EP2076669B1 - Tappet assembly for a high-pressure pump and high-pressure pump comprising at least one tappet assembly - Google Patents

Tappet assembly for a high-pressure pump and high-pressure pump comprising at least one tappet assembly Download PDF

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Publication number
EP2076669B1
EP2076669B1 EP07788020A EP07788020A EP2076669B1 EP 2076669 B1 EP2076669 B1 EP 2076669B1 EP 07788020 A EP07788020 A EP 07788020A EP 07788020 A EP07788020 A EP 07788020A EP 2076669 B1 EP2076669 B1 EP 2076669B1
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EP
European Patent Office
Prior art keywords
roller
tappet
axis
rotation
roller shoe
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Not-in-force
Application number
EP07788020A
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German (de)
French (fr)
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EP2076669A1 (en
Inventor
Walter Fuchs
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
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Robert Bosch GmbH
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Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP2076669A1 publication Critical patent/EP2076669A1/en
Application granted granted Critical
Publication of EP2076669B1 publication Critical patent/EP2076669B1/en
Not-in-force legal-status Critical Current
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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
    • F02M59/02—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
    • 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
    • F02M59/04—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 special arrangement of cylinders with respect to piston-driving shaft, e.g. arranged parallel to that shaft or swash-plate type pumps
    • F02M59/06—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 special arrangement of cylinders with respect to piston-driving shaft, e.g. arranged parallel to that shaft or swash-plate type pumps with cylinders arranged radially to driving shaft, e.g. in V or star arrangement
    • 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
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/21—Elements
    • Y10T74/2101—Cams
    • Y10T74/2107—Follower

