EP1697636B1 - High-pressure pump, in particular for a fuel-injection device of an internal combustion engine - Google Patents

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

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Publication number
EP1697636B1
EP1697636B1 EP04786760A EP04786760A EP1697636B1 EP 1697636 B1 EP1697636 B1 EP 1697636B1 EP 04786760 A EP04786760 A EP 04786760A EP 04786760 A EP04786760 A EP 04786760A EP 1697636 B1 EP1697636 B1 EP 1697636B1
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EP
European Patent Office
Prior art keywords
pump
piston
tappet
support element
pressure pump
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Application number
EP04786760A
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German (de)
French (fr)
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EP1697636A1 (en
Inventor
Alfons Schoetz
Walter Fuchs
Gerhard Meier
Jochen Aleker
Andreas Dutt
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication of EP1697636A1 publication Critical patent/EP1697636A1/en
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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
    • F02M59/04—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
    • 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
    • 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
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/0404—Details or component parts
    • F04B1/0439—Supporting or guiding means for the pistons

Definitions

  • the invention relates to a 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 for a fuel injection device of an internal combustion engine is characterized by the DE 101 57 076 A known.
  • This high-pressure pump has at least one pump element which has a pump piston which delimits a pump working space and which is driven at least indirectly by a drive shaft against the force of a restoring spring in a lifting movement.
  • the pump piston is supported at least indirectly via a sleeve-shaped plunger on the drive shaft.
  • the return spring engages the pump piston via a spring plate.
  • a support element is used, on which the pump piston is supported to the drive shaft and which is at least indirectly supported on the drive shaft.
  • a high-pressure pump for a fuel injection device of an internal combustion engine in which the restoring spring engages via a spring plate on the pump piston and on the sleeve-shaped plunger.
  • the restoring spring engages via a spring plate on the pump piston and on the sleeve-shaped plunger.
  • very low manufacturing tolerances of the components are required.
  • the US-A-5,752,430 is a high pressure pump for a fuel injector of an internal combustion engine, in which the return spring via a spring plate on the pump piston and on engages sleeve-shaped plunger, which also very small manufacturing tolerances of the components are required to ensure the installation of the spring plate on the pump piston and the plunger.
  • the high-pressure pump according to the invention with the features of claim 1 has the advantage that a support of the return spring on the pump piston and the plunger is ensured regardless of manufacturing tolerances of these components by the elastically deformable spring plate.
  • FIG. 1 shows a fuel injection device of an internal combustion engine with a high-pressure pump in a longitudinal section and Figure 2 a designated in Figure 1 with II section of the high-pressure pump in an enlarged view.
  • FIGS. 1 and 2 show a high-pressure pump for a fuel injection device of an internal combustion engine.
  • the high-pressure pump has a housing 10, which is designed in several parts and in which a 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 of the housing 10.
  • the drive shaft 12 has an eccentrically formed to its axis of rotation 13 cam 26, wherein the cam 26 may be a multiple cam.
  • the high pressure pump has at least one or more arranged in the housing 10 pump elements 32, each with a pump piston 34 which is driven by the drive shaft 12 via the cam 26 in a lifting movement in at least approximately radial direction to the rotation axis 13 of the drive shaft 12 and along its longitudinal axis 35 ,
