EP2167818B1 - High-pressure fuel pump with roller tappet - Google Patents

High-pressure fuel pump with roller tappet Download PDF

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Publication number
EP2167818B1
EP2167818B1 EP08774082A EP08774082A EP2167818B1 EP 2167818 B1 EP2167818 B1 EP 2167818B1 EP 08774082 A EP08774082 A EP 08774082A EP 08774082 A EP08774082 A EP 08774082A EP 2167818 B1 EP2167818 B1 EP 2167818B1
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EP
European Patent Office
Prior art keywords
tappet
drive shaft
radial piston
piston pump
bore
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Not-in-force
Application number
EP08774082A
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German (de)
French (fr)
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EP2167818A1 (en
Inventor
Eberhard Maier
Bernd Haeusser
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication date
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Publication of EP2167818A1 publication Critical patent/EP2167818A1/en
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Publication of EP2167818B1 publication Critical patent/EP2167818B1/en
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/0404—Details or component parts
    • F04B1/0426—Arrangements for pressing the pistons against the actuated cam; Arrangements for connecting the pistons to the actuated cam
    • F04B1/043—Hydraulic arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0001—Fuel-injection apparatus with specially arranged lubricating system, e.g. by fuel oil
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/0404—Details or component parts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
    • F04B9/02—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical
    • F04B9/04—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical the means being cams, eccentrics or pin-and-slot mechanisms
    • F04B9/042—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical the means being cams, eccentrics or pin-and-slot mechanisms the means being cams

