EP1931875B1 - 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
EP1931875B1
EP1931875B1 EP06793348A EP06793348A EP1931875B1 EP 1931875 B1 EP1931875 B1 EP 1931875B1 EP 06793348 A EP06793348 A EP 06793348A EP 06793348 A EP06793348 A EP 06793348A EP 1931875 B1 EP1931875 B1 EP 1931875B1
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EP
European Patent Office
Prior art keywords
tappet
pump
ball
pressure pump
receptacle
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
EP06793348A
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German (de)
French (fr)
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EP1931875A1 (en
Inventor
Alfons Schoetz
Gerhard Meier
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication date
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Publication of EP1931875A1 publication Critical patent/EP1931875A1/en
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Publication of EP1931875B1 publication Critical patent/EP1931875B1/en
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    • 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

Definitions

  • the invention relates to a high-pressure pump, in particular for a fuel injection device of an internal combustion engine according to the preamble of claim 1.
  • Such a high-pressure pump is through the DE 199 07 311 A1 known.
  • This high-pressure pump has a pump housing and at least one pump element arranged in the pump element.
  • the pump element has a driven by a drive shaft of the high pressure pump in a stroke pump piston.
  • the pump piston is tightly guided in a cylinder bore of a pump housing part of the high-pressure pump and delimits a pump working space in the cylinder bore.
  • the pump piston is supported at least indirectly via a hollow-cylindrical ram on the drive shaft.
  • the plunger is slidably guided in a bore of a pump housing in the direction of the longitudinal axis of the pump piston.
  • the high pressure pump according to the invention with the features of claim 1 has the advantage that an anti-rotation of the plunger is ensured by simple means.
  • the ball is a standard part that can be purchased inexpensively as a vendor.
  • FIG. 1 a high-pressure pump for a fuel injection device of an internal combustion engine in a longitudinal section
  • FIG. 2 one in FIG. 1 with II designated section of the high pressure pump in an enlarged view according to a first embodiment
  • FIG. 3 the high-pressure pump in a section along line III-III in FIG. 2
  • FIG. 4 one in FIG. 3 with IV designated section in again enlarged view
  • FIG. 5 the detail II of the high pressure pump according to a second embodiment.
  • the high-pressure pump has a multipart pump housing 10 in which a drive shaft 12 driven in rotation by the internal combustion engine is arranged.
  • the drive shaft 12 is rotatably supported, for example, via two bearing points spaced apart from one another in the direction of the axis of rotation 13 of the drive shaft 12.
  • the bearings can be arranged in different parts of the pump housing 10, for example, a first bearing point in a base body 14 of the pump housing 10 and a second bearing point can be arranged in a connected to the base body 14 flange 15.
  • the drive shaft 12 at least one cam 16 or eccentrically to its axis of rotation 13 formed portion, wherein the cam 16 may be formed as a multiple cam.
  • the high pressure pump has at least one or more arranged in the housing 10 pump elements 18, each with a pump piston 20 which is driven by the cam 16 of the drive shaft 12 in a lifting movement in at least approximately radial direction to the axis of rotation 13 of the drive shaft 12.
  • a pump housing part 22 connected to the main body 14 is provided, which is designed as a cylinder head.
  • the pump housing part 22 has a voltage applied to an outer side of the base body 14 and a flange 24 through an opening in the base body 14 to the drive shaft 12 through protruding, at least approximately cylindrical projection 26 with respect to the flange 24 of smaller diameter.
  • the pump piston 20 is guided tightly displaceable in a shoulder 26 formed in the cylinder bore 28 in the pump housing part 22 and limited with its drive shaft 12 facing away from the end face in the cylinder bore 28 a pump working space 30.
  • the cylinder bore 28 may extend into the flange 24, in the then the pump working space 30 is arranged.
  • the pump working chamber 30 has a connection with a fuel feed, for example a feed pump, via a fuel feed channel 32 extending in the pump housing 10.
  • the pump working chamber 30 also has a connection in the pump housing 10 extending fuel drain passage 36 to an outlet with an outlet, which is connected for example to a high-pressure accumulator 110.
  • One or preferably a plurality of injectors 120 arranged on the cylinders of the internal combustion engine are connected to the high-pressure accumulator 110, through which fuel is injected into the cylinders of the internal combustion engine.
  • an outlet valve 38 opening out of the pump working chamber 30 is arranged.
  • a plunger 40 is arranged, via which the pump piston 20 at least indirectly on the cam 16 of the drive shaft 12 is supported.
  • the plunger 40 is formed in a hollow cylindrical shape with a round outer cross section and is guided displaceably in a bore 42 of the main body 14 of the pump housing 10 in the direction of the longitudinal axis 21 of the pump piston 20.