  • the pump piston 34 is guided in a cylinder bore 36 in the housing 10 or an insert in the housing 10 and slidably limited with its the drive shaft 12 facing away from the end in the cylinder bore 36 a pump chamber 38.
  • the pump chamber 38 has a running in the housing 10 fuel inlet channel 40 a Connection with a fuel inlet, such as a feed 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 10 fuel drain passage 44 to an outlet with an outlet, for example, with a High-pressure accumulator 110 is connected.
  • an outlet valve 46 which opens out of the pump working chamber 38 is arranged, which likewise has a spring-loaded valve member 47.
  • 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.
  • the pump piston 34 is supported on the cam 26 of the drive shaft 12 via a support element 50 and a cylindrical roller 52 mounted in the latter on its side facing the drive shaft 12.
  • the support member 50 is for example approximately cylindrical and has a recess 54 in which the roller 52 is rotatably mounted.
  • the axis of rotation 53 of the roller 52 extends at least approximately parallel to the axis of rotation 13 of the drive shaft 12.
  • the pump piston 34 has at its the support member 50 facing the end of a diameter greater than the rest of the pump piston 34 enlarged piston 56 and the pump piston 34 is located with the end face of his piston 56 on the support member 50 at.
  • the support member 50 is inserted into a sleeve-shaped plunger 60 which is guided in a bore 62 of the housing 10 of the high-pressure pump in the direction of movement of the pump piston 34, that is, in the direction of its longitudinal axis 35 slidably.
  • the plunger 60 is formed hollow throughout and has an end portion facing the drive shaft 12, in which the support member 50 is received with little play in the plunger 50, to which the drive shaft 12 facing away from an inwardly projecting annular collar 64 connects, the support member 50th on which the drive shaft 12 facing away from overlaps.
  • a spring plate 66 On the pump piston 34, a spring plate 66, which is supported on the piston foot 56, is pushed by its end limiting the pump working space 38. Between the spring plate 66 and the housing 10 of the high pressure pump, a biased return spring 68 is arranged, which is formed for example as a helical compression spring.
  • the spring plate 66 rests with its central region 166 in the direction of the longitudinal axis 35 of the pump piston 34 on the piston foot 56. With its peripheral region 266 of the spring plate 66 is located in the direction of the longitudinal axis 35 of the pump piston 34 in the plunger 60 on the annular collar 64 on the support member 50 opposite side.
  • the spring plate 66 is formed so elastically deformable that its peripheral portion 266 relative to the central region 166 in the direction of the longitudinal axis 35 of the pump piston 34 is movable.
  • the spring plate 66 is shown in its elastically deformed state. In its undeformed initial state, the spring plate 66 may be planar or may already have a deflection according to FIG. 2 in its peripheral region 266.
  • the spring plate 66 may for example consist of sheet metal and preferably has a lower rigidity than the return spring 68.
  • the return spring 68 is also held on the spring plate 66 of the plunger 60 with its annular collar 64 in contact with the support member 50. Due to the elastic deformability of the spring plate 66, its abutment is ensured both on the piston foot 56 and on the annular collar 64 of the plunger 60, even if the contact surfaces for the spring plate 66 on the piston base 56 and the annular collar 64 of the plunger 60 in the direction of the longitudinal axis 35 of the pump piston 34th offset from each other, which will be the case as a result of manufacturing tolerances of the individual components can. By compared to the spring plate 66 greater rigidity of the return spring 68, the elastic deformation of the spring plate 66 is achieved so that it rests securely on both the piston foot 56 and the annular collar 64 of the plunger 60.

