgestaltung der Erfindung ist als Kreuzlager ein den Gelenkkopf mindestens teilweise und die Achse durchdringender Bolzen vorhanden, so daß die Zentrierung auf einen Kraftangriffspunkt exakt zwischen den beiden Laschen des Führungshebels gewährleistet ist. Die Lösung kann bevorzugt bei einem Regler angewendet werden, bei dem in an sich bekannter Weise der Führungshebel mit seitlichem Spiel auf dem Schwenklager angeordnet ist.
The centrifugal speed governor according to the invention with the characterizing features of the main claim has various advantages:
  • - The guide lever can be largely torsionally rigid, in order to achieve an almost error-free transmission of the control lever force acting on one side with such a rigid guide lever and also to obtain a reduction in rework on the guide lever;
  • - Manufacturing-related inaccuracies, which mainly lead to misalignment, can be done completely and without twisting the lever or be compensated for without effort;
  • - The power transmission from the joint head to the guide lever takes place via line contact within the cross bearing instead of via point contact, such as with the ball head, so that firstly less wear occurs and secondly a higher load is possible;
  • - The power transmission of the adjusting forces, for example from the adjusting piece to the joint head, can take place without lateral force, since the axis can be pivoted to the required extent about the cross bearing due to the ovality of the bore receiving the axis, so that above all the force application largely in the center of the axis and thus takes place in the desired line of force. The double-armed guide lever can then easily twist even with greater resistance on one side, without the force application point therefore being shifted out of this line of force, for example toward one of the two tabs. According to an advantageous embodiment of the invention, a cross bearing is provided at least partially with the joint head and the pin penetrating the axis, so that the centering on a force application point is guaranteed exactly between the two tabs of the guide lever. The solution can preferably be applied to a controller in which the guide lever is arranged on the pivot bearing with lateral play in a manner known per se.

Nach einer anderen vorteilhaften Ausgestaltung der Erfindung ist als Kreuzlager ein den Gelenkkopf mindestens teilweise durchdringender und von der Achse durchdrungener Kreuzbolzen vorhanden, wodurch eine einfachere Konstruktion für die Montage erzielbar ist. Nach einer weiteren Ausgestaltung der Erfindung ist zwischen dem Gelenkkopf und den Laschen ein Spiel vorhanden, wodurch ein leichtes seitliches Verschieben des Gelenkkopfes in Bezug auf den Führungshebel und in Bezug auf die zentrale Kraftlinie möglich ist; wenn beispielsweise ein fertigungsbedingter seitlicher Versatz von Führungshebel zu Fliehgewichtsversteller gegeben ist. Diese Verschiebung des Gelenkkopfes kann auf der Achse erfolgen oder aber durch Verschieben der Achsenden in den Laschen des Führungshebels.According to another advantageous embodiment of the invention, a cross pin is present as a cross bearing, which at least partially penetrates the joint head and is penetrated by the axis, as a result of which a simpler construction for assembly can be achieved. According to a further embodiment of the invention, there is play between the joint head and the tabs, which allows the joint head to be moved slightly sideways with respect to the guide lever and with respect to the central line of force; if, for example, there is a production-related lateral offset from the guide lever to the flyweight adjuster. This displacement of the joint head can take place on the axle or by moving the axle ends in the tabs of the guide lever.

Nach einer zusätzlichen Ausgestaltung der Erfindung sind die Achsenden fest mit den Laschen des Führungshebelsverbunden, um dadurch dessen Steifigkeit zu verbessern. In gleiche Richtung geht eine weitere Ausgestaltung der Erfindung gemäß der zwischen den Laschen als eine der Querverbindungen nahe des Schwenklagers des Führungshebels ein beiderseits fest mit den Lasehen verbundener - beispielsweise vernieteter - Abstandsbolzen vorhanden ist.According to an additional embodiment of the invention, the axle ends are firmly connected to the tabs of the guide lever in order to improve its rigidity. In the same direction, a further embodiment of the invention according to which a spacer bolt, for example riveted, is provided on both sides between the tabs as one of the transverse connections near the pivot bearing of the guide lever.

Weitere Vorteile und vorteilhafte Ausgestaltungen der Erfindung sind der nachfolgenden Beschreibung, der Zeichnung und den Ansprüchen entnehmbar:
ZeichnungFurther advantages and advantageous embodiments of the invention can be found in the following description, the drawing and the claims:
drawing

Zwei Ausführungsbeispiele des Gegenstandes der Erfindung sind in der Zeichnung dargestellt und werden im folgenden näher beschrieben.Two embodiments of the object of the invention are shown in the drawing and are described in more detail below.

