EP0167697B1 - Injection timing advance device for injection pumps for combustion engines - Google Patents

Injection timing advance device for injection pumps for combustion engines Download PDF

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Publication number
EP0167697B1
EP0167697B1 EP85100357A EP85100357A EP0167697B1 EP 0167697 B1 EP0167697 B1 EP 0167697B1 EP 85100357 A EP85100357 A EP 85100357A EP 85100357 A EP85100357 A EP 85100357A EP 0167697 B1 EP0167697 B1 EP 0167697B1
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EP
European Patent Office
Prior art keywords
pressure
injection timing
piston
timing adjuster
hydraulic
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EP85100357A
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German (de)
French (fr)
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EP0167697A1 (en
Inventor
Albert Nolte
Joachim Altdorf
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Kloeckner Humboldt Deutz AG
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Kloeckner Humboldt Deutz AG
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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
    • F02D1/16—Adjustment of injection timing
    • F02D1/18—Adjustment of injection timing with non-mechanical means for transmitting control impulse; with amplification of control impulse
    • 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
    • F02D1/16—Adjustment of injection timing
    • F02D1/18—Adjustment of injection timing with non-mechanical means for transmitting control impulse; with amplification of control impulse
    • F02D1/183—Adjustment of injection timing with non-mechanical means for transmitting control impulse; with amplification of control impulse hydraulic