  • the longitudinal axis 41 of the plunger 40 is thus at least substantially identical to the longitudinal axis 21 of the pump piston 20.
  • a support element 44 is inserted in the drive shaft 12 facing end portion in which a roller 46 is rotatably mounted, which rolls on the cam 16 of the drive shaft 12.
  • the axis of rotation 47 of the roller 46 is at least approximately parallel to the axis of rotation 13 of the drive shaft 12.
  • the support member 44 has on its side facing the drive shaft 12 a recess 48 in which the roller 46 is mounted.
  • the pump piston 20 may be coupled to the plunger 40, at least in the direction of its longitudinal axis 21. Alternatively, the pump piston 20 may not be connected to the plunger 40, then by the return spring 52, the system of the pump piston 20 is secured to the plunger 40.
  • the restoring spring 52 engages, for example, via a spring plate 53 on an enlarged diameter piston base of the pump piston 20, which is thereby held in abutment against a flange projecting inwardly from the sleeve on the plunger 40, which in turn bears against the support element 44 is held, so that the entire composite of pump piston 20, plunger 40 and support member 44 is acted upon with roller 46 to the cam 16 of the drive shaft 12 out.
  • groove 56 In the outer casing of the plunger 40, at least one extending in the direction of the longitudinal axis 41 groove 56 is arranged, which preferably at least in cross section is approximately circular section shaped. In the groove 56 engages at least approximately radially to the longitudinal axis 41 of the plunger 40, a ball 58 with a part of its circumference, which is fixed in the pump housing 10 in the tangential direction to the plunger 40.
  • the high-pressure pump is shown according to a first embodiment, in which the ball 58 is movably guided in a receptacle 60 in the direction of the longitudinal axis 41 of the plunger 40.
  • the receptacle 60 has as in FIGS.
  • FIG. 2 and 4 1 illustrates a channel-shaped recess 62, which is at least substantially prismatic in cross-section perpendicular to the longitudinal axis 41 of the plunger 40 and has two mutually opposite oblique walls against which the ball 58 abuts.
  • the ball 58 dives with part of its circumference in the recess 62 and is thereby fixed in the tangential direction of the plunger 40, so that the plunger 40 is secured by the ball 58 against rotation about its longitudinal axis 41.
  • the ball 58 rolls both in the groove 56 of the plunger 40 and in the recess 62 of the receptacle 60, so that only a small rolling friction occurs.
  • the recording 60 is like in the FIGS. 2 and 3 represented for example in a at least approximately radially with respect to the longitudinal axis 41 of the plunger 40 arranged bore 64 in the base body 14 of the pump housing 10 is inserted.
  • the receptacle 60 is cylindrical in shape, on the tappet 40 facing the inside of the recess 62 is formed.
  • the bore 64 is closed to the outside of the main body 14 of the pump housing 10 by means of a plug 66.
  • a prestressed spring 68 for example a helical compression spring, clamped by the displaceable in the bore 64 receptacle 60 and thus the ball 58th is pressed towards the plunger 40.
  • an elastic sealing ring 70 for example, an O-ring, be arranged to seal the interior of the pump housing 10 to the outside. It can be provided that the plug 66 is screwed or pressed into the bore 64. In addition, it can be provided that the flange part 15 at least partially covers the bore 64 in a state assembled with the base body 14 and thus secures the stopper 66 in the bore 64.
  • the receptacle 60 with the ball 58, the plug 66 and the spring 68 are inserted before the assembly of the pump housing 10 in the bore 64 from the outside of the base body 14 forth. When mounting the receptacle 60, it must be ensured that its recess 62 is aligned exactly parallel to the groove 56 of the plunger 40 in order to allow the lifting movement of the plunger 40 with the least possible friction.
  • the depth of the groove 56 in the plunger 40 and thus the immersion depth of the ball 58 in the groove 56 and the bias of the spring 68 determine the magnitude of the torque against which the plunger 40 can be secured against rotation.
  • FIG. 5 is the high-pressure pump according to a second embodiment shown, in which the basic structure of the high-pressure pump is the same as in the first embodiment, but the receptacle 160 is modified for the ball 58.
  • the receptacle 160 has on its side facing the plunger 40 on a kugelkalottenförmige recess 162 in which the ball 58 is rotatably mounted.
  • the receptacle 160 is in a blind bore of the Hole 64 in the base body 14 of the pump housing 10 occluding stopper 166 slidably inserted. Between the plug 166 and the receptacle 160, the prestressed spring 68 is arranged.
  • An advantage of the embodiment of the high pressure pump according to the second embodiment is that the receptacle 160 is formed simpler than in the first embodiment and that the receptacle 160 can be used in any rotational positions in the pump housing 10. However, in the second embodiment, only between the ball 58 and the plunger 40 rolling friction exists, while between the ball 58 and the receptacle 160 is sliding friction.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)

