EP2079923A1 - Piston pump, in particular high-pressure fuel pump, having roller tappet - Google Patents

Piston pump, in particular high-pressure fuel pump, having roller tappet

Info

Publication number
EP2079923A1
EP2079923A1 EP07802934A EP07802934A EP2079923A1 EP 2079923 A1 EP2079923 A1 EP 2079923A1 EP 07802934 A EP07802934 A EP 07802934A EP 07802934 A EP07802934 A EP 07802934A EP 2079923 A1 EP2079923 A1 EP 2079923A1
Authority
EP
European Patent Office
Prior art keywords
roller
collar
cam portion
piston pump
piston
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.)
Granted
Application number
EP07802934A
Other languages
German (de)
French (fr)
Other versions
EP2079923B1 (en
Inventor
Gerhard Meier
Jochen Aleker
Arnold Gente
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Priority to PL07802934T priority Critical patent/PL2079923T3/en
Publication of EP2079923A1 publication Critical patent/EP2079923A1/en
Application granted granted Critical
Publication of EP2079923B1 publication Critical patent/EP2079923B1/en
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • 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
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/02—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type
    • F02M59/10—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by the piston-drive
    • F02M59/102—Mechanical drive, e.g. tappets or cams
    • 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
    • F04B1/0439—Supporting or guiding means for the pistons