Definitions

  • the invention relates to a radial piston pump for high-pressure fuel generation according to the preamble of claim 1.
  • Such a radial piston pump is through EP-A-0 972 936 known.
  • This radial piston pump has a drive shaft mounted in a pump housing.
  • the radial piston pump also has at least one with respect to the drive shaft radially in each case an element bore arranged piston, wherein the at least one piston is movable by rotating the drive shaft in the element bore in the radial direction back and forth.
  • a plunger is arranged and guided in the pump housing of the plunger and the pump housing in each case a plunger space is limited, wherein the plunger space is hydraulically in communication with an engine room.
  • An indentation for receiving a roller is provided on an end of the tappet facing the drive shaft, with at least part of the hydraulic connections between the tappet space and the engine compartment opening into the recess.
  • a radial piston pump which has a drive shaft mounted in a pump housing.
  • the radial piston pump also has at least one with respect to the drive shaft radially in each case an element bore arranged piston, wherein the at least one piston is movable by rotating the drive shaft in the element bore in the radial direction back and forth.
  • a plunger is arranged and guided in the pump housing of the plunger and the pump housing in each case a plunger space is limited, wherein the plunger space is hydraulically in communication with an engine room.
  • An indentation for receiving a roller is provided on an end of the tappet facing the drive shaft, with at least part of the hydraulic connections between the tappet space and the engine compartment opening into the recess. Also in this radial piston pump lubrication of the roller is achieved by the hydraulic connections, which may still be insufficient under certain circumstances.
  • the radial piston pump according to the invention with the features according to claim 1 has the advantage that the subsidized by the plunger fuel directly to the tribologically most krestensten points, namely the contact zones between Guide body and roller, is supplied. In addition, in this way particles which have developed due to wear between the plunger body and the roller can best be conveyed away from this contact zone.
  • the plunger has at least one groove, but preferably a groove at both ends of the recess, wherein the groove extends substantially in the axial direction of the plunger.
  • At least one connecting bore is provided in the pump housing, and that the at least one Connecting bore two ram spaces hydraulic interconnects.
  • the amount of fuel delivered by the hydraulic fuel of the invention can be limited to the necessary extent, so that the pumping work of the plunger is reduced to the necessary level.
  • two plunger chambers can be hydraulically connected by an external connection line. This variant is recommended if, for structural or other reasons, a connection bore in the pump housing can not be accommodated.
  • the function of the radial piston pump according to the invention can be further improved if the already existing supply of the drive shaft with fuel for cooling and lubrication opens into the hydraulic connection between two plunger chambers, since in this case a defined amount of lubricant for lubrication and cooling purposes the plungers and the Tappet spaces can be supplied. Thereby increases the load capacity of the radial piston pump according to the invention, without additional manufacturing or manufacturing costs.
  • the drive shaft may be formed as a camshaft or as an eccentric shaft. It is also possible to provide the plungers with a roller which roll on the camshaft so that the frictional forces between the plunger and the camshaft are reduced.
  • FIG. 1 schematically shows a radial piston pump for high-pressure fuel supply in fuel injection systems, in particular common rail fuel injection systems, of internal combustion engines in section.
  • radial piston pump is equipped with an integrated demand quantity control.
  • the flow rate control is carried out on the low pressure side via a metering unit ZME.
  • radial piston pump comprises a mounted in a pump housing 1 drive shaft 2 with two offset by 180 ° seconded cam 36. Against the cam 36, two pistons 8 are supported. The pistons 8 are each received in an element bore 11 in the radial direction movable back and forth. The pistons 8 are arranged at an angle of about 90 ° to each other and limit at its end remote from the drive shaft 2 a delivery chamber (not shown).
  • a plate 14 is provided on the piston 8. These plates 14 may be either integral with the piston 8 or removably attached thereto.
  • a spring 17 is biased. The springs 17 press the pistons 8 against the bottoms 20 of the plungers 23.
  • From the bottoms 20 of the plungers 23 extends a cylindrical guide body 26 in the direction of the delivery chambers, not shown. The guide body 26 are part of the plunger 23 and prevent tilting of the plunger 23 in a guide bore 29.
  • the plunger 23 are slidable in the pump housing 1.
  • a semicircular recess 27 is provided which serves to support a roller 28.
  • the recess 27 and the roller 28 form a sliding bearing, while the roller 28 rolls on the cam 36 of the drive shaft 2.
  • the roller 28 i, guide body 26 is fixed. In this case, a relative movement between the end faces of the roller 28 and the guide body 26 takes place, which can cause wear.
  • radial piston pump serves to pressurize fuel that is supplied from a Vor fundamentalpumpe from a tank with high pressure.
  • the pistons 8 are moved away from the axis of rotation of the drive shaft camshaft 2 as a result of the eccentric movement of the cams 36 of the drive shaft 2.
  • the pistons 8 move radially toward the axis of the camshaft 2 in order to suck fuel into the delivery chamber (not shown).
  • FIG. 2 a is the plunger 23 in longitudinal section and in FIG. 2 b) shown in a side view. From the longitudinal section ( Fig. 2a ) can be clearly seen that in the illustrated embodiment, the bottom 20 is inserted into the guide body 26 becomes. To make a positive connection between the bottom 20 and guide body 26, a Seeger ring 30 may be provided.
  • the roller 28 is rounded at its end faces and is fixed in the lateral direction by the guide body 26. Due to the oscillating movement of the plunger 23 in the guide bore 29, the end faces of the roller 28 rotate on the inside of the guide body 26.
  • a hydraulic connection between the plunger chambers 32, 33 on the one hand and the recess 28 is provided according to the invention . Furthermore, the hydraulic connection according to the invention improves the tribological relationships between roller 28 and plunger 23.
  • FIG. 2a Two variants of inventive hydraulic connections are shown. On the right side of FIG. 2a ), a groove 53 is shown, which supplies the contact point between the roller 28 and the guide body 26 with fuel. At the left side of FIG. 2a ) an alternative embodiment of the hydraulic connection according to the invention in the form of a bore 55 is shown, which supplies the contact point between the roller 28 and the guide body 26 with fuel. In general, you will make both sides of a plunger 23 the same.
  • the groove 53 and the bore 55 are alternative embodiments of the invention. Which of these alternatives is given preference in the individual case depends on the circumstances of the individual case.
  • the plunger 23 when the plunger 23 is driven by the cam 36 of the drive shaft, it performs an oscillating motion in FIG. 2a indicated by a double arrow, from. Since there is fuel in both the plunger chambers 32, 33 and in the engine compartment 35, the oscillating movement of the plunger 23 causes fuel to be delivered from the engine compartment 35 into the plunger chambers 32 and 33 when the piston engages FIG. 2a moved from top to bottom. As soon as the plunger 23 moves from the bottom to the top, the flow direction is reversed and fuel from the plunger chambers 32, 33 is conveyed into the engine compartment 35.
  • the volume changes in the plunger chambers 32 and 33 are phase-shifted by 90 °.
  • This phase shift can be exploited by providing a communication bore 37 between the plunger spaces 32 and 33 such that whenever the volume of a plunger space decreases, the fuel in that plunger space is partially ejected into the adjacent plunger space whose volume is the same Time is increasing. The other part of the fuel flows through the groove 53 or the bore 55 and the compensation bores 41 (if present) in the bottom 20 of the plungers 23 and 24.
  • the lubrication of the camshaft 2 and its storage takes place via a lubricant supply 38 with a throttle 39, which directly with fuel from the fuel tank, not shown Internal combustion engine is fed via a supply line 40. From the supply line 40 branches off a line 43 which supplies the metering unit ZME of the radial piston pump with fuel.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Control Of The Air-Fuel Ratio Of Carburetors (AREA)
  • Reciprocating Pumps (AREA)

Abstract

A radial piston pump with a roller tappet in which the service life of the tappet is increased by delivering fuel to the contact faces between the tappet and the roller by way of a hydraulic connection between the tappet chamber and the engine chamber.

Description

Die Erfindung betrifft eine Radialkolbenpumpe zur Kraftstoffhochdruckerzeugung nach der Gattung des Anspruchs 1.The invention relates to a radial piston pump for high-pressure fuel generation according to the preamble of claim 1.