Abstract

The pump has a pump piston (20) that is indirectly supported in a drive shaft by a hollow cylindrical tappet (40). The tappet is displaceably guided in a bore (42) of a part of a base plate (14) in a direction of the longitudinal axis (21) of the piston. The tappet has a groove (56) running in the direction of a longitudinal axis (41) of the tappet. A ball (58) is indirectly fixed in a part of the plate in a tangential direction to the tappet and is engaged in the groove approximately radial to the longitudinal axis (41). A rolling friction exists between the ball and the tappet.

Description

Stand der TechnikState of the art

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

Eine solche Hochdruckpumpe ist durch die DE 199 07 311 A1 bekannt. Diese Hochdruckpumpe weist ein Pumpengehäuse und wenigstens ein im Pumpengehäuse angeordnetes Pumpenelement auf. Das Pumpenelement weist einen durch eine Antriebswelle der Hochdruckpumpe in einer Hubbewegung angetriebenen Pumpenkolben auf. Der Pumpenkolben ist in einer Zylinderbohrung eines Pumpengehäuseteils der Hochdruckpumpe dicht geführt und begrenzt in der Zylinderbohrung einen Pumpenarbeitsraum. Der Pumpenkolben stützt sich zumindest mittelbar über einen hohlzylinderförmigen Stößel an der Antriebswelle ab. Der Stößel ist in einer Bohrung eines Pumpengehäuseheils in Richtung der Längsachse des Pumpenkolbens verschiebbar geführt. Unter Umständen kann es zu einer Verdrehung des Stößels um seine Längsachse in der Bohrung kommen, wodurch ein erhöhter Verschleiss des Stößels und/oder des Pumpengehäuses sowie gegebenenfalls weiterer Teile der Hochdruckpumpe verursacht wird. Übliche Verdrehsicherungen für den Stößel sind aufwendig in der Herstellung und Montage.Such a high-pressure pump is through the DE 199 07 311 A1 known. This high-pressure pump has a pump housing and at least one pump element arranged in the pump element. The pump element has a driven by a drive shaft of the high pressure pump in a stroke pump piston. The pump piston is tightly guided in a cylinder bore of a pump housing part of the high-pressure pump and delimits a pump working space in the cylinder bore. The pump piston is supported at least indirectly via a hollow-cylindrical ram on the drive shaft. The plunger is slidably guided in a bore of a pump housing in the direction of the longitudinal axis of the pump piston. Under certain circumstances, there may be a rotation of the plunger about its longitudinal axis in the bore, whereby an increased wear of the plunger and / or the pump housing and possibly other parts of the high-pressure pump is caused. Conventional anti-rotation for the ram are expensive to manufacture and assembly.