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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)

Description

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 für eine Kraftstoffeinspritzeinrichtung einer Brennkraftmaschine ist durch die DE 101 57 076 A bekannt. Diese Hochdruckpumpe hat wenigstens ein Pumpenelement, das einen Pumpenkolben aufweist, der einen Pumpenarbeitsraum begrenzt und der zumindest mittelbar durch eine Antriebswelle gegen die Kraft einer Rückstellfeder in einer Hubbewegung angetrieben wird. Der Pumpenkolben stützt sich zumindest mittelbar über einen hülsenförmigen Stößel an der Antriebswelle ab. Die Rückstellfeder greift am Pumpenkolben über einen Federteller an. In den Stößel ist ein Stützelement eingesetzt, an dem sich der Pumpenkolben zur Antriebswelle hin abstützt und das sich zumindest mittelbar an der Antriebswelle abstützt. Durch den Stößel wird dabei die Funktion der Querkraftaufnahme für den Pumpenkolben und durch das Stützelement wird die Funktion der Abstützung an der Antriebswelle übernommen. Die Rückstellfeder greift jedoch über den Federteller nur am Pumpenkolben an, der dann auf das Stützelement und dieses wiederum auf den Stößel wirkt, wodurch alle diese Bauteile zur Antriebswelle hin beaufschlagt werden. Aufgrund von Fertigungstoleranzen der Bauteile kann zwischen diesen jedoch ein Spiel vorhanden sein, das insbesondere in den Bereichen der Bewegungsumkehr des Pumpenkolbens, das ist dessen innerer und äußerer Totpunkt, durchlaufen wird und dazu führt, dass die Bauteile gegeneinanderschlagen, was zu einem erhöhten Verschleiß derselben führt.Such a high-pressure pump for a fuel injection device of an internal combustion engine is characterized by the DE 101 57 076 A known. This high-pressure pump has at least one pump element which has a pump piston which delimits a pump working space and which is driven at least indirectly by a drive shaft against the force of a restoring spring in a lifting movement. The pump piston is supported at least indirectly via a sleeve-shaped plunger on the drive shaft. The return spring engages the pump piston via a spring plate. In the plunger, a support element is used, on which the pump piston is supported to the drive shaft and which is at least indirectly supported on the drive shaft. By the plunger while the function of the transverse force absorption for the pump piston and the support member, the function of the support is taken on the drive shaft. However, the return spring acts on the spring plate only on the pump piston, which then acts on the support element and this in turn on the plunger, whereby all these components are acted upon the drive shaft. However, due to manufacturing tolerances of the components may be present between them, a game that is particularly in the areas of motion reversal of the pump piston, which is its inner and outer dead center, traversed and causes the components against each other, which leads to increased wear of the same ,

Durch die JP 2000-145572 A ist eine Hochdruckpumpe für eine Kraftstoffeinspritzeinrichtung einer Brennkraftmaschine bekannt, bei der die Rückstellfeder über einen Federteller am Pumpenkolben und am hülsenförmigen Stößel angreift. Um die Anlage des Federtellers am Pumpenkolben und am Stößel zu ermöglichen sind sehr geringe Fertigungstoleranzen der Bauteile erforderlich. Auch durch die US-A-5,752,430 ist eine Hochdruckpumpe für eine Kraftstoffeinspritzeinrichtung einer Brennkraftmaschine bekannt, bei der die Rückstellfeder über einen Federteller am Pumpenkolben und am hülsenförmigen Stößel angreift, wobei auch hier sehr geringe Fertigungstoleranzen der Bauteile erforderlich sind, um die Anlage des Federtellers am Pumpenkolben und am Stößel sicherzustellen.By the JP 2000-145572 A a high-pressure pump for a fuel injection device of an internal combustion engine is known, in which the restoring spring engages via a spring plate on the pump piston and on the sleeve-shaped plunger. To allow the installation of the spring plate on the pump piston and the plunger very low manufacturing tolerances of the components are required. Also by the US-A-5,752,430 is a high pressure pump for a fuel injector of an internal combustion engine, in which the return spring via a spring plate on the pump piston and on engages sleeve-shaped plunger, which also very small manufacturing tolerances of the components are required to ensure the installation of the spring plate on the pump piston and the plunger.

Vorteile der ErfindungAdvantages of the invention

Die erfindungsgemäße Hochdruckpumpe mit den Merkmalen gemäß Anspruch 1 hat demgegenüber den Vorteil, dass durch den elastisch verformbaren Federteller eine Abstützung der Rückstellfeder am Pumpenkolben und am Stößel unabhängig von Fertigungstoleranzen dieser Bauteile sichergestellt ist.The high-pressure pump according to the invention with the features of claim 1 has the advantage that a support of the return spring on the pump piston and the plunger is ensured regardless of manufacturing tolerances of these components by the elastically deformable spring plate.

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.