Definitions

  • the invention relates to a fuel injection timing adjuster according to the preamble of claim 1.
  • a generic injection timing adjuster is known from GB-A 2 029 934.
  • This injection timing adjuster has its own hydraulic pump, which is followed by a hydraulic control valve that can alternately control the hydraulic control fluid in two different pressure chambers. Depending on the position of the control valve and the consequently pressurized pressure chamber, an injection timing adjustment is achieved by moving a helical adjustment device between the primary part and the secondary part.
  • a disadvantage of this injection timing adjuster is the complex hydraulic adjustment device, which has a separate high-pressure pump and a complicated control valve.
  • Another injection timing adjuster (US-A 3,401,572) also requires a hydraulic high-pressure pump, from which the hydraulic fluid must be supplied to the injection timing adjuster in a controlled manner.
  • the hydraulic fluid only adjusts the injection time in one direction, and the return adjustment is carried out by a spring alone. This results in additional problems in coordinating the pressure forces required for the adjustment.
  • the invention is based on the object of proposing a separate injection timing adjuster, which converts the specified size of the injection timing of a control device in a simple manner without retroactive effect on or from the attacking drive torques into an angle of rotation of the injection pump camshaft relative to the drive part.
  • the injection timing distributor should do without complex additional units necessary for adjustment.
  • the primary part is moved on the secondary part by a pressure piston which is acted upon by a pressure medium.
  • the pressure piston is firmly connected to the primary part and forms two pressure chambers in the secondary part, the outflows of which are controlled by a hydraulic control pin.
  • the hydraulic control bolt is controlled directly and without feedback by control electronics.
  • the pressure medium which can be engine oil or fuel of the internal combustion engine in particular and which is under low pressure, is supplied to the two pressure chambers via two check valves.
  • the use of a hydraulic transmission element is particularly useful in connection with the drive of an injection pump.
  • strong alternating torques arise in the entire drive train of the injection pump, which generate a kind of pulsating movement between the drive and output parts of the injection timing adjuster. If the drive part (primary part) is now to be rotated relative to the output part (secondary part), it is not necessary, if these alternating torques are used appropriately, to adjust against the output torque of the injection pump, i. H.
  • the provision of a comparatively low hydraulic medium pressure is sufficient to carry out the adjustment.
  • the injection timing adjuster does not take the force required for the adjustment from the hydraulics, but advantageously adjusts itself self-amplifyingly with the energy of the alternating torques.
  • the control electronics determine the axial position of the pressure piston, and thus also the axial position of the primary part on the secondary part, by opening the discharge opening of the pressure chambers via the hydraulic control pin.
  • An axial displacement of the hydraulic control pin always follows the axial displacement of the primary part and thus the adjustment of the injection timing. Since the displacement of the hydraulic control pin advantageously corresponds exactly to the displacement of the primary part, a return of the controlled variable, namely the angle of rotation of the secondary part to the primary part, is not absolutely necessary, but can also have a positive influence on the quality of the controlled variable.
  • Fig. 1 the individual components of a generic injection timing adjuster are shown schematically, arrows indicating the operative connection between them.
  • the injection timing adjuster is arranged directly on the injection pump camshaft 5 with a secondary part 4.
  • the hub-shaped secondary part 4 is provided with a ring gear-like primary part 3, which is angularly movable and axially displaceable with the secondary part 4 in engagement with helical teeth 9.
  • the primary part 3 can be driven by a driving gear 49 via its external teeth and drives on the other hand, via the secondary part 4, the injection pump camshaft 5.
  • a toothed disk 8 is in turn firmly connected to the secondary part 4.
  • a mark is made both on the ring gear of the primary part 3 and on the toothed disk 8.
  • Two electrical pulse generators 6 and 7 register each passage of the markings and in each case send an electrical pulse to control electronics 1. These pulses give control electronics 1 both information about the speed of the injection pump camshaft 5 and information about the exact instantaneous angle of rotation of the secondary to the primary part of the injection timing adjuster.
  • the two further arrows leading into the control electronics 1 are intended to indicate further operating parameters of the internal combustion engine, which have been converted to electrical quantities by suitable sensors and / or sensors.
  • the control electronics 1 processes all incoming quantities to an electrical setpoint of the angle of rotation of the secondary part to the primary part, ie to a setpoint of the injection time. This electrical signal must be converted into a displacement path of a connecting part 10 with the aid of a converter 2.
  • a hydraulic control pin is axially displaced, for which purpose the electrical signal from the control electronics 1 is converted with a known electrical auxiliary device into a feedback-free displacement path which actuates the hydraulic control pin largely without force.
  • the axial displacement of the connecting part 10 leads through the helical toothing 9 to a change in the angular position of the secondary to the primary part, whereby the control loop of the injection point adjuster is closed via the feedback to the pulse generators 6 and 7.
  • the adjustment of the rotational angle position of the secondary part 4 to the primary part 3 is provided with a hydraulic system.
  • the primary part 3 is arranged on the secondary part 4 axially displaceable with a helical toothing 9.
  • the secondary part 4 is provided with a ring gear 8, two pulse generators 6 and 7 forwarding the rotational angle position of the secondary part 4 to the primary part 3 to separate control electronics 1 by means of electrical pulses.
  • a pressure piston 29 is arranged centrally in the inner bore. This pressure piston 29 forms, with the end of the injection pump camshaft 5 and an annular extension of the secondary part 4, two pressure chambers 36 and 37.
  • the pressure piston 29 is designed as an ordinary differential piston 48 with a piston rod 39.
  • the pressure piston 29 is led out of the secondary part 4 on the cylindrical sealing surface 38 with its piston rod 39 in a pressure-tight manner and is connected in a stationary manner to the connecting part 10 via a screw connection of a nut 19 in a central bore 18 of the same.
  • an axial displacement of the pressure piston 29 leads to the same displacement of the primary part 3 on the secondary part 4.
  • a hydraulic control pin 31 is provided in a bore 30 which is arranged axially parallel in its center.
  • This hydraulic control pin has a drain hole 32, two control edges 33 and two connecting drain holes 47.
  • the two pressure chambers 36, 37 are connected via holes 34 to the hole 30 of the hydraulic control bolt 31.
  • the two control edges 33 of the hydraulic control bolt 31 control the outflow of the two pressure chambers 36 and 37 via the connecting bores 34 fed to the two pressure chambers 36 and 37 via two check valves 45. Furthermore, the pressure piston 29 is acted upon in the axial direction by a spring force (spring 35).
  • the injection timing adjuster does not take the force required for the adjustment from the hydraulics, but advantageously adjusts itself self-amplifying with the energy of the alternating torques.
  • an expensive high-pressure hydraulic pump is superfluous and, in particular, the use of the pressurized engine oil of the internal combustion engine as a hydraulic medium is suggested.
  • the primary part 3 is driven from the outside and in turn drives the secondary part 4 via the helical teeth 9.
  • the connecting part 10 and the pressure piston 29 rotate accordingly.
  • the hydraulic control bolt closes with its control edges 33 all connecting bores 34 to the two pressure chambers 36 and 37.
  • no hydraulic fluid can flow into the two pressure chambers 36 and 37 via the two check valves 45, the pressure piston 29 is therefore fixed in its axial position with respect to the secondary part.
  • the control electronics 1 specifies an axial displacement of the hydraulic control pin 31.
  • the electrical impulses or signals of the control electronics 1 from one Known converter implemented in a displacement path proportional to the electrical signals and feedback-free.
  • a feedback of the angle of rotation position of the secondary part 4 to the primary part 3 via electrical pulse generators 6 and 7 can be omitted, since the axial position of the hydraulic control pin 31 uniquely specifies the size of the change in the angle of rotation position. In some cases, however, in the interest of the control quality, it may prove advantageous to feed back the angle of rotation position.
  • the hydraulic control pin 31 To change the injection timing in the other direction, the hydraulic control pin 31 must be shifted in the opposite direction. The process then takes place accordingly on the second control edge 33 of the hydraulic control pin 31.
  • the pressure piston 29 is still acted upon by a spring force of a spring 35.
  • This spring force is not necessary for the operation of the injection timing adjuster, but it ensures that a well-defined value of the injection timing is reached when the internal combustion engines are switched on.

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

Description

Die Erfindung bezieht sich auf einen Kraftstoffeinspritzzeitpunktversteller gemäß dem Oberbegriff des Patentanspruchs 1.The invention relates to a fuel injection timing adjuster according to the preamble of claim 1.

Ein gattungsgemäßer Einspritzzeitpunktversteller ist aus der GB-A 2 029 934 bekannt. Dieser Einspritzzeitpunktversteller weist eine eigene Hydraulikpumpe auf, der ein hydraulisches Steuerventil nachgeschaltet ist, das die hydraulische Steuerflüssigkeit abwechselnd in zwei verschiedene Druckräume steuern kann. Entsprechend der Stellung des Steuerventils und des demzufolge druckbeaufschlagten Druckraums wird eine Einspritzzeitpunktverstellung durch Verschieben einer schrägverzahnten Verstellvorrichtung zwischen Primärteil und Sekundärteil erreicht. Nachteilig an diesem Einspritzzeitpunktversteller ist die aufwendige hydraulische Verstellvorrichtung, die eine separate Hochdruckpumpe sowie ein kompliziertes Steuerventil aufweist.A generic injection timing adjuster is known from GB-A 2 029 934. This injection timing adjuster has its own hydraulic pump, which is followed by a hydraulic control valve that can alternately control the hydraulic control fluid in two different pressure chambers. Depending on the position of the control valve and the consequently pressurized pressure chamber, an injection timing adjustment is achieved by moving a helical adjustment device between the primary part and the secondary part. A disadvantage of this injection timing adjuster is the complex hydraulic adjustment device, which has a separate high-pressure pump and a complicated control valve.