Vorteile der ErfindungAdvantages of the invention

Die erfindungsgemäße Hochdruckpumpe mit den Merkmalen gemäß Anspruch 1 hat demgegenüber den Vorteil, dass eine Verdrehsicherung des Stößels mit einfachen Mitteln gewährleistet ist. Bei der Kugel handelt es sich um ein Standardteil, das als Zulieferteil kostengünstig erworben werden kann.The high pressure pump according to the invention with the features of claim 1 has the advantage that an anti-rotation of the plunger is ensured by simple means. The ball is a standard part that can be purchased inexpensively as a vendor.

In den abhängigen Ansprüchen sind vorteilhafte Ausgestaltungen und Weiterbildungen der erfindungsgemäßen Hochdruckpumpe angegeben. Durch die Ausbildung gemäß Anspruch 2 ist eine geringe Reibung bei der Verdrehsicherung des Stößels erreicht, da zumindest an einer Abstützung der Kugel am Stößel Rollreibung vorliegt. Durch die Ausbildung gemäß Anspruch 3 wird eine sichere Anlage der Kugel in der Nut des Stößels erreicht. Durch die Ausbildung gemäß Anspruch 4 wird eine besonders geringe Reibung erreicht, da sowohl zwischen der Kugel und dem Stößel als auch zwischen der Kugel und der Aufnahme Rollreibung vorliegt. Durch die Ausbildung gemäß Anspruch 8 ist eine besonders einfache Montage der Aufnahme und der Kugel ermöglicht.In the dependent claims advantageous refinements and developments of the high pressure pump according to the invention are given. Due to the design according to claim 2, a low friction in the rotation of the plunger is achieved because there is at least on a support of the ball on the plunger rolling friction. Due to the design according to claim 3, a safe investment of the ball is achieved in the groove of the plunger. The embodiment according to claim 4, a particularly low friction is achieved because there is rolling friction between both the ball and the plunger and between the ball and the recording. The embodiment according to claim 8, a particularly simple mounting of the receptacle and the ball is possible.

Zeichnungdrawing

Zwei Ausführungsbeispiele der Erfindung sind in der Zeichnung dargestellt und in der nachfolgenden Beschreibung näher erläutert. Es zeigen Figur 1 eine Hochdruckpumpe für eine Kraftstoffeinspritzeinrichtung einer Brennkraftmaschine in einem Längsschnitt, Figur 2 einen in Figur 1 mit II bezeichneten Ausschnitt der Hochdruckpumpe in vergrößerter Darstellung gemäß einem ersten Ausführungsbeispiel, Figur 3 die Hochdruckpumpe in einem Schnitt entlang Linie III-III in Figur 2, Figur 4 einen in Figur 3 mit IV bezeichneten Ausschnitt in nochmals vergrößerter Darstellung und Figur 5 den Ausschnitt II der Hochdruckpumpe gemäß einem zweiten Ausführungsbeispiel.Two embodiments of the invention are illustrated in the drawing and explained in more detail in the following description. Show it FIG. 1 a high-pressure pump for a fuel injection device of an internal combustion engine in a longitudinal section, FIG. 2 one in FIG. 1 with II designated section of the high pressure pump in an enlarged view according to a first embodiment, FIG. 3 the high-pressure pump in a section along line III-III in FIG. 2, FIG. 4 one in FIG. 3 with IV designated section in again enlarged view and FIG. 5 the detail II of the high pressure pump according to a second embodiment.