Definitions

  • the invention relates to a piston pump, in particular a high-pressure fuel pump, with a housing, a piston, and a drive shaft with an eccentric or cam portion, on which the piston is supported at least indirectly via a plunger element.
  • a piston pump of the type mentioned is known from DE 43 00 631 Al.
  • the fuel injection pump shown in this publication has a piston which can be displaced by a camshaft in a reciprocating motion. In this case, the piston is acted upon by a spring to the camshaft.
  • a plunger body with a roller shoe is attached to a piston foot. On the roller shoe, a roller is rotatably supported and held. The roller runs on the cam track of the cam.
  • This assembly comprising a tappet body, a roller shoe and a roller, is referred to as a roller tappet.
  • a hydrodynamic sliding bearing is formed, which is lubricated by the fuel present in the interior of the pump housing.
  • roller tappet Another undesirable effect with the known from the prior art piston pumps with roller tappet is that the roller can start during operation in the axial direction of, for example, the plunger element or other components of the piston pump, since they are not fixed in the axial direction.
  • This uncontrolled axial start of the roller on other components can lead to heavy wear of the components involved. As a result of this wear and the associated metallic abrasion can lead to consequential damage to the piston pump.
  • the invention has for its object to provide a piston pump, in particular a high-pressure fuel pump for a fuel injection system of an internal combustion engine, which avoids the known from the prior art disadvantages and still has a simple structure.
  • a piston pump in particular a high-pressure fuel pump, with a housing, a piston and a drive shaft with a cam portion on which the piston is at least indirectly supported by a roller, characterized in that the side of the cam portion, a collar is provided, and that the collar protrudes in the radial direction over the cam portion.
  • This collar ensures that the roller can not move uncontrollably in the axial direction during operation. As a result, the start of the roller on other components of the piston pump, which are not suitable, prevented and thus occurs on these parts no wear. Since the collar is preferably hardened, as well as the cam track of the cam portion, both the collar and the likewise hardened roller are very resistant to wear, so that the tarnishing of the roller on the collar brings no wear. As a result, the function of the piston pump is not affected by the start of the roller.
  • a particularly advantageous effect results from the tarnishing of the roller on the collar, because occurs by the contact of the roller on the collar occurs friction, which exerts a torque on the roller. For this reason, if the pulley should not turn, but slides on the cam portion, it will rotate again by starting at the collar. This causes the roller to slide back onto the roller shoe and the roller rolls on the cam section. Thus, the desired state is restored, in which both between the cam portion and roller and between roller and roller shoe almost no wear occurs and thus the life of the piston pump operated in this way is very high.
  • camshaft and collar or cam portion and collar are integrally formed.
  • the collar is made together with the cam portion, for example, by grinding from a blank of a drive shaft.
  • the collar for example, as a sheet metal blank and firmly connected to the drive shaft or with its cam portion. It is possible to press the collar with the camshaft and / or connect by a weld.
  • Figure 1 is a partial section through a piston pump
  • Figure 2 is a section along the line II-II of Figure 1;
  • Figure 3 is a constructive detail of an embodiment of an inventive
  • a piston pump carries the reference numeral 10 as a whole. It comprises a housing 12 in which a drive shaft 14 is mounted via two bearings 16 and 18. As can be seen in particular from FIG. 2, the drive shaft 14 has a cross-sectionally oval cam section 20 between the two bearings 16 and 18.
  • the piston pump 10 shown in FIGS. 1 and 2 serves as a high-pressure fuel pump for an internal combustion engine in a motor vehicle. With it, the fuel is compressed to a very high pressure and conveyed to a fuel rail (not shown). The drive shaft 14 of the piston pump 10 is thereby directly from the internal combustion engine driven. Therefore, the drive shaft 14 has a corresponding coupling portion 22 which is disposed outside of the housing 12.
  • the piston pump 10 is a 1-cylinder radial piston pump. For reasons of clarity, however, neither the piston nor the delivery chamber bounded by it nor the associated intake and exhaust valves are shown in the two figures. These elements are integrated into a cylinder head, not shown, which can be attached to a cylinder section 24 of the housing 12 that is perpendicular to the longitudinal axis of the drive shaft 14.
  • the piston of the piston pump 10 is indirectly driven by the cam portion 20 of the drive shaft 14.
  • the term "indirectly” is understood here to mean that the piston does not directly touch the cam section 20, but that a so-called roller tappet 26 is arranged between the piston and the cam section 20. This comprises a plunger body 28 and a roller 30th
  • the roller tappet 26 is pressed together with the piston against the cam portion 20 to ensure that the roller 26 does not lift off from the cam portion 20 of the drive shaft 14.
  • the plunger body 28 is a sintered part. Alternatively, it could also be an aluminum pressed part or a metal skeleton, which is encapsulated in plastic. As can be seen in particular from FIG. 3, the plunger body 28 comprises a central, cuboid roller shoe or plunger block 34, on whose upper region in FIG. 3 on both sides an outwardly extending projection 36 or 38 is integrally formed.
  • a vertically upwardly extending guide portion 40 or 42 is integrally formed on this.
  • the two guide portions 40 and 42 engage in the mounting position in corresponding grooves 44 and 46 in the cylinder portion 24 of the housing 12 (see Figure 1), which form the housing-side guide areas. In this way, the plunger body 28 can not rotate about a longitudinal axis of the cylinder portion 24.
  • a cylindrical recess 48 is inserted into the plunger block 34, the longitudinal axis of which in the installed position is parallel to the longitudinal axis of the Drive shaft 14 extends.
  • the recess is open to the cam portion 20 and extends over the entire width of the plunger body 28. Their maximum depth is approximately equal to the radius of the cylindrical roller 30 so that it protrudes approximately half a diameter beyond the edge of the recess 48.
  • Plunger body 28 and plunger block 34 may be formed integrally or as separate components.
  • roller 30 is inserted into the recess 48 and is supported with its lateral surface 49 on the wall of the recess 48 from. Roller 30 and recess 48 form a plain bearing.
  • the securing element 32 serves to secure the roller 30 in the recess 48 in the tappet body 28 and, in particular, to prevent the roller 30 from falling out of the tappet element 28 during assembly.
  • a collar 50 is provided on the drive shaft 14 on both sides of the cam section 20.
  • the collar 50 projects in the radial direction over the
  • Cam portion 20 out, so that the roller 30 when it travels during operation in the axial direction, against one of the two frets 50 starts. Thereby, the axial movement of the roller 30 is limited during operation to a defined extent.
  • care can be taken that by a suitable tribological pairing of the roller 30 and the collars 50, the wear on both the roller 30 and the collar 50 is so small that it does not lead to malfunction or a shortening of the life of the piston pump 10 , This can for example be achieved in that the collar as well as the cam portion 20 and the roller tappet 26 are made of hardened steel.
  • an undercut 52 is provided in each case, which ensures that the notch effect at the transition between cam portion 20 and collar 50 is reduced. Furthermore, the undercuts 52 provide for defined contact surfaces between roller 30 and cam portion 20 on the one hand and roller tappet 26 and the collars 50 on the other.
  • roller 30 is rotated by the friction that occurs when starting at one of the collars 50, if it does not already by the rolling friction between the cam portion 20 and roller 30 rotates. It has been found in practical experiments that the rolling friction between roller 30 and cam portion 20 is not always sufficient to enable the rollers 30 in rotation, so that not always between the recess 48 in the plunger block 34 and the roller 30 as desired, a hydrodynamic Plain bearing forms. This undesirable effect is avoided in the embodiment of the drive shaft 14 according to the invention.
  • a particularly advantageous embodiment of a roller tappet 26 is shown.
  • a respective centrally disposed recess 54 is recessed at the end faces (without reference numeral) of the roller 30. This ensures that the roller 30 comes into contact with the collar 50 of the drive shaft 14 only in the region of its outer diameter, so that the torque exerted on the roller 30 by the adhesive or sliding friction between roller 30 and collar 50 is maximum due to the large lever arm becomes.
  • FIG. 3 shows a detail of a constructional detail of a further advantageous embodiment of a piston pump according to the invention.
  • the collar 50, the cam portion 20 and the drive shaft 14 are integrally formed.
  • the collar is designed as a separate component.
  • the collar 50 can be formed for example as a sheet metal blank.
  • a shoulder 56 is machined laterally of the undercut 52.
  • the collar 50 is permanently attached, for example by pressing. It is also possible, alternatively or in addition to the press connection, to fasten the collar 50 to the shoulder 56 by means of a weld 58.

Abstract

Proposed is a piston pump having a roller tappet (26), in which a collar (50) is provided at the side of a cam section (20) of a driveshaft, on which collar (50) a roller (30) can run during operation.