Auch ein weiterer Einspritzzeitpunktversteiier (US-A 3,401,572) benötigt eine Hydraulik-Hochdruckpumpe, von der das Hydraulikfluid gesteuert dem Einspritzzeitpunktversteller zugeführt werden muß. Dabei bewirkt die Hydraulikflüssigkeit nur eine Einspritzzeitverstellung in eine Richtung, und die Rückverstellung wird von einer Feder alleinig vorgenommen. Dadurch ergeben sich zusätzliche Probleme bei der Abstimmung der zur Verstellung erforderlichen Druckkräfte.Another injection timing adjuster (US-A 3,401,572) also requires a hydraulic high-pressure pump, from which the hydraulic fluid must be supplied to the injection timing adjuster in a controlled manner. The hydraulic fluid only adjusts the injection time in one direction, and the return adjustment is carried out by a spring alone. This results in additional problems in coordinating the pressure forces required for the adjustment.

Der Erfindung liegt die Aufgabe zugrunde, einen separaten Einspritzzeitpunktversteller vorzuschlagen, der die Vorgabegröße des Einspritzzeitpunktes einer Regeleinrichtung auf einfache Weise ohne Rückwirkung auf oder von den angreifenden Antriebsmomenten in einen Verdrehwinkel der Einspritzpumpennockenwelle zum Antriebsteil umsetzt. Dabei soll der Einspritzzeitpunktversteiler ohne aufwendige, zur Verstellung notwendige Zusatzaggregate auskommen.The invention is based on the object of proposing a separate injection timing adjuster, which converts the specified size of the injection timing of a control device in a simple manner without retroactive effect on or from the attacking drive torques into an angle of rotation of the injection pump camshaft relative to the drive part. The injection timing distributor should do without complex additional units necessary for adjustment.

Diese Aufgabe wird von dem erfindungsgemä-βen Einspritzzeitpunktversteller durch die im Kennzeichen des Anspruchs 1 aufgeführten Merkmale gelöst.This object is achieved by the injection timing adjuster according to the invention by the features listed in the characterizing part of claim 1.

Dazu wird das Primärteil auf dem Sekundärteil durch einen Druckkolben verschoben, der von einem Druckmittel beaufschlagt wird. Der Druckkolben ist mit dem Primärteil fest verbunden und bildet im Sekundärteil zwei Druckräume, deren Abflüsse von einem Hydraulikansteuerungsbolzen, beherrscht werden. Der Hydraulikansteuerungsbolzen wird von einer Regelelektronik direkt und rückführungsfrei angesteuert. Das Druckmittel, welches insbesondere Motoröl oder Kraftstoff der Brennkraftmaschine sein kann, der/das unter geringem Druck steht, wird über zwei Rückschlagventile den beiden Druckräumen zugeführt.For this purpose, the primary part is moved on the secondary part by a pressure piston which is acted upon by a pressure medium. The pressure piston is firmly connected to the primary part and forms two pressure chambers in the secondary part, the outflows of which are controlled by a hydraulic control pin. The hydraulic control bolt is controlled directly and without feedback by control electronics. The pressure medium, which can be engine oil or fuel of the internal combustion engine in particular and which is under low pressure, is supplied to the two pressure chambers via two check valves.

Die Verwendung eines hydraulischen Übertragungselementes ist gerade in Verbindung mit dem Antrieb eine Einspritzpumpe besonders sinnvoll. Im Betrieb entstehen im gesamten Antriebsstrang der Einspritzpumpe starke Wechselmomente, die eine Art pulsierende Bewegung zwischen Antriebs- und Abtriebsteil des Einspritzzeitpunktverstellers erzeugen. Soll jetzt das Antriebsteil (Primärteil) gegenüber dem Abtriebsteil (Sekundärteil) verdreht werden, so ist es, wenn man diese Wechselmomente geeignet ausnutzt, nicht nötig, entgegen dem Abtriebsmoment der Einspritzpumpe zu verstellen, d. h. bei Verwendung einer Hydraulik genügt die Bereitstellung eines vergleichsweise geringen Hydraulikmitteldruckes, um die Verstellung durchzuführen. Der Einspritzzeitpunktversteller entnimmt die zur Verstellung nötige Kraft nicht aus der Hydraulik, sondem verstellt sich vorteilhafterweise selbstverstärkend mit der Energie der Wechselmomente. Dadurch ist eine teure Hydraulikhochdruckpumpe überflüssig und insbesondere die Verwendung des unter Druck stehenden Motoröls der Brennkraftmaschine als Hydraulikdruckmittel möglich. Es sind im weiteren alle bekannten Hydraulikflüssigkeiten möglich, wenn sie beispielsweise durch eine Pumpe auf einen, im Vergleich zu sonst üblichen Werten bei Hydrauliken, geringen Hydraulikdruck gebracht werden.The use of a hydraulic transmission element is particularly useful in connection with the drive of an injection pump. During operation, strong alternating torques arise in the entire drive train of the injection pump, which generate a kind of pulsating movement between the drive and output parts of the injection timing adjuster. If the drive part (primary part) is now to be rotated relative to the output part (secondary part), it is not necessary, if these alternating torques are used appropriately, to adjust against the output torque of the injection pump, i. H. When using a hydraulic system, the provision of a comparatively low hydraulic medium pressure is sufficient to carry out the adjustment. The injection timing adjuster does not take the force required for the adjustment from the hydraulics, but advantageously adjusts itself self-amplifyingly with the energy of the alternating torques. This makes an expensive hydraulic high-pressure pump superfluous and in particular the use of the pressurized engine oil of the internal combustion engine as hydraulic pressure medium is possible. In addition, all known hydraulic fluids are possible if, for example, they are brought to a low hydraulic pressure by means of a pump, in comparison to values which are otherwise customary in hydraulics.