Eine solche Radialkolbenpumpe ist durch die EP-A-0 972 936 bekannt. Diese Radialkolbenpumpe weist eine in einem Pumpengehäuse gelagerte Antriebswelle auf. Die Radialkolbenpumpe weist außerdem mindestens einen bezüglich der Antriebswelle radial in jeweils einer Elementbohrung angeordneten Kolben auf, wobei der mindestens eine Kolben durch Drehen der Antriebswelle in der Elementbohrung in radialer Richtung hin und her bewegbar ist. Zwischen dem Kolben und der Antriebswelle ist ein Stößel angeordnet und im Pumpengehäuse geführt Von den Stößeln und dem Pumpengehäuse ist jeweils ein Stößelraum begrenzt, wobei der Stößelraum hydraulisch mit einen Triebwerksraum in Verbindung steht. An einem der Antriebwelle zugewandten Ende des Stößels ist eine Vertiefung zur Aufnahme einer Rolle vorgesehen, wobei mindestens ein Teil der hydraulischen Verbindungen zwischen Stößelraum und dem Triebwerksraum in der Vertiefung mündet. Hierdurch wird eine Schmierung der Rolle erreicht, die jedoch unter Umständen dennoch nicht ausreichend ist.Such a radial piston pump is through EP-A-0 972 936 known. This radial piston pump has a drive shaft mounted in a pump housing. The radial piston pump also has at least one with respect to the drive shaft radially in each case an element bore arranged piston, wherein the at least one piston is movable by rotating the drive shaft in the element bore in the radial direction back and forth. Between the piston and the drive shaft, a plunger is arranged and guided in the pump housing of the plunger and the pump housing in each case a plunger space is limited, wherein the plunger space is hydraulically in communication with an engine room. An indentation for receiving a roller is provided on an end of the tappet facing the drive shaft, with at least part of the hydraulic connections between the tappet space and the engine compartment opening into the recess. As a result, a lubrication of the role is achieved, which may still not be sufficient under certain circumstances.

Durch die WO 94/27041 A ist ebenfalls eine Radialkolbenpumpe bekannt, die eine in einem Pumpengehäuse gelagerte Antriebswelle aufweist. Die Radialkolbenpumpe weist außerdem mindestens einen bezüglich der Antriebswelle radial in jeweils einer Elementbohrung angeordneten Kolben auf, wobei der mindestens eine Kolben durch Drehen der Antriebswelle in der Elementbohrung in radialer Richtung hin und her bewegbar ist. Zwischen dem Kolben und der Antriebswelle ist ein Stößel angeordnet und im Pumpengehäuse geführt Von den Stößeln und dem Pumpengehäuse ist jeweils ein Stößelraum begrenzt, wobei der Stößelraum hydraulisch mit einen Triebwerksraum in Verbindung steht. An einem der Antriebwelle zugewandten Ende des Stößels ist eine Vertiefung zur Aufnahme einer Rolle vorgesehen, wobei mindestens ein Teil der hydraulischen Verbindungen zwischen Stößelraum und dem Triebwerksraum in der Vertiefung mündet. Auch bei dieser Radialkolbenpumpe wird durch die hydraulischen Verbindungen eine Schmierung der Rolle erreicht, die jedoch unter Umständen dennoch nicht ausreichend ist.By the WO 94/27041 A Also, a radial piston pump is known which has a drive shaft mounted in a pump housing. The radial piston pump also has at least one with respect to the drive shaft radially in each case an element bore arranged piston, wherein the at least one piston is movable by rotating the drive shaft in the element bore in the radial direction back and forth. Between the piston and the drive shaft, a plunger is arranged and guided in the pump housing of the plunger and the pump housing in each case a plunger space is limited, wherein the plunger space is hydraulically in communication with an engine room. An indentation for receiving a roller is provided on an end of the tappet facing the drive shaft, with at least part of the hydraulic connections between the tappet space and the engine compartment opening into the recess. Also in this radial piston pump lubrication of the roller is achieved by the hydraulic connections, which may still be insufficient under certain circumstances.

Vorteile der ErfindungAdvantages of the invention

Die erfindungsgemäße Radialkolbenpumpe mit den Merkmalen gemäß Anspruch 1 hat demgegenüber den Vorteil, dass der durch den Stößel geförderte Kraftstoff direkt an den tribologisch krtischsten Stellen, nämlich den Kontaktzonen zwischen Führungskörper und Rolle, zugeführt wird. Außerdem können auf diese Weise Partikel, die auf Grund von Verschleiß zwischen Stößelkörper und Rolle entstanden sind, am besten von dieser Kontaktzone weg gefördert werden.The radial piston pump according to the invention with the features according to claim 1 has the advantage that the subsidized by the plunger fuel directly to the tribologically most krestensten points, namely the contact zones between Guide body and roller, is supplied. In addition, in this way particles which have developed due to wear between the plunger body and the roller can best be conveyed away from this contact zone.

Eine vorteilhafte Ausgestaltung der Erfindung sieht vor, dass der stößel mindestens eine Nut aufweist, bevorzugt jedoch eine Nut an beiden Enden der Vertiefung, wobei die Nut im Wesentlichen in axialer Richtung des Stößels verläuft. Dadurch ist es auf einfachste Weise möglich, die erfindungsgemäße hydraulische Verbindung zwischen Stößelraum und Vertiefung herzustellen. Alternativ ist es auch möglich, in den Stößel eine Bohrung einzubringen, welche die erfindungsgemäße hydraulische Verbindung zwischen Stößelraum und den Enden der Vertiefung herstelk.An advantageous embodiment of the invention provides that the plunger has at least one groove, but preferably a groove at both ends of the recess, wherein the groove extends substantially in the axial direction of the plunger. This makes it possible in the simplest way to produce the inventive hydraulic connection between plunger space and recess. Alternatively, it is also possible to introduce into the plunger bore, which manufacture the inventive hydraulic connection between plunger space and the ends of the recess.