Description

Beschreibung description
Titeltitle
Kolbenpumpe, insbesondere Kjaftstoffhochdruckpumpe, mit RollenstößelPiston pump, in particular Kjaftstoffhochdruckpumpe, with roller tappet
Stand der TechnikState of the art
Die Erfindung betrifft eine Kolbenpumpe, insbesondere eine Hochdruck-Kraftstoffpumpe, mit einem Gehäuse, einem Kolben, und einer Antriebswelle mit einem Exzenter- oder Nockenabschnitt, an dem sich der Kolben wenigstens mittelbar über ein Stößelelement abstützt.The invention relates to a piston pump, in particular a high-pressure fuel pump, with a housing, a piston, and a drive shaft with an eccentric or cam portion, on which the piston is supported at least indirectly via a plunger element.
Eine Kolbenpumpe der eingangs genannten Art ist aus der DE 43 00 631 Al bekannt. Die in dieser Druckschrift gezeigte Kraftstoffeinspritzpumpe verfügt über einen Kolben, der von einer Nockenwelle in eine Hin- und Herbewegung versetzt werden kann. Dabei wird der Kolben von einer Feder zur Nockenwelle hin beaufschlagt. Um die Reibung zwischen dem Kolben und der Nockenwelle zu minimieren, ist an einem Kolbenfuß ein Stößelkörper mit einem Rollenschuh befestigt. An dem Rollenschuh ist eine Laufrolle drehbar gelagert und gehalten. Die Laufrolle läuft auf der Nockenbahn des Nockens ab. Diese Baugruppe, umfassend einen Stößelkörper, einen Rollenschuh und eine Laufrolle, wird als Rollenstößel bezeichnet.A piston pump of the type mentioned is known from DE 43 00 631 Al. The fuel injection pump shown in this publication has a piston which can be displaced by a camshaft in a reciprocating motion. In this case, the piston is acted upon by a spring to the camshaft. In order to minimize the friction between the piston and the camshaft, a plunger body with a roller shoe is attached to a piston foot. On the roller shoe, a roller is rotatably supported and held. The roller runs on the cam track of the cam. This assembly, comprising a tappet body, a roller shoe and a roller, is referred to as a roller tappet.
Zwischen dem Rollenschuh und der Laufrolle bildet sich ein hydrodynamisches Gleitlager aus, welches von dem im Innenraum des Pumpengehäuses vorhandenen Kraftstoff geschmiert wird.Between the roller shoe and the roller, a hydrodynamic sliding bearing is formed, which is lubricated by the fuel present in the interior of the pump housing.
Da die Anpresskraft mit der der Rollenstößel auf dem Nockenabschnitt der Antriebswelle angepresst wird, aufgrund der hydraulischen Kräfte im Förderraum des Pumpenelements und der Trägheitskräfte des Kolbens und des Rollenstößels während einer Umdrehung der Antriebswelle stark unterschiedlich ist und außerdem in hohem Maße von der Drehzahl der Antriebswelle sowie Fördermenge und Förderdruck des Pumpenelements abhängt, kann es dazu kommen, dass sich die Laufrolle in manchen Betriebspunkten der Kraftstoffhochdruckpumpe nicht in dem Rollenschuh dreht, sondern auf dem Nockenabschnitt der Antriebswelle gleitet. Dieser Betriebszustand ist unerwünscht, da er zu Beschädigungen der Nockenbahn und/oder des Rollenstößels führen kann. Insbesondere können Beschädigungen des Rollenstößels dazu führen, dass das Gleitlager zwischen Rollenschuh und Laufrolle nicht mehr funktionsfähig ist. Infolgedessen fällt die Kraftstoffhochdruckpumpe innerhalb kürzester Zeit aus.Since the contact pressure with which the roller tappet is pressed onto the cam portion of the drive shaft, due to the hydraulic forces in the pump chamber and the inertial forces of the piston and the roller tappet during a revolution of the drive shaft is greatly different and also highly dependent on the speed of the drive shaft and Flow rate and delivery pressure of the pump element depends, it may happen that the roller in some operating points of the high-pressure fuel pump is not in the roller shoe rotates but slides on the cam portion of the drive shaft. This operating state is undesirable because it can lead to damage of the cam track and / or the roller tappet. In particular, damage to the roller tappet can cause the sliding bearing between roller shoe and roller is no longer functional. As a result, the high-pressure fuel pump fails within a very short time.
Ein weiterer unerwünschter Effekt bei den aus dem Stand der Technik bekannten Kolbenpumpen mit Rollenstößel ist, dass die Laufrolle während des Betriebs in axialer Richtung an beispielsweise dem Stößelelement oder anderen Bauteilen der Kolbenpumpe anlaufen kann, da sie in axialer Richtung nicht fixiert sind. Dieses unkontrollierte axiale Anlaufen der Laufrolle an anderen Bauteilen kann zu starkem Verschleiß der beteiligten Bauteile führen. Als Folge dieses Verschleißes und des damit verbundenen metallischen Abriebs kann es zu Folgeschäden an der Kolbenpumpe kommen.Another undesirable effect with the known from the prior art piston pumps with roller tappet is that the roller can start during operation in the axial direction of, for example, the plunger element or other components of the piston pump, since they are not fixed in the axial direction. This uncontrolled axial start of the roller on other components can lead to heavy wear of the components involved. As a result of this wear and the associated metallic abrasion can lead to consequential damage to the piston pump.
Offenbarung der ErfindungDisclosure of the invention