Definitions

  • the invention relates to a plunger assembly for a high-pressure pump and a high-pressure pump with at least one plunger assembly according to the preamble of claim 1 or of claim 8 or of claim 9.
  • Such a plunger assembly and high pressure pump is through the DE 103 45 061 A1 known.
  • This high-pressure pump has at least one plunger assembly, which in turn has a hollow cylindrical plunger body and a roller shoe inserted therein in the direction of the longitudinal axis of the plunger body, in which a roller is rotatably mounted.
  • the high-pressure pump has at least one pump element, which in turn has a pump piston, by which a pump working space is limited.
  • the plunger assembly is disposed between the pump piston and a rotationally driven drive shaft of the high pressure pump, wherein the drive shaft has at least one cam or eccentric on which the roller runs.
  • the plunger body is guided displaceably in a bore of a housing part of the high-pressure pump.
  • the plunger assembly is used to convert the rotational movement of the drive shaft in a lifting movement of the pump piston, which are to be absorbed by the plunger assembly at least substantially the resulting lateral forces, so that they do not act on the pump piston.
  • the axis of rotation of the roller must be aligned as closely as possible parallel to the axis of rotation of the drive shaft, otherwise it can come to so-called edge supports when the axis of rotation of the roller obliquely to the axis of rotation of the drive shaft and the roller rests only at one end on the cam or eccentric.
  • the lateral forces acting perpendicular to the axis of rotation of the roller and the drive shaft must be securely received by the plunger assembly, so that they do not act on the pump piston.
  • the ram assembly according to the invention with the features according to claim 1 has the advantage that the roller shoe can execute a tilting movement within the plunger body in a defined extent and align, such that the axis of rotation of the roller is parallel to the axis of rotation of the drive shaft and thus edge beams are avoided while on the other hand in the vertical direction with respect to the axes of rotation of the roller and the drive shaft acting lateral forces are absorbed by the small game.
  • the high-pressure pump according to claim 8 In the high-pressure pump with the features of claim 9, a tilting movement of the plunger body in the bore of the pump housing part is made possible, such that the axis of rotation of the roller parallel to the axis of rotation of the Can align drive shaft and thus edge beams are avoided.
  • FIG. 1 a high-pressure pump 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 with III designated section with a plunger assembly of the high-pressure pump in an enlarged view
  • FIG. 4 the ram assembly in a cross section along line IV-IV in FIG. 3 according to a first embodiment
  • FIG. 5 the plunger assembly in cross-section according to a second embodiment
  • FIG. 6 the plunger assembly in a longitudinal section according to a third embodiment
  • FIG. 7 a roller shoe in a view in the direction of arrow VII in FIG. 6
  • FIG. 8 the plunger assembly in a longitudinal section according to a fourth embodiment.
  • FIGS. 1 to 8 a high pressure pump for a fuel injector of an internal combustion engine is shown.
  • the high-pressure pump has a housing 10, which is designed in several parts and in which a rotationally driven drive shaft 12 is arranged.
  • the drive shaft 12 is rotatably supported in the housing 10 via two spaced apart in the direction of the axis of rotation 13 of the drive shaft 12 bearings.
  • the bearings can be arranged in different parts 14,16 of the housing 10.
  • the drive shaft 12 has at least one cam 26 or eccentric, wherein the cam 26 may also be formed as a multiple cam.
  • the high-pressure pump has at least one or more in each case a housing 18 arranged pump elements 32 each having a pump piston 34 which is indirectly driven by the cam 26 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.
  • the pump piston 34 is guided in a cylinder bore 36 in the housing part 18 and slidably limited with its end facing away from the drive shaft 12 in the cylinder bore 36 a pump chamber 38.
  • the pump chamber 38 has a running in the housing 10 fuel inlet channel 40 is connected to a fuel inlet, for example a delivery pump.
  • the pump working chamber 38 also has a connection extending in the housing part 18 fuel drain passage 44 with an outlet, which is connected for example with a high-pressure accumulator 110.
  • a high-pressure accumulator 110 With the high-pressure accumulator 110 one or more preferably arranged on the cylinders of the internal combustion engine injectors 120 are connected by the fuel in the cylinder Internal combustion engine is injected.
  • an outlet valve 46 which opens out of the pump working chamber 38 is arranged, which likewise has a spring-loaded valve member 47.
  • the pump element 32 is associated with a plunger assembly 50, via which the pump piston 34 is supported on the cam 26 of the drive shaft 12.
  • the plunger assembly 50 includes a hollow cylindrical plunger body 52 which is slidably guided in a bore 54 of a portion 14 of the housing 10 of the high pressure pump.
  • the pump piston 34 has a smaller diameter than the plunger body 52 and projects with its end facing away from the pump working chamber 38 from the cylinder bore 36 and into the plunger body 52 inside. At its end facing away from the pump working chamber 38, the pump piston 34 may have a piston foot 35 which is larger in diameter than its remaining area.
  • a roller shoe 56 is inserted in the plunger body 52 of the drive shaft 12 side facing in the direction of the longitudinal axis 53 of the plunger body 52.
  • a cylindrical roller 60 is rotatably mounted in a cylinder-section-shaped receptacle 58 on the cam 26 of the drive shaft 12 facing side of the roller shoe 56.
  • the axis of rotation of the roller 60 is designated 61.
  • the roller shoe 56 comes into abutment in the plunger body 52 in the direction of the longitudinal axis 53 against a stop 62 which, for example, is formed by an annular web projecting radially inwardly from the plunger body 52.
  • the roller shoe 56 has as in the FIGS. 4 and 5 1 or preferably a plurality of openings 57, which allow the passage of fuel during the lifting movement of the plunger assembly 50.
  • the plunger assembly 50 and pump piston 34 are urged by a biased spring 64 toward the cam 26 of the drive shaft 12.
  • the spring 64 is formed as the pump piston 34 surrounding and projecting into the plunger body 52 helical compression spring.
  • the spring 64 is supported on the one hand on the pump housing part 18 and on the other hand on a spring plate 65 from.
  • the spring plate 65 is connected to the pump piston 34 and rests on the roller shoe 56 facing away from the side of the annular web 62. The spring 64 thus acts on the spring plate 65 both on the pump piston 34 and on the plunger body 52nd
  • the roller shoe 56 is arranged in the plunger body 52 such that the roller shoe 56 in the direction of the axis of rotation 61 of the roller 60 has a greater play in the plunger body 52 than in directions perpendicular to the axis of rotation 61 of the roller 60th
  • the roller shoe 56 is in particular pressed into the plunger body 52, wherein the pressing takes place in directions perpendicular to the axis of rotation 61 of the roller 60, so that in these directions no play between roller shoe 56 and plunger body 52 is present.
  • the roller shoe 56 is thus in the plane of the FIG. 2 free of play in the ram body 52 arranged.
  • the roller shoe 56 In the direction of the axis of rotation 61 of the roller 60 is between the roller shoe 56 and the plunger body 52 game available.
  • the roller shoe 56 is in the plane of the FIG. 1 arranged with play in the ram body 52.
  • the roller shoe 56 can thus perform a limited tilting movement in the tappet body 52 about an imaginary tilting axis perpendicular to the axis of rotation 61 of the roller 60 and perpendicular to the longitudinal axis 53 of the tappet body 52 this intersecting, whereby an alignment of the axis of rotation 61 of the roller 60 at least approximately parallel to Rotary axis 13 of the drive shaft 12 is possible.
  • the tilting movement of the roller shoe 56 is with the arrows K in the Figures 3 . 6 and 8th indicated.
  • the plunger body 52 at least before the pressing of the roller shoe 56 has a constant Tnnen barnmesser.
  • the above-described tilting movement of the roller shoe 56 in the plunger body 52 can according to a in FIG. 4 shown in that the roller shoe 56 viewed in cross section perpendicular to the longitudinal axis 53 of the plunger body 52 in directions perpendicular to the axis of rotation 61 of the roller 60 has a larger diameter D than in the direction of the axis of rotation 61 of the roller 60, where the diameter d is designated.
  • the areas of the roller shoe 56 with the diameter D extend on both sides of a longitudinal axis 53 of the plunger body 52 intersecting center plane 55 of the roller shoe 56 and the areas with the diameter d on both sides of the axis of rotation 61 of the roller 60 containing center plane of the roller shoe 56.
  • the transitions between the regions of large diameter D and small diameter d may be rounded, for example approximately sinusoidal.
  • the areas of large diameter D and small diameter d are each formed cylindrical with constant diameter D or d. In FIG. 4 the difference of the diameters D and d is greatly exaggerated for reasons of clarity.
  • the difference between the diameters D and d may be, for example, depending on the application about 10 to 100 microns.
  • the roller shoe 56 is made of, for example, hardened steel, and the portions having the different diameters D and d can be formed thereon before or after the hardening treatment of the roller shoe 56, for example, by grinding the roller shoe 56.
  • FIG. 5 is the roller shoe 56 shown according to a second embodiment, in which this in Cross-section viewed perpendicular to the longitudinal axis 53 of the plunger body 52 is oval, for example, elliptical.
  • the roller shoe 56 In directions perpendicular to the axis of rotation 61 of the roller 60, the roller shoe 56 has a large diameter D and in the direction of the axis of rotation 61 of the roller 60 has a small diameter d. Between the diameters D and d, the diameter of the roller shoe 56 changes continuously.
  • the oval cross-sectional shape of the roller shoe 56 can be generated even before its hardening treatment or thereafter, for example, by grinding the roller shoe 56 having a circular cross-section in the initial state.
  • the difference between the diameters D and d may be, for example, depending on the application about 10 to 100 microns.
  • the plunger body 52 is formed relatively thin-walled, which then changes during pressing of the roller shoe 56 formed as described above in the plunger body 52 whose outer shape according to the shape of the roller shoe 56.
  • the plunger body 52 then has after pressing the roller shoe 56 in directions perpendicular to the axis of rotation 61 of the roller 60 has a larger outer diameter D 'as in the direction of the axis of rotation 61 of the roller 60, where the outer diameter is denoted by d'.
  • This design of the plunger body 52 allows that the plunger body 52 in the bore 54 of the pump housing part 14 can perform a limited tilting movement to enable the alignment of the axis of rotation 61 of the roller 60 at least approximately parallel to the axis of rotation 13 of the drive shaft 12.
  • the plunger body 52 is guided in the bore 54 in directions perpendicular to the axis of rotation 61 of the roller 60 with little play and arranged in the direction of the axis of rotation 61 of the roller 60 with a larger clearance.
  • the difference of the games of the plunger body 52 in directions perpendicular to the axis of rotation 61 and in the direction of the axis of rotation 61 of the roller 60 in the bore 54 may each for example, be about 10 to 100 microns after use.
  • Embodiments of the plunger assembly 50 are shown in which the tilting movement of the roller shoe 56 in the plunger body 52 is further facilitated.
  • the roller shoe 56 on its stop 62 facing the top of a survey 68, but only on both sides of the longitudinal axis 53 of the plunger body 52 and extending perpendicular to the axis of rotation 61 of the roller 60 extending center plane 55 of the roller shoe 56, while the in Direction of the axis of rotation 61 of the roller 60 at a distance from the central plane 55 arranged edge regions 70 of the top of the roller shoe 56 in the direction of the longitudinal axis 53 of the plunger body 52 are lower.
  • the required removal of material in the edge regions 70 of the roller shoe 56 can be done for example by milling or grinding.
  • the roller shoe 56 rests on its upper side only with its collection 68 on the stop 62, while the edge regions 70 are arranged at a distance from the stop 62.
  • the roller shoe 56 in the tappet body 52 can execute the tilting movement already explained above without this being hindered by the stop 62.
  • FIG. 8 is the roller shoe 56 shown according to a fourth embodiment, in which the roller shoe 56 has on its stop 62 facing the top of a convex curvature through which an elevation 72 is formed on this top of the roller shoe 56, whose highest line in the median plane 55 of the roller shoe 56 runs.
  • the curvature of the top of the roller shoe 56 is only in sections parallel to the axis of rotation 61 of the roller 60 present, while in sections perpendicular to the axis of rotation 61 of the roller 60 through the roller shoe 56 at the top thereof produce straight cutting lines.
  • the curvature of the upper side of the roller shoe 56 can be produced, for example, by grinding a contour having a relatively large radius R whose center M lies on the extension of the longitudinal axis 53 of the tappet body 52. Due to the curvature of the upper side of the roller shoe 56 results in a only linear contact of the roller shoe 56 with its top on stop 62, so that the roller shoe 56 in the plunger body 52 can perform the tilting movement already explained above without this being hindered by the stop 62. In addition, for the piston foot 35 of the pump piston 34 also results in a linear contact with the upper side of the roller shoe 56, whereby the tilting movement of the roller shoe 56 is facilitated with respect to the pump piston 34.
  • the pump piston 34 is in FIG. 8 not shown for reasons of clarity.
  • the roller shoe 56 is rigidly arranged in the plunger body 52, for example, is pressed or that the roller shoe 56 is integral with the plunger body 52 and no tilting movement of the roller shoe 56 in the plunger body 52 is possible.
  • the plunger body 52 is arranged in the bore 54 of the pump housing part 14 so that the plunger body 52 is guided in the bore 54 in directions perpendicular to the axis of rotation 61 of the roller 60 with less play than in the direction of the axis of rotation 61 of the roller 60th Die Bohrung 54 in the pump housing part 14 has a constant diameter.
  • the plunger body 52 may be formed as described above for the roller shoe 56 and thus in directions perpendicular to the axis of rotation 61 of the roller 60 has a larger outer diameter D 'as in the direction of the axis of rotation 61 of the roller 60, where the outer diameter d 'is.
  • the plunger body 52 can cross-section areas with large outer diameter D 'and areas with smaller outer diameter d' analogous to the formation of the roller shoe 56 according to FIG. 4 or the plunger body 52 may be oval in cross-section similar to the formation of the roller shoe 56 according to FIG.
  • the difference of the games of the plunger body 52 in directions perpendicular to the axis of rotation 61 and in the direction of the axis of rotation 61 of the roller 60 in the bore 54 may be, for example, about 10 to 100 microns depending on the application.
  • the plunger assembly 50 is held on the roller 60 in contact with the cam 26 of the drive shaft 12.
  • the plunger assembly 50 is driven in a lifting movement.
  • the suction stroke of the pump piston 34 in which this moves radially inward, the pump chamber 38 is filled by the fuel inlet passage 40 with the inlet valve 42 open with fuel, the exhaust valve 46 is closed.
  • the delivery stroke of the pump piston 34 in which this moves radially outward, fuel is pumped under high pressure through the fuel discharge passage 44 with the outlet valve 46 open to the high-pressure accumulator 110 by the pump piston 34, wherein the inlet valve 42 is closed.