Die Regelelektronik legt über den Hydraulikansteuerungsbolzen durch Freigabe der Abflußöffnung der Druckräume die axiale Lage des Druckkolbens, und damit auch die axiale Stellung des Primärteils auf dem Sekundärteil, fest. Einer axialen Verschiebung des Hydraulikansteuerungsbolzens folgt also stets die axiale Verschiebung des Primärteils und somit die Verstellung des Einspritzzeitpunktes. Da die Verschiebung des Hydraulikansteuerungsbolzens in vorteilhafter Weise genau der Verschiebung des Primärteils entspricht, ist eine Rückführung der Regelgröße, nämlich des Verdrehwinkels des Sekundärteils zum Primärteil nicht unbedingt nötig, kann aber auch hier positive Einflüsse auf die Güte der Regelgröße haben.The control electronics determine the axial position of the pressure piston, and thus also the axial position of the primary part on the secondary part, by opening the discharge opening of the pressure chambers via the hydraulic control pin. An axial displacement of the hydraulic control pin always follows the axial displacement of the primary part and thus the adjustment of the injection timing. Since the displacement of the hydraulic control pin advantageously corresponds exactly to the displacement of the primary part, a return of the controlled variable, namely the angle of rotation of the secondary part to the primary part, is not absolutely necessary, but can also have a positive influence on the quality of the controlled variable.

Zur weiteren Erläuterung der Erfindung wird auf die Zeichnung verwiesen, in der ein Ausführungsbeispiel der Erfindung dargestellt ist. Es zeigen :

  • Fig. 1 eine schematische Darstellung der einzelnen Komponenten eines gattungsgemäßen Einspritzzeitpunktverstellers ;
  • Fig. 2 einen Längsschnitt durch einen-Einspritzzeitpunktversteller mit einem hydraulischen Druckkolben.
To further explain the invention, reference is made to the drawing, in which an embodiment of the invention is shown. Show it :
  • Figure 1 is a schematic representation of the individual components of a generic injection timing adjuster.
  • Fig. 2 shows a longitudinal section through an injection timing adjuster with a hydraulic pressure piston.

In Fig. 1 sind schematisch die einzelenen Komponenten eines gattungsgemäßen Einspritzzeitpunktverstellers dargestellt, wobei Pfeile die Wirkverbindung zwischen diesen andeuten. Der Einspritzzeitpunktversteiier ist mit einem Sekundärteil 4 auf der Einspritzpumpennockenwelle 5 direkt angeordnet. Das nabenförmige Sekundärteil 4 ist mit einem zahnkranzartigen Primärteil 3 versehen, das mit einer Schrägverzahnung 9 angular beweglich und axial verschieblich mit dem Sekundärteil 4 im Eingriff steht. Das Primärteil 3 ist von einem antreibenden Zahnrad 49 über seine Außenverzahnung antreibbar und treibt seinerseits über das Sekundärteil 4 die Einspritzpumpennockenwelle 5 an. Eine Zahnscheibe 8 ist wiederum mit dem Sekundärteil 4 fest verbunden. Sowohl auf dem Zahnkranz des Primärteils 3 als auch auf der Zahnscheibe 8 ist je eine Markierung angebracht. Zwei elektrischen Impulsgeber 6 und 7 registrieren jeden Vorbeilauf der Markierungen und senden dabei je einen elektrischen Impuls an eine Regelelektronik 1. Durch diese Impulse besitzt die Regelelektronik 1 sowohl Informationen über die Drehzahl der Einspritzpumpennockenwelle 5, als auch Informationen über den exakten momentanen Verdrehwinkel des Sekundär- zum Primärteil des Einspritzzeitpunktverstellers. Die zwei weiteren in die Regelelektronik 1 hineinführenden Pfeile sollen weitere Betriebsparameter der Brennkraftmaschine andeuten, die durch geeignete Geber und/oder Meßfühler zu elektrischen Größen umgewandelt worden sind. Die Regelelektronik 1 verarbeitet alle eingehenden Größen zu einem elektrischen Sollwert des Verdrehwinkels des Sekundär- zum Primärteil, d. h. zu einem Sollwert des Einspritzzeitpunktes. Dieses elektrische Signal muß mit Hilfe eines Umsetzers 2 in einen Verschiebeweg eines Verbindungsteils 10 umgesetzt werden.In Fig. 1, the individual components of a generic injection timing adjuster are shown schematically, arrows indicating the operative connection between them. The injection timing adjuster is arranged directly on the injection pump camshaft 5 with a secondary part 4. The hub-shaped secondary part 4 is provided with a ring gear-like primary part 3, which is angularly movable and axially displaceable with the secondary part 4 in engagement with helical teeth 9. The primary part 3 can be driven by a driving gear 49 via its external teeth and drives on the other hand, via the secondary part 4, the injection pump camshaft 5. A toothed disk 8 is in turn firmly connected to the secondary part 4. A mark is made both on the ring gear of the primary part 3 and on the toothed disk 8. Two electrical pulse generators 6 and 7 register each passage of the markings and in each case send an electrical pulse to control electronics 1. These pulses give control electronics 1 both information about the speed of the injection pump camshaft 5 and information about the exact instantaneous angle of rotation of the secondary to the primary part of the injection timing adjuster. The two further arrows leading into the control electronics 1 are intended to indicate further operating parameters of the internal combustion engine, which have been converted to electrical quantities by suitable sensors and / or sensors. The control electronics 1 processes all incoming quantities to an electrical setpoint of the angle of rotation of the secondary part to the primary part, ie to a setpoint of the injection time. This electrical signal must be converted into a displacement path of a connecting part 10 with the aid of a converter 2.