Es zeigen Fig.1 eine perspektivische Darstellung der wesentlichen Teile des Reglers mit schematisch dargestellten ergänzenden Teilen des Reglers ; Fig. 2 einen Längsschnitt durch den Bereich des Fliehgewichtsverstellers und Gelenkkopfes des ersten Ausführungsbeispiels ; Fig. 3 einen Schnitt durch den Gelenkkopf nach Linie III-III in Fig. 2 und Fig. 4 bis 6 das zweite Ausführungsbeispiel in drei Schnitten bzw. Ansichten.1 shows a perspective view of the essential parts of the regulator with schematically illustrated supplementary parts of the regulator; 2 shows a longitudinal section through the area of the flyweight adjuster and joint head of the first embodiment; Fig. 3 shows a section through the joint head along line III-III in Fig. 2 and Fig. 4 to 6, the second embodiment in three sections or views.

Beschreibung der AusführungsbeispieleDescription of the embodiments

Bei der allgemeinen perspektivischen Darstellung eines erfindungsgemäßen Reglers in Fig. 1 ist mit 1 ein Fliehgewichtsversteller bezeichnet. der auf ein Verstellstück wirkt, welches über ein Hebelsystem 3 auf ein nur schematisch dargestelltes Mengensteuerglied 4 wirkt. In das Hebelsystem 3 kann willkürlich über einen Verstellhebel 5 eingegriffen werden.In the general perspective representation of a controller according to the invention in FIG. 1, 1 denotes a flyweight adjuster. which acts on an adjusting piece which acts via a lever system 3 on a quantity control element 4 which is only shown schematically. An interventional lever 5 can be used to intervene arbitrarily in the lever system 3.

Bei dem in Fig. 1 rein schematisch und in Fig. 2 dargestellten Fliehgewichtsversteller 1 wirken Fliehgewichte 6 über Winkelhebel 7 auf das Verstellstück 2, wobei die Verstellkräfte den Fliehkräften und dadurch der Drehzahl entsprechen. Der Fliehgewichtsversteller 1 wird über eine Welle 8 angetrieben, deren Ende 9 in einer Innenbohrung 10 des Verstellstückes 2 geführt ist. Die Fliehgewichte 6 mit Hebeln 7 sind an Traversen 11 gelagert, welche mit der Welle 8 rotieren.In the centrifugal weight adjuster 1 shown purely schematically in FIG. 1 and in FIG. 2, centrifugal weights 6 act on the adjusting piece 2 via angled lever 7, the adjusting forces corresponding to the centrifugal forces and thus the rotational speed. The flyweight adjuster 1 is driven via a shaft 8, the end 9 of which is guided in an inner bore 10 of the adjusting piece 2. The flyweights 6 with levers 7 are mounted on crossbars 11 which rotate with the shaft 8.

Bei dem in den Figuren 2 und 3 dargestellten ersten Ausführungsbeispiel ist das Verstellstück 2 jeweils in anderen Teilschnitten dargestellt. Das Verstellstück 2 weist einen Bund 12 auf, der drehsymmetrisch ausgebildet ist und an dessen dem Fliehgewichtsversteller 1 zugewandten Seite unter Zwischenschaltung eines Wälzlagers 13 die Hebel 7 des Fliehgewichtsverstellers 1 angreifen. Innerhalb des Wälzlagers 13 ist ein Muffenteil 14 des Verstellstückes 2 angeordnet, in dessen Innenbohrung 10 das Ende der Welle 8 ragt, auf dem das Verstellstück 2 axial verschiebbar ist. Auf der diesem Muffenteil 14 abgewandten Seite des Bundes 12 ist ein Gelenkkopf 15 vorgesehen, der bei diesem ersten Ausführungsbeispiel einstückig mit dem Verstellstück 2 ausgebildet ist und der ein Kreuzlager aufweist mit einer Querbohrung 16 länglichen Querschnitts (Langloch), durch die eine Achse 17 ragt. Gelenkkopf 15 und Achse 17 werden durch einen beide durchquerenden Bolzen 18 zueinander fixiert, so daß die Achse 17 um einen bestimmten durch den Querschnitt der Querbohrung 16 begrenzten Winkel um den Bolzen 18 schwenkbar ist (Fig. 3).In the first exemplary embodiment shown in FIGS. 2 and 3, the adjusting piece 2 is shown in different partial sections. The adjustment piece 2 has a collar 12 which is rotationally symmetrical and on the side facing the centrifugal weight adjuster 1, with the interposition of a roller bearing 13, the levers 7 of the centrifugal weight adjuster 1 engage. Arranged within the roller bearing 13 is a sleeve part 14 of the adjusting piece 2, in the inner bore 10 of which the end of the shaft 8 projects, on which the adjusting piece 2 is axially displaceable. On the side of the collar 12 facing away from this sleeve part 14, an articulated head 15 is provided, which in this first exemplary embodiment is formed in one piece with the adjusting piece 2 and which has a cross bearing with a transverse bore 16 of elongated cross section (elongated hole) through which an axis 17 projects. The joint head 15 and the axis 17 are fixed to one another by a bolt 18 which traverses both, so that the axis 17 can be pivoted about the bolt 18 by a certain angle limited by the cross section of the transverse bore 16 (FIG. 3).