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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)
  • Infusion, Injection, And Reservoir Apparatuses (AREA)

Abstract

The invention relates to a tappet assembly for a high-pressure pump, especially for the prose of fuel supply, and to a high-pressure pump including such a tappet assembly. The tappet assembly has a hollow cylindrical tappet base into which a roller support is inserted in the direction of the longitudinal axis of the tappet base. A roller is rotatably received in the roller support. The roller support is arranged at a right angle to the rotational axis of the roller with little or no play in the tappet base and in the direction of the rotational axis of the roller with larger play than at a right angle to the rotational axis of the roller in the tappet base. As a result, the roller support can perform a limited tilting motion in the tappet base, thereby allowing the rotational axis of the roller to be aligned in relation to the rotational axis of a driving shaft driving the tappet assembly in a lifting motion and avoiding edge loading of the roller on a cam or avoiding the need for eccentrics on the driving shaft.

Description

Stand der TechnikState of the art

Die Erfindung geht aus von einer Stößelbaugruppe für eine Hochdruckpumpe und einer Hochdruckpumpe mit wenigstens einer Stößelbaugruppe nach der Gattung des Anspruchs 1 bzw. des Anspruchs 8 bzw. des Anspruchs 9.The invention relates to a plunger assembly for a high-pressure pump and a high-pressure pump with at least one plunger assembly according to the preamble of claim 1 or of claim 8 or of claim 9.

Eine solche Stößelbaugruppe und Hochdruckpumpe ist durch die DE 103 45 061 A1 bekannt. Diese Hochdruckpumpe weist wenigstens eine Stößelbaugruppe auf, die wiederum einen hohlzylindrischen Stößelkörper und einen in diesen in Richtung der Längsachse des Stößelkörpers eingesetzten Rollenschuh aufweist, in dem eine Rolle drehbar gelagert ist. Die Hochdruckpumpe weist wenigstens ein Pumpenelement auf, das wiederum einen Pumpenkolben aufweist, durch den ein Pumpenarbeitsraum begrenzt wird. Die Stößelbaugruppe ist zwischen dem Pumpenkolben und einer rotierend angetriebenen Antriebswelle der Hochdruckpumpe angeordnet, wobei die Antriebswelle wenigstens einen Nocken oder Exzenter aufweist, auf dem die Rolle abläuft. Der Stößelkörper ist in einer Bohrung eines Gehäuseteils der Hochdruckpumpe verschiebbar geführt. Die Stößelbaugruppe dient dazu die Drehbewegung der Antriebswelle in eine Hubbewegung des Pumpenkolbens umzuwandeln, wobei durch die Stößelbaugruppe zumindest im wesentlichen die sich hierbei ergebenden seitlichen Kräfte aufgenommen werden sollen, so dass diese nicht auf den Pumpenkolben wirken. Die Drehachse der Rolle muss möglichst genau parallel zur Drehachse der Antriebswelle ausgerichtet sein, da es sonst zu sogenannten Kantenträgern kommen kann wenn die Drehachse der Rolle schräg zur Drehachse der Antriebswelle verläuft und die Rolle nur an einem Ende am Nocken oder Exzenter anliegt. Andererseits müssen durch die Stößelbaugruppe vor allem die senkrecht zur Drehachse der Rolle und der Antriebswelle wirkenden seitlichen Kräfte sicher aufgenommen werden, damit diese nicht auf den Pumpenkolben wirken. Um den exakt parallelen Verlauf der Drehachsen der Rolle und der Antriebswelle zu erreichen ist es bei der bekannten Hochdruckpumpe erforderlich, dass sämtliche Bauteile mit sehr geringen Fertigungstoleranzen ausgeführt werden, was die Fertigung entsprechend verteuert.Such a plunger assembly and high pressure pump is through the DE 103 45 061 A1 known. This high-pressure pump has at least one plunger assembly, which in turn has a hollow cylindrical plunger body and a roller shoe inserted therein in the direction of the longitudinal axis of the plunger body, in which a roller is rotatably mounted. The high-pressure pump has at least one pump element, which in turn has a pump piston, by which a pump working space is limited. The plunger assembly is disposed between the pump piston and a rotationally driven drive shaft of the high pressure pump, wherein the drive shaft has at least one cam or eccentric on which the roller runs. The plunger body is guided displaceably in a bore of a housing part of the high-pressure pump. The plunger assembly is used to convert the rotational movement of the drive shaft in a lifting movement of the pump piston, which are to be absorbed by the plunger assembly at least substantially the resulting lateral forces, so that they do not act on the pump piston. The axis of rotation of the roller must be aligned as closely as possible parallel to the axis of rotation of the drive shaft, otherwise it can come to so-called edge supports when the axis of rotation of the roller obliquely to the axis of rotation of the drive shaft and the roller rests only at one end on the cam or eccentric. On the other hand, the lateral forces acting perpendicular to the axis of rotation of the roller and the drive shaft must be securely received by the plunger assembly, so that they do not act on the pump piston. In order to achieve the exactly parallel course of the axes of rotation of the roller and the drive shaft, it is necessary in the known high-pressure pump that all components are designed with very low manufacturing tolerances, which makes the production more expensive.

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

Die erfindungsgemäße Stößelbaugruppe mit den Merkmalen gemäß Anspruch 1 hat demgegenüber den Vorteil, dass der Rollenschuh innerhalb des Stößelkörpers in definiertem Ausmass eine Kippbewegung ausführen und sich ausrichten kann, derart, dass die Drehachse der Rolle parallel zur Drehachse der Antriebswelle verläuft und somit Kantenträger vermieden sind, während andererseits in senkrechter Richtung bezüglich der Drehachsen der Rolle und der Antriebswelle wirkenden seitlichen Kräfte durch das geringe Spiel aufgenommen werden. Entsprechende Vorteile ergeben sich für die Hochdruckpumpe gemäß Anspruch 8. Bei der Hochdruckpumpe mit den Merkmalen gemäß Anspruch 9 ist eine Kippbewegung des Stößelkörpers in der Bohrung des Pumpengehäuseteils ermöglicht, derart, dass sich die Drehachse der Rolle parallel zur Drehachse der Antriebswelle ausrichten kann und somit Kantenträger vermieden sind.The ram assembly according to the invention with the features according to claim 1 has the advantage that the roller shoe can execute a tilting movement within the plunger body in a defined extent and align, such that the axis of rotation of the roller is parallel to the axis of rotation of the drive shaft and thus edge beams are avoided while on the other hand in the vertical direction with respect to the axes of rotation of the roller and the drive shaft acting lateral forces are absorbed by the small game. Corresponding advantages arise for the high-pressure pump according to claim 8. In the high-pressure pump with the features of claim 9, a tilting movement of the plunger body in the bore of the pump housing part is made possible, such that the axis of rotation of the roller parallel to the axis of rotation of the Can align drive shaft and thus edge beams are avoided.