Dazu wird gemäß der Erfindung (Fig. 2) ein Hydraulikansteuerungsbolzen axial verschoben, wozu das elektrische Signal der Regelelektronik 1 noch mit einer bekannten elektrischen Hilfseinrichtung in einen rückführungsfreien Verschiebeweg, der den Hydraulikansteuerungsbolzen weitgehend kraftfrei betätigt, umgesetzt wird. Der axiale Verschiebeweg des Verbindungsteil 10 führt durch die Schrägverzahnung 9 zu einer Veränderung der Drehwinkelstellung des Sekundär- zum Primärteil, womit der Regelkreis des Einspritzzeipuntkverstellers über die Rückkopplung an den Impulsgebem 6 und 7 geschlossen ist.For this purpose, according to the invention (FIG. 2), a hydraulic control pin is axially displaced, for which purpose the electrical signal from the control electronics 1 is converted with a known electrical auxiliary device into a feedback-free displacement path which actuates the hydraulic control pin largely without force. The axial displacement of the connecting part 10 leads through the helical toothing 9 to a change in the angular position of the secondary to the primary part, whereby the control loop of the injection point adjuster is closed via the feedback to the pulse generators 6 and 7.

In Fig. 2 ist die Verstellung der Drehwinkelstellung des Sekundärteils 4 zum Primärteil 3 mit einer Hydraulik vorgesehen. Das Primärteil 3 ist auf dem Sekundärteil 4 axial verschieblich mit einer Schrägverzahnung 9 angeordnet. Im weiteren ist das Sekundärteil 4 mit einem Zahnkranz 8 versehen, wobei zwei Impulsgeber 6 und 7 die Drehwinkelstellung des Sekundärteils 4 zum Primärteil 3 an eine separate Regelelektronik 1 mittels elektrischer Impulse weiterleiten. In dem Sekundärteil 4 ist in der Innenbohrung ein Druckkolben 29 zentrisch angeordnet. Dieser Druckkolben 29 bildet mit dem Ende der Einspritzpumpennockenwelle 5 und einem ringförmigen Fortsatz des Sekundärteils 4 zwei Druckräume 36 und 37. Der Druckkolben 29 ist dabei als gewöhnlicher Differentialkolben 48 mit einer Kolbenstange 39 ausgeführt. Im weiteren ist der Druckkolben 29 druckmitteldicht aus dem Sekundärteil 4 an der zylindrischen Dichtfläche 38 mit seiner Kolbenstange 39 herausgeführt und ortsfest mit dem Verbindungsteil 10 über eine Verschraubung einer Mutter 19 in einer zentrischen Bohrung 18 desselben verbunden. Somit führt eine axiale Verschiebung des Druckkolbens 29 zu einer gleichen Verschiebung des Primärteils 3 auf dem Sekundärteil 4. In dem Druckkolben 29 ist in einer Bohrung 30, die achsparallel in seiner Mitte angeordnet ist, ein Hydraulikansteuerungsbolzen 31 vorgesehen. Dieser Hydraulikansteuerungsbolzen weist eine Abflußbohrung 32, zwei Steuerkanten 33 und zwei verbindende Abflußbohrungen 47 auf. Die beiden Druckräume 36, 37 sind über Bohrungen 34 mit der Bohrung 30 des Hydraulikansteuerungsbolzens 31 verbunden. Die beiden Steuerkanten 33 des Hydraulikansteuerungsbolzens 31 beherrschen über die Verbindungsbohrungen 34 den Abfluß der beiden Druckräume 36 und 37. Das Hydraulikmittel wird durch Hohlbohrungen 41 in dem Gehäuse 11 über ein Lager 42 der Einspritzpumpennockenwelle 5, einem Ringkanal 43 und weitere Bohrungen 44 in der Einspritzpumpennockenwelle 5 über zwei Rückschlagventile 45 den beiden Druckräumen 36 und 37 zugeführt. Im weiteren wird der Druckkolben 29 noch durch eine Federkraft (Feder 35) in axialer Richtung beaufschlagt.2, the adjustment of the rotational angle position of the secondary part 4 to the primary part 3 is provided with a hydraulic system. The primary part 3 is arranged on the secondary part 4 axially displaceable with a helical toothing 9. Furthermore, the secondary part 4 is provided with a ring gear 8, two pulse generators 6 and 7 forwarding the rotational angle position of the secondary part 4 to the primary part 3 to separate control electronics 1 by means of electrical pulses. In the secondary part 4, a pressure piston 29 is arranged centrally in the inner bore. This pressure piston 29 forms, with the end of the injection pump camshaft 5 and an annular extension of the secondary part 4, two pressure chambers 36 and 37. The pressure piston 29 is designed as an ordinary differential piston 48 with a piston rod 39. Furthermore, the pressure piston 29 is led out of the secondary part 4 on the cylindrical sealing surface 38 with its piston rod 39 in a pressure-tight manner and is connected in a stationary manner to the connecting part 10 via a screw connection of a nut 19 in a central bore 18 of the same. Thus, an axial displacement of the pressure piston 29 leads to the same displacement of the primary part 3 on the secondary part 4. In the pressure piston 29, a hydraulic control pin 31 is provided in a bore 30 which is arranged axially parallel in its center. This hydraulic control pin has a drain hole 32, two control edges 33 and two connecting drain holes 47. The two pressure chambers 36, 37 are connected via holes 34 to the hole 30 of the hydraulic control bolt 31. The two control edges 33 of the hydraulic control bolt 31 control the outflow of the two pressure chambers 36 and 37 via the connecting bores 34 fed to the two pressure chambers 36 and 37 via two check valves 45. Furthermore, the pressure piston 29 is acted upon in the axial direction by a spring force (spring 35).