Der Erfindung liegt die Aufgabe zugrunde, eine Kolbenpumpe, insbesondere eine Kraftstoffhochdruckpumpe für ein Kraftstoffeinspritzsystem einer Brennkraftmaschine, bereitzustellen, welche die aus dem Stand der Technik bekannten Nachteile vermeidet und trotzdem einfach aufgebaut ist.The invention has for its object to provide a piston pump, in particular a high-pressure fuel pump for a fuel injection system of an internal combustion engine, which avoids the known from the prior art disadvantages and still has a simple structure.
Diese Aufgabe wird erfindungsgemäß bei einer Kolbenpumpe, insbesondere einer Hochdruckkraftstoffpumpe, mit einem Gehäuse, einem Kolben und einer Antriebswelle mit einem Nockenabschnitt, an dem sich der Kolben wenigstens mittelbar über eine Laufrolle abstützt, dadurch gelöst, dass seitlich des Nockenabschnitts ein Bund vorgesehen ist, und dass der Bund in radialer Richtung über den Nockenabschnitt hinausragt.This object is achieved with a piston pump, in particular a high-pressure fuel pump, with a housing, a piston and a drive shaft with a cam portion on which the piston is at least indirectly supported by a roller, characterized in that the side of the cam portion, a collar is provided, and that the collar protrudes in the radial direction over the cam portion.
Durch diesen Bund ist gewährleistet, dass sich die Laufrolle während des Betriebs nicht unkontrolliert in axialer Richtung bewegen kann. Dadurch wird das Anlaufen der Laufrolle an anderen Bauteilen der Kolbenpumpe, die nicht dafür geeignet sind, verhindert und es tritt somit an diesen Teilen kein Verschleiß auf. Da der Bund vorzugsweise, ebenso wie die Nockenbahn des Nockenabschnitts, gehärtet wird, sind sowohl der Bund als auch die ebenfalls gehärtete Laufrolle sehr verschleißunempfindlich, so dass das Anlaufen der Laufrolle an dem Bund keinen Verschleiß mit sich bringt. Infolgedessen wird die Funktion der Kolbenpumpe durch das Anlaufen der Laufrolle nicht beeinträchtigt.This collar ensures that the roller can not move uncontrollably in the axial direction during operation. As a result, the start of the roller on other components of the piston pump, which are not suitable, prevented and thus occurs on these parts no wear. Since the collar is preferably hardened, as well as the cam track of the cam portion, both the collar and the likewise hardened roller are very resistant to wear, so that the tarnishing of the roller on the collar brings no wear. As a result, the function of the piston pump is not affected by the start of the roller.
Ein besonders vorteilhafter Effekt ergibt sich durch das Anlaufen der Laufrolle an dem Bund, weil durch den Kontakt der Laufrolle an dem Bund tritt Reibung auftritt, welche ein Drehmoment auf die Laufrolle ausübt. Aus diesem Grund wird die Laufrolle, falls sie sich nicht drehen sollte, sondern auf der dem Nockenabschnitt gleitet, durch das Anlaufen an dem Bund wieder in Drehung versetzt. Dies führt dazu, dass die Laufrolle wieder auf dem Rollenschuh gleitet und dass sich die Laufrolle auf dem Nockenabschnitt abwälzt. Damit wird der gewünschte Zustand wieder hergestellt, bei dem sowohl zwischen Nockenabschnitt und Laufrolle als auch zwischen Laufrolle und Rollenschuh nahezu kein Verschleiß auftritt und somit die Lebensdauer der in dieser Weise betriebenen Kolbenpumpe sehr hoch ist.A particularly advantageous effect results from the tarnishing of the roller on the collar, because occurs by the contact of the roller on the collar occurs friction, which exerts a torque on the roller. For this reason, if the pulley should not turn, but slides on the cam portion, it will rotate again by starting at the collar. This causes the roller to slide back onto the roller shoe and the roller rolls on the cam section. Thus, the desired state is restored, in which both between the cam portion and roller and between roller and roller shoe almost no wear occurs and thus the life of the piston pump operated in this way is very high.
Es hat sich als vorteilhaft erwiesen, wenn zu beiden Seiten des Nockenabschnitts jeweils ein Bund vorhanden ist. Allerdings kann es auch bei einfacheren Ausführungen von Kolbenpumpen ausreichend sein, wenn nur an einer Seite des Nockenabschnitts ein Bund vorgesehen ist. Dies ist insbesondere immer dann ausreichend, wenn aufgrund bestimmter physikalischer Effekte die Laufrolle dazu neigt, immer in eine bestimmte axiale Richtung zu wandern.It has proven to be advantageous if a collar is present on both sides of the cam portion. However, even with simpler embodiments of piston pumps, it may be sufficient if a collar is provided only on one side of the cam portion. This is especially always sufficient if due to certain physical effects, the roller tends to always wander in a particular axial direction.
Eine vorteilhafte Ausgestaltung der Erfindung sieht vor, dass Nockenwelle und Bund beziehungsweise Nockenabschnitt und Bund einstückig ausgebildet sind. In diesem Fall wird der Bund zusammen mit dem Nockenabschnitt beispielsweise durch Schleifen aus einem Rohling einer Antriebswelle hergestellt.An advantageous embodiment of the invention provides that the camshaft and collar or cam portion and collar are integrally formed. In this case, the collar is made together with the cam portion, for example, by grinding from a blank of a drive shaft.
Alternativ ist es auch möglich, den Bund beispielsweise als Blechzuschnitt herzustellen und mit der Antriebswelle oder mit deren Nockenabschnitt fest zu verbinden. Dabei ist es möglich, den Bund mit der Nockenwelle zu verpressen und/oder durch eine Schweißnaht zu verbinden.Alternatively, it is also possible to produce the collar, for example, as a sheet metal blank and firmly connected to the drive shaft or with its cam portion. It is possible to press the collar with the camshaft and / or connect by a weld.