In den abhängigen Ansprüchen sind vorteilhafte Ausgestaltungen und Weiterbildungen der erfindungsgemäßen Stößelbaugruppe bzw. Hochdruckpumpe angegeben. Durch die Ausbildungen gemäß den Ansprüchen 2 und 3 sowie 10 und 11 wird auf einfache Weise das erforderliche größere Spiel in Richtung der Drehachsen der Rolle bzw. der Antriebswelle und das erforderliche geringe Spiel senkrecht zu den Drehachsen der Rolle bzw. Antriebswelle erreicht.In the dependent claims advantageous refinements and developments of the plunger assembly according to the invention or high pressure pump are given. Due to the embodiments according to claims 2 and 3 and 10 and 11, the required greater clearance in the direction of the axes of rotation of the roller or the drive shaft and the required low clearance perpendicular to the axes of rotation of the roller or drive shaft is achieved in a simple manner.

Zeichnungdrawing

Mehrere Ausführungsbeispiele der Erfindung sind in der Zeichnung dargestellt und in der nachfolgenden Beschreibung näher erläutert. Es zeigen Figur 1 eine Hochdruckpumpe 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 mit einer Stößelbaugruppe der Hochdruckpumpe in vergrößerter Darstellung, Figur 4 die Stößelbaugruppe in einem Querschnitt entlang Linie IV-IV in Figur 3 gemäß einem ersten Ausführungsbeispiel, Figur 5 die Stößelbaugruppe im Querschnitt gemäß einem zweiten Ausführungsbeispiel, Figur 6 die Stößelbaugruppe in einem Längsschnitt gemäß einem dritten Ausführungsbeispiel, Figur 7 einen Rollenschuh in einer Ansicht in Pfeilrichtung VII in Figur 6, und Figur 8 die Stößelbaugruppe in einem Längsschnitt gemäß einem vierten Ausführungsbeispiel.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 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 with III designated section with a plunger assembly of the high-pressure pump in an enlarged view, FIG. 4 the ram assembly in a cross section along line IV-IV in FIG. 3 according to a first embodiment, FIG. 5 the plunger assembly in cross-section according to a second embodiment, FIG. 6 the plunger assembly in a longitudinal section according to a third embodiment, FIG. 7 a roller shoe in a view in the direction of arrow VII in FIG. 6 , and FIG. 8 the plunger assembly in a longitudinal section according to a fourth embodiment.

Beschreibung der AusführungsbeispieleDescription of the embodiments

In den Figuren 1 bis 8 ist eine Hochdruckpumpe für eine Kraftstoffeinspritzeinrichtung einer Brennkraftmaschine dargestellt. Die Hochdruckpumpe weist ein Gehäuse 10 auf, das mehrteilig ausgebildet ist und in dem eine rotierend angetriebene Antriebswelle 12 angeordnet ist. Die Antriebswelle 12 ist im Gehäuse 10 über zwei in Richtung der Drehachse 13 der Antriebswelle 12 voneinander beabstandete Lagerstellen drehbar gelagert. Die Lagerstellen können in verschiedenen Teilen 14,16 des Gehäuses 10 angeordnet sein.In the FIGS. 1 to 8 a high pressure pump for a fuel injector of an internal combustion engine is shown. The high-pressure pump has a housing 10, which is designed in several parts and in which a rotationally driven drive shaft 12 is arranged. The drive shaft 12 is rotatably supported in the housing 10 via two spaced apart in the direction of the axis of rotation 13 of the drive shaft 12 bearings. The bearings can be arranged in different parts 14,16 of the housing 10.

In einem zwischen den beiden Lagerstellen liegenden Bereich weist die Antriebswelle 12 wenigstens einen Nocken 26 oder Exzenter auf, wobei der Nocken 26 auch als Mehrfachnocken ausgebildet sein kann. Die Hochdruckpumpe weist wenigstens ein oder mehrere in jeweils einem Gehäusetail 18 angeordnet Pumpenelemente 32 mit jeweils einem Pumpenkolben 34 auf, der durch den Nocken 26 der Antriebswelle 12 mittelbar in einer Hubbewegung in zumindest annähernd radialer Richtung zur Drehachse 13 der Antriebsewelle 12 angetrieben wird. Der Pumpenkolben 34 ist in einer Zylinderbohrung 36 im Gehäuseteil 18 dicht verschiebbar geführt und begrenzt mit seiner der Antriebswelle 12 abgewandten Stirnseite in der Zylinderbohrung 36 einen Pumpenarbeitsraum 38. Der Pumpenarbeitsraum 38 weist über einen im Gehäuse 10 verlaufenden Kraftstoffzulaufkanal 40 eine Verbindung mit einem Kraftstoffzulauf, beispielsweise einer Förderpumpe auf. An der Mündung des Kraftstoffzulaufkanals 40 in den Pumpenarbeitsraum 38 ist ein in den Pumpenarbeitsraum 38 öffnendes Einlassventil 42 angeordnet, das ein federbelastetes Ventilglied 43 aufweist. Der Pumpenarbeitsraum 38 weist ausserdem über einen im Gehäuseteil 18 verlaufenden Kraftstoffablaufkanal 44 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 44 in den Pumpenarbeitsraum 38 ist ein aus dem Pumpenarbeitsraum 38 öffnendes Auslassventil 46 angeordnet, das ebenfalls ein federbelastetes Ventilglied 47 aufweist.In a region lying between the two bearing points, the drive shaft 12 has at least one cam 26 or eccentric, wherein the cam 26 may also be formed as a multiple cam. The high-pressure pump has at least one or more in each case a housing 18 arranged pump elements 32 each having a pump piston 34 which is indirectly driven by the cam 26 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. The pump piston 34 is guided in a cylinder bore 36 in the housing part 18 and slidably limited with its end facing away from the drive shaft 12 in the cylinder bore 36 a pump chamber 38. The pump chamber 38 has a running in the housing 10 fuel inlet channel 40 is connected to a fuel inlet, for example a delivery pump. At the mouth of the fuel inlet channel 40 into the pump working chamber 38 an opening into the pump working chamber 38 inlet valve 42 is arranged, which has a spring-loaded valve member 43. The pump working chamber 38 also has a connection extending in the housing part 18 fuel drain passage 44 with an outlet, which is connected for example with a high-pressure accumulator 110. With the high-pressure accumulator 110 one or more preferably arranged on the cylinders of the internal combustion engine injectors 120 are connected by the fuel in the cylinder Internal combustion engine is injected. At the mouth of the fuel discharge channel 44 into the pump working chamber 38, an outlet valve 46 which opens out of the pump working chamber 38 is arranged, which likewise has a spring-loaded valve member 47.

Dem Pumpenelement 32 ist eine Stößelbaugruppe 50 zugeordnet, über die sich der Pumpenkolben 34 am Nocken 26 der Antriebswelle 12 abtützt. Die Stößelbaugruppe 50 umfasst einen hohlzylindrischen Stößelkörper 52, der in einer Bohrung 54 eines Teils 14 des Gehäuses 10 der Hochdruckpumpe verschiebbar geführt ist. Der Pumpenkolben 34 weist einen kleineren Durchmesser auf als der Stößelkörper 52 und ragt mit seinem dem Pumpenarbeitsraum 38 abgewandten Endbereich aus der Zylinderbohrung 36 heraus und in den Stößelkörper 52 hinein. An seinem dem Pumpenarbeitsraum 38 abgewandten Ende kann der Pumpenkolben 34 einen im Durchmesser gegenüber seinem übrigen Bereich vergrößerten Kolbenfuß 35 aufweisen.The pump element 32 is associated with a plunger assembly 50, via which the pump piston 34 is supported on the cam 26 of the drive shaft 12. The plunger assembly 50 includes a hollow cylindrical plunger body 52 which is slidably guided in a bore 54 of a portion 14 of the housing 10 of the high pressure pump. The pump piston 34 has a smaller diameter than the plunger body 52 and projects with its end facing away from the pump working chamber 38 from the cylinder bore 36 and into the plunger body 52 inside. At its end facing away from the pump working chamber 38, the pump piston 34 may have a piston foot 35 which is larger in diameter than its remaining area.