Die Wirkungsweise eines derartigen hydraulischen Einspritzzeitpunktverstellers beruht auf den auf der Einspritzpumpennockenwelle angreifenden Wechselmomenten. Im Betrieb entstehen im gesamten Antriebsstrang der Einspritzpumpe starke Wechselmomente, die eine Art pulsierende Bewegung zwischen Antriebs- und Abtriebsteil des Einspritzzeitpunktversteller erzeugen. Soll jetzt das Antriebsteil (Primärteil) gegenüber dem Abtriebsteil (Sekundärteil) verdreht werden, so ist es, wenn man diese Wechselmomente geeignet ausnutzt, nicht nötig, entgegen den Antriebsmomenten der Einspritzpumpe zu verstellen, d. h. bei Verwendung einer Hydraulik genügt die Bereitstellung eines vergleichsweise geringen Hydraulikmitteldruckes, um die Verstellung durchzuführen. Der Einspritzzeitpunktversteiier entnimmt die zur Verstellung nötige Kraft nicht aus der Hydraulik, sondem verstellt sich vorteilhaiterweise selbstverstärkend mit der Energie der Wechslmomente. Dadurch ist eine teure Hydraulikhochdruckpumpe überflüssig und insbesondere die Verwendung des unter Druck stehendes Motoröls der Brennkraftmaschine als Hydraulikmittel nahegelegt.The operation of such a hydraulic injection timing adjuster is based on the alternating torques acting on the injection pump camshaft. During operation, strong alternating torques are generated in the entire drive train of the injection pump, which generate a kind of pulsating movement between the drive and output parts of the injection timing adjuster. If the drive part (primary part) is now to be rotated relative to the output part (secondary part), it is not necessary, if these alternating torques are used appropriately, to adjust against the drive torques of the injection pump, i. H. When using a hydraulic system, the provision of a comparatively low hydraulic medium pressure is sufficient to carry out the adjustment. The injection timing adjuster does not take the force required for the adjustment from the hydraulics, but advantageously adjusts itself self-amplifying with the energy of the alternating torques. As a result, an expensive high-pressure hydraulic pump is superfluous and, in particular, the use of the pressurized engine oil of the internal combustion engine as a hydraulic medium is suggested.

