EP1727983B1 - High-pressure pump, in particular for a fuel-injection device in an internal combustion engine - Google Patents

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

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Publication number
EP1727983B1
EP1727983B1 EP05707796A EP05707796A EP1727983B1 EP 1727983 B1 EP1727983 B1 EP 1727983B1 EP 05707796 A EP05707796 A EP 05707796A EP 05707796 A EP05707796 A EP 05707796A EP 1727983 B1 EP1727983 B1 EP 1727983B1
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EP
European Patent Office
Prior art keywords
pump
bore
valve member
housing part
valve
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP05707796A
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German (de)
French (fr)
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EP1727983A1 (en
Inventor
Andreas Dutt
Jochen Aleker
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Robert Bosch GmbH
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Robert Bosch GmbH
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Filing date
Publication date
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Publication of EP1727983A1 publication Critical patent/EP1727983A1/en
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Publication of EP1727983B1 publication Critical patent/EP1727983B1/en
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Classifications

    • 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
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/10—Valves; Arrangement of valves
    • F04B53/1087—Valve seats
    • 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
    • F02M59/46—Valves
    • F02M59/464—Inlet valves of the check valve type
    • 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
    • F02M59/48—Assembling; Disassembling; Replacing
    • F02M59/485—Means for fixing delivery valve casing and barrel to each other or to pump casing
    • 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
    • F04B1/0452—Distribution members, e.g. valves
    • 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
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/10—Valves; Arrangement of valves
    • F04B53/102—Disc valves
    • 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
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/16—Casings; Cylinders; Cylinder liners or heads; Fluid connections

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 in the form of a compressor is through the US 1 445 073 A known.
  • This high-pressure pump has a pump element, with a pump piston guided displaceably in a cylinder bore of a housing part of the high-pressure pump and driven in a stroke movement.
  • the pump piston delimits a pump working space into which a medium is sucked in via an inlet valve during the suction stroke of the pump piston and from which medium is displaced during the delivery stroke of the pump piston.
  • the inlet valve has a piston-shaped valve member which cooperates with a sealing surface with a valve seat for controlling the connection of the pump working space with an inlet.
  • the valve member is acted upon by a closing spring and by the pressure prevailing in the inlet in the opening direction and by the pressure prevailing in the pump working chamber in the closing direction.
  • the valve member is arranged in the pump working space with a head on which the sealing surface is formed, and protrudes out of the pump working space with a shaft adjoining the head.
  • the closing spring is arranged outside the pump working space and engages the shaft.
  • the valve seat is formed on the housing part at the transition of the cylinder bore to a subsequent, smaller diameter bore, wherein the valve member protrudes with its shaft through the bore in a pump working space remote from the housing part and the closing spring is disposed in this region of the housing part.
  • the region of the housing part in which the closing spring is arranged is sealed to the outside of the housing part by means of a closure element, and the inlet opens into this area.
  • a disadvantage of this high pressure pump is that the valve member is not guided and thus the function of the inlet valve is not permanently ensured.
  • the high pressure pump according to the invention with the features of claim 1 has the advantage that the valve member is guided, whereby a secure sealing action of the inlet valve and a low wear of the sealing surface and the valve seat is made possible.
  • the design of the sealing surface according to claim 2 allows a further improvement of the sealing effect of the inlet valve.
  • the housing part of the high pressure pump is used.
  • the high-pressure pump is expensive to manufacture and manufacture and therefore expensive.
  • the pump housing is covered by the valve housing, so that between the housing part of the high pressure pump and the valve housing a complex seal against the high pressure in the pump working space is required.
  • the high pressure pump according to the invention with the features of claim 1 has the advantage that no separate valve housing and thus no seal to the high pressure in the pump working space is required for the inlet valve.
  • only the valve seat needs to be manufactured on the housing part, which can be processed in a simple manner from the inside of the cylinder bore. The valve member is thereby introduced from the inside of the cylinder bore with its shaft ahead and from the cylinder bore opposite the outside of the housing part forth the closing spring is placed and connected to the shaft of the valve member.
  • the embodiment according to claim 2 allows an easy-to-manufacture course of the fuel inlet.
  • the embodiment according to claim 4 allows a guide of the valve member and thus a secure sealing action of the inlet valve and a low wear of the sealing surface and the valve seat.
  • the embodiment according to claim 5 allows a safe sealing effect of the inlet valve even without guiding the valve member.
  • 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 with an inlet valve in an enlarged view according to a non-inventive embodiment
  • FIG. 3 the detail II with an inlet valve according to an embodiment of the invention.
  • the high-pressure pump has a multipart pump housing 10, in which a drive shaft 12, which can be driven in rotation by the internal combustion engine, is rotatably mounted.
  • the drive shaft 12 is rotatably supported in a base body 14 of the housing 10 via two spaced apart in the direction of the axis of rotation 13 of the drive shaft 12 bearings.
  • the main body 14 of the housing 10 may in turn be designed in several parts and the bearings may be arranged in different parts of the main body 14.
  • the main body 14 is made of a material with the required for the storage of the drive shaft 12 strength, in particular of light metal such as aluminum or an aluminum alloy.
  • the drive shaft 12 at least one eccentric to its axis of rotation 13 section 16 or a cam, wherein the cam 16 as a multiple cam can be trained.
  • the high-pressure pump has at least one or more pump elements 10 arranged in the pump housing 18, each with a pump piston 20 which is driven by the eccentric portion 16 or the cam 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 housing part 22 connected to the main body 14 is provided, which is designed as a cylinder head.
  • the housing part 22 has a voltage applied to an outer side of the base body 14 and a flange 24 through an opening 15 in the base body 14 to the drive shaft 12 through projecting approximately cylindrical projection 26 with respect to the flange 24 of smaller diameter.
  • the pump piston 20 is guided in a displaceable manner in a cylinder bore 28 formed in the housing part 22 and limited with its end facing away from the drive shaft 12 in the cylinder bore 28 a pump chamber 30.
  • the pump chamber 30 is disposed in the region of the flange 24 of the housing part 22 and the cylinder bore 28 extends up to the drive shaft 12 facing the end of the projection 26 of the housing part 22.
  • the pump working chamber 30 has a running in the pump housing 10 fuel inlet channel 32 is in communication with a fuel inlet, for example