Zeichnungdrawing

Ein Ausführungsbeispiel der Erfindung ist in der Zeichnung dargestellt und in der nachfolgenden Beschreibung näher erläutert. Es zeigen Figur 1 eine Kraftstoffeinspritzeinrichtung einer Brennkraftmaschine mit einer Hochdruckpumpe in einem Längsschnitt und Figur 2 einen in Figur 1 mit II bezeichneten Ausschnitt der Hochdruckpumpe in vergrößerter Darstellung.An embodiment of the invention is illustrated in the drawing and explained in more detail in the following description. 1 shows a fuel injection device of an internal combustion engine with a high-pressure pump in a longitudinal section and Figure 2 a designated in Figure 1 with II section of the high-pressure pump in an enlarged view.

Beschreibung des AusführungsbeispielsDescription of the embodiment

In den Figuren 1 und 2 ist eine Hochdruckpumpe für eine Kraftstoffeinspritzeinrichtung einer Brennkraftmaschine dargestellt. Die Hochdruckpumpe weist ein Gehäuse 10 auf, das mehrteilig ausgebildet ist und in dem eine 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 des Gehäuses 10 angeordnet sein.FIGS. 1 and 2 show a high-pressure pump for a fuel injection device of an internal combustion engine. The high-pressure pump has a housing 10, which is designed in several parts and in which a 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 of the housing 10.

In einem zwischen den beiden Lagerstellen liegenden Bereich weist die Antriebswelle 12 einen exzentrisch zu ihrer Drehachse 13 ausgebildeten Nocken 26 auf, wobei der Nocken 26 ein Mehrfachnocken sein kann. Die Hochdruckpumpe weist wenigstens ein oder mehrere im Gehäuse 10 angeordnete Pumpenelemente 32 mit jeweils einem Pumpenkolben 34 auf, der durch die Antriebswelle 12 über deren Nocken 26 in einer Hubbewegung in zumindest annähernd radialer Richtung zur Drehachse 13 der Antriebswelle 12 und entlang seiner Längsachse 35 angetrieben wird. Der Pumpenkolben 34 ist in einer Zylinderbohrung 36 im Gehäuse 10 oder einem Einsatz im Gehäuse 10 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 Gehäuse 10 verlaufenden Kraftstoffablaufkanal 44 eine Verbindung mit einem Auslass auf, der beispielsweise mit einem Hochdruckspeicher 110 verbunden ist. 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. 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.In a region lying between the two bearing points, the drive shaft 12 has an eccentrically formed to its axis of rotation 13 cam 26, wherein the cam 26 may be a multiple cam. The high pressure pump has at least one or more arranged in the housing 10 pump elements 32, each with a pump piston 34 which is driven by the drive shaft 12 via the cam 26 in a lifting movement in at least approximately radial direction to the rotation axis 13 of the drive shaft 12 and along its longitudinal axis 35 , The pump piston 34 is guided in a cylinder bore 36 in the housing 10 or an insert in the housing 10 and slidably limited with its the drive shaft 12 facing away from the end in the cylinder bore 36 a pump chamber 38. The pump chamber 38 has a running in the housing 10 fuel inlet channel 40 a Connection with a fuel inlet, such as a feed 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 10 fuel drain passage 44 to an outlet with an outlet, for example, with a High-pressure accumulator 110 is connected. 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. 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.