Von dem dargestellten Hebelsystem 3 sind auf den freien Achsenden 19 der Achse 17 die Enden von Laschen 20 eines doppelarmig ausgebildeten Führungshebels 21 und die Enden eines ebenfalls doppelarmig ausgebildeten Umlenkhebels 22 gelagert. Das Umlenkhebelpaar 22 ist durch einen Stift 23 miteinander verbunden. Am einen Arm des Umlenkhebels 22 greift übereine Kurbel 24, die nur schematisch dargestellt ist, der Verstellhebel 5 an. Am freien Ende des anderen Armes des Umlenkhebels 22 ist eine Schwenkachse 25 für einen Regelhebel 26 angeordnet, welcher am einen Ende 27 im Reglergehäuse gelagert ist und am anderen Ende 28 das Mengensteuerglied 4, insbesondere eine Regelstange, anlenkt. Die der Achse 17 abgewandten Enden des Führungshebels 21 sind über ein ortsfestes Schwenklager 29, auf dem auch das Ende eines Krafthebels 30 gelagert ist, im Reglergehäuse schwenkbar angeordnet. An dem Krafthebel greift eine der Fliehkraft entgegenwirkende Regierfeder 31 an. Der Krafthebel 30 stützt sich mit seinem Ende 32 an einem Anschlag 33 des Gehäuses ab. Zwischen Gelenkkopf 15 und Krafthebel 30 ist eine Angleichvorrichtung 34 mit Angleichfeder 35 vorgesehen, welche erst ab einer bestimmten Fliehkraft bzw. Drehzahl nachgibt und damit die bis dahin durch die Reglerfeder 31 bestimmte Kennlinie des Reglers beeinflußt. Die Einspritzmenge wird so der vom Motor rußfrei verbrennbaren Menge « angeg lichen.".Of the lever system 3 shown, the ends of tabs 20 of a double-arm guide lever 21 and the ends of a likewise double-arm deflection lever 22 are supported on the free axle ends 19 of the axis 17. The pair of deflection levers 22 is connected to one another by a pin 23. On one arm of the bell crank 22, a crank 24 engages, which is only shown schematically, the adjusting lever 5. At the free end of the other arm of the deflection lever 22, a pivot axis 25 for a control lever 26 is arranged, which is mounted at one end 27 in the controller housing and at the other end 28 the quantity control member 4, in particular a control rod, articulates. The ends of the guide lever 21 facing away from the axis 17 are pivotably arranged in the controller housing via a fixed pivot bearing 29, on which the end of a power lever 30 is also mounted. On the motor lever engages a counteracting the centrifugal force f Regier Eder 31 at. The power lever 30 is supported with its end 32 on a stop 33 of the housing. Between the joint head 15 and the power lever 30 there is provided an adjustment device 34 with an adjustment spring 35, which only yields from a certain centrifugal force or speed and thus influences the characteristic curve of the controller determined up to that point by the control spring 31. The injection quantity is thus "adjusted to the quantity that can be burned by the engine without soot."