In weiterer Ergänzung der Erfindung kann vorgesehen sein, dass im Pumpengehäuse mindestens eine Verbindungsbohrung vorgesehen ist, und dass die mindestens eine Verbindungsbohrung zwei Stößelräume hydraulische miteinander verbindet.In a further supplement of the invention it can be provided that at least one connecting bore is provided in the pump housing, and that the at least one Connecting bore two ram spaces hydraulic interconnects.

Dadurch ist es möglich, das "Fördervolumen", des von den Stößeln aus dem Triebwerksraum in die Stößelräume und zurück geförderten Kraftstoffs zu begrenzen.This makes it possible to limit the "delivery volume" of the fuel delivered by the tappets from the engine room into the tappet spaces and back.

Durch eine geeignete Abstimmung des Strömungswiderstands der Verbindungsbohrung und der erfindungsgemäßen hydraulischen Verbindung kann die durch die erfindungsgemäße hydraulische geförderte Kraftstoffmenge auf das notwendige Maß beschränkt werden, so dass die Pumparbeit der Stößel auf das notwendige Maß reduziert wird.By a suitable coordination of the flow resistance of the connecting bore and the hydraulic connection according to the invention, the amount of fuel delivered by the hydraulic fuel of the invention can be limited to the necessary extent, so that the pumping work of the plunger is reduced to the necessary level.

Bei dieser Variante ist es lediglich erforderlich, eine Verbindungsbohrung zusätzlich in das Pumpengehäuse anzubringen, so dass zwei benachbarte Stößelräume hydraulisch miteinander verbunden sind. Diese Maßnahme kann bisweilen auch an bereits in Serie gefertigten Pumpengehäusen vorgenommen werden, so dass eine Nachrüstung bereits in Serie befindlicher Radialkolbenpumpen mit der erfindungsgemäßen hydraulischen Verbindungsbohrung in manchen Fällen möglich ist.In this variant, it is only necessary to additionally attach a connecting bore in the pump housing, so that two adjacent plunger chambers are hydraulically connected to each other. This measure can sometimes be carried out on already manufactured in series pump housings, so that retrofitting already in series befindlicher radial piston pumps with the hydraulic connection bore according to the invention in some cases is possible.

Zusätzlich ist es auch möglich, in die hydraulische Verbindung eine Schmierstoffversorgung münden zu lassen, so dass immer frischer und kühler Kraftstoff an die tribologisch kritische Kontaktstelle zwischen Rolle und Führungskörper gefördert wird.In addition, it is also possible to open a lubricant supply in the hydraulic connection, so that always fresh and cool fuel is conveyed to the tribologically critical contact point between the roller and guide body.

Alternativ können auch zwei Stößelräume durch eine externe Verbindungsleitung hydraulisch verbunden werden. Diese Variante empfiehlt sich dann, wenn aus konstruktiven oder sonstigen Gründen eine Verbindungsbohrung im Pumpengehäuse nicht untergebracht werden kann.Alternatively, two plunger chambers can be hydraulically connected by an external connection line. This variant is recommended if, for structural or other reasons, a connection bore in the pump housing can not be accommodated.

Die Funktion der erfindungsgemäßen Radialkolbenpumpe kann weiter verbessert werden, wenn die ohnehin vorhandene Versorgung der Antriebswelle mit Kraftstoff zur Kühlung und Schmierung in die hydraulische Verbindung zwischen zwei Stößelräumen mündet, da in diesem Fall eine definierte Menge von Schmierstoff zu Schmier- und Kühlzwecken den Stößeln und den Stößelräumen zugeführt werden kann. Dadurch steigt die Belastbarkeit der erfindungsgemäßen Radialkolbenpumpe, ohne zusätzlichen Herstellungs- oder Fertigungsaufwand.The function of the radial piston pump according to the invention can be further improved if the already existing supply of the drive shaft with fuel for cooling and lubrication opens into the hydraulic connection between two plunger chambers, since in this case a defined amount of lubricant for lubrication and cooling purposes the plungers and the Tappet spaces can be supplied. Thereby increases the load capacity of the radial piston pump according to the invention, without additional manufacturing or manufacturing costs.

Bei der erfindungsgemäßen Radialkolbenpumpe kann die Antriebswelle als Nockenwelle oder als Exzenterwelle ausgebildet sein. Ebenso ist es möglich, die Stößel mit einer Rolle zu versehen, welche auf der Nockenwelle abrollen, so dass die Reibungskräfte zwischen Stößel und Nockenwelle reduziert werden.In the radial piston pump according to the invention, the drive shaft may be formed as a camshaft or as an eccentric shaft. It is also possible to provide the plungers with a roller which roll on the camshaft so that the frictional forces between the plunger and the camshaft are reduced.

