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EP2032850B1 - High pressure pump in particular for a fuel injection device on an internal combustion engine - Google Patents

High pressure pump in particular for a fuel injection device on an internal combustion engine Download PDF

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Publication number
EP2032850B1
EP2032850B1 EP07726234A EP07726234A EP2032850B1 EP 2032850 B1 EP2032850 B1 EP 2032850B1 EP 07726234 A EP07726234 A EP 07726234A EP 07726234 A EP07726234 A EP 07726234A EP 2032850 B1 EP2032850 B1 EP 2032850B1
Authority
EP
European Patent Office
Prior art keywords
roller
support
pressure pump
pump according
pump
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.)
Active
Application number
EP07726234A
Other languages
German (de)
French (fr)
Other versions
EP2032850A1 (en
Inventor
Peter Bauer
Markus Koch
Gernot Repphun
Wolfram Rittmannsberger
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
Publication of EP2032850A1 publication Critical patent/EP2032850A1/en
Application granted granted Critical
Publication of EP2032850B1 publication Critical patent/EP2032850B1/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
    • 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
    • F04B1/0413—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
    • F04B1/053—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement with actuating or actuated elements at the inner ends of the cylinders
    • 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
    • F04B1/053—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement with actuating or actuated elements at the inner ends of the cylinders
    • F04B1/0531—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement with actuating or actuated elements at the inner ends of the cylinders with cam-actuated distribution members
    • 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
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/02—Fuel-injection apparatus having means for reducing wear
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2210/00—Working fluid
    • F05B2210/10—Kind or type
    • F05B2210/11—Kind or type liquid, i.e. incompressible
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S415/00—Rotary kinetic fluid motors or pumps
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S417/00—Pumps