Dieser erfindungsgemäße im ersten Ausführungsbeispiel als Leerlaufenddrehzahlregler aus- . gebildete Fliehkraftdrehzahlregler arbeitet wie folgt : Wenn bei einer bestimmten Einstellung des Verstellhebels 5 die Endabregeldrehzahl überschritten wird, wird durch die Fliehkraft der Fliehgewichte 6 über die Winkelhebel 7 eine Kraft auf das Verstellstück 2 ausgeübt, die dieses entgegen der Kraft der Feder 31 bzw. 35 verschiebt. Hierbei wird über die Achse 17 das Führungshebelpaar 21 verschoben und nimmt dabei-den Regelhebel 26 und Krafthebel 30 mit. Durch die Mitnahme des Regelhebels 26 wird das Mengensteuerglied 4 in eine Lage für geringere Einspritzmenge verschoben, und durch die Mitnahme des Krafthebels 30 muß die Feder 31 bzw. 35 überwunden werden solange, bis eine neue Gleichgewichtslage erreicht ist. Bevor diese Grenzdrehzahl erreicht wird, kann über den Verstellhebel 5 die Einspritzmenge zum Beschleunigen und Abbremsen des Motors willkürlich eingestellt werden. Hierfür wird durch die Kurbel 24 der Umlenkhebel 22 verstellt, wodurch über die Schwenkachse 25 ebenfalls der Regelhebel 26 in eine gewünschte Stellung geschwenkt wird. Die Regelung der Leerlaufdrehzahl funktioniert im Prinzip wie die der Enddrehzahl mit dem Unterschied, daß, sobald der Motor eine gewisse Drehzahl unterschreitet, der Drehzahlregler das Mengensteuerglied 4 in eine Lage für größere Einspritzmengen bringt, bis auch hier wieder ein Gleichgewicht erzielt ist.This according to the invention in the first embodiment as an idle speed controller. Centrifugal speed controller formed works as follows: If the final control speed is exceeded at a certain setting of the adjusting lever 5, a force is exerted on the adjusting element 2 by the centrifugal force of the centrifugal weights 6 via the angle lever 7, which displaces it against the force of the spring 31 or 35 . Here, the pair of guide levers 21 is displaced via the axis 17 and thereby takes the control lever 26 and power lever 30 with it. By driving the control lever 26, the quantity control element 4 is shifted into a position for a smaller injection quantity, and by driving the power lever 30, the spring 31 or 35 must be overcome until a new equilibrium position is reached. Before this limit speed is reached, the injection quantity for accelerating and braking the engine can be set arbitrarily via the adjusting lever 5. For this purpose, the bell crank 22 is adjusted by the crank 24, whereby the control lever 26 is also pivoted into a desired position via the pivot axis 25. The regulation of the idle speed works in principle like that of the final speed with the difference that as soon as the engine falls below a certain speed, the speed controller brings the quantity control element 4 into a position for larger injection quantities until a balance is again achieved here.

Natürlich ist die Erfindung genauso gut. anwendbar bei Verstellreglern (Alldrehzahlreglern). Bei diesen Alldrehzahlreglern wird im Gegensatz zum Leerlaufenddrehzahlregler auch die Zwischendrehzahl geregelt, die bei letzterem willkürlich einstellbar ist, so daß die Hebelanordnung etwas von der in Fig. 1 gezeigten abweicht.Of course, the invention is just as good. applicable to variable speed controllers (all-speed controllers). In contrast to the idle speed controller, the intermediate speed is also regulated in these all-speed controllers, which can be set arbitrarily in the latter, so that the lever arrangement deviates somewhat from that shown in FIG. 1.

Der Umlenkhebel 22 ist nicht erforderlich und die Regelfäder greift einerseits wiederum am Krafthebel an, andererseits aber im Unterschied zum Leerlaufenddrehzahlregler an einem durch den willkürlich verstellbaren Verstellhebel verstellbaren Schwenkhebel, wobei sich je nach Schwenklage die Vorspannung der Regelfeder ändert. So ist es durchaus möglich, daß das zweite in den Figuren 4 bis 6 dargestellte Ausführuhgsbeispiel bei Verstellreglern Anwendung findet, wie auch das erste Ausführungsbeispiel bei diesen Reglern verwendet werden kann. Da die Erfindung bei beiden Reglerarten verwendbar ist, ist auf eine nähere Beschreibung eines Verstellreglers im einzelnen verzichtet.The bellcrank 22 is not required and the control wheels act on the power lever on the one hand, but on the other hand, in contrast to the idle speed controller, on a swivel lever which can be adjusted by the arbitrarily adjustable adjusting lever, the pretension of the control spring changing depending on the swivel position. So it is quite possible that the second exemplary embodiment shown in FIGS. 4 to 6 is used in the case of adjustment regulators, just as the first exemplary embodiment can be used with these regulators. Since the invention can be used with both types of controller, a detailed description of an adjustment controller is dispensed with in detail.