Weitere Vorteile, Merkmale und Einzelheiten der Erfindung ergeben sich aus der nachfolgenden Beschreibung, in der unter Bezugnahme auf die Zeichnung mehrere Ausführungsbeispiele der Erfindung im Einzelnen beschrieben sind. Dabei können die in den Ansprüchen und in der Beschreibung erwähnten Merkmale jeweils einzeln für sich oder in beliebiger Kombination erfindungswesentlich sein.Further advantages, features and details of the invention will become apparent from the following description in which several embodiments of the invention are described in detail with reference to the drawing. The features mentioned in the claims and in the description may each be essential to the invention individually or in any desired combination.

In der Zeichnung zeigt:

  • Zeichnungen
  • Figur 1
    einen Schnitt durch ein Ausführungsbeispiel einer erfindungsgemäßen Radialkolbenpumpe;
    Figur 2
    eine vergrößerte Darstellung eines erfindungsgemäßen Rollenstößels.
In the drawing shows:
  • drawings
  • FIG. 1
    a section through an embodiment of a radial piston pump according to the invention;
    FIG. 2
    an enlarged view of a roller tappet according to the invention.

Ausführungsformen der ErfindungEmbodiments of the invention

Die Figur 1 zeigt schematisch eine Radialkolbenpumpe zur Kraftstoffhochdruckversorgung bei Kraftstoffeinspritzsystemen, insbesondere Common-Rail-Kraftstoffeinspritzsystemen, von Brennkraftmaschinen im Schnitt. Die in Figur 1 dargestellte Radialkolbenpumpe ist mit einer integrierten Bedarfsmengenregelung ausgestattet. Die Fördermengenregelung erfolgt niederdruckseitig über eine Zumesseinheit ZME.The FIG. 1 schematically shows a radial piston pump for high-pressure fuel supply in fuel injection systems, in particular common rail fuel injection systems, of internal combustion engines in section. In the FIG. 1 shown radial piston pump is equipped with an integrated demand quantity control. The flow rate control is carried out on the low pressure side via a metering unit ZME.

Die in Figur 1 gezeigte Radialkolbenpumpe umfasst eine in einem Pumpengehäuse 1 gelagerte Antriebswelle 2 mit zwei um 180° versetzt abgeordneten Nocken 36. Gegen die Nocken 36 stützen sich zwei Kolben 8 ab. Die Kolben 8 sind jeweils in einer Elementbohrung 11 in radialer Richtung hin und her bewegbar aufgenommen. Die Kolben 8 sind in einem Winkel von etwa 90° zueinander angeordnet und begrenzen an ihrem der Antriebswelle 2 abgewandten Ende einen Förderraum (nicht dargestellt). denIn the FIG. 1 shown radial piston pump comprises a mounted in a pump housing 1 drive shaft 2 with two offset by 180 ° seconded cam 36. Against the cam 36, two pistons 8 are supported. The pistons 8 are each received in an element bore 11 in the radial direction movable back and forth. The pistons 8 are arranged at an angle of about 90 ° to each other and limit at its end remote from the drive shaft 2 a delivery chamber (not shown). the

An dem zu der Antriebswelle 2 hin gerichteten Ende der Kolben 8 stützen sich die Kolben 8 gegen einen Boden 20 eines Stößels 23 ab. Um die Kraftübertragung zwischen Kolben 8 und Boden 20 des Stößels 23 zu verbessern, ist am Kolben 8 ein Teller 14 vorgesehen. Diese Teller 14 können entweder einstückig mit dem Kolben 8 oder abnehmbar daran befestigt sein. Gegen den Teller 14 ist eine Feder 17 vorgespannt. Die Federn 17 drücken die Kolben 8 gegen die Böden 20 der Stößel 23. Von den Böden 20 der Stößel 23 erstreckt sich ein zylinderförmiger Führungskörper 26 in Richtung der nicht dargestellten Förderräume. Die Führungskörper 26 sind Teil der Stößel 23 und verhindern ein Kippen der Stößel 23 in einer Führungsbohrung 29. Die Stößel 23 sind in dem Pumpengehäuse 1 verschiebbar.At the end of the piston 8 directed toward the drive shaft 2, the pistons 8 are supported against a bottom 20 of a plunger 23. In order to improve the power transmission between the piston 8 and the bottom 20 of the plunger 23, a plate 14 is provided on the piston 8. These plates 14 may be either integral with the piston 8 or removably attached thereto. Against the plate 14, a spring 17 is biased. The springs 17 press the pistons 8 against the bottoms 20 of the plungers 23. From the bottoms 20 of the plungers 23 extends a cylindrical guide body 26 in the direction of the delivery chambers, not shown. The guide body 26 are part of the plunger 23 and prevent tilting of the plunger 23 in a guide bore 29. The plunger 23 are slidable in the pump housing 1.