Definitions

  • the invention relates to a high-pressure pump, in particular for a fuel injection device of an internal combustion engine according to the preamble of claim 1.
  • Such a high-pressure pump is through the DE 199 07 311 A1 known.
  • This high-pressure pump has a drive shaft with at least one cam or eccentric.
  • the high-pressure pump also has at least one pump element which has a pump piston which is driven by the cam or eccentric of the drive shaft in a lifting movement.
  • a support member is arranged and in the support member is rotatably mounted a roller which rolls on the cam or eccentric of the drive shaft.
  • a pump is known with a drive shaft having at least one cam or eccentric.
  • the pump has at least one pump element, which in turn has a pump piston which is driven by the cam or eccentric of the drive shaft in a lifting movement.
  • a support member and a rotatably mounted in this roller is arranged between the pump piston and the cam or eccentric of the drive shaft.
  • a support for the roller is arranged in the direction of the axis of rotation of the roller next to this a support for the roller is arranged
  • the support is formed by annular discs, which are flat and the roller has at its end facing the support each have a chamfer or chamfer, wherein the end faces of the roller also just trained. Even with this design of the role increased wear can occur.
  • the high pressure pump according to the invention with the features of claim 1 has the advantage that the wear of the roller and / or the support is reduced and thus increased friction is avoided here.
  • FIG. 1 a high-pressure pump for a fuel injection device of an internal combustion engine in a longitudinal section
  • FIG. 2 the high pressure pump in a cross section along line II-II in FIG. 1
  • FIG. 3 one in FIG. 1 III section of the high pressure pump in an enlarged view according to a first embodiment
  • FIG. 4 the detail III of the high pressure pump according to a second embodiment
  • FIG. 5 the detail III of the high pressure pump according to a third embodiment
  • FIG. 6 a part of the high-pressure pump according to a fourth embodiment
  • FIG. 7 a section of the high-pressure pump in a section along line VII-VII in FIG. 2
  • FIGS. 1 to 6 a high pressure pump for a fuel injector of an internal combustion engine is shown.
  • the high-pressure pump has a multi-part pump housing 10, in which one through the Internal combustion engine rotationally driven drive shaft 12 is arranged.
  • the drive shaft 12 is rotatably supported, for example, via two bearing points spaced apart from one another in the direction of the axis of rotation 13 of the drive shaft 12.
  • the bearings can be arranged in different parts of the pump housing 10, for example, a first bearing point in a base body 14 of the pump housing 10 and a second bearing point can be arranged in a connected to the base body 14 flange 15.
  • the drive shaft 12 at least one cam 16 or eccentrically to its axis of rotation 13 formed portion, wherein the cam 16 may be formed as a multiple cam.
  • the high pressure pump has at least one or more arranged in the housing 10 pump elements 18, each with a pump piston 20 which is driven by the cam 16 of the drive shaft 12 in a lifting movement in at least approximately radial direction to the axis of rotation 13 of the drive shaft 12.
  • a pump housing part 22 connected to the main body 14 is provided, which is designed as a cylinder head.
  • the pump housing part 22 has a voltage applied to an outer side of the base body 14 and a flange 24 projecting through an opening in the base body 14 to the drive shaft 12 through, at least approximately cylindrical projection 26 with respect to the flange 24 of smaller diameter.
  • the pump piston 20 is guided tightly displaceable in a shoulder 26 formed in the cylinder bore 28 in the pump housing part 22 and limited with its drive shaft 12 facing away from the end face in the cylinder bore 28 a pump working space 30.
  • the cylinder bore 28 may extend into the flange 24, in the then the pump working space 30 is arranged is.
  • the pump working chamber 30 has a connection with a fuel feed, for example a feed pump, via a fuel feed channel 32 extending in the pump housing 10.
  • the pump working chamber 30 also has a connection in the pump housing 10 extending fuel drain passage 36 to an outlet with an outlet, which is connected for example to a high-pressure accumulator 110.
  • One or preferably a plurality of injectors 120 arranged on the cylinders of the internal combustion engine are connected to the high-pressure accumulator 110, through which fuel is injected into the cylinders of the internal combustion engine.
  • an outlet valve 38 opening out of the pump working chamber 30 is arranged.
  • a plunger 40 is arranged, via which the pump piston 20 at least indirectly on the cam 16 of the drive shaft 12 is supported.
  • the plunger 40 is formed in a hollow cylindrical shape with a round outer cross section and is guided displaceably in a bore 42 of the main body 14 of the pump housing 10 in the direction of the longitudinal axis 21 of the pump piston 20.
  • the longitudinal axis 41 of the plunger 40 is thus at least substantially identical to the longitudinal axis 21 of the pump piston 20.
  • a support member 44 is inserted, in which a roller 46 is rotatably mounted on the cam 16 the drive shaft 12 rolls.
  • the axis of rotation 47 of the roller 46 is at least approximately parallel to the axis of rotation 13 of the drive shaft 12.
  • the support member 44 has on its side facing the drive shaft 12 a recess 48 in which the roller 46 is rotatably mounted.
  • the support element 44 and the plunger 40 may also be integrally formed.
  • the pump piston 20 may be coupled to the plunger 40, at least in the direction of the longitudinal axis 21. Alternatively, the pump piston 20 may not be connected to the plunger 40, then by the return spring 52, the system of the pump piston 20 is secured to the plunger 40.
  • the restoring spring 52 engages, for example, via a spring plate 53 on an enlarged diameter piston base of the pump piston 20, which is thereby held in abutment against a flange projecting inwardly from the jacket on the plunger 40, which in turn bears against the support element 44 is held, so that the entire composite of pump piston 20, plunger 40 and support member 44 is acted upon with roller 46 to the cam 16 of the drive shaft 12 out.
  • a support 60 is arranged laterally next to the roller 46 for this purpose, by which the roller 46 is prevented from moving out of the support element 44 in the direction of its axis of rotation 47.
  • the roller 46 is convexly curved at its side facing the support 60 side surfaces 56, for example, at least approximately spherically curved.
  • the side surfaces 56 of the roller 46 facing surface of the support 60 is curved, in particular concavely curved, for example as in FIG. 7 shown as a section of a circular cylinder.
  • the concave curvature of the support 60 is thus only in sectional planes perpendicular to the longitudinal axis 41 of the plunger 40 according to FIG.
  • the support 60 in sectional planes parallel to the longitudinal axis 41 in accordance with FIGS. 3 to 6 has no curvature.
  • the support 60 can as in FIG. 7 illustrated as a ring surrounding the roller 46 may be formed or only laterally adjacent to the side surfaces 56 of the roller 46 may be arranged.
  • the geometry of the side surfaces 56 of the roller 46 and the support 60 is optimized in terms of minimum surface pressure and maximum cooling, so that the tribological stress of the roller 46 and the support 60 is minimized. If the support 60 is formed with a radius R1 concave, as shown in FIG. 7 is shown, the radius R of the convex curvature of the side surfaces 56 of the roller 46, for example, about 70 to 100%, preferably about 85 to 95% of the radius R1 of the support 60th
  • the roller 46 and / or the support 60 at least in the contact area between the roller 46 and the support 60 has a surface with high wear resistance.
  • the roller 46 is made entirely of a material with high wear resistance, for example of a ceramic material or a hard metal.
  • the support 60 as a whole consists of a material with high wear resistance, for example of a ceramic material or a hard metal.
  • the roller 46 itself consists of a material with lower wear resistance and according to a in FIG. 3 illustrated embodiment on their support 60 facing side surfaces 56 is provided with a coating 62 made of a material with high wear resistance.
  • the support 60 can also be provided with a coating 62 made of a material with high wear resistance.
  • the coating 62 may consist of a ceramic material, of a hard metal or of a carbon compound, in particular a diamond-like carbon compound.
  • the coating 62 may consist of a metal oxide or a metal nitride, for example titanium nitride.
  • the coating 62 may also be made by nitrocarburizing.
  • the roller 46 itself consists of a material with lower wear resistance and according to a in FIG. 4 illustrated embodiment in their support 60 facing side surfaces 56 each having an insert 64 made of a material having high wear resistance.
  • the insert 64 may be formed as a thin plate which is inserted into a corresponding recess of the side surface 56 of the roller 46.
  • an insert 64 made of a material with high wear resistance can also be inserted into the support 60 in its regions facing the side surfaces 56 of the roller 46.
  • the insert 64 can be made of a material as indicated above for the coating 62.
  • the coating 62 according to a in FIG. 5 illustrated embodiment directly on the plunger 40, as in FIG. 5 shown in the left half, or the support member 44, as in FIG. 5 shown in the right half, is applied, in particular on an adjacent to the roller 46 laterally in the direction of its axis of rotation 47 inner wall of the plunger 40 or support member 44. It can be provided that in the inner wall of the plunger 40 or support member 44 at least one groove 66 is arranged, in which the coating 62 is introduced, wherein in the at least one groove 66 good adhesion of the coating 62 on the plunger 40 and support member 44 is ensured.
  • the coating 62 can be applied for example by spraying as a spray ceramic.
  • the support 60 may be formed by a part of the plunger 40 or the support member 44 or by a separate, in the plunger 40, as in FIG. 6 shown in the left half, or the support member 44, as in FIG. 6 shown in the right half, inserted in particular annular component, which is then arranged between the roller 46 and the plunger 40 and the support member 44.
  • the support 60 may be inserted into the plunger 40 or the support member 44, for example, pressed.
  • a receptacle 68 may be formed for the support 60.
  • the receptacle 68 may be formed, for example, by an area enlarged in the inner diameter of the inner wall of the plunger 40 surrounding the roller 46.
  • the wall thickness of the plunger 40 can be reduced in the region of the receptacle 68 relative to the remaining plunger 40 or support element 44.
  • An identically formed receptacle 68 for the support 60 may alternatively, as in FIG. 6 shown in the right half, be formed in the support member 44.
  • Support can be formed as explained above, ie even consist of a material with high wear resistance or have a coating or insert made of a material with high wear resistance.