Das Primärteil 3 wird von außen angetrieben und treibt seinerseits über die Schrägverzahnung 9 das Sekundärteil 4 an. Das Verbindungsteil 10 und der Druckkolben 29 drehen sich entsprechend mit. Der Hydraulikansteuerungsbolzen verschließt mit seinen Steuerkanten 33 alle Verbindungsbohrungen 34 zu den beiden Druckräumen 36 und 37. Infolgedessen kann über die beiden Rückschlagventile 45 kein Hydraulikmittel in die beiden Druckräume 36 und 37 nachfließen, der Druckkolben 29 ist also in seiner axialen Position gegenüber dem Sekundärteil fixiert. Soll jetzt der Einspritzzeitpunkt verändert werden, d. h. die Drehwinkelstellung des Sekundärteils 4 zum Primärteil 3, so gibt die Regelelektronik 1 eine axiale Verschiebung des Hydraulikansteuerungsbolzens 31 vor. Dabei werden die elektrischen Impulse oder Signale der Regelelektronik 1 von einem bekannten Umsetzer in einen den elektrischen Signalen proportionalen und rückführungsfreien Verschiebeweg umgesetzt. Es braucht hierbei insbesondere keine größere Kraft aufgebracht zu werden. Infolge dieser Verschiebung des Hydraulikansteuerungsbolzens 31 gibt eine Steuerkante 33 die Verbindungsbohrungen 34 zu einem der Druckräume, beispielsweise 37, frei. Das Hydraulikdruckmittel kann so über die erwähnten Verbindungsbohrungen 34 und die Abflußbohrung 47 durch die weitere Abflußbohrung 32 in dem Hydraulikansteuerungsbolzen 31 aus dem Sekundärteil heraus ins Freie abfließen. Eine Verschiebung des Druckkolbens 29 in Richtung dieses Druckraums 37 kann also erfolgen und wird, durch die Wechselmomente angetrieben, ausgeführt. Gleichzeitig füllt sich der andere Druckraum 36 über das Rückschlagventil 45 mit Hydraulikmittel weiter auf. Der Druckkolben 29 kann sich nicht in Richtung des Druckraumes 36 verschieben, da das Rückschlagventil 45 nur einen Hydraulikmittelzufluß gestattet und die Verbindungsbohrung 34 des Druckrames 36 von dem Hydraulikansteuerungsbolzen 31 verschlossen ist Dies funktioniert solange, bis der Druckkolben über die Steuerkanten 33 hinweggeglitten ist, d. h. die Verbindungsbohrungen 34 des Druckraums 37 wieder verschlossen sind. Damit ist eine erneute stabile axiale Lage des Druckkolbens erreicht, welcher sich jetzt nicht mehr verschieben kann. Durch die axiale Verschiebung des Druckkolbens ist das Primärteil 3 auf dem Sekundärteil 4 ebenfalls in dieselbe axiale Richtung gewandert und hat damit die Drehwinkelstellung des Sekundärteils 4 zum Primärteil 3 entsprechend geändert.The primary part 3 is driven from the outside and in turn drives the secondary part 4 via the helical teeth 9. The connecting part 10 and the pressure piston 29 rotate accordingly. The hydraulic control bolt closes with its control edges 33 all connecting bores 34 to the two pressure chambers 36 and 37. As a result, no hydraulic fluid can flow into the two pressure chambers 36 and 37 via the two check valves 45, the pressure piston 29 is therefore fixed in its axial position with respect to the secondary part. If the injection timing is to be changed now, ie the angle of rotation position of the secondary part 4 relative to the primary part 3, then the control electronics 1 specifies an axial displacement of the hydraulic control pin 31. The electrical impulses or signals of the control electronics 1 from one Known converter implemented in a displacement path proportional to the electrical signals and feedback-free. In particular, no greater force needs to be applied. As a result of this displacement of the hydraulic control pin 31, a control edge 33 releases the connecting bores 34 to one of the pressure spaces, for example 37. The hydraulic pressure medium can thus flow out of the secondary part out of the secondary part via the connection bores 34 and the drain bore 47 through the further drain bore 32 in the hydraulic control bolt 31. A displacement of the pressure piston 29 in the direction of this pressure chamber 37 can thus take place and is carried out, driven by the alternating torques. At the same time, the other pressure chamber 36 continues to fill up with hydraulic fluid via the check valve 45. The pressure piston 29 cannot move in the direction of the pressure chamber 36, since the check valve 45 only allows hydraulic fluid to flow in and the connecting bore 34 of the pressure ram 36 is closed by the hydraulic control bolt 31. This works until the pressure piston has slid over the control edges 33, that is to say that Connection bores 34 of the pressure chamber 37 are closed again. A renewed stable axial position of the pressure piston is thus achieved, which can no longer move. Due to the axial displacement of the pressure piston, the primary part 3 on the secondary part 4 has also migrated in the same axial direction and has accordingly changed the angular position of the secondary part 4 relative to the primary part 3.

Eine Rückkopplung der Drehwinkelstellung des Sekundärteils 4 zum Primärteil 3 über elektrische Impulsgeber 6 und 7 kann entfallen, da die axiale Lage des Hydraulikansteuerungsbolzens 31 in eindeutiger Weise die Größe der Drehwinkelstellungsänderung vorgibt. In einigen Fällen kann es sich im Interesse der Regelgüte jedoch als vorteilhaft erweisen, auch hier eine Rückkopplung der Drehwinkelstellung vorzunehmen. Für die Änderung des Einspritzzeitpunktes in die andere Richtung muß der Hydraulikansteurungsbolzen 31 entgegengesetzt verschoben werden. Der Vorgang läuft dann entsprechend an der zweiten Steuerkante 33 des Hydraulikansteuerungsbolzens 31 ab.A feedback of the angle of rotation position of the secondary part 4 to the primary part 3 via electrical pulse generators 6 and 7 can be omitted, since the axial position of the hydraulic control pin 31 uniquely specifies the size of the change in the angle of rotation position. In some cases, however, in the interest of the control quality, it may prove advantageous to feed back the angle of rotation position. To change the injection timing in the other direction, the hydraulic control pin 31 must be shifted in the opposite direction. The process then takes place accordingly on the second control edge 33 of the hydraulic control pin 31.

Der Druckkolben 29 ist noch durch eine Federkraft einer Feder 35 beaufschlagt. Diese Federkraft ist für den Betrieb des Einspritzzeitpunktverstellers nicht notwendig, sie stellt jedoch sicher, daß bei Einschalten der Brennkraftmaschinen ein wohldefinierter Wert des Einspritzzeitpunktes erreicht wird.The pressure piston 29 is still acted upon by a spring force of a spring 35. This spring force is not necessary for the operation of the injection timing adjuster, but it ensures that a well-defined value of the injection timing is reached when the internal combustion engines are switched on.