In den Böden 20 der Stößel 23 ist eine halbrunde Vertiefung 27 vorhanden, die zur Lagerung einer Rolle 28 dient. Die Vertiefung 27 und die Rolle 28 bilden ein Gleitlager, während sich die Rolle 28 auf der Nocke 36 der Antriebswelle 2 abwälzt. In seitlicher Richtung wird die Rolle 28 i, Führungskörper 26 fixiert. Dabei findet eine Relativbewegung zwischen den Stirnseiten der Rolle 28 und dem Führungskörper 26 statt, die Verschleiß verursachen kann.In the bottoms 20 of the plunger 23, a semicircular recess 27 is provided which serves to support a roller 28. The recess 27 and the roller 28 form a sliding bearing, while the roller 28 rolls on the cam 36 of the drive shaft 2. In the lateral direction, the roller 28 i, guide body 26 is fixed. In this case, a relative movement between the end faces of the roller 28 and the guide body 26 takes place, which can cause wear.

Die in Fig. 1 dargestellte Radialkolbenpumpe dient dazu, Kraftstoff, der von einer Vorförderpumpe aus einem Tank geliefert wird, mit Hochdruck zu beaufschlagen. Im Förderhub werden die Kolben 8 infolge der Exzenterbewegung der Nocken 36 der Antriebswelle 2 von der Drehachse der Antriebswelle Nockenwelle 2 wegbewegt. Im Saughub bewegen sich die Kolben 8 radial auf die Achse der Nockenwelle 2 zu, um Kraftstoff in den nicht dargestellten Förderraum zu saugen.In the Fig. 1 shown radial piston pump serves to pressurize fuel that is supplied from a Vorförderpumpe from a tank with high pressure. In the delivery stroke, the pistons 8 are moved away from the axis of rotation of the drive shaft camshaft 2 as a result of the eccentric movement of the cams 36 of the drive shaft 2. In the suction stroke, the pistons 8 move radially toward the axis of the camshaft 2 in order to suck fuel into the delivery chamber (not shown).

In Figur 2 a) ist der Stößel 23 im Längsschnitt und in Figur 2 b) in einer Seitenansicht dargestellt. Aus dem Längsschnitt (Fig. 2a) ist gut zu erkennen, dass bei dem dargestellten Ausführungsbeispiel der Boden 20 in den Führungskörper 26 eingesetzt wird. Um eine formschlüssige Verbindung zwischen Boden 20 und Führungskörper 26 herzustellen, kann ein Seeger-Ring 30 vorgesehen werden.In FIG. 2 a) is the plunger 23 in longitudinal section and in FIG. 2 b) shown in a side view. From the longitudinal section ( Fig. 2a ) can be clearly seen that in the illustrated embodiment, the bottom 20 is inserted into the guide body 26 becomes. To make a positive connection between the bottom 20 and guide body 26, a Seeger ring 30 may be provided.

Wie man dem Längsschnitt weiter entnehmen kann, ist die Rolle 28 an ihren Stirnseiten verrundet und wird in seitlicher Richtung von dem Führungskörper 26 fixiert. Aufgrund der oszillierenden Bewegung des Stößels 23 in der Führungsbohrung 29 drehen sich die Stirnseiten der Rolle 28 auf der Innenseite des Führungskörpers 26. Um den dabei entstehenden Verschleiß zu verringern, ist erfindungsgemäß eine hydraulische Verbindung zwischen den Stößelräumen 32, 33 einerseits und der Vertiefung 28 vorgesehen. Des Weiteren verbessert die erfindungsgemäße hydraulische Verbindung die tribologischen Verhältnisse zwischen Rolle 28 und Stößel 23.As can further be seen from the longitudinal section, the roller 28 is rounded at its end faces and is fixed in the lateral direction by the guide body 26. Due to the oscillating movement of the plunger 23 in the guide bore 29, the end faces of the roller 28 rotate on the inside of the guide body 26. To reduce the resulting wear, a hydraulic connection between the plunger chambers 32, 33 on the one hand and the recess 28 is provided according to the invention , Furthermore, the hydraulic connection according to the invention improves the tribological relationships between roller 28 and plunger 23.

In Figur 2a) sind zwei Varianten erfindungsgemäßer hydraulischer Verbindungen dargestellt. An der rechten Seite von Figur 2a) ist eine Nut 53 dargestellt, welche die Kontaktstelle zwischen Rolle 28 und Führungskörper 26 mit Kraftstoff versorgt. An der linken Seite von Figur 2a) ist eine alternative Ausgestaltung der erfindungsgemäßen hydraulischen Verbindung in Form einer Bohrung 55 dargestellt, welche die Kontaktstelle zwischen Rolle 28 und Führungskörper 26 mit Kraftstoff versorgt. In der Regel wird man beide Seiten eines Stößels 23 gleich gestalten. Die Nut 53 und die Bohrung 55 sind alternative Ausführungsformen der Erfindung. Welcher dieser Alternativen im Einzelfall der Vorzug gegeben wird, hängt von den Umständen des Einzelfalls ab.In FIG. 2a ) Two variants of inventive hydraulic connections are shown. On the right side of FIG. 2a ), a groove 53 is shown, which supplies the contact point between the roller 28 and the guide body 26 with fuel. At the left side of FIG. 2a ) an alternative embodiment of the hydraulic connection according to the invention in the form of a bore 55 is shown, which supplies the contact point between the roller 28 and the guide body 26 with fuel. In general, you will make both sides of a plunger 23 the same. The groove 53 and the bore 55 are alternative embodiments of the invention. Which of these alternatives is given preference in the individual case depends on the circumstances of the individual case.