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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)
  • Reciprocating Pumps (AREA)

Abstract

A high pressure pump, especially for fuel injection in an IC engine has a cam follower (46) between the drive cam (16) and the piston (42) The ends of the cylindrical cam follower are convex and provided with a hard coating as is the inner wall of the pup bore, covering the stroke of the pump. The hard coating reduce pump wear and provide a low drag pumping system. Suitable coatings include ceramics and carbon compounds. Typical coatings include metal oxides and metal nitrides such as titanium nitride.

Description

Stand der TechnikState of the art

Die Erfindung geht aus von einer Hochdruckpumpe, insbesondere für eine Kraftstoffeinspritzeinrichtung einer Brennkraftmaschine nach der Gattung des Anspruchs 1.The invention relates to a high-pressure pump, in particular for a fuel injection device of an internal combustion engine according to the preamble of claim 1.

Eine solche Hochdruckpumpe ist durch die DE 199 07 311 A1 bekannt. Diese Hochdruckpumpe weist eine Antriebswelle mit wenigstens einem Nocken oder Exzenter auf. Die Hochdruckpumpe weist außerdem wenigstens ein Pumpenelement auf, das einen Pumpenkolben aufweist, der durch den Nocken oder Exzenter der Antriebswelle in einer Hubbewegung angetrieben wird. Zwischen dem Pumpenkolben und dem Nocken oder Exzenter der Antriebswelle ist ein Stützelement angeordnet und im Stützelement ist eine Rolle drehbar gelagert, die auf dem Nocken oder Exzenter der Antriebswelle abrollt. Es wurde festgestellt, dass beim Betrieb der Hochdruckpumpe auf die Rolle auch Kräfte in Richtung ihrer Drehachse wirken, wobei beim Anlauf der Rolle an benachbarte Bauteile an der Rolle und/oder diesen Bauteilen Verschleiß auftreten kann, der zu erhöhter Reibung zwischen der Rolle und den benachbarten Bauteilen führt. Diese erhöhte Reibung behindert die Drehbewegung der Rolle wodurch Schlupf zwischen der Rolle und dem Nocken oder Exzenter der Antriebswelle auftreten kann, was auch hier zu Verschleiß führt.Such a high-pressure pump is through the DE 199 07 311 A1 known. This high-pressure pump has a drive shaft with at least one cam or eccentric. The high-pressure pump also has at least one pump element which has a pump piston which is driven by the cam or eccentric of the drive shaft in a lifting movement. Between the pump piston and the cam or eccentric drive shaft, a support member is arranged and in the support member is rotatably mounted a roller which rolls on the cam or eccentric of the drive shaft. It has been found that during operation of the high-pressure pump on the roller and forces acting in the direction of its axis of rotation, which can occur when the roller starts to adjacent components on the roller and / or these components wear, resulting in increased friction between the roller and the adjacent Leads components. This increased friction hinders the rotational movement of the roller whereby slippage between the roller and the cam or eccentric of the drive shaft may occur, which also leads to wear.

Durch die DE 39 19 267 A1 ist eine Pumpe bekannt, mit einer Antriebswelle, die wenigstens einen Nocken oder Exzenter aufweist. Die Pumpe weist wenigstens ein Pumpenelement auf, das wiederum einen Pumpenkolben aufweist, der durch den Nocken oder Exzenter der Antriebswelle in einer Hubbewegung angetrieben wird. Zwischen dem Pumpenkolben und dem Nocken oder Exzenter der Antriebswelle ist ein Stützelement und eine in diesem drehbar gelagerte Rolle angeordnet. In Richtung der Drehachse der Rolle ist neben dieser eine Abstützung für die Rolle angeordnet Die Abstützung ist durch Ringscheiben gebildet, die eben ausgebildet sind und die Rolle weist an ihren der Abstützung zugewandten Stirnseiten jeweils eine Fase bzw. Anschrägung auf, wobei die Stirnseiten der Rolle ebenfalls eben ausgebildet sind. Auch bei dieser Ausbildung der Rolle kann erhöhter Verschleiß auftreten.By the DE 39 19 267 A1 For example, a pump is known with a drive shaft having at least one cam or eccentric. The pump has at least one pump element, which in turn has a pump piston which is driven by the cam or eccentric of the drive shaft in a lifting movement. Between the pump piston and the cam or eccentric of the drive shaft, a support member and a rotatably mounted in this roller is arranged. In the direction of the axis of rotation of the roller next to this a support for the roller is arranged The support is formed by annular discs, which are flat and the roller has at its end facing the support each have a chamfer or chamfer, wherein the end faces of the roller also just trained. Even with this design of the role increased wear can occur.

Offenbarung der ErfindungDisclosure of the invention Vorteile der ErfindungAdvantages of the invention

Die erfindungsgemäße Hochdruckpumpe mit den Merkmalen gemäß Anspruch 1 hat demgegenüber den Vorteil, dass der Verschleiß der Rolle und/oder der Abstützung reduziert ist und damit erhöhte Reibung hier vermieden wird.The high pressure pump according to the invention with the features of claim 1 has the advantage that the wear of the roller and / or the support is reduced and thus increased friction is avoided here.

In den abhängigen Ansprüchen sind vorteilhafte Ausgestaltungen und Weiterbildungen der erfindungsgemäßen Hochdruckpumpe angegeben.In the dependent claims advantageous refinements and developments of the high pressure pump according to the invention are given.