Beschreibung der AusführungsbeispieleDescription of the embodiments

In den Figuren 1 bis 5 ist eine Hochdruckpumpe für eine Kraftstoffeinspritzeinrichtung einer Brennkraftmaschine dargestellt. Die Hochdruckpumpe weist ein mehrteiliges Pumpengehäuse 10 auf, in dem eine durch die Brennkraftmaschine rotierend angetriebene Antriebswelle 12 angeordnet ist. Die Antriebswelle 12 ist beispielsweise über zwei in Richtung der Drehachse 13 der Antriebswelle 12 voneinander beabstandete Lagerstellen drehbar gelagert. Die Lagerstellen können in verschiedenen Teilen des Pumpengehäuses 10 angeordnet sein, beispielsweise kann eine erste Lagerstelle in einem Grundkörper 14 des Pumpengehäuses 10 und eine zweite Lagerstelle in einem mit dem Grundkörper 14 verbundenen Flanschteil 15 angeordnet sein.In the FIGS. 1 to 5 a high pressure pump for a fuel injector of an internal combustion engine is shown. The high-pressure pump has a multipart pump housing 10 in which a drive shaft 12 driven in rotation by the internal combustion engine is arranged. The drive shaft 12 is rotatably supported, for example, via two bearing points spaced apart from one another in the direction of the axis of rotation 13 of the drive shaft 12. The bearings can be arranged in different parts of the pump housing 10, for example, a first bearing point in a base body 14 of the pump housing 10 and a second bearing point can be arranged in a connected to the base body 14 flange 15.

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

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

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

Im Außenmantel des Stößels 40 ist wenigstens eine in Richtung von dessen Längsachse 41 verlaufende Nut 56 angeordnet, die vorzugsweise im Querschnitt zumindest annähernd kreisabschnittförmig geformt ist. In die Nut 56 greift zumindest annähernd radial zur Längsachse 41 des Stößels 40 eine Kugel 58 mit einem Teil ihres Umfangs ein, die im Pumpengehäuse 10 in tangentialer Richtung zum Stößel 40 fixiert ist. In den Figuren 2 bis 4 ist die Hochdruckpumpe gemäß einem ersten Ausführungsbeispiel dargestellt, bei dem die Kugel 58 in einer Aufnahme 60 in Richtung der Längsachse 41 des Stößels 40 beweglich geführt ist. Die Aufnahme 60 weist dabei wie in Figur 2 und 4 dargestellt eine rinnenförmige Vertiefung 62 auf, die im Querschnitt senkrecht zur Längsachse 41 des Stößels 40 zumindest im wesentlichen prismatisch ausgebildet ist und zwei einander gegenüberliegende schräge Wände aufweist, an denen die Kugel 58 jeweils anliegt. Die Kugel 58 taucht mit einem Teil ihres Umfangs in die Vertiefung 62 ein und ist dadurch in tangentialer Richtung des Stößels 40 fixiert, so dass der Stößel 40 durch die Kugel 58 gegen Verdrehen um seine Längsachse 41 gesichert ist. Bei der Hubbewegung des Stößels 40 zusammen mit dem Pumpenkolben 20 rollt die Kugel 58 sowohl in der Nut 56 des Stößels 40 als auch in der Vertiefung 62 der Aufnahme 60 ab, so dass nur eine geringe Rollreibung auftritt.In the outer casing of the plunger 40, at least one extending in the direction of the longitudinal axis 41 groove 56 is arranged, which preferably at least in cross section is approximately circular section shaped. In the groove 56 engages at least approximately radially to the longitudinal axis 41 of the plunger 40, a ball 58 with a part of its circumference, which is fixed in the pump housing 10 in the tangential direction to the plunger 40. In the FIGS. 2 to 4 the high-pressure pump is shown according to a first embodiment, in which the ball 58 is movably guided in a receptacle 60 in the direction of the longitudinal axis 41 of the plunger 40. The receptacle 60 has as in FIGS. 2 and 4 1 illustrates a channel-shaped recess 62, which is at least substantially prismatic in cross-section perpendicular to the longitudinal axis 41 of the plunger 40 and has two mutually opposite oblique walls against which the ball 58 abuts. The ball 58 dives with part of its circumference in the recess 62 and is thereby fixed in the tangential direction of the plunger 40, so that the plunger 40 is secured by the ball 58 against rotation about its longitudinal axis 41. During the lifting movement of the plunger 40 together with the pump piston 20, the ball 58 rolls both in the groove 56 of the plunger 40 and in the recess 62 of the receptacle 60, so that only a small rolling friction occurs.