Wenn nun der Stößel 23 von den Nocken 36 der Antriebswelle angetrieben wird, führt er eine oszillierende Bewegung, die in Figur 2a durch einen Doppelpfeil angedeutet ist, aus. Da sich sowohl in den Stößelräumen 32, 33 als auch in dem Triebwerksraum 35 Kraftstoff befindet, führt die oszillierende Bewegung des Stößels 23 dazu, dass Kraftstoff von dem Triebwerksraum 35 in die Stößelräume 32 und 33 gefördert wird, wenn der Kolben sich in Figur 2a von oben nach unten bewegt. Sobald der Stößel 23 sich von unten nach oben bewegt, wird die Strömungsrichtung umgekehrt und es wird Kraftstoff aus den Stößelräumen 32, 33 in den Triebwerksraum 35 gefördert. Diesen zwangsläufig auftretenden Effekt macht sich die erfindungsgemäße hydraulische Verbindung, sei es in Form der Nut 53 oder einer Bohrung 55 zunutze, indem Kraftstoff gezielt an die Kontaktstelle zwischen der Rolle 28 und dem Führungskörper 26 gefördert wird. Die erfindungsgemäße hydraulische Verbindung führt zu einer starken Reduktion dieses Verschleißes, da die tribologisch kritischen Stellen mit Kraftstoff geschmiert wird. Des Weiteren werden, falls doch Verschleiß auftritt, die dabei entstehenden Partikel sofort aus dem Kontaktbereich zwischen Rolle 28 und Führungskörper 26 herausgespült, so dass sie dort keinen weiteren Schaden anrichten.Now, when the plunger 23 is driven by the cam 36 of the drive shaft, it performs an oscillating motion in FIG. 2a indicated by a double arrow, from. Since there is fuel in both the plunger chambers 32, 33 and in the engine compartment 35, the oscillating movement of the plunger 23 causes fuel to be delivered from the engine compartment 35 into the plunger chambers 32 and 33 when the piston engages FIG. 2a moved from top to bottom. As soon as the plunger 23 moves from the bottom to the top, the flow direction is reversed and fuel from the plunger chambers 32, 33 is conveyed into the engine compartment 35. This inevitably occurring effect makes the inventive hydraulic Connection, whether in the form of the groove 53 or a bore 55 advantage by fuel is selectively conveyed to the contact point between the roller 28 and the guide body 26. The hydraulic connection according to the invention leads to a strong reduction of this wear, since the tribologically critical points are lubricated with fuel. Furthermore, if it does wear, the resulting particles are immediately flushed out of the contact area between the roller 28 and guide body 26, so that they do no further damage there.

Außerdem werden die Dissipationsverluste, die beim Pumpen von Kraftstoff von den Stößelräumen 32, 33 in den m Triebwerksraum 35 und zurück entstehen, deutlich reduziert, so dass sich der Pumpenwirkungsgrad verbessert und der Kraftstoff nicht so stark aufgeheizt wird.In addition, the dissipation losses, which arise when pumping fuel from the plunger chambers 32, 33 in the engine compartment 35 and back, significantly reduced, so that the pump efficiency improves and the fuel is not heated as much.

Wegen des Winkels von 90° zwischen den Kolben 8 und 9 finden die Volumenänderungen in den Stößelräumen 32 und 33 um 90° phasenverschoben statt. Diese Phasenverschiebung kann ausgenützt werden, indem eine Verbindungsbohrung 37 zwischen den Stößelräumen 32 und 33 vorgesehen wird, so dass immer dann, wenn sich das Volumen eines Stößelraumes verringert, der in diesem Stößelraum befindliche Kraftstoff teilweise in den benachbarten Stößelraum ausgeschoben wird, dessen Volumen zur gleichen Zeit zunimmt. Der andere Teil des Kraftstoffs strömt durch die Nut 53 bzw. die Bohrung 55 und die Ausgleichsbohrungen 41 (falls vorhanden) im Boden 20 der Stößel 23 und 24.Because of the angle of 90 ° between the pistons 8 and 9, the volume changes in the plunger chambers 32 and 33 are phase-shifted by 90 °. This phase shift can be exploited by providing a communication bore 37 between the plunger spaces 32 and 33 such that whenever the volume of a plunger space decreases, the fuel in that plunger space is partially ejected into the adjacent plunger space whose volume is the same Time is increasing. The other part of the fuel flows through the groove 53 or the bore 55 and the compensation bores 41 (if present) in the bottom 20 of the plungers 23 and 24.