Vom zweiten Ausführungsbeispiel ist nur der Führungshebel 121 in seiner kastenartigen Form und der Gelenkkopf 115 dargestellt und zwar in Fig. 4 als Längsschnitt, in Fig. 5 als Teilschnitt und Ansicht gemäß Linie V-V in Fig. 4 und in Fig. 6 als Schnitt nach Linie VI-VI in Fig. 4.From the second exemplary embodiment, only the guide lever 121 is shown in its box-like shape and the joint head 115, specifically in FIG. 4 as a longitudinal section, in FIG. 5 as a partial section and view along line VV in FIG. 4 and in FIG. 6 as a section along line VI-VI in Fig. 4.

Der Führungshebel 121 weist auch hier seine zwei Laschen 120 auf, die durch die Achse 117 des Gelenkkopfes 115 und durch einen Abstandsbolzen 37 am anderen Ende des Hebels fest miteinander verbunden sind. Die Verbindung ist hier durch Vernieten der Achsenden 119 bzw. der Enden des Abstandsbolzens 37 ausgeführt. Eine zusätzliche Versteifung wird durch eine Buchse '38 erreicht, die zwischen den beiden Laschen 120 eingeklemmt ist und in der ein Lagerbolzen 39 mit axialer Einspannung geführt ist, auf dem der Regelhebel 126 gelagert ist. Auf diese Weise entsteht ein verhältnismäßig verwindungssteifes System, bei dem die Anordung des ortsfesten Schwenklagers 129 zur Versteifung beiträgt.The guide lever 121 also has its two tabs 120 here, which are firmly connected to one another by the axis 117 of the joint head 115 and by a spacer bolt 37 at the other end of the lever. The connection is made here by riveting the axle ends 119 or the ends of the spacer bolt 37. An additional stiffening is achieved by a bushing 38, which is clamped between the two tabs 120 and in which a bearing pin 39 with axial clamping is guided, on which the control lever 126 is mounted. In this way, a relatively torsionally rigid system is created, in which the arrangement of the fixed pivot bearing 129 contributes to the stiffening.

.Im Unterschied zum ersten Ausführungsbeispiel ist hier der Gelenkkopf 115 getrennt von dem Verstellstück 2 ausgebildet und weist zum Fliehkraftversteller hin ein Steckstück 40 auf. Im Unterschied zum ersten Ausführungsbeispiel durchdringt hier die Achse 117 einen Kreuzbolzen 36, der jedoch ebenfalls den Gelenkkopf 115 durchquert. Zwischen dem Gelenkkopf 115 und den Laschen 120 ist ein Spiel 41 vorhanden, so daß auch eine quer zur durch den Doppelpfeil I angedeuteten Verstellrichtung mögliche Verschiebung des Gelenkkopfes 115 auf der Achse 117 gegeben ist.In contrast to the first exemplary embodiment, the joint head 115 is formed separately from the adjusting piece 2 and has a plug 40 towards the centrifugal force adjuster. In contrast to the first exemplary embodiment, the axis 117 penetrates a cross bolt 36, which, however, also traverses the joint head 115. A play 41 is present between the joint head 115 and the tabs 120, so that there is also a possible displacement of the joint head 115 on the axis 117 transversely to the direction of adjustment indicated by the double arrow I.

Claims (6)