Die Aufnahme 60 ist wie in den Figuren 2 und 3 dargestellt beispielsweise in einer zumindest annähernd radial bezüglich der Längsachse 41 des Stößels 40 angeordneten Bohrung 64 im Grundkörper 14 des Pumpengehäuses 10 eingesetzt. Die Aufnahme 60 ist dabei zylinderförmig ausgebildet, wobei auf deren dem Stößel 40 zugewandten Innenseite die Vertiefung 62 ausgebildet ist. Die Bohrung 64 ist zur Außenseite des Grundkörpers 14 des Pumpengehäuses 10 hin mittels eines Stopfens 66 verschlossen. Zwischen dem Stopfen 66 und der Aufnahme 60 ist vorzugsweise eine vorgespannte Feder 68, beispielsweise eine Schraubendruckfeder, eingespannt, durch die die in der Bohrung 64 verschiebbare Aufnahme 60 und damit die Kugel 58 zum Stößel 40 hin gepresst wird. In einer Ringnut des Stopfens 66 kann ein elastischer Dichtring 70, beispielsweise ein O-Ring, angeordnet sein, um das Innere des Pumpengehäuses 10 nach außen abzudichten. Es kann vorgesehen sein, dass der Stopfen 66 in die Bohrung 64 eingeschraubt oder eingepresst ist. Außerdem kann vorgesehen sein, dass das Flanschteil 15 in mit dem Grundkörper 14 zusammengebautem Zustand die Bohrung 64 zumindest teilweise überdeckt und somit den Stopfen 66 in der Bohrung 64 sichert. Die Aufnahme 60 mit der Kugel 58, der Stopfen 66 und die Feder 68 werden vor dem Zusammenbau des Pumpengehäuses 10 in die Bohrung 64 von der Außenseite des Grundkörpers 14 her eingesetzt. Bei der Montage der Aufnahme 60 muss sichergestellt sein, dass deren Vertiefung 62 exakt parallel zur Nut 56 des Stößels 40 ausgerichtet ist, um die Hubbewegung des Stößels 40 bei geringstmöglicher Reibung zu ermöglichen.The recording 60 is like in the FIGS. 2 and 3 represented for example in a at least approximately radially with respect to the longitudinal axis 41 of the plunger 40 arranged bore 64 in the base body 14 of the pump housing 10 is inserted. The receptacle 60 is cylindrical in shape, on the tappet 40 facing the inside of the recess 62 is formed. The bore 64 is closed to the outside of the main body 14 of the pump housing 10 by means of a plug 66. Between the plug 66 and the receptacle 60 is preferably a prestressed spring 68, for example a helical compression spring, clamped by the displaceable in the bore 64 receptacle 60 and thus the ball 58th is pressed towards the plunger 40. In an annular groove of the plug 66 may be an elastic sealing ring 70, for example, an O-ring, be arranged to seal the interior of the pump housing 10 to the outside. It can be provided that the plug 66 is screwed or pressed into the bore 64. In addition, it can be provided that the flange part 15 at least partially covers the bore 64 in a state assembled with the base body 14 and thus secures the stopper 66 in the bore 64. The receptacle 60 with the ball 58, the plug 66 and the spring 68 are inserted before the assembly of the pump housing 10 in the bore 64 from the outside of the base body 14 forth. When mounting the receptacle 60, it must be ensured that its recess 62 is aligned exactly parallel to the groove 56 of the plunger 40 in order to allow the lifting movement of the plunger 40 with the least possible friction.