Claims (12)

1. An injection timing adjuster of an injection pump for an intemal combustion engine, which adjuster is arranged on the drive of the injection pump, comprising a driving primary part (3) and a driven secondary part (4) which is connected with the injection pump cam shaft (5), wherein the mechanical force transmission from the primary part (3) to the secondary part (4) takes place through a helical gearing (9) and for the achieving of an adjustment of angle of rotation between the primary part (3) and the secondary part (4), a hydraulic displacer device is provided for the shifting of one of the parts (3, 4), which device consists of a hydraulic piston (29) acting upon one part, which piston is movable by pressure charging of a first pressure chamber (36) in the one shifting direction and by pressure charging of a second pressure chamber (37) in the other shifting direction, and in that for the controlling of the movement in the shifting directions a hydraulic control valve is provided which is actuated according to the rotation angle position preset value ascertained by an electric regulating device, the rotation angle position preset value being ascertained at least from the rotation rate of the primary part or of the crank-shaft detected by the pulse emitters, characterised in that the pressure chambers (36, 37) are fed through non- return valves (45) in common by way of a hydraulic medium supply with low-pressure pressure means and the control valve (31) controls the outflows (34) of the pressure chambers (36, 37).
2. An injection timing adjuster according to Claim 1, characterised in that the piston is a double-acting pressure piston (29) firmly connected with the primary part (3) which pressure piston defines, in the secondary part, two pressure chambers with the secondary part.
3. An injection timing adjuster according to Claim 1 or 2, characterised in that the control valve is a hydraulic control bolt (31) arranged in the centre of the pressure piston (29) in a blind bore (30), which bolt is actuatable from the exterior through a bore (18) in the primary part (3).
4. An injection timing adjuster according to any one of Claims 1 to 3, characterised in that the pressure piston (29) comprises a differential piston (48) and a piston rod (39), the pressure piston defining two annular pressure chambers (36, 37).
5. An injection timing adjuster according to any one of Claims 1 to 4, characterised in that the pressure piston (29) protrudes with its cylindrical, sealed-off piston rod (39) from the secondary part (4).
6. An injection timing adjuster according to any one of Claims 1 to 5, characterised in that the pressure piston (29) is loaded from one side by a spring (35).
7. An injection timing adjuster according to any one of Claims 1 to 6, characterised in that the pressure medium supply into the two pressure chambers (36, 37) is provided through hollow bores (41) in the housing (11) of the injection timing adjuster, through the bearings (42) of the injection pump cam shaft (5) and through hollow bores (44) in the injection pump cam shaft (5).
8. An injection timing adjuster according to any one of Claims 1 to 7, characterised in that the operating lubricant of the internal combustion engine or the fuel thereof is usable as pressure medium.
9. An injection timing adjuster according to any one of Claims 1 to 8, characterised in that the hydraulic control bolt (31) is provided with an axial hollow bore (32), two control edges (33), and at least one outflow bore (47) connected with the hollow bore (32).
10. An injection timing adjuster according to any one of Claims 1 to 9, characterised in that the hydraulic control bolt (31) in its rest position closes both the outflow opening (34) of the first pressure chamber (36) and the outflow opening (34), of the second pressure chamber (37).
11. An injection timing adjuster according to any one of Claims 1 to 10, characterised in that on displacement of the hydraulic control bolt (31) in one direction the outflow opening (34) of a pressure chamber is cleared by a control edge (33) while the outflow opening (34) of the other pressure chamber remains closed, and vice versa.
12. An injection timing adjuster according to any one of Claims 1 to 11, characterised in that the hydraulic control bolt (31) is actuatable by the electronic regulating system through a converter (2) which converts the electric signal into a proportional distance, while the position of the pressure piston (29) is fixed by way of the position of the hydraulic control bolt (31).
EP85100357A 1984-05-17 1985-01-15 Injection timing advance device for injection pumps for combustion engines Expired - Lifetime EP0167697B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3418321 1984-05-17
DE19843418321 DE3418321A1 (en) 1984-05-17 1984-05-17 INJECTION TIMING ADJUSTMENT OF AN INJECTION PUMP FOR INTERNAL COMBUSTION ENGINES

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EP0167697A1 EP0167697A1 (en) 1986-01-15
EP0167697B1 true EP0167697B1 (en) 1990-01-24

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EP85100357A Expired - Lifetime EP0167697B1 (en) 1984-05-17 1985-01-15 Injection timing advance device for injection pumps for combustion engines

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JP (1) JPS60249629A (en)
DE (2) DE3418321A1 (en)

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DE3830382C1 (en) * 1988-09-07 1990-01-18 Daimler-Benz Aktiengesellschaft, 7000 Stuttgart, De
DE3929620A1 (en) * 1989-09-06 1991-03-07 Bayerische Motoren Werke Ag Adjustment with drive wheel and shaft - has hollow hub mounted in shafts end cavity with flange and thrust ring
CN113738548B (en) * 2021-07-27 2022-06-03 东风汽车集团股份有限公司 High-pressure oil rail pressure control method and system after failure of air inlet phase sensor

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Also Published As

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DE3575588D1 (en) 1990-03-01
DE3418321A1 (en) 1986-04-24
JPS60249629A (en) 1985-12-10
EP0167697A1 (en) 1986-01-15

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