Um definierte Kräfte und geometrische Verhältnisse vom Übergang zwischen Nockenabschnitt und Bund zu gewährleisten und außerdem die Kerbwirkung zu verringern, kann vorteilhafterweise zwischen dem Bund und dem Nockenabschnitt ein Freistich ausgebildet sein. Weitere Vorteile und vorteilhafte Ausgestaltungen der Erfindung sind der nachfolgenden Zeichnung, deren Beschreibung und den Patentansprüchen entnehmbar. Alle in der Zeichnung, deren Beschreibung und den Patentansprüchen offenbarten Merkmale können sowohl einzeln als auch in beliebiger Kombination miteinander erfindungswesentlich sein.In order to ensure defined forces and geometric conditions of the transition between the cam portion and collar and also to reduce the notch effect, can advantageously be formed between the collar and the cam portion an undercut. Further advantages and advantageous embodiments of the invention are the following drawings, the description and the claims removable. All of the features disclosed in the drawing, the description and the claims can be essential to the invention both individually and in any combination with one another.
Nachfolgend wird ein besonders bevorzugtes Ausführungsbeispiel der vorliegenden Erfindung unter Bezugnahme auf die beiliegende Zeichnung näher erläutert.Hereinafter, a particularly preferred embodiment of the present invention will be explained in more detail with reference to the accompanying drawings.
Kurze Beschreibung der ZeichnungenBrief description of the drawings
In der Zeichnung zeigen:In the drawing show:
Figur 1 einen Teilschnitt durch eine Kolbenpumpe;Figure 1 is a partial section through a piston pump;
Figur 2 einen Schnitt längs der Linie II-II von Figur 1 ; undFigure 2 is a section along the line II-II of Figure 1; and
Figur 3 ein konstruktives Detail einer Ausführungsform eines erfindungsgemäßenFigure 3 is a constructive detail of an embodiment of an inventive
Bundes.Federal.
Ausführungsformen der ErfindungEmbodiments of the invention
Eine Kolbenpumpe trägt in Figur 1 insgesamt das Bezugszeichen 10. Sie umfasst ein Gehäuse 12, in dem eine Antriebswelle 14 über zwei Lager 16 und 18 gelagert ist. Wie insbesondere aus Figur 2 hervorgeht, umfasst die Antriebswelle 14 zwischen den beiden Lagern 16 und 18 einen im Querschnitt ovalen Nockenabschnitt 20.In FIG. 1, a piston pump carries the reference numeral 10 as a whole. It comprises a housing 12 in which a drive shaft 14 is mounted via two bearings 16 and 18. As can be seen in particular from FIG. 2, the drive shaft 14 has a cross-sectionally oval cam section 20 between the two bearings 16 and 18.
Die in den Figuren 1 und 2 gezeigte Kolbenpumpe 10 dient als Hochdruck-Kraftstoffpumpe für eine Brennkraftmaschine in einem Kraftfahrzeug. Mit ihr wird der Kraftstoff auf einen sehr hohen Druck verdichtet und zu einer Kraftstoff- Sammelleitung (nicht gezeigt) gefördert. Die Antriebswelle 14 der Kolbenpumpe 10 wird dabei direkt von der Brennkraftmaschine angetrieben. Daher verfugt die Antriebswelle 14 über einen entsprechenden Kupplungsabschnitt 22, der außerhalb des Gehäuses 12 angeordnet ist.The piston pump 10 shown in FIGS. 1 and 2 serves as a high-pressure fuel pump for an internal combustion engine in a motor vehicle. With it, the fuel is compressed to a very high pressure and conveyed to a fuel rail (not shown). The drive shaft 14 of the piston pump 10 is thereby directly from the internal combustion engine driven. Therefore, the drive shaft 14 has a corresponding coupling portion 22 which is disposed outside of the housing 12.
Bei der Kolbenpumpe 10 handelt es sich um eine 1 -Zylinder-Radialkolbenpumpe. In den beiden Figuren sind aus Gründen der Übersichtlichkeit jedoch weder der Kolben noch der von diesem begrenzte Förderraum noch die zugehörigen Einlass- und Auslassventile gezeigt. Diese Elemente sind in einen nicht gezeigten Zylinderkopf integriert, der an einem senkrecht zur Längsachse der Antriebswelle 14 stehenden Zylinderabschnitt 24 des Gehäuses 12 befestigt werden kann.The piston pump 10 is a 1-cylinder radial piston pump. For reasons of clarity, however, neither the piston nor the delivery chamber bounded by it nor the associated intake and exhaust valves are shown in the two figures. These elements are integrated into a cylinder head, not shown, which can be attached to a cylinder section 24 of the housing 12 that is perpendicular to the longitudinal axis of the drive shaft 14.
Der Kolben der Kolbenpumpe 10 wird von dem Nockenabschnitt 20 der Antriebswelle 14 mittelbar angetrieben. Unter dem Begriff "mittelbar" wird hier verstanden, dass der Kolben den Nockenabschnitt 20 nicht direkt berührt, sondern dass zwischen dem Kolben und dem Nockenabschnitt 20 ein sog. Rollenstößel 26 angeordnet ist. Dieser umfasst einen Stößelkörper 28 und eine Laufrolle 30.The piston of the piston pump 10 is indirectly driven by the cam portion 20 of the drive shaft 14. The term "indirectly" is understood here to mean that the piston does not directly touch the cam section 20, but that a so-called roller tappet 26 is arranged between the piston and the cam section 20. This comprises a plunger body 28 and a roller 30th