Die Tiefe der Nut 56 im Stößel 40 und damit die Eintauchtiefe der Kugel 58 in die Nut 56 sowie die Vorspannung der Feder 68 bestimmen die Größe des Drehmoments gegen das der Stößel 40 gegen Verdrehung gesichert werden kann. Je größer die Tiefe der Nut 56 und damit die Eintauchtiefe der Kugel 58 in diese ist und je größer die Vorspannung der Feder 68 ist, desto größer ist das Drehmoment, gegen das der Stößel 40 gegen Verdrehung gesichert werden kann.The depth of the groove 56 in the plunger 40 and thus the immersion depth of the ball 58 in the groove 56 and the bias of the spring 68 determine the magnitude of the torque against which the plunger 40 can be secured against rotation. The greater the depth of the groove 56 and thus the immersion depth of the ball 58 in this and the greater the bias of the spring 68, the greater the torque against which the plunger 40 can be secured against rotation.

In Figur 5 ist die Hochdruckpumpe gemäß einem zweiten Ausführungsbeispiel dargestellt, bei dem der grundsätzliche Aufbau der Hochdruckpumpe gleich wie beim ersten Ausführungsbeispiel ist, jedoch die Aufnahme 160 für die Kugel 58 modifiziert ist. Die Aufnahme 160 weist auf ihrer dem Stößel 40 zugewandten Seite eine kugelkalottenförmige Vertiefung 162 auf, in der die Kugel 58 drehbar gelagert ist. Die Aufnahme 160 ist in eine Sackbohrung eines die Bohrung 64 im Grundkörper 14 des Pumpengehäuses 10 verschließenden Stopfens 166 verschiebbar eingesetzt. Zwischen dem Stopfen 166 und der Aufnahme 160 ist die vorgespannte Feder 68 angeordnet. Vorteilhaft bei der Ausführung der Hochdruckpumpe gemäß dem zweiten Ausführungsbeispiel ist, dass die Aufnahme 160 einfacher ausgebildet ist als beim ersten Ausführungsbeispiel und dass die Aufnahme 160 in beliebigen Drehstellungen in das Pumpengehäuse 10 eingesetzt werden kann. Allerdings ist beim zweiten Ausführungsbeispiel nur zwischen der Kugel 58 und dem Stößel 40 Rollreibung vorhanden, während zwischen der Kugel 58 und der Aufnahme 160 Gleitreibung vorliegt.In FIG. 5 is the high-pressure pump according to a second embodiment shown, in which the basic structure of the high-pressure pump is the same as in the first embodiment, but the receptacle 160 is modified for the ball 58. The receptacle 160 has on its side facing the plunger 40 on a kugelkalottenförmige recess 162 in which the ball 58 is rotatably mounted. The receptacle 160 is in a blind bore of the Hole 64 in the base body 14 of the pump housing 10 occluding stopper 166 slidably inserted. Between the plug 166 and the receptacle 160, the prestressed spring 68 is arranged. An advantage of the embodiment of the high pressure pump according to the second embodiment is that the receptacle 160 is formed simpler than in the first embodiment and that the receptacle 160 can be used in any rotational positions in the pump housing 10. However, in the second embodiment, only between the ball 58 and the plunger 40 rolling friction exists, while between the ball 58 and the receptacle 160 is sliding friction.