In den Stößelkörper 52 ist von dessen der Antriebswelle 12 zugewandter Seite her in Richtung der Längsachse 53 des Stößelkörpers 52 ein Rollenschuh 56 eingefügt. Im Rollenschuh 56 ist in einer zylinderabschnittförmigen Aufnahme 58 auf der dem Nocken 26 der Antriebswelle 12 zugewandten Seite des Rollenschuhs 56 eine zylindrische Rolle 60 drehbar gelagert. Die Drehachse der Rolle 60 ist mit 61 bezeichnet. Der Rollenschuh 56 kommt im Stößelkörper 52 in Richtung der Längsachse 53 an einem Anschlag 62 zur Anlage, der beispielsweise durch einen vom Stößelkörper 52 radial nach innen hervorstehenden Ringsteg gebildet ist. Der Rollenschuh 56 weist wie in den Figuren 4 und 5 dargestellt eine oder vorzugsweise mehrere Öffnungen 57 auf, die bei der Hubbewegung der Stößelbaugruppe 50 einen Durchtritt von Kraftstoff ermöglichen.In the plunger body 52 of the drive shaft 12 side facing in the direction of the longitudinal axis 53 of the plunger body 52, a roller shoe 56 is inserted. In the roller shoe 56, a cylindrical roller 60 is rotatably mounted in a cylinder-section-shaped receptacle 58 on the cam 26 of the drive shaft 12 facing side of the roller shoe 56. The axis of rotation of the roller 60 is designated 61. The roller shoe 56 comes into abutment in the plunger body 52 in the direction of the longitudinal axis 53 against a stop 62 which, for example, is formed by an annular web projecting radially inwardly from the plunger body 52. The roller shoe 56 has as in the FIGS. 4 and 5 1 or preferably a plurality of openings 57, which allow the passage of fuel during the lifting movement of the plunger assembly 50.

Die Stößelbaugruppe 50 und der Pumpenkolben 34 werden durch eine vorgespannte Feder 64 zum Nocken 26 der Antriebswelle 12 hin gedrückt. Die Feder 64 ist als den Pumpenkolben 34 umgebende und in den Stößelkörper 52 hineinragende Schraubendruckfeder ausgebildet. Die Feder 64 stützt sich einerseits am Pumpengehäuseteil 18 und andererseits an einem Federteller 65 ab. Der Federteller 65 ist mit dem Pumpenkolben 34 verbunden und liegt auf der dem Rollenschuh 56 abgewandten Seite des Ringstegs 62 an. Die Feder 64 wirkt somit über den Federteller 65 sowohl auf den Pumpenkolben 34 als auch auf den Stößelkörper 52.The plunger assembly 50 and pump piston 34 are urged by a biased spring 64 toward the cam 26 of the drive shaft 12. The spring 64 is formed as the pump piston 34 surrounding and projecting into the plunger body 52 helical compression spring. The spring 64 is supported on the one hand on the pump housing part 18 and on the other hand on a spring plate 65 from. The spring plate 65 is connected to the pump piston 34 and rests on the roller shoe 56 facing away from the side of the annular web 62. The spring 64 thus acts on the spring plate 65 both on the pump piston 34 and on the plunger body 52nd

Gemäß einem ersten Ausführungsbeispiel der Erfindung ist vorgesehen, das der Rollenschuh 56 im Stößelkörper 52 derart angeordnet ist, dass der Rollenschuh 56 in Richtung der Drehachse 61 der Rolle 60 ein größeres Spiel im Stößelkörper 52 aufweist als in Richtungen senkrecht zur Drehachse 61 der Rolle 60. Der Rollenschuh 56 ist in den Stößelkörper 52 insbesondere eingepresst, wobei die Pressung in Richtungen senkrecht zur Drehachse 61 der Rolle 60 erfolgt, so dass in diesen Richtungen kein Spiel zwischen Rollenschuh 56 und Stößelkörper 52 vorhanden ist. Der Rollenschuh 56 ist somit in der Zeichenebene der Figur 2 spielfrei im Stößelkörper 52 angeordnet. In Richtung der Drehachse 61 der Rolle 60 ist zwischen dem Rollenschuh 56 und dem Stößelkörper 52 Spiel vorhanden. Der Rollenschuh 56 ist in der Zeichenebene der Figur 1 mit Spiel im Stößelkörper 52 angeordnet. Der Rollenschuh 56 kann somit im Stößelkörper 52 eine begrenzte Kippbewegung ausführen um eine imaginäre Kippachse, die senkrecht zur Drehachse 61 der Rolle 60 und senkrecht zur Längsachse 53 des Stößelkörpers 52 diese schneidend verläuft, wodurch eine Ausrichtung der Drehachse 61 der Rolle 60 zumindest annähernd parallel zur Drehachse 13 der Antriebswelle 12 ermöglicht ist. Die Kippbewegung des Rollenschuhs 56 ist mit den Pfeilen K in den Figuren 3,6 und 8 angedeutet. Vorzugsweise weist der Stößelkörper 52 zumindest vor dem Einpressen des Rollenschuhs 56 einen konstanten Tnnendurchmesser auf. Die vorstehend erläuterte Kippbewegung des Rollenschuhs 56 im Stößelkörper 52 kann gemäß einem in Figur 4 dargestellten ersten Ausführungsbeispiel dadurch erreicht werden, dass der Rollenschuh 56 im Querschnitt senkrecht zur Längsachse 53 des Stößelkörpers 52 betrachtet in Richtungen senkrecht zur Drehachse 61 der Rolle 60 einen größeren Durchmesser D aufweist als in Richtung der Drehachse 61 der Rolle 60, wo der Durchmesser mit d bezeichnet ist. Die Bereiche des Rollenschuhs 56 mit dem Durchmesser D erstrecken sich dabei beidseits einer die Längsachse 53 des Stößelkörpers 52 schneidenden Mittelebene 55 des Rollenschuhs 56 und die Bereiche mit dem Durchmesser d beidseits einer die Drehachse 61 der Rolle 60 enthaltenden Mittelebene des Rollenschuhs 56. Die Übergänge zwischen den Bereichen mit großem Durchmesser D und kleinem Durchmesser d können gerundet sein, beispielsweise etwa sinusförmig. Die Bereiche mit großem Durchmesser D und mit kleinem Durchmesser d sind jeweils zylindrisch ausgebildet mit konstantem Durchmesser D bzw. d. In Figur 4 ist die Differenz der Durchmesser D und d aus Anschaulichkeitsgründen stark übertrieben dargestellt. Die Differenz zwischen den Durchmessern D und d kann beispielsweise je nach Anwendungsfall etwa 10 bis 100 µm betragen. Der Rollenschuh 56 ist beispielsweise aus gehärtetem Stahl hergestellt, wobei die Bereiche mit den unterschiedlichen Durchmessern D und d vor oder nach der Härtebehandlung des Rollenschuhs 56 an diesem ausgebildet werden können, beispielsweise mittels einer Schleifbearbeitung des Rollenschuhs 56.According to a first embodiment of the invention, it is provided that the roller shoe 56 is arranged in the plunger body 52 such that the roller shoe 56 in the direction of the axis of rotation 61 of the roller 60 has a greater play in the plunger body 52 than in directions perpendicular to the axis of rotation 61 of the roller 60th The roller shoe 56 is in particular pressed into the plunger body 52, wherein the pressing takes place in directions perpendicular to the axis of rotation 61 of the roller 60, so that in these directions no play between roller shoe 56 and plunger body 52 is present. The roller shoe 56 is thus in the plane of the FIG. 2 free of play in the ram body 52 arranged. In the direction of the axis of rotation 61 of the roller 60 is between the roller shoe 56 and the plunger body 52 game available. The roller shoe 56 is in the plane of the FIG. 1 arranged with play in the ram body 52. The roller shoe 56 can thus perform a limited tilting movement in the tappet body 52 about an imaginary tilting axis perpendicular to the axis of rotation 61 of the roller 60 and perpendicular to the longitudinal axis 53 of the tappet body 52 this intersecting, whereby an alignment of the axis of rotation 61 of the roller 60 at least approximately parallel to Rotary axis 13 of the drive shaft 12 is possible. The tilting movement of the roller shoe 56 is with the arrows K in the Figures 3 . 6 and 8th indicated. Preferably, the plunger body 52 at least before the pressing of the roller shoe 56 has a constant Tnnendurchmesser. The above-described tilting movement of the roller shoe 56 in the plunger body 52 can according to a in FIG. 4 shown in that the roller shoe 56 viewed in cross section perpendicular to the longitudinal axis 53 of the plunger body 52 in directions perpendicular to the axis of rotation 61 of the roller 60 has a larger diameter D than in the direction of the axis of rotation 61 of the roller 60, where the diameter d is designated. The areas of the roller shoe 56 with the diameter D extend on both sides of a longitudinal axis 53 of the plunger body 52 intersecting center plane 55 of the roller shoe 56 and the areas with the diameter d on both sides of the axis of rotation 61 of the roller 60 containing center plane of the roller shoe 56. The transitions between the regions of large diameter D and small diameter d may be rounded, for example approximately sinusoidal. The areas of large diameter D and small diameter d are each formed cylindrical with constant diameter D or d. In FIG. 4 the difference of the diameters D and d is greatly exaggerated for reasons of clarity. The difference between the diameters D and d may be, for example, depending on the application about 10 to 100 microns. The roller shoe 56 is made of, for example, hardened steel, and the portions having the different diameters D and d can be formed thereon before or after the hardening treatment of the roller shoe 56, for example, by grinding the roller shoe 56.