Mittels einer in der Zeichnung ebenfalls nicht dargestellten Kolbenfeder wird der Rollenstößel 26 zusammen mit dem Kolben gegen den Nockenabschnitt 20 gedrückt, um sicherzustellen, dass die Laufrolle 26 nicht von dem Nockenabschnitt 20 der Antriebswelle 14 abhebt. Bei dem Stößelkörper 28 handelt es sich im vorliegenden Ausführungsbeispiel um ein Sinterteil. Alternativ könnte es sich aber auch um ein Aluminium-Pressteil oder um ein Metallskelett handeln, welches mit Kunststoff umspritzt ist. Wie insbesondere aus Figur 3 hervorgeht, umfasst der Stößelkörper 28 einen zentralen, quaderförmigen Rollenschuh oder Stößelblock 34, an dessen in Figur 3 oberen Bereich auf beiden Seiten jeweils ein sich nach außen erstreckender Ansatz 36 bzw. 38 angeformt ist.By means of a piston spring, also not shown in the drawing, the roller tappet 26 is pressed together with the piston against the cam portion 20 to ensure that the roller 26 does not lift off from the cam portion 20 of the drive shaft 14. In the present embodiment, the plunger body 28 is a sintered part. Alternatively, it could also be an aluminum pressed part or a metal skeleton, which is encapsulated in plastic. As can be seen in particular from FIG. 3, the plunger body 28 comprises a central, cuboid roller shoe or plunger block 34, on whose upper region in FIG. 3 on both sides an outwardly extending projection 36 or 38 is integrally formed.
An diese ist wiederum jeweils ein sich senkrecht nach oben erstreckender Führungsabschnitt 40 bzw. 42 angeformt. Die beiden Führungsabschnitte 40 und 42 greifen in Einbaulage in entsprechende Nuten 44 und 46 im Zylinderabschnitt 24 des Gehäuses 12 ein (vergleiche Figur 1), welche gehäuseseitige Führungsbereiche bilden. Auf diese Weise kann sich der Stößelkörper 28 nicht um eine Längsachse des Zylinderabschnitts 24 verdrehen.In turn, in each case a vertically upwardly extending guide portion 40 or 42 is integrally formed on this. The two guide portions 40 and 42 engage in the mounting position in corresponding grooves 44 and 46 in the cylinder portion 24 of the housing 12 (see Figure 1), which form the housing-side guide areas. In this way, the plunger body 28 can not rotate about a longitudinal axis of the cylinder portion 24.
Auf seiner dem Nockenabschnitt 20 zugewandten Seite ist in den Stößelblock 34 eine zylindrische Ausnehmung 48 eingebracht, deren Längsachse in Einbaulage parallel zur Längsachse der Antriebswelle 14 verläuft. Die Ausnehmung ist zum Nockenabschnitt 20 hin offen und erstreckt sich über die gesamte Breite des Stößelkörpers 28. Ihre maximale Tiefe entspricht ungefähr dem Radius der zylindrischen Laufrolle 30, so dass diese ungefähr mit einem halben Durchmesser über den Rand der Ausnehmung 48 übersteht. Stößelkörper 28 und Stößelblock 34 können einstückig oder als separate Bauteile ausgebildet sein.On its side facing the cam portion 20, a cylindrical recess 48 is inserted into the plunger block 34, the longitudinal axis of which in the installed position is parallel to the longitudinal axis of the Drive shaft 14 extends. The recess is open to the cam portion 20 and extends over the entire width of the plunger body 28. Their maximum depth is approximately equal to the radius of the cylindrical roller 30 so that it protrudes approximately half a diameter beyond the edge of the recess 48. Plunger body 28 and plunger block 34 may be formed integrally or as separate components.
Die Laufrolle 30 ist in die Ausnehmung 48 eingesetzt und stützt sich mit ihrer Mantelfläche 49 an der Wand der Ausnehmung 48 ab. Laufrolle 30 und Ausnehmung 48 bilden ein Gleitlager.The roller 30 is inserted into the recess 48 and is supported with its lateral surface 49 on the wall of the recess 48 from. Roller 30 and recess 48 form a plain bearing.
Das Sicherungselement 32 dient dazu, die Laufrolle 30 in der Ausnehmung 48 im Stößelkörper 28 zu sichern und insbesondere auch bei der Montage ein Herausfallen der Laufrolle 30 aus dem Stößelelement 28 zu verhindern.The securing element 32 serves to secure the roller 30 in the recess 48 in the tappet body 28 and, in particular, to prevent the roller 30 from falling out of the tappet element 28 during assembly.
Wie aus Figur 1 ersichtlich, ist zu beiden Seiten des Nockenabschnitts 20 jeweils ein Bund 50 an der Antriebswelle 14 vorgesehen. Der Bund 50 ragt in radialer Richtung über denAs can be seen from FIG. 1, a collar 50 is provided on the drive shaft 14 on both sides of the cam section 20. The collar 50 projects in the radial direction over the
Nockenabschnitt 20 hinaus, so dass die Laufrolle 30, wenn sie während des Betriebs in axialer Richtung wandert, gegen einen der beiden Bünde 50 anläuft. Dadurch wird die Axialbewegung der Laufrolle 30 während des Betriebs auf ein definiertes Maß beschränkt. Gleichzeitig kann dafür Sorge getragen werden, dass durch eine geeignete tribologische Paarung der Laufrolle 30 und der Bünde 50 der Verschleiß sowohl an der Laufrolle 30 als auch am Bund 50 so gering ist, dass er nicht zu Funktionsstörungen oder einer Verkürzung der Lebensdauer der Kolbenpumpe 10 führt. Dies kann beispielsweise dadurch erreicht werden, dass der Bund ebenso wie der Nockenabschnitt 20 und der Rollenstößel 26 aus gehärtetem Stahl angefertigt werden.Cam portion 20 out, so that the roller 30 when it travels during operation in the axial direction, against one of the two frets 50 starts. Thereby, the axial movement of the roller 30 is limited during operation to a defined extent. At the same time, care can be taken that by a suitable tribological pairing of the roller 30 and the collars 50, the wear on both the roller 30 and the collar 50 is so small that it does not lead to malfunction or a shortening of the life of the piston pump 10 , This can for example be achieved in that the collar as well as the cam portion 20 and the roller tappet 26 are made of hardened steel.