Mehrere Ausführungsbeispiele der Erfindung sind in der Zeichnung dargestellt und in der nachfolgenden Beschreibung näher erläutert. Es zeigen Figur 1 eine Hochdruckpumpe für eine Kraftstoffeinspritzeinrichtung einer Brennkraftmaschine in einem Längsschnitt, Figur 2 die Hochdruckpumpe in einem Querschnitt entlang Linie II-II in Figur 1, Figur 3 einen in Figur 1 mit III bezeichneten Ausschnitt der Hochdruckpumpe in vergrößerter Darstellung gemäß einem ersten Ausführungsbeispiel, Figur 4 den Ausschnitt III der Hochdruckpumpe gemäß einem zweiten Ausführungsbeispiel, Figur 5 den Ausschnitt III der Hochdruckpumpe gemäß einem dritten Ausführungsbeispiel, Figur 6 einen Teil der Hochdruckpumpe gemäß einem vierten Ausführungsbeispiel und Figur 7 einen Ausschnitt der Hochdruckpumpe in einem Schnitt entlang Linie VII-VII in Figur 2.Several embodiments of the invention are illustrated in the drawings and explained in more detail in the following description. Show it FIG. 1 a high-pressure pump for a fuel injection device of an internal combustion engine in a longitudinal section, FIG. 2 the high pressure pump in a cross section along line II-II in FIG. 1 . FIG. 3 one in FIG. 1 III section of the high pressure pump in an enlarged view according to a first embodiment, FIG. 4 the detail III of the high pressure pump according to a second embodiment, FIG. 5 the detail III of the high pressure pump according to a third embodiment, FIG. 6 a part of the high-pressure pump according to a fourth embodiment and FIG. 7 a section of the high-pressure pump in a section along line VII-VII in FIG. 2 ,

Beschreibung der AusführungsbeispieleDescription of the embodiments

In den Figuren 1 bis 6 ist eine Hochdruckpumpe für eine Kraftstoffeinspritzeinrichtung einer Brennkraftmaschine dargestellt. Die Hochdruckpumpe weist ein mehrteiliges Pumpengehäuse 10 auf, in dem eine durch die Brennkraftmaschine rotierend angetriebene Antriebswelle 12 angeordnet ist. Die Antriebswelle 12 ist beispielsweise über zwei in Richtung der Drehachse 13 der Antriebswelle 12 voneinander beabstandete Lagerstellen drehbar gelagert. Die Lagerstellen können in verschiedenen Teilen des Pumpengehäuses 10 angeordnet sein, beispielsweise kann eine erste Lagerstelle in einem Grundkörper 14 des Pumpengehäuses 10 und eine zweite Lagerstelle in einem mit dem Grundkörper 14 verbundenen Flanschteil 15 angeordnet sein.In the FIGS. 1 to 6 a high pressure pump for a fuel injector of an internal combustion engine is shown. The high-pressure pump has a multi-part pump housing 10, in which one through the Internal combustion engine rotationally driven drive shaft 12 is arranged. The drive shaft 12 is rotatably supported, for example, via two bearing points spaced apart from one another in the direction of the axis of rotation 13 of the drive shaft 12. The bearings can be arranged in different parts of the pump housing 10, for example, a first bearing point in a base body 14 of the pump housing 10 and a second bearing point can be arranged in a connected to the base body 14 flange 15.

In einem zwischen den beiden Lagerstellen liegenden Bereich weist die Antriebswelle 12 wenigstens einen Nocken 16 oder einen exzentrisch zu ihrer Drehachse 13 ausgebildeten Abschnitt auf, wobei der Nocken 16 auch als Mehrfachnocken ausgebildet sein kann. Die Hochdruckpumpe weist wenigstens ein oder mehrere im Gehäuse 10 angeordnete Pumpenelemente 18 mit jeweils einem Pumpenkolben 20 auf, der durch den Nocken 16 der Antriebswelle 12 in einer Hubbewegung in zumindest annähernd radialer Richtung zur Drehachse 13 der Antriebsewelle 12 angetrieben wird. Im Bereich jedes Pumpenelements 18 ist ein mit dem Grundkörper 14 verbundenes PumpengehäuseLeil 22 vorgesehen, das als Zylinderkopf ausgebildet ist. Das Pumpengehäuseteil 22 weist einen an einer Außenseite des Grundkörpers 14 anliegenden Flansch 24 und einen durch eine Öffnung im Grundkörper 14 zur Antriebswelle 12 hin durchragenden, zumindest annähernd zylinderförmigen Ansatz 26 mit gegenüber dem Flansch 24 kleinerem Durchmesser auf. Der Pumpenkolben 20 ist in einer im Ansatz 26 ausgebildeten Zylinderbohrung 28 im Pumpengehäuseteil 22 dicht verschiebbar geführt und begrenzt mit seiner der Antriebswelle 12 abgewandten Stirnseite in der Zylinderbohrung 28 einen Pumpenarbeitsraum 30. Die Zylinderbohrung 28 kann sich bis in den Flansch 24 hinein erstrecken, in dem dann der Pumpenarbeitsraum 30 angeordnet ist. Der Pumpenarbeitsraum 30 weist über einen im Pumpengehäuse 10 verlaufenden Kraftstoffzulaufkanal 32 eine Verbindung mit einem Kraftstoffzulauf, beispielsweise einer Förderpumpe auf. An der Mündung des Kraftstoffzulaufkanals 32 in den Pumpenarbeitsraum 30 ist ein in den Pumpenarbeitsraum 30 öffnendes Einlassventil 34 angeordnet. Der Pumpenarbeitsraum 30 weist ausserdem über einen im Pumpengehäuse 10 verlaufenden Kraftstoffablaufkanal 36 eine Verbindung mit einem Auslass auf, der beispielsweise mit einem Hochdruckspeicher 110 verbunden ist. Mit dem Hochdruckspeicher 110 sind ein oder vorzugsweise mehrere an den Zylindern der Brennkraftmaschine angeordnete Injektoren 120 verbunden, durch die Kraftstoff in die Zylinder der Brennkraftmaschine eingespritzt wird. An der Mündung des Kraftstoffablaufkanals 36 in den Pumpenarbeitsraum 30 ist ein aus dem Pumpenarbeitsraum 30 öffnendes Auslassventil 38 angeordnet.In a lying between the two bearing areas, the drive shaft 12 at least one cam 16 or eccentrically to its axis of rotation 13 formed portion, wherein the cam 16 may be formed as a multiple cam. The high pressure pump has at least one or more arranged in the housing 10 pump elements 18, each with a pump piston 20 which is driven by the cam 16 of the drive shaft 12 in a lifting movement in at least approximately radial direction to the axis of rotation 13 of the drive shaft 12. In the region of each pump element 18, a pump housing part 22 connected to the main body 14 is provided, which is designed as a cylinder head. The pump housing part 22 has a voltage applied to an outer side of the base body 14 and a flange 24 projecting through an opening in the base body 14 to the drive shaft 12 through, at least approximately cylindrical projection 26 with respect to the flange 24 of smaller diameter. The pump piston 20 is guided tightly displaceable in a shoulder 26 formed in the cylinder bore 28 in the pump housing part 22 and limited with its drive shaft 12 facing away from the end face in the cylinder bore 28 a pump working space 30. The cylinder bore 28 may extend into the flange 24, in the then the pump working space 30 is arranged is. The pump working chamber 30 has a connection with a fuel feed, for example a feed pump, via a fuel feed channel 32 extending in the pump housing 10. At the mouth of the fuel inlet channel 32 into the pump working chamber 30, an inlet valve 34 opening into the pump working chamber 30 is arranged. The pump working chamber 30 also has a connection in the pump housing 10 extending fuel drain passage 36 to an outlet with an outlet, which is connected for example to a high-pressure accumulator 110. One or preferably a plurality of injectors 120 arranged on the cylinders of the internal combustion engine are connected to the high-pressure accumulator 110, through which fuel is injected into the cylinders of the internal combustion engine. At the mouth of the fuel drainage channel 36 into the pump working chamber 30, an outlet valve 38 opening out of the pump working chamber 30 is arranged.