In Figur 5 ist der Rollenschuh 56 gemäß einem zweiten Ausführungsbeispiel dargestellt, bei dem dieser im Querschnitt senkrecht zur Längsachse 53 des Stößelkörpers 52 betrachtet oval ausgebildet ist, beispielsweise elliptisch. In Richtungen senkrecht zur Drehachse 61 der Rolle 60 weist der Rollenschuh 56 einen großen Durchmesser D und in Richtung der Drehachse 61 der Rolle 60 einen kleinen Durchmesser d auf. Zwischen den Durchmessern D und d ändert sich der Durchmesser des Rollenschuhs 56 kontinuierlich. Die ovale Querschnittsform des Rollenschuhs 56 kann bereits vor dessen Härtebehandlung oder danach beispielsweise durch Schleifen des im Ausgangszustand einen kreisrunden Querschnitt aufweisenden Rollenschuhs 56 erzeugt werden. Die Differenz zwischen den Durchmessern D und d kann beispielsweise je nach Anwendungsfall etwa 10 bis 100 µm betragen.In FIG. 5 is the roller shoe 56 shown according to a second embodiment, in which this in Cross-section viewed perpendicular to the longitudinal axis 53 of the plunger body 52 is oval, for example, elliptical. In directions perpendicular to the axis of rotation 61 of the roller 60, the roller shoe 56 has a large diameter D and in the direction of the axis of rotation 61 of the roller 60 has a small diameter d. Between the diameters D and d, the diameter of the roller shoe 56 changes continuously. The oval cross-sectional shape of the roller shoe 56 can be generated even before its hardening treatment or thereafter, for example, by grinding the roller shoe 56 having a circular cross-section in the initial state. The difference between the diameters D and d may be, for example, depending on the application about 10 to 100 microns.

Es kann vorgesehen sein, dass der Stößelkörper 52 relativ dünnwandig ausgebildet ist, wobei sich dann beim Einpressen des wie vorstehend erläutert ausgebildeten Rollenschuhs 56 in den Stößelkörper 52 dessen Außenform entsprechend der Form des Rollenschuhs 56 ändert. Der Stößelkörper 52 weist dann nach dem Einpressen des Rollenschuhs 56 in Richtungen senkrecht zur Drehachse 61 der Rolle 60 einen größeren Außendurchmesser D' auf als in Richtung der Drehachse 61 der Rolle 60, wo der Außendurchmesser mit d' bezeichnet ist. Diese Ausbildung des Stößelkörpers 52 ermöglicht es, dass auch der Stößelkörper 52 in der Bohrung 54 des Pumpengehäuseteils 14 eine begrenzte Kippbewegung zur Ermöglichung der Ausrichtung der Drehachse 61 der Rolle 60 zumindest annähernd parallel zur Drehachse 13 der Antriebswelle 12 ausführen kann. Der Stößelkörper 52 ist dabei in der Bohrung 54 in Richtungen senkrecht zur Drehachse 61 der Rolle 60 mit geringem Spiel geführt und in Richtung der Drehachse 61 der Rolle 60 mit größerem Spiel angeordnet. Die Differenz der Spiele des Stößelkörpers 52 in Richtungen senkrecht zur Drehachse 61 und in Richtung der Drehachse 61 der Rolle 60 in der Bohrung 54 kann je nach Anwendungsfall beispielsweise etwa 10 bis 100 µm betragen.It can be provided that the plunger body 52 is formed relatively thin-walled, which then changes during pressing of the roller shoe 56 formed as described above in the plunger body 52 whose outer shape according to the shape of the roller shoe 56. The plunger body 52 then has after pressing the roller shoe 56 in directions perpendicular to the axis of rotation 61 of the roller 60 has a larger outer diameter D 'as in the direction of the axis of rotation 61 of the roller 60, where the outer diameter is denoted by d'. This design of the plunger body 52 allows that the plunger body 52 in the bore 54 of the pump housing part 14 can perform a limited tilting movement to enable the alignment of the axis of rotation 61 of the roller 60 at least approximately parallel to the axis of rotation 13 of the drive shaft 12. The plunger body 52 is guided in the bore 54 in directions perpendicular to the axis of rotation 61 of the roller 60 with little play and arranged in the direction of the axis of rotation 61 of the roller 60 with a larger clearance. The difference of the games of the plunger body 52 in directions perpendicular to the axis of rotation 61 and in the direction of the axis of rotation 61 of the roller 60 in the bore 54 may each for example, be about 10 to 100 microns after use.