Der Pumpenkolben 34 stützt sich über ein Stützelement 50 und eine in diesem auf dessen der Antriebswelle 12 zugewandter Seite gelagerten zylinderförmigen Rolle 52 am Nocken 26 der Antriebswelle 12 ab. Das Stützelement 50 ist beispielsweise etwa zylinderförmig ausgebildet und weist eine Vertiefung 54 auf, in der die Rolle 52 drehbar gelagert ist. Die Drehachse 53 der Rolle 52 verläuft zumindest annähernd parallel zur Drehachse 13 der Antriebswelle 12. Der Pumpenkolben 34 weist an seinem dem Stützelement 50 zugewandten Ende einen im Durchmesser gegenüber dem restlichen Pumpenkolben 34 vergrößerten Kolbenfuß 56 auf und der Pumpenkolben 34 liegt mit der Stirnseite seines Kolbenfußes 56 am Stützelement 50 an.The pump piston 34 is supported on the cam 26 of the drive shaft 12 via a support element 50 and a cylindrical roller 52 mounted in the latter on its side facing the drive shaft 12. The support member 50 is for example approximately cylindrical and has a recess 54 in which the roller 52 is rotatably mounted. The axis of rotation 53 of the roller 52 extends at least approximately parallel to the axis of rotation 13 of the drive shaft 12. The pump piston 34 has at its the support member 50 facing the end of a diameter greater than the rest of the pump piston 34 enlarged piston 56 and the pump piston 34 is located with the end face of his piston 56 on the support member 50 at.

Das Stützelement 50 ist in einen hülsenförmigen Stößel 60 eingesetzt, der in einer Bohrung 62 des Gehäuses 10 der Hochdruckpumpe in Bewegungsrichtung des Pumpenkolbens 34, das heißt in Richtung von dessen Längsachse 35 verschiebbar geführt ist. Der Stößel 60 ist durchgehend hohl ausgebildet und weist einen der Antriebswelle 12 zugewandten Endbereich auf, in dem das Stützelement 50 mit geringem Spiel im Stößel 50 aufgenommen ist, an den sich der Antriebswelle 12 abgewandt ein nach innen ragender Ringbund 64 anschließt, der das Stützelement 50 auf dessen der Antriebswelle 12 abgewandter Seite übergreift.The support member 50 is inserted into a sleeve-shaped plunger 60 which is guided in a bore 62 of the housing 10 of the high-pressure pump in the direction of movement of the pump piston 34, that is, in the direction of its longitudinal axis 35 slidably. The plunger 60 is formed hollow throughout and has an end portion facing the drive shaft 12, in which the support member 50 is received with little play in the plunger 50, to which the drive shaft 12 facing away from an inwardly projecting annular collar 64 connects, the support member 50th on which the drive shaft 12 facing away from overlaps.