Dabei ist darauf zu achten, dass durch die geeignete Abstimmung der hydraulischen Querschnitte von Nut 53 beziehungsweise Bohrung 55, der Ausgleichsbohrungen 41 und der Verbindungsbohrung 37 zwischen den Stößelräumen 32 und 33 sichergestellt ist, dass eine ausreichend große Kraftstoffmenge durch die Nut 53 beziehungsweise die Bohrungen 55 strömt, um den Verschleiß in dem Kontaktbereich zwischen Rolle 28 und Führungskörper 26 auf das erforderliche Maß zu reduzieren.It is important to ensure that is ensured by the appropriate vote of the hydraulic cross sections of groove 53 and bore 55, the compensation holes 41 and the connecting bore 37 between the plunger chambers 32 and 33, that a sufficiently large amount of fuel through the groove 53 and the bores 55th flows to reduce the wear in the contact area between roller 28 and guide body 26 to the required extent.

Bei diesem Ausführungsbeispiel findet die Schmierung der Nockenwelle 2 und deren Lagerung (nicht dargestellt) über eine Schmierstoffversorgung 38 mit einer Drossel 39 statt, die direkt mit Kraftstoff aus dem nicht dargestellten Kraftstofftank der Brennkraftmaschine über eine Versorgungsleitung 40 gespeist wird. Von der Versorgungsleitung 40 zweigt eine Leitung 43 ab, welche die Zumesseinheit ZME der Radialkolbenpumpe mit Kraftstoff versorgt.In this embodiment, the lubrication of the camshaft 2 and its storage (not shown) takes place via a lubricant supply 38 with a throttle 39, which directly with fuel from the fuel tank, not shown Internal combustion engine is fed via a supply line 40. From the supply line 40 branches off a line 43 which supplies the metering unit ZME of the radial piston pump with fuel.

Claims (8)

  1. Radial piston pump for high-pressure fuel generation in fuel injection systems of internal combustion engines, in particular in a common-rail injection system, with a drive shaft (2) mounted in a pump casing (1), with at least one piston (8) arranged radially with respect to the drive shaft in each case in an element bore (11), with at least one piston (8) being moveable to and fro in the radial direction in the element bore (11) as a result of the rotation of the drive shaft (2), with a tappet (23) arranged between the piston (8) and the drive shaft (2) and guided in the pump casing (1), in each case with a tappet space (32, 33) delimited by the tappets (23) in the pump casing (1), the tappet space (32, 33) being connected hydraulically to an engine space (35), a depression (27) for receiving a roller (28) being provided at an end of the tappet (23) which faces the drive shaft (2), at least some of the hydraulic connections between the tappet space (32, 33) and the engine space (25) issuing in the depression (27), characterized in that the hydraulic connection (53, 55) issues into the depression (27) at the ends of the latter.
  2. Radial piston pump according to Claim 1, characterized in that the tappet (23) has at least one groove (53), and in that the groove (53) runs essentially in the axial direction of the tappet (23).
  3. Radial piston pump according to Claim 1, characterized in that the tappet (23) has at least one bore (55), and in that the bore (55) runs essentially in the axial direction of the tappet (23).
  4. Radial piston pump according to one of the preceding claims, characterized in that the depression (27) is formed in a bottom (20) of the tappet (23).
  5. Radial piston pump according to one of the preceding claims, characterized in that at least one connecting bore (37) is provided in the pump casing (1), and in that the at least one connecting bore (37) connects two tappet spaces (32, 33) hydraulically.
  6. Radial piston pump according to one of the preceding claims, characterized in that a lubricant supply (38) issues into the hydraulic connection (37) between two tappet spaces (32, 33).
  7. Radial piston pump according to one of the preceding claims, characterized in that the tappets (23) have additional compensating bores (41) or compensating grooves.
  8. Radial piston pump according to one of the preceding claims, characterized in that the drive shaft (2) is designed as a camshaft.
EP08774082A 2007-07-20 2008-06-13 High-pressure fuel pump with roller tappet Not-in-force EP2167818B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102007034036A DE102007034036A1 (en) 2007-07-20 2007-07-20 High-pressure fuel pump with roller tappet
PCT/EP2008/057457 WO2009013068A1 (en) 2007-07-20 2008-06-13 High-pressure fuel pump with roller tappet

Publications (2)

Publication Number Publication Date
EP2167818A1 EP2167818A1 (en) 2010-03-31
EP2167818B1 true EP2167818B1 (en) 2011-01-26

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EP08774082A Not-in-force EP2167818B1 (en) 2007-07-20 2008-06-13 High-pressure fuel pump with roller tappet

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US (1) US20100170480A1 (en)
EP (1) EP2167818B1 (en)
JP (1) JP2010533818A (en)
AT (1) ATE497106T1 (en)
DE (2) DE102007034036A1 (en)
WO (1) WO2009013068A1 (en)

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DE502008002488D1 (en) 2011-03-10
WO2009013068A1 (en) 2009-01-29
JP2010533818A (en) 2010-10-28
DE102007034036A1 (en) 2009-01-22
EP2167818A1 (en) 2010-03-31
ATE497106T1 (en) 2011-02-15
US20100170480A1 (en) 2010-07-08

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