Zwischen dem Pumpenkolben 20 und dem Nocken 16 der Antriebswelle 12 ist ein Stößel 40 angeordnet, über den sich der Pumpenkolben 20 zumindest mittelbar am Nocken 16 der Antriebswelle 12 abstützt. Der Stößel 40 ist hohlzylinderförmig mit rundem Außenquerschnitt ausgebildet und ist in einer Bohrung 42 des Grundkörpers 14 des Pumpengehäuses 10 in Richtung der Längsachse 21 des Pumpenkolbens 20 verschiebbar geführt. Die Längsachse 41 des Stößels 40 ist somit zumindest im wesentlichen identisch mit der Längsachse 21 des Pumpenkolbens 20. Im Stößel 40 ist in dessen der Antriebswelle 12 zugewandtem Endbereich ein Stützelement 44 eingesetzt, in dem eine Rolle 46 drehbar gelagert ist, die auf dem Nocken 16 der Antriebswelle 12 abrollt. Die Drehachse 47 der Rolle 46 ist zumindest annähernd parallel zur Drehachse 13 der Antriebswelle 12. Das Stützelement 44 weist auf seiner der Antriebswelle 12 zugewandten Seite eine Vertiefung 48 auf, in der die Rolle 46 drehbar gelagert ist. Das Stützelement 44 und der Stößel 40 können auch einstückig ausgebildet sein.Between the pump piston 20 and the cam 16 of the drive shaft 12, a plunger 40 is arranged, via which the pump piston 20 at least indirectly on the cam 16 of the drive shaft 12 is supported. The plunger 40 is formed in a hollow cylindrical shape with a round outer cross section and is guided displaceably in a bore 42 of the main body 14 of the pump housing 10 in the direction of the longitudinal axis 21 of the pump piston 20. The longitudinal axis 41 of the plunger 40 is thus at least substantially identical to the longitudinal axis 21 of the pump piston 20. In the plunger 40 in the drive shaft 12 facing end portion, a support member 44 is inserted, in which a roller 46 is rotatably mounted on the cam 16 the drive shaft 12 rolls. The axis of rotation 47 of the roller 46 is at least approximately parallel to the axis of rotation 13 of the drive shaft 12. The support member 44 has on its side facing the drive shaft 12 a recess 48 in which the roller 46 is rotatably mounted. The support element 44 and the plunger 40 may also be integrally formed.

Am Stößel 40 oder am Pumpenkolben 20 greift eine vorgespannte Rückstellfeder 52 an, die sich am Pumpengehäuseteil 22 abstützt. Durch die Rückstellfeder 52 werden der Pumpenkolben 20 und der Stößel 40 zum Nocken 16 der Antriebswelle 12 hin beaufschlagt, so dass die Anlage der Rolle 44 am Nocken 16 auch beim zur Antriebswelle 12 hin gerichteten Saughub des Pumpenkolbens 20 und auch bei hoher Drehzahl der Antriebswelle 12 sichergestellt ist. Der Pumpenkolben 20 kann mit dem Stößel 40 gekoppelt sein, zumindest in Richtung von dessen Längsachse 21. Alternativ kann der Pumpenkolben 20 auch nicht mit dem Stößel 40 verbunden sein, wobei dann durch die Rückstellfeder 52 die Anlage des Pumpenkolbens 20 am Stößel 40 sichergestellt wird. Es kann vorgesehen sein, dass die Rückstellfeder 52 beispielsweise über einen Federteller 53 an einem im Durchmesser vergrößerten Kolbenfuß des Pumpenkolbens 20 angreift, der dadurch in Anlage an einem am Stößel 40 von dessen Mantel nach innen ragenden Flansch gehalten wird, der wiederum in Anlage am Stützelement 44 gehalten wird, so dass der gesamte Verbund aus Pumpenkolben 20, Stößel 40 und Stützelement 44 mit Rolle 46 zum Nocken 16 der Antriebswelle 12 hin beaufschlagt ist.On the plunger 40 or on the pump piston 20 engages a prestressed return spring 52, which is supported on the pump housing part 22. By the return spring 52, the pump piston 20 and the plunger 40 are acted upon cam 16 of the drive shaft 12 out, so that the contact of the roller 44 on the cam 16 and the intake shaft 12 toward the suction stroke of the pump piston 20 and at high speed of the drive shaft 12th is ensured. The pump piston 20 may be coupled to the plunger 40, at least in the direction of the longitudinal axis 21. Alternatively, the pump piston 20 may not be connected to the plunger 40, then by the return spring 52, the system of the pump piston 20 is secured to the plunger 40. It can be provided that the restoring spring 52 engages, for example, via a spring plate 53 on an enlarged diameter piston base of the pump piston 20, which is thereby held in abutment against a flange projecting inwardly from the jacket on the plunger 40, which in turn bears against the support element 44 is held, so that the entire composite of pump piston 20, plunger 40 and support member 44 is acted upon with roller 46 to the cam 16 of the drive shaft 12 out.