In den Figuren 6 bis 8 sind Ausführungsbeispiele der Stößelbaugruppe 50 dargestellt, bei denen die Kippbewegung des Rollenschuhs 56 im Stößelkörper 52 weiter erleichtert ist. Bei einem in den Figuren 6 und 7 dargestellten dritten Ausführungsbeispiel weist der Rollenschuh 56 auf seiner dem Anschlag 62 zugewandten Oberseite eine Erhebung 68 auf, die jedoch nur beiderseits der die Längsachse 53 des Stößelkörpers 52 enthaltenden und senkrecht zur Drehachse 61 der Rolle 60 verlaufenden Mittelebene 55 des Rollenschuhs 56 verläuft, während die in Richtung der Drehachse 61 der Rolle 60 mit Abstand von der Mittelebene 55 angeordneten Randbereiche 70 der Oberseite des Rollenschuhs 56 in Richtung der Längsachse 53 des Stößelkörpers 52 tiefer liegen. Der erforderliche Materialabtrag in den Randbereichen 70 des Rollenschuhs 56 kann beispielsweise durch Fräsen oder Schleifen erfolgen. Durch die vorstehend erläuterte Ausbildung des Rollenschuhs 56 ist erreicht, dass der Rollenschuh 56 an seiner Oberseite nur mit seiner Erhebung 68 am Anschlag 62 anliegt, während die Randbereiche 70 mit Abstand vom Anschlag 62 angeordnet sind. Hierdurch ist erreicht, dass der Rollenschuh 56 im Stößelkörper 52 die bereits vorstehend erläuterte Kippbewegung ausführen kann ohne dass diese durch den Anschlag 62 behindert wird.In the FIGS. 6 to 8 Embodiments of the plunger assembly 50 are shown in which the tilting movement of the roller shoe 56 in the plunger body 52 is further facilitated. At one in the FIGS. 6 and 7 illustrated third embodiment, the roller shoe 56 on its stop 62 facing the top of a survey 68, but only on both sides of the longitudinal axis 53 of the plunger body 52 and extending perpendicular to the axis of rotation 61 of the roller 60 extending center plane 55 of the roller shoe 56, while the in Direction of the axis of rotation 61 of the roller 60 at a distance from the central plane 55 arranged edge regions 70 of the top of the roller shoe 56 in the direction of the longitudinal axis 53 of the plunger body 52 are lower. The required removal of material in the edge regions 70 of the roller shoe 56 can be done for example by milling or grinding. By the above-described embodiment of the roller shoe 56 is achieved that the roller shoe 56 rests on its upper side only with its collection 68 on the stop 62, while the edge regions 70 are arranged at a distance from the stop 62. As a result, it is achieved that the roller shoe 56 in the tappet body 52 can execute the tilting movement already explained above without this being hindered by the stop 62.

In Figur 8 ist der Rollenschuh 56 gemäß einem vierten Ausführungsbeispiel dargestellt, bei dem der Rollenschuh 56 auf seiner dem Anschlag 62 zugewandten Oberseite eine konvexe Wölbung aufweist, durch die auf dieser Oberseite des Rollenschuhs 56 eine Erhebung 72 gebildet ist, deren höchste Linie in der Mittelebene 55 des Rollenschuhs 56 verläuft. Die Wölbung der Oberseite des Rollenschuhs 56 ist dabei nur in Schnitten parallel zur Drehachse 61 der Rolle 60 vorhanden, während sich in Schnitten senkrecht zur Drehachse 61 der Rolle 60 durch den Rollenschuh 56 an dessen Oberseite gerade Schnittlinien ergeben. Die Wölbung der Oberseite des Rollenschuhs 56 kann beispielsweise durch Schleifen einer Kontur erzeugt werden mit einem relativ großen Radius R, dessen Mittelpunkt M auf der Verlängerung der Längsachse 53 des Stößelkörpers 52 liegt. Durch die Wölbung der Oberseite des Rollenschuhs 56 ergibt sich eine nur linienförmige Anlage des Rollenschuhs 56 mit seiner Oberseite am Anschlag 62, so dass der Rollenschuh 56 im Stößelkörper 52 die bereits vorstehend erläuterte Kippbewegung ausführen kann ohne dass diese durch den Anschlag 62 behindert wird. Außerdem ergibt sich für den Kolbenfuß 35 des Pumpenkolbens 34 ebenfalls eine linienförmige Anlage an der Oberseite des Rollenschuhs 56, wodurch die Kippbewegung des Rollenschuhs 56 bezüglich des Pumpenkolbens 34 erleichtert wird. Der Pumpenkolben 34 ist in Figur 8 aus Gründen der Übersichtlichkeit nicht dargestellt.In FIG. 8 is the roller shoe 56 shown according to a fourth embodiment, in which the roller shoe 56 has on its stop 62 facing the top of a convex curvature through which an elevation 72 is formed on this top of the roller shoe 56, whose highest line in the median plane 55 of the roller shoe 56 runs. The curvature of the top of the roller shoe 56 is only in sections parallel to the axis of rotation 61 of the roller 60 present, while in sections perpendicular to the axis of rotation 61 of the roller 60 through the roller shoe 56 at the top thereof produce straight cutting lines. The curvature of the upper side of the roller shoe 56 can be produced, for example, by grinding a contour having a relatively large radius R whose center M lies on the extension of the longitudinal axis 53 of the tappet body 52. Due to the curvature of the upper side of the roller shoe 56 results in a only linear contact of the roller shoe 56 with its top on stop 62, so that the roller shoe 56 in the plunger body 52 can perform the tilting movement already explained above without this being hindered by the stop 62. In addition, for the piston foot 35 of the pump piston 34 also results in a linear contact with the upper side of the roller shoe 56, whereby the tilting movement of the roller shoe 56 is facilitated with respect to the pump piston 34. The pump piston 34 is in FIG. 8 not shown for reasons of clarity.

Bei einer alternativen Ausführungsform der Hochdruckpumpe kann auch vorgesehen sein, dass der Rollenschuh 56 im Stößelkörper 52 starr angeordnet, beispielsweise eingepresst ist oder dass der Rollenschuh 56 einstückig mit dem Stößelkörper 52 ausgeführt ist und keine Kippbewegung des Rollenschuhs 56 im Stößelkörper 52 möglich ist. Der Stößelkörper 52 ist dabei in der Bohrung 54 des Pumpengehäuseteils 14 so angeordnet, dass der Stößelkörper 52 in der Bohrung 54 in Richtungen senkrecht zur Drehachse 61 der Rolle 60 mit geringerem Spiel geführt ist als in Richtung der Drehachse 61 der Rolle 60. Die Bohrung 54 im Pumpengehäuseteil 14 weist dabei einen konstanten Durchmesser auf. Hierbei kann der Stößelkörper 52 wie vorstehend zum Rollenschuh 56 beschrieben ausgebildet sein und somit in Richtungen senkrecht zur Drehachse 61 der Rolle 60 einen größeren Außendurchmesser D' aufweisen als in Richtung der Drehachse 61 der Rolle 60, wo der Außendurchmesser d' beträgt. Der Stößelkörper 52 kann im Querschnitt Bereiche mit großem Außendurchmesser D' und Bereiche mit kleinerem Außendurchmesser d' analog zur Ausbildung des Rollenschuhs 56 gemäß Figur 4 aufweisen oder der Stößelkörper 52 kann im Querschnitt oval ausgebildet sein analog zur Ausbildung des Rollenschuhs 56 gemäß Figur 5. Die Differenz der Spiele des Stößelkörpers 52 in Richtungen senkrecht zur Drehachse 61 und in Richtung der Drehachse 61 der Rolle 60 in der Bohrung 54 kann je nach Anwendungsfall beispielsweise etwa 10 bis 100 µm betragen.In an alternative embodiment of the high pressure pump can also be provided that the roller shoe 56 is rigidly arranged in the plunger body 52, for example, is pressed or that the roller shoe 56 is integral with the plunger body 52 and no tilting movement of the roller shoe 56 in the plunger body 52 is possible. The plunger body 52 is arranged in the bore 54 of the pump housing part 14 so that the plunger body 52 is guided in the bore 54 in directions perpendicular to the axis of rotation 61 of the roller 60 with less play than in the direction of the axis of rotation 61 of the roller 60th Die Bohrung 54 in the pump housing part 14 has a constant diameter. Here, the plunger body 52 may be formed as described above for the roller shoe 56 and thus in directions perpendicular to the axis of rotation 61 of the roller 60 has a larger outer diameter D 'as in the direction of the axis of rotation 61 of the roller 60, where the outer diameter d 'is. The plunger body 52 can cross-section areas with large outer diameter D 'and areas with smaller outer diameter d' analogous to the formation of the roller shoe 56 according to FIG. 4 or the plunger body 52 may be oval in cross-section similar to the formation of the roller shoe 56 according to FIG. 5 , The difference of the games of the plunger body 52 in directions perpendicular to the axis of rotation 61 and in the direction of the axis of rotation 61 of the roller 60 in the bore 54 may be, for example, about 10 to 100 microns depending on the application.