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

Claims (10)

  1. High-pressure pump, in particular for a fuel injection device of an internal combustion engine, with a pump casing (10, 14, 22), with at least one pump element (18) which has a pump piston (20) which is driven in a lifting movement by a drive shaft (12) and which is guided displaceably in a cylinder bore (28) of part of the pump casing (22) and delimits a pump working space (30) in the said cylinder bore, the pump piston (20) being supported at least indirectly via a hollow-cylindrical tappet (40) on the drive shaft (12), the tappet (40) being guided displaceably in a bore (42) of part of the pump casing (14) in the direction of the longitudinal axis (21) of the pump piston (20), characterized in that the tappet (40) has in its outer casing a groove (56) which runs in the direction of its longitudinal axis (41) and into which a ball (58) fixed at least indirectly in part of the pump casing (14) in the tangential direction to the tappet (40) engages, at least approximately radially to the longitudinal axis (41) of the tappet (40), so as to protect the tappet (40) against twisting.
  2. High-pressure pump according to Claim 1, characterized in that rolling friction prevails at least between the ball (58) and the tappet (40).
  3. High-pressure pump according to Claim 1 or 2, characterized in that the ball (58) is pressed into the groove (56) of the tappet (40) at least indirectly by a prestressed spring (68).
  4. High-pressure pump according to Claim 2 or 3, characterized in that the ball (58) is guided movably in the direction of the longitudinal axis (41) of the tappet (40) in a receptacle (60) arranged in the pump-casing part (14).
  5. High-pressure pump according to Claim 4, characterized in that the guide (62) for the ball (58) in the receptacle (60) is of at least approximately prismatic design in cross section perpendicularly to the longitudinal axis (41) of the tappet (40).
  6. High-pressure pump according to Claim 2 or 3, characterized in that the ball (58) is mounted rotatably in a receptacle (160) arranged in the pump-casing part (14).
  7. High-pressure pump according to Claim 6, characterized in that the receptacle (160) has an at least approximately spherical-cap-shaped depression (162) in which the ball (58) is mounted.
  8. High-pressure pump according to one of Claims 4 to 7, characterized in that the receptacle (60; 160) is inserted in a bore (64) in the pump-casing part (14), preferably from an outer side of the pump-casing part (14) which faces away from the bore (42) in which the tappet (40) is guided.
  9. High-pressure pump according to Claim 3, and at least one of Claims 4 to 8, characterized in that the receptacle (60; 160) is movable in an at least approximately radial direction with respect to the longitudinal axis (41) of the tappet (40) and in that the spring (68) acts on that outer side of the receptacle (60; 160) which faces away from the tappet (40).
  10. High-pressure pump according to one of the preceding claims, characterized in that a roller (46), via which the tappet (40) is supported on the drive shaft (12), is at least indirectly mounted rotatably in the tappet (40).
EP06793348A 2005-09-29 2006-09-08 High pressure pump, in particular for a fuel injection device of an internal combustion engine Not-in-force EP1931875B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102005046670A DE102005046670A1 (en) 2005-09-29 2005-09-29 High pressure pump for fuel injection device of internal combustion engine, has ball indirectly fixed in part of base plate in tangential direction to tappet and engaged in groove approximately radial to longitudinal axis of tappet
PCT/EP2006/066162 WO2007036423A1 (en) 2005-09-29 2006-09-08 High pressure pump, in particular for a fuel injection device of an internal combustion engine

Publications (2)

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EP1931875A1 EP1931875A1 (en) 2008-06-18
EP1931875B1 true EP1931875B1 (en) 2010-03-10

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EP (1) EP1931875B1 (en)
AT (1) ATE460584T1 (en)
DE (2) DE102005046670A1 (en)
WO (1) WO2007036423A1 (en)

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DE502006006407D1 (en) 2010-04-22
ATE460584T1 (en) 2010-03-15
DE102005046670A1 (en) 2007-04-05
WO2007036423A1 (en) 2007-04-05
EP1931875A1 (en) 2008-06-18

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