In Richtung der Drehachse 47 ist seitlich neben der Rolle 46 für diese eine Abstützung 60 angeordnet, durch die verhindert wird, dass sich die Rolle 46 in Richtung ihrer Drehachse 47 aus dem Stützelement 44 herausbewegt. Die Rolle 46 ist an ihren der Abstützung 60 zugewandten Seitenflächen 56 konvex gewölbt ausgebildet, beispielsweise zumindest annähernd kugelförmig gewölbt. Die den Seitenflächen 56 der Rolle 46 zugewandte Fläche der Abstützung 60 ist gewölbt, insbesondere konkav gewölbt ausgebildet, beispielsweise wie in Figur 7 dargestellt als Abschnitt eines Kreiszylinders. Die konkave Wölbung der Abstützung 60 ist somit nur in Schnittebenen senkrecht zur Längsachse 41 des Stößels 40 gemäß Figur 7 vorhanden, während die Abstützung 60 in Schnittebenen parallel zur Längsachse 41 gemäß den Figuren 3 bis 6 keine Wölbung aufweist. Die Abstützung 60 kann wie in Figur 7 dargestellt als ein die Rolle 46 umgebender Ring ausgebildet sein oder nur seitlich neben den Seitenflächen 56 der Rolle 46 angeordnet sein.In the direction of the axis of rotation 47, a support 60 is arranged laterally next to the roller 46 for this purpose, by which the roller 46 is prevented from moving out of the support element 44 in the direction of its axis of rotation 47. The roller 46 is convexly curved at its side facing the support 60 side surfaces 56, for example, at least approximately spherically curved. The side surfaces 56 of the roller 46 facing surface of the support 60 is curved, in particular concavely curved, for example as in FIG. 7 shown as a section of a circular cylinder. The concave curvature of the support 60 is thus only in sectional planes perpendicular to the longitudinal axis 41 of the plunger 40 according to FIG. 7 present, while the support 60 in sectional planes parallel to the longitudinal axis 41 in accordance with FIGS. 3 to 6 has no curvature. The support 60 can as in FIG. 7 illustrated as a ring surrounding the roller 46 may be formed or only laterally adjacent to the side surfaces 56 of the roller 46 may be arranged.

Die Geometrie der Seitenflächen 56 der Rolle 46 und der Abstützung 60 ist hinsichtlich minimaler Flächenpressung und maximaler Kühlung optimiert, so dass die tribologische Beanspruchung der Rolle 46 und der Abstützung 60 minimiert ist. Wenn die Abstützung 60 mit einem Radius R1 konkav gewölbt ausgebildet ist, wie dies in Figur 7 dargestellt ist, so beträgt der Radius R der konvexen Wölbung der Seitenflächen 56 der Rolle 46 beispielsweise etwa 70 bis 100%, vorzugsweise etwa 85 bis 95% des Radius R1 der Abstützung 60.The geometry of the side surfaces 56 of the roller 46 and the support 60 is optimized in terms of minimum surface pressure and maximum cooling, so that the tribological stress of the roller 46 and the support 60 is minimized. If the support 60 is formed with a radius R1 concave, as shown in FIG FIG. 7 is shown, the radius R of the convex curvature of the side surfaces 56 of the roller 46, for example, about 70 to 100%, preferably about 85 to 95% of the radius R1 of the support 60th

Es ist vorgesehen, dass die Rolle 46 und/oder die Abstützung 60 zumindest im Kontaktbereich zwischen der Rolle 46 und der Abstützung 60 eine Oberfläche mit hoher Verschleißfestigkeit aufweist. Hierbei kann vorgesehen sein, dass die Rolle 46 insgesamt aus einem Werkstoff mit hoher Verschleißfestigkeit besteht, beispielsweise aus einem keramischen Werkstoff oder einem Hartmetall. Alternativ oder zusätzlich kann auch vorgesehen sein, dass die Abstützung 60 insgesamt aus einem Werkstoff mit hoher Verschleißfestigkeit besteht, beispielsweise aus einem keramischen Werkstoff oder einem Hartmetall.It is envisaged that the roller 46 and / or the support 60 at least in the contact area between the roller 46 and the support 60 has a surface with high wear resistance. It can be provided that the roller 46 is made entirely of a material with high wear resistance, for example of a ceramic material or a hard metal. Alternatively or additionally, it can also be provided that the support 60 as a whole consists of a material with high wear resistance, for example of a ceramic material or a hard metal.

Alternativ ist vorgesehen, dass die Rolle 46 selbst aus einem Werkstoff mit geringerer Verschleißfestigkeit besteht und gemäß einem in Figur 3 dargestellten Ausführungsbeispiel auf ihren der Abstützung 60 zugewandten Seitenflächen 56 jeweils mit einer Beschichtung 62 aus einem Werkstoff mit hoher Verschleißfestigkeit versehen ist. Alternativ oder zusätzlich zur Beschichtung der Seitenflächen 56 der Rolle kann auch die Abstützung 60 mit einer Beschichtung 62 aus einem Werkstoff mit hoher Verschleißfestigkeit versehen sein. Die Beschichtung 62 kann aus einem keramischen Werkstoff, aus einem Hartmetall oder aus einer Kohlenstoffverbindung, insbesondere einer diamantähnlichen Kohlenstoffverbindung bestehen. Alternativ kann die Beschichtung 62 aus einem Metalloxid oder einem Metallnitrid bestehen, beispielsweise Titannitrid. Die Beschichtung 62 kann auch durch Nitrocarburieren hergestellt sein.Alternatively, it is provided that the roller 46 itself consists of a material with lower wear resistance and according to a in FIG. 3 illustrated embodiment on their support 60 facing side surfaces 56 is provided with a coating 62 made of a material with high wear resistance. As an alternative or in addition to the coating of the side surfaces 56 of the roller, the support 60 can also be provided with a coating 62 made of a material with high wear resistance. The coating 62 may consist of a ceramic material, of a hard metal or of a carbon compound, in particular a diamond-like carbon compound. Alternatively, the coating 62 may consist of a metal oxide or a metal nitride, for example titanium nitride. The coating 62 may also be made by nitrocarburizing.