Auf den Pumpenkolben 34 ist von dessen den Pumpenarbeitsraum 38 begrenzendem Ende her ein Federteller 66 aufgeschoben, der sich am Kolbenfuß 56 abstützt. Zwischen dem Federteller 66 und dem Gehäuse 10 der Hochdruckpumpe ist eine vorgespannte Rückstellfeder 68 angeordnet, die beispielsweise als Schraubendruckfeder ausgebildet ist. Der Federteller 66 liegt mit seinem zentralen Bereich 166 in Richtung der Längsachse 35 des Pumpenkolbens 34 am Kolbenfuß 56 an. Mit seinem peripheren Bereich 266 liegt der Federteller 66 in Richtung der Längsachse 35 des Pumpenkolbens 34 im Stößel 60 an dessen Ringbund 64 auf der dem Stützelement 50 abgewandten Seite an. Der Federteller 66 ist derart elastisch verformbar ausgebildet, dass dessen peripherer Bereich 266 gegenüber dessen zentralem Bereich 166 in Richtung der Längsachse 35 des Pumpenkolbens 34 bewegbar ist. In Figur 2 ist der Federteller 66 in seinem elastisch verformten Zustand dargestellt. In seinem unverformten Ausgangszustand kann der Federteller 66 eben ausgebildet sein oder bereits in seinem peripheren Bereich 266 eine Durchbiegung gemäß Figur 2 aufweisen. Der Federteller 66 kann beispielsweise aus Blech bestehen und weist vorzugsweise eine geringere Steifigkeit auf als die Rückstellfeder 68. Durch die Rückstellfeder 68 wird über den Federteller 66 der Pumpenkolben 34 mit seinem Kolbenfuß 56 in Anlage am Stützelement 50 und dieses mit seiner Rolle 52 in Anlage am Nocken 26 der Antriebswelle 12 gehalten. Durch die Rückstellfeder 68 wird außerdem über den Federteller 66 der Stößel 60 mit seinem Ringbund 64 in Anlage am Stützelement 50 gehalten. Durch die elastische Verformbarkeit des Federtellers 66 ist dessen Anlage sowohl am Kolbenfuß 56 als auch am Ringbund 64 des Stößels 60 sichergestellt, auch wenn die Anlageflächen für den Federteller 66 am Kolbenfuß 56 und am Ringbund 64 des Stößels 60 in Richtung der Längsachse 35 des Pumpenkolbens 34 zueinander versetzt sind, was infolge von Fertigungstoleranzen der einzelnen Bauteile der Fall sein kann. Durch die gegenüber dem Federteller 66 größere Steifigkeit der Rückstellfeder 68 wird die elastische Verformung des Federtellers 66 erreicht, so dass dieser sicher sowohl am Kolbenfuß 56 als auch am Ringbund 64 des Stößels 60 anliegt.On the pump piston 34, a spring plate 66, which is supported on the piston foot 56, is pushed by its end limiting the pump working space 38. Between the spring plate 66 and the housing 10 of the high pressure pump, a biased return spring 68 is arranged, which is formed for example as a helical compression spring. The spring plate 66 rests with its central region 166 in the direction of the longitudinal axis 35 of the pump piston 34 on the piston foot 56. With its peripheral region 266 of the spring plate 66 is located in the direction of the longitudinal axis 35 of the pump piston 34 in the plunger 60 on the annular collar 64 on the support member 50 opposite side. The spring plate 66 is formed so elastically deformable that its peripheral portion 266 relative to the central region 166 in the direction of the longitudinal axis 35 of the pump piston 34 is movable. In Figure 2, the spring plate 66 is shown in its elastically deformed state. In its undeformed initial state, the spring plate 66 may be planar or may already have a deflection according to FIG. 2 in its peripheral region 266. The spring plate 66 may for example consist of sheet metal and preferably has a lower rigidity than the return spring 68. By the return spring 68 is the spring piston 66 of the pump piston 34 with its piston 56 in abutment against the support member 50 and this with its role 52 in Appendix Cam 26 of the drive shaft 12 is held. By the return spring 68 is also held on the spring plate 66 of the plunger 60 with its annular collar 64 in contact with the support member 50. Due to the elastic deformability of the spring plate 66, its abutment is ensured both on the piston foot 56 and on the annular collar 64 of the plunger 60, even if the contact surfaces for the spring plate 66 on the piston base 56 and the annular collar 64 of the plunger 60 in the direction of the longitudinal axis 35 of the pump piston 34th offset from each other, which will be the case as a result of manufacturing tolerances of the individual components can. By compared to the spring plate 66 greater rigidity of the return spring 68, the elastic deformation of the spring plate 66 is achieved so that it rests securely on both the piston foot 56 and the annular collar 64 of the plunger 60.

Beim Saughub des Pumpenkolbens 34, bei dem sich dieser bewirkt durch die Rückstellfeder 68 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 bewirkt durch den Nocken 26 der Antriebswelle 12 gegen die Kraft der Rückstellfeder 68 radial nach aussen bewegt, wird durch den Pumpenkolben 34 Kraftstoff unter Hochdruck durch den Kraftstoffablaufkanal 44 bei geöffnetem Auslassventil 46 zum Speicher 110 gefördert, wobei das Einlassventil 42 geschlossen ist.When the suction stroke of the pump piston 34, in which this causes by the return spring 68 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 causes the cam 26 of the drive shaft 12 moves radially outward against the force of the return spring 68, fuel is pumped under high pressure through the fuel discharge passage 44 with the exhaust valve 46 open to the storage 110 by the pump piston 34, wherein the inlet valve 42 is closed.