Durch die vorgespannte Rückstellfeder 56 wird die Stößelbaugruppe 50 über die Rolle 60 in Anlage am Nocken 26 der Antriebswelle 12 gehalten. Bei der Drehbewegung der Antriebswelle 12 wird die Stößelbaugruppe 50 in einer Hubbewegung angetrieben. Beim Saughub des Pumpenkolbens 34, bei dem sich dieser radial nach innen bewegt, wird der Pumpenarbeitsraum 38 durch den Kraftstoffzulaufkanal 40 bei geöffnetem Einlassventil 42 mit Kraftstoff befüllt, wobei das Auslassventil 46 geschlossen ist. Beim Förderhub des Pumpenkolbens 34, bei dem sich dieser radial nach aussen bewegt, wird durch den Pumpenkolben 34 Kraftstoff unter Hochdruck durch den Kraftstoffablaufkanal 44 bei geöffnetem Auslassventil 46 zum Hochdruckspeicher 110 gefördert, wobei das Einlassventil 42 geschlossen ist.By the biased return spring 56, the plunger assembly 50 is held on the roller 60 in contact with the cam 26 of the drive shaft 12. During the rotational movement of the drive shaft 12, the plunger assembly 50 is driven in a lifting movement. When the suction stroke of the pump piston 34, in which this moves radially inward, the pump chamber 38 is filled by the fuel inlet passage 40 with the inlet valve 42 open with fuel, the exhaust valve 46 is closed. During the delivery stroke of the pump piston 34, in which this moves radially outward, fuel is pumped under high pressure through the fuel discharge passage 44 with the outlet valve 46 open to the high-pressure accumulator 110 by the pump piston 34, wherein the inlet valve 42 is closed.

Claims (11)

  1. Tappet subassembly, for a high-pressure pump, in particular for fuel conveyance, with a hollow-cylindrical tappet body (52), into which a roller shoe (56) is inserted in the direction of the longitudinal axis (53) of the tappet body (52), a roller (60) being mounted rotatably in the roller shoe (56), characterized in that the roller shoe (56) is arranged, perpendicularly to the axis of rotation (61) of the roller (60), in the tappet body (52) with low play or so as to be free of play and is arranged, in the direction of the axis of rotation (61) of the roller (60), in the tappet body (52) with a greater play than perpendicularly to the axis of rotation (61) of the roller (60).
  2. Tappet subassembly according to Claim 1, characterized in that the roller shoe (56) is pressed into the tappet body (52), and a press fit between the roller shoe (56) and the tappet body (52) is present perpendicularly to the axis of rotation (61) of the roller (60).
  3. Tappet subassembly according to Claim 1 or 2, characterized in that, in cross section, the roller shoe (56) has a larger diameter (D) perpendicularly to the longitudinal axis (53) of the tappet body (52) than the diameter (d) of the roller shoe (56) in the direction of the axis of rotation (61) of the roller (60).
  4. Tappet subassembly according to Claim 3, characterized in that, in cross section, the roller shoe (56) is of oval design perpendicularly to the longitudinal axis (53) of the tappet body (52).
  5. Tappet subassembly according to one of Claims 1 to 4, characterized in that the roller shoe (56) comes to bear against a stop (62) in the direction of the longitudinal axis (53) of the tappet body (52), and in that the roller shoe (56) bears against the stop (62) at least essentially only in the region of a mid-plane (55) running through the roller shoe (56) perpendicularly to the axis of rotation (61) of the roller (60).
  6. Tappet subassembly according to Claim 5, characterized in that the roller shoe (56), on its side facing the stop (62), has in the region of the mid-plane (55) an elevation (68) with which the roller shoe (56) bears against the stop (62).
  7. Tappet subassembly according to one of Claims 2 to 6, characterized in that, when the roller shoe (56) is being pressed in, the tappet body (52) is deformed in such a way that the tappet body (52) has a larger outside diameter (D') perpendicularly to the axis of rotation (61) of the roller (60) than the outside diameter (d') of the tappet body (52) in the direction of the axis of rotation (61) of the roller (60).
  8. High-pressure pump, in particular for high-pressure fuel conveyance for a fuel injection device of an internal combustion engine, with a drive shaft (12) having at least one cam (26) or eccentric and with at least one pump element (32) which has a pump piston (34) which is supported via a tappet subassembly (50) on the cam (26) or eccentric of the drive shaft (12) and is driven in a lifting movement by the said cam or eccentric, characterized in that the tappet subassembly (50) is designed according to one of Claims 1 to 7.
  9. High-pressure pump, in particular for high-pressure fuel conveyance for a fuel injection device of an internal combustion engine, with a drive shaft (12) having at least one cam (26) or eccentric and with at least one pump element (32) which has a pump piston (34) which is supported via a tappet subassembly (50) on the cam (26) or eccentric of the drive shaft (12) and is driven in a lifting movement by the said cam or eccentric, the tappet subassembly (50) having a tappet body (52) which is guided displaceably in a bore (54) of a housing part (10) of the high-pressure pump, and the tappet subassembly (50) having a roller shoe (56) in which is mounted rotatably a roller (60) which rolls on the cam (26) or eccentric of the drive shaft (12), characterized in that, in the bore (54) of the pump housing part (10), the tappet body (52) is arranged with low play in the perpendicular direction with respect to the axis of rotation (61) of the roller (60) and is arranged with greater play in the direction of the axis of rotation (61) of the roller (60).
  10. High-pressure pump according to Claim 9, characterized in that the tappet body (52) has a larger outside diameter (D') in the perpendicular direction with respect to the axis of rotation (61) of the roller (60) than the outside diameter (d') of the tappet body (52) in the direction of the axis of rotation (61) of the roller (60).
  11. High-pressure pump according to Claim 10, characterized in that, in cross section, the tappet body (52) is of oval design perpendicularly to its longitudinal axis (53).
EP07788020A 2006-09-28 2007-07-30 Tappet assembly for a high-pressure pump and high-pressure pump comprising at least one tappet assembly Not-in-force EP2076669B1 (en)

Applications Claiming Priority (2)

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DE102006045933A DE102006045933A1 (en) 2006-09-28 2006-09-28 Plunger assembly for a high pressure pump and high pressure pump with at least one plunger assembly
PCT/EP2007/057811 WO2008037524A1 (en) 2006-09-28 2007-07-30 Tappet assembly for a high-pressure pump and high-pressure pump comprising at least one tappet assembly

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EP2076669A1 EP2076669A1 (en) 2009-07-08
EP2076669B1 true EP2076669B1 (en) 2010-10-06

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US (1) US20100037865A1 (en)
EP (1) EP2076669B1 (en)
JP (1) JP2010505058A (en)
CN (1) CN101523044A (en)
AT (1) ATE483907T1 (en)
BR (1) BRPI0716260A2 (en)
DE (2) DE102006045933A1 (en)
WO (1) WO2008037524A1 (en)

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JP2010505058A (en) 2010-02-18
US20100037865A1 (en) 2010-02-18
DE502007005293D1 (en) 2010-11-18
ATE483907T1 (en) 2010-10-15
WO2008037524A1 (en) 2008-04-03
DE102006045933A1 (en) 2008-04-03
CN101523044A (en) 2009-09-02
EP2076669A1 (en) 2009-07-08
BRPI0716260A2 (en) 2013-08-06

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