Weiterhin alternativ ist vorgesehen, dass die Rolle 46 selbst aus einem Werkstoff mit geringerer Verschleißfestigkeit besteht und gemäß einem in Figur 4 dargestellten Ausführungsbeispiel in ihren der Abstützung 60 zugewandten Seitenflächen 56 jeweils einen Einsatz 64 aus einem Werkstoff mit hoher Verschleißfestigkeit aufweist. Der Einsatz 64 kann dabei als eine dünne Platte ausgebildet sein, die in eine entsprechende Vertiefung der Seitenfläche 56 der Rolle 46 eingefügt ist. Alternativ oder zusätzlich zur Rolle 46 kann auch in die Abstützung 60 in ihren den Seitenflächen 56 der Rolle 46 zugewandten Bereichen jeweils ein Einsatz 64 aus einem Werkstoff mit hoher Verschleißfestigkeit eingefügt sein. Der Einsatz 64 kann aus einem Werkstoff bestehen, wie er vorstehend zu der Beschichtung 62 angegeben ist.Further alternatively, it is provided that the roller 46 itself consists of a material with lower wear resistance and according to a in FIG. 4 illustrated embodiment in their support 60 facing side surfaces 56 each having an insert 64 made of a material having high wear resistance. The insert 64 may be formed as a thin plate which is inserted into a corresponding recess of the side surface 56 of the roller 46. As an alternative or in addition to the roller 46, an insert 64 made of a material with high wear resistance can also be inserted into the support 60 in its regions facing the side surfaces 56 of the roller 46. The insert 64 can be made of a material as indicated above for the coating 62.

Es kann auch vorgesehen sein, dass die Beschichtung 62 gemäß einem in Figur 5 dargestellten Ausführungsbeispiel direkt auf den Stößel 40, wie in Figur 5 in der linken Hälfte dargestellt, oder das Stützelement 44, wie in Figur 5 in der rechten Hälfte dargestellt, aufgebracht ist, insbesondere auf eine an die Rolle 46 seitlich in Richtung ihrer Drehachse 47 angrenzende Innenwand des Stößels 40 oder Stützelements 44. Es kann dabei vorgesehen sein, dass in der Innenwand des Stößels 40 oder Stützelements 44 wenigstens eine Nut 66 angeordnet ist, in die die Beschichtung 62 eingebracht ist, wobei in der wenigstens einen Nut 66 eine gute Haftung der Beschichtung 62 am Stößel 40 bzw. Stützelement 44 sichergestellt wird. Die Beschichtung 62 kann beispielsweise durch Spritzen als Spritzkeramik aufgebracht werden.It can also be provided that the coating 62 according to a in FIG. 5 illustrated embodiment directly on the plunger 40, as in FIG. 5 shown in the left half, or the support member 44, as in FIG. 5 shown in the right half, is applied, in particular on an adjacent to the roller 46 laterally in the direction of its axis of rotation 47 inner wall of the plunger 40 or support member 44. It can be provided that in the inner wall of the plunger 40 or support member 44 at least one groove 66 is arranged, in which the coating 62 is introduced, wherein in the at least one groove 66 good adhesion of the coating 62 on the plunger 40 and support member 44 is ensured. The coating 62 can be applied for example by spraying as a spray ceramic.

Die Abstützung 60 kann durch einen Teil des Stößels 40 oder des Stützelements 44 gebildet sein oder durch ein separates, in den Stößel 40, wie in Figur 6 in der linken Hälfte dargestellt, oder das Stützelement 44, wie in Figur 6 in der rechten Hälfte dargestellt, eingesetztes insbesondere ringförmiges Bauteil, das dann zwischen der Rolle 46 und dem Stößel 40 bzw. dem Stützelement 44 angeordnet ist. Die Abstützung 60 kann in den Stößel 40 oder das Stützelement 44 eingefügt sein, beispielsweise eingepresst. Im Stößel 40 kann dabei gemäß einem in Figur 6 dargestellten Ausführungsbeispiel eine Aufnahme 68 für die Abstützung 60 ausgebildet sein. Die Aufnahme 68 kann beispielsweise von einem im Innendurchmesser der die Rolle 46 umgebenden Innenwand des Stößels 40 vergrößerten Bereich gebildet sein. Die Wandstärke des Stößels 40 kann dabei im Bereich der Aufnahme 68 gegenüber dem übrigen Stößel 40 bzw. Stützelement 44 verringert sein. Eine gleich ausgebildete Aufnahme 68 für die Abstützung 60 kann alternativ, wie in Figur 6 in der rechten Hälfte dargestellt, auch im Stützelement 44 ausgebildet sein. DieThe support 60 may be formed by a part of the plunger 40 or the support member 44 or by a separate, in the plunger 40, as in FIG. 6 shown in the left half, or the support member 44, as in FIG. 6 shown in the right half, inserted in particular annular component, which is then arranged between the roller 46 and the plunger 40 and the support member 44. The support 60 may be inserted into the plunger 40 or the support member 44, for example, pressed. In the ram 40 can according to a in FIG. 6 illustrated embodiment, a receptacle 68 may be formed for the support 60. The receptacle 68 may be formed, for example, by an area enlarged in the inner diameter of the inner wall of the plunger 40 surrounding the roller 46. The wall thickness of the plunger 40 can be reduced in the region of the receptacle 68 relative to the remaining plunger 40 or support element 44. An identically formed receptacle 68 for the support 60 may alternatively, as in FIG. 6 shown in the right half, be formed in the support member 44. The

Abstützung kann wie vorstehend erläutert ausgebildet sein, also selbst aus einem Werkstoff mit hoher Verschleißfestigkeit bestehen oder eine Beschichtung oder einen Einsatz aus einem Werkstoff mit hoher Verschleißfestigkeit aufweisen.Support can be formed as explained above, ie even consist of a material with high wear resistance or have a coating or insert made of a material with high wear resistance.