Zwischen dem Nockenabschnitt 20 und den Bünden 50 ist jeweils ein Freistich 52 vorgesehen, welcher dafür sorgt, dass die Kerbwirkung am Übergang zwischen Nockenabschnitt 20 und Bund 50 reduziert wird. Des Weiteren sorgen die Freistiche 52 für definierte Kontaktflächen zwischen Laufrolle 30 und Nockenabschnitt 20 einerseits sowie Rollenstößel 26 und den Bünden 50 andererseits.Between the cam portion 20 and the collars 50, an undercut 52 is provided in each case, which ensures that the notch effect at the transition between cam portion 20 and collar 50 is reduced. Furthermore, the undercuts 52 provide for defined contact surfaces between roller 30 and cam portion 20 on the one hand and roller tappet 26 and the collars 50 on the other.
Ein weiterer Vorteil der Bünde 50 besteht darin, dass die Laufrolle 30 durch die Reibung, welche beim Anlaufen an einen der Bünde 50 entsteht, in Drehung versetzt wird, falls sie sich nicht ohnehin schon durch die Wälzreibung zwischen Nockenabschnitt 20 und Laufrolle 30 dreht. Es hat sich nämlich bei praktischen Versuchen herausgestellt, dass die Wälzreibung zwischen Laufrolle 30 und Nockenabschnitt 20 nicht immer ausreicht, um die Laufrollen 30 in Drehung zu versetzen, so dass sich nicht immer zwischen der Ausnehmung 48 im Stößelblock 34 und der Laufrolle 30 wie gewünscht ein hydrodynamisches Gleitlager ausbildet. Dieser unerwünschte Effekt wird bei der erfindungsgemäßen Ausgestaltung der Antriebswelle 14 vermieden.Another advantage of the collars 50 is that the roller 30 is rotated by the friction that occurs when starting at one of the collars 50, if it does not already by the rolling friction between the cam portion 20 and roller 30 rotates. It has been found in practical experiments that the rolling friction between roller 30 and cam portion 20 is not always sufficient to enable the rollers 30 in rotation, so that not always between the recess 48 in the plunger block 34 and the roller 30 as desired, a hydrodynamic Plain bearing forms. This undesirable effect is avoided in the embodiment of the drive shaft 14 according to the invention.
In der Schnittdarstellung gemäß Figur 2 ist gut ersichtlich, dass der Bund 50 über den gesamten Umfang des Nockenabschnitts 20 in radialer Richtung etwas über den Nockenabschnitt 20 hinausragt.In the sectional view according to FIG. 2, it can be clearly seen that the collar 50 projects over the entire circumference of the cam section 20 slightly beyond the cam section 20 in the radial direction.
In dem Detail X der Figur 1 ist eine besonders vorteilhafte Ausgestaltung eines Rollenstößels 26 dargestellt. Bei diesem Ausführungsbeispiel ist an den Stirnseiten (ohne Bezugszeichen) der Laufrolle 30 jeweils eine mittig angeordnete Vertiefung 54 ausgespart. Dadurch ist gewährleistet, dass die Laufrolle 30 nur im Bereich seines Außendurchmessers in Kontakt mit dem Bund 50 der Antriebswelle 14 gelangt, so dass das durch die Haft - oder Gleitreibung zwischen Laufrolle 30 und Bund 50 auf die Laufrolle 30 ausgeübte Drehmoment aufgrund des großen Hebelarms maximal wird.In the detail X of Figure 1, a particularly advantageous embodiment of a roller tappet 26 is shown. In this embodiment, a respective centrally disposed recess 54 is recessed at the end faces (without reference numeral) of the roller 30. This ensures that the roller 30 comes into contact with the collar 50 of the drive shaft 14 only in the region of its outer diameter, so that the torque exerted on the roller 30 by the adhesive or sliding friction between roller 30 and collar 50 is maximum due to the large lever arm becomes.
In Figur 3 ist ein konstruktives Detail einer weiteren vorteilhaften Ausgestaltung einer erfindungsgemäßen Kolbenpumpe im Detail dargestellt.FIG. 3 shows a detail of a constructional detail of a further advantageous embodiment of a piston pump according to the invention.
Bei dem Ausführungsbeispiel gemäß der Figuren 1 und 2 sind der Bund 50, der Nockenabschnitt 20 und die Antriebswelle 14 einstückig ausgebildet. Im Gegensatz dazu ist bei dem Ausführungsbeispiel gemäß Figur 3 der Bund als gesondertes Bauteil ausgeführt. Der Bund 50 kann beispielsweise als Blechzuschnitt ausgebildet werden. Um den Bund 50 an der Antriebswelle 14 zu befestigen, ist ein Absatz 56 seitlich des Freistichs 52 ausgearbeitet. Auf diesem Absatz wird der Bund 50 beispielsweise durch Pressen unlösbar befestigt. Es ist auch möglich, alternativ oder zusätzlich zu der Pressverbindung den Bund 50 durch eine Schweißnaht 58 an dem Absatz 56 zu befestigen. In the embodiment according to Figures 1 and 2, the collar 50, the cam portion 20 and the drive shaft 14 are integrally formed. In contrast, in the embodiment according to FIG. 3, the collar is designed as a separate component. The collar 50 can be formed for example as a sheet metal blank. To secure the collar 50 to the drive shaft 14, a shoulder 56 is machined laterally of the undercut 52. On this paragraph, the collar 50 is permanently attached, for example by pressing. It is also possible, alternatively or in addition to the press connection, to fasten the collar 50 to the shoulder 56 by means of a weld 58.