Claims (8)

  1. High-pressure pump, in particular for a fuel injection device of an internal combustion engine, having at least one pump element (32) which has a pump piston (34) which delimits a pump working space (38) and which is driven in a reciprocating movement counter to the force of a restoring spring (68) at least indirectly by a driveshaft (12), with the pump piston (34) being supported on the driveshaft (12) at least indirectly by means of a sleeve-shaped tappet (60), with the restoring spring (68) engaging at least on the pump piston (34), with a support element (50) being inserted into the tappet (60), on which support element (50) the pump piston (34) is supported in the direction of the driveshaft (12) and which support element (50) is supported at least indirectly on the driveshaft (12), with the restoring spring (68) engaging by means of a plate spring (66) at least on the pump piston (34), characterized in that the restoring spring (68) engages by means of the plate spring (66) on the pump piston (34) and on the tappet (60), and in that the plate spring (66) is elastically deformable in the movement direction of the pump piston (34) in such a way that, by means of its elastic deformation, deviations in the position of its contact faces (56; 64) against the pump piston (34) and against the tappet (60) are compensated.
  2. High-pressure pump according to Claim 1, characterized in that the tappet (60) is held in contact against the support element (50) by means of the restoring spring (68).
  3. High-pressure pump according to Claim 2, characterized in that the tappet (60) has a rest (64), which projects inward into said tappet (60), for the support element (50), with which rest (64) the tappet (60) comes into contact against the support element (50) in the direction of the driveshaft (12).
  4. High-pressure pump according to one of Claims 1 to 3, characterized in that the plate spring (66) engages with its central region (166) on the pump piston (34) and with its peripheral region (266) on the tappet (60).
  5. High-pressure pump according to Claim 4, characterized in that the pump piston (34) has, at its end facing towards the support element (50), a piston foot (56) which is of greater diameter than its remaining region, on which piston foot (56) the plate spring (66) engages.
  6. High-pressure pump according to one of the preceding claims, characterized in that the plate spring (66) has a lower stiffness than the restoring spring (68).
  7. High-pressure pump according to one of the preceding claims, characterized in that a roller (52) is rotatably mounted in the support element (50) on its side facing towards the driveshaft (12), which roller (52) rolls on the driveshaft (12).
  8. High-pressure pump according to Claim 7, characterized in that the support element (50) is provided with a wear-prevention layer at least in the region of the bearing (54) of the roller (52).
EP04786760A 2003-11-25 2004-09-14 High-pressure pump, in particular for a fuel-injection device of an internal combustion engine Active EP1697636B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10355027A DE10355027A1 (en) 2003-11-25 2003-11-25 High-pressure pump, in particular for a fuel injection device of an internal combustion engine
PCT/DE2004/002039 WO2005052367A1 (en) 2003-11-25 2004-09-14 High-pressure pump, in particular for a fuel-injection device of an internal combustion engine

Publications (2)

Publication Number Publication Date
EP1697636A1 EP1697636A1 (en) 2006-09-06
EP1697636B1 true EP1697636B1 (en) 2007-11-14

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Family Applications (1)

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EP04786760A Active EP1697636B1 (en) 2003-11-25 2004-09-14 High-pressure pump, in particular for a fuel-injection device of an internal combustion engine

Country Status (6)

Country Link
US (1) US7308849B2 (en)
EP (1) EP1697636B1 (en)
JP (1) JP4243630B2 (en)
CN (1) CN100422551C (en)
DE (2) DE10355027A1 (en)
WO (1) WO2005052367A1 (en)

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Also Published As

Publication number Publication date
DE502004005537D1 (en) 2007-12-27
EP1697636A1 (en) 2006-09-06
DE10355027A1 (en) 2005-06-23
JP4243630B2 (en) 2009-03-25
US7308849B2 (en) 2007-12-18
US20070071620A1 (en) 2007-03-29
CN1886594A (en) 2006-12-27
JP2006528744A (en) 2006-12-21
WO2005052367A1 (en) 2005-06-09
CN100422551C (en) 2008-10-01

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