1. Centrifugal speed governor of fuel injection pumps for internal combustion engines,
- having a centrifugal-weight regulator (1) producing an axial regulating movement of a regulating piece (2) against the force of at least one spring (31) and driven in synchronism with the engine speed ;
- having a guide lever (21) which serves to at least indirectly transmit the regulating movement to a delivery-quantity regulating member (control rod), is mounted for this purpose on a pivot bearing (29), consists of two brackets (20), firmly connected to one another and running in the same direction, and is thus of double-armed (box- shaped) configuration and on which the spring (31) acts at least indirectly ;
- and having an articulated head (15) between regulating piece (2) and guide lever (21) which on one side, towards the regulating piece, has a connection provided in the regulating direction of the regulating piece (2) and on the other side is connected to the guide lever (21) via two spindle ends (19), each acting, that is, on one of the brackets (20),
characterized in that
- the brackets (20), via transverse connections (17, 37, 38), form an inherently rigid frame,
- the spindle ends (19) are such as have a spindle (17) penetrating through the articulated head (15),
- the spindle (17) is arranged in a bore (16) which is present in the articulated head (15) and runs largely at right angles to the regulating direction and the brackets (20),
- the bore (16) has a cross-section of elongated configuration (oval) in the regulating direction. and
- the spindle (17) is mounted in the bore (16) approximately in the longitudinal centre of the spindle (17) by a cross bearing (18, 36) running at right angles to it and to the regulating direction, so that it can execute a limited pivoting movement in the bore (16) about the cross bearing.
2. Centrifugal speed governor according to Claim 1, characterized in that a bolt (18) penetrating at least partly through the articulated head (15) and completely through the spindle (17) is present as the cross bearing.
3. Centrifugal speed governor according to Claim 1, characterized in that a cross bolt (36) which penetrates at least partly through the articulated head (115) and through which the spin- die (117) completely penetrates is present as the cross bearing.
4. Centrifugal speed governor according to any of the preceding claims, characterized in that a clearance is present between the articulated head (15) and the brackets (20) of the guide lever (21).
5. Centrifugal speed governor according to any of the preceding claims, characterized in that the spindle ends (119) are firmly connected to the brackets (120).
6. Centrifugal speed governor according to any of the preceding claims, characterized in that a spacer bolt (37) is present between the brackets (120), near to the pivot bearing (129) of the guide lever (121), which spacer bolt (37) serves as a transverse connection and is firmly connected on both sides to the brackets.
EP86905192A 1985-08-16 1986-08-14 Centrifugal-force rpm regulator for fuel injection pumps Expired EP0232393B1 (en)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE3529449 1985-08-16
DE3529449 1985-08-16
DE3625985 1986-07-31
DE19863625985 DE3625985A1 (en) 1985-08-16 1986-07-31 CENTRIFUGAL SPEED REGULATOR OF FUEL INJECTION PUMPS

Publications (2)

Publication Number Publication Date
EP0232393A1 EP0232393A1 (en) 1987-08-19
EP0232393B1 true EP0232393B1 (en) 1988-11-09

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EP86905192A Expired EP0232393B1 (en) 1985-08-16 1986-08-14 Centrifugal-force rpm regulator for fuel injection pumps

Country Status (4)

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US (1) US4735182A (en)
EP (1) EP0232393B1 (en)
DE (2) DE3625985A1 (en)
WO (1) WO1987001162A1 (en)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4242880A1 (en) * 1992-12-18 1994-06-23 Bosch Gmbh Robert Centrifugal speed controller for fuel injection pumps of internal combustion engines
DE4242879A1 (en) * 1992-12-18 1994-06-23 Bosch Gmbh Robert Centrifugal speed controller for fuel injection pumps of internal combustion engines
CN106089448B (en) * 2016-08-16 2022-05-31 无锡威孚高科技集团股份有限公司 Negative correction mechanism for high-pressure oil pump speed regulator of forklift diesel engine

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1080814B (en) * 1956-07-03 1960-04-28 Bosch Gmbh Robert Centrifugal governor for internal combustion engines
DE1185413B (en) * 1960-07-27 1965-01-14 Motorpal Jihlava Np Injection quantity control device of an internal combustion engine, which acts as a function of the speed, with a device for damping the influence of torsional vibrations
AT298880B (en) * 1968-10-17 1972-05-25 Bosch Gmbh Robert Centrifugal governor for speed control of internal combustion engines
AT301949B (en) * 1970-03-24 1972-09-25 Friedmann & Maier Ag Flyweight regulator for internal combustion engines
DE2224758C3 (en) * 1972-05-20 1978-12-07 Robert Bosch Gmbh, 7000 Stuttgart Centrifugal governor for internal combustion engines
DE2311044A1 (en) * 1973-03-06 1974-09-12 Bosch Gmbh Robert Centrifugal governor for fuel injection engines
DE2904709A1 (en) * 1979-02-08 1980-08-21 Bosch Gmbh Robert SPEED REGULATOR FOR INJECTION INTERNAL COMBUSTION ENGINES, IN PARTICULAR CENTRIFUGAL SPEED REGULATOR OF AN INJECTION PUMP FOR VEHICLE DIESEL ENGINES

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
Bosch, Technische Unterrichtung VDT-VBP 210/1 DE, S. 29, (1975), R. Bosch GmbH, Stuttgart (DE) *

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DE3625985A1 (en) 1987-02-26
EP0232393A1 (en) 1987-08-19
US4735182A (en) 1988-04-05
DE3661148D1 (en) 1988-12-15
WO1987001162A1 (en) 1987-02-26

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