Beim Saughub des Pumpenkolbens 20, bei dem sich dieser radial nach innen bewegt, wird der Pumpenarbeitsraum 30 durch den Kraftstoffzulaufkanal 32 bei geöffnetem Einlassventil 34 mit Kraftstoff befüllt, wobei das Auslassventil 38 geschlossen ist. Beim Förderhub des Pumpenkolbens 20, bei dem sich dieser radial nach aussen bewegt, wird durch den Pumpenkolben 20 Kraftstoff unter Hochdruck durch den Kraftstoffablaufkanal 36 bei geöffnetem Auslassventil 38 zum Hochdruckspeicher 110 gefördert, wobei das Einlassventil 34 geschlossen ist.When the suction stroke of the pump piston 20, in which this moves radially inward, the pump chamber 30 is filled by the fuel inlet channel 32 with the inlet valve 34 open with fuel, the exhaust valve 38 is closed. During the delivery stroke of the pump piston 20, in which this moves radially outward, fuel is pumped under high pressure through the fuel discharge passage 36 with the exhaust valve 38 open to the high-pressure accumulator 110 by the pump piston 20, wherein the inlet valve 34 is closed.

Claims (10)

  1. High-pressure pump, in particular for a fuel injection arrangement of an internal combustion engine, with a drive shaft (12) which has at least one cam (16) or eccentric, and with at least one pump element (18) having a pump piston (20) which is driven in a lifting movement by the cam (16) or eccentric of the drive shaft (12), a supporting element (44) and a roller (46) mounted rotatably in the latter being disposed between the pump piston (20) and the cam (16) or eccentric of the drive shaft (12), a support (40; 44; 60) for the roller (46) being disposed next to the roller (46) in the direction of the axis of rotation (47) of the latter, characterized in that the roller (46) and/or the support (40; 44; 60) have/has, at least in the contact region between the roller (46) and the support (40; 44; 60), a surface having high wear resistance, in that the roller (46) is designed to be convexly curved on its side face (56) facing the support (40; 44; 60), in that the convex curvature of the side face (56) of the roller (46) is at least approximately spherical, in that the support (60) is designed to be concavely curved, and in that the radius (R) of curvature of the side face (56) of the roller (46) amounts to about 70 to 100%, preferably about 85 to 95%, of the radius (R1) of curvature of the support (60).
  2. High-pressure pump according to Claim 1, characterized in that the roller (46) and/or the support (40; 44; 60) are/is provided in the contact region with a coating (62) composed of a material having high wear resistance.
  3. High-pressure pump according to Claim 1, characterized in that an insert (64) composed of a material having high wear resistance is introduced in the contact region into the roller (46) and/or into the support (40; 44; 60).
  4. High-pressure pump according to Claim 2 or 3, characterized in that the coating (62) or insert (64) consists of a ceramic material.
  5. High-pressure pump according to Claim 2 or 3, characterized in that the coating (62) or insert (64) consists of a metal oxide or metal nitride.
  6. High-pressure pump according to Claim 5, characterized in that the coating (62) or insert (64) consists of titanium nitride.
  7. High-pressure pump according to Claim 2 or 3, characterized in that the coating (62) or insert (64) consists of a carbon compound, in particular of a diamond-like carbon compound.
  8. High-pressure pump according to Claim 1, characterized in that the roller (46) and/or the support (60) consist/consists of a ceramic material.
  9. High-pressure pump according to one of the preceding claims, characterized in that the support (60) is designed as a ring surrounding the roller (46).
  10. High-pressure pump according to one of the preceding claims, characterized in that the support (60) is introduced into the supporting element (44) or into a tappet (40) receiving the supporting element (44).
EP07726234A 2006-02-20 2007-01-26 High pressure pump in particular for a fuel injection device on an internal combustion engine Active EP2032850B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102006007697 2006-02-20
DE102006041673A DE102006041673A1 (en) 2006-02-20 2006-09-06 High pressure pump especially for fuel injection in IC engine has the cam follower supported axially by hardened low wear surfaces
PCT/EP2007/050762 WO2007096224A1 (en) 2006-02-20 2007-01-26 High pressure pump in particular for a fuel injection device on an internal combustion engine

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EP2032850A1 EP2032850A1 (en) 2009-03-11
EP2032850B1 true EP2032850B1 (en) 2011-03-16

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US (1) US8191459B2 (en)
EP (1) EP2032850B1 (en)
JP (1) JP4768826B2 (en)
KR (1) KR101076170B1 (en)
CN (1) CN101389858B (en)
AT (1) ATE502209T1 (en)
BR (1) BRPI0706556A2 (en)
DE (2) DE102006041673A1 (en)
WO (1) WO2007096224A1 (en)

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EP2032850A1 (en) 2009-03-11
ATE502209T1 (en) 2011-04-15
KR101076170B1 (en) 2011-10-21
DE102006041673A1 (en) 2007-08-23
DE502007006731D1 (en) 2011-04-28
CN101389858A (en) 2009-03-18
US8191459B2 (en) 2012-06-05
WO2007096224A1 (en) 2007-08-30
KR20080093131A (en) 2008-10-20
CN101389858B (en) 2011-04-06
BRPI0706556A2 (en) 2011-03-29
JP4768826B2 (en) 2011-09-07
JP2009527675A (en) 2009-07-30
US20080295807A1 (en) 2008-12-04

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