Claims

Ansprüche claims
1. Kolbenpumpe , insbesondere Hochdruck-Kraftstoffpumpe, mit einem Gehäuse (12), einem Kolben, und einer Antriebswelle (14) mit einem Nockenabschnitt (20), an dem sich der Kolben wenigstens mittelbar über eine Laufrolle (30) abstützt, dadurch gekennzeichnet, dass seitlich des Nockenabschnitts (20) ein Bund (50) vorgesehen ist, und dass der Bund (50) in radialer Richtung über den Nockenabschnitt (20) hinausragt.1. piston pump, in particular high-pressure fuel pump, with a housing (12), a piston, and a drive shaft (14) with a cam portion (20) on which the piston is supported at least indirectly via a roller (30), characterized in that a collar (50) is provided laterally of the cam portion (20), and in that the collar (50) projects beyond the cam portion (20) in the radial direction.
2. Kolbenpumpe nach Anspruch 1, dadurch gekennzeichnet, dass zu beiden Seiten des Nockenabschnitts (20) jeweils ein Bund (50) vorhanden ist.2. Piston pump according to claim 1, characterized in that on both sides of the cam portion (20) each have a collar (50) is present.
3. Kolbenpumpe nach einem der Ansprüche 1 oder 2, dadurch gekennzeichnet, dass der mindestens eine Bund (50) und der Nockenabschnitt (20 ) einstückig ausgebildet sind.3. Piston pump according to one of claims 1 or 2, characterized in that the at least one collar (50) and the cam portion (20) are integrally formed.
4. Kolbenpumpe nach einem der Ansprüche 1 oder 2, dadurch gekennzeichnet, dass der mindestens eine Bund (50) als Blechzuschnitt ausgeführt ist und mit der Antriebswelle (14) oder mit deren Nockenabschnitt (20 ) fest verbunden ist.4. Piston pump according to one of claims 1 or 2, characterized in that the at least one collar (50) is designed as a sheet metal blank and with the drive shaft (14) or with its cam portion (20) is firmly connected.
5. Kolbenpumpe nach Anspruch 4, dadurch gekennzeichnet, dass der mindestens eine Bund (50) mit der Antriebswelle (14) oder deren Nockenabschnitt (20) verpresst und/oder durch eine5. Piston pump according to claim 4, characterized in that the at least one collar (50) with the drive shaft (14) or the cam portion (20) pressed and / or by a
Schweißnaht (58) verbunden ist.Weld seam (58) is connected.
6. Kolbenpumpe nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass zwischen dem mindestens einen Bund (50) und dem Nockenabschnitt (20 ) ein Freistich (52) ausgebildet ist.6. Piston pump according to one of the preceding claims, characterized in that between the at least one collar (50) and the cam portion (20) an undercut (52) is formed.
7. Kolbenpumpe nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass der mindestens eine Bund (50) gehärtet ist.7. Piston pump according to one of the preceding claims, characterized in that the at least one collar (50) is hardened.
8. Kolbenpumpe nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass die Laufrolle (30) an ihren Stirnseiten eine mittig angeordnete Vertiefung (54) aufweist. 8. Piston pump according to one of the preceding claims, characterized in that the roller (30) has at its end faces a centrally disposed recess (54).
EP07802934A 2006-10-16 2007-08-28 Piston pump, in particular high-pressure fuel pump, having roller tappet Not-in-force EP2079923B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PL07802934T PL2079923T3 (en) 2006-10-16 2007-08-28 Piston pump, in particular high-pressure fuel pump, having roller tappet

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102006048722A DE102006048722A1 (en) 2006-10-16 2006-10-16 Piston pump, in particular high-pressure fuel pump, with roller tappet
PCT/EP2007/058897 WO2008046683A1 (en) 2006-10-16 2007-08-28 Piston pump, in particular high-pressure fuel pump, having roller tappet

Publications (2)

Publication Number Publication Date
EP2079923A1 true EP2079923A1 (en) 2009-07-22
EP2079923B1 EP2079923B1 (en) 2010-05-12

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EP07802934A Not-in-force EP2079923B1 (en) 2006-10-16 2007-08-28 Piston pump, in particular high-pressure fuel pump, having roller tappet

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EP (1) EP2079923B1 (en)
CN (1) CN101529082B (en)
AT (1) ATE467760T1 (en)
DE (2) DE102006048722A1 (en)
PL (1) PL2079923T3 (en)
WO (1) WO2008046683A1 (en)

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Also Published As

Publication number Publication date
DE502007003793D1 (en) 2010-06-24
EP2079923B1 (en) 2010-05-12
PL2079923T3 (en) 2010-10-29
CN101529082A (en) 2009-09-09
DE102006048722A1 (en) 2008-04-17
ATE467760T1 (en) 2010-05-15
WO2008046683A1 (en) 2008-04-24
CN101529082B (en) 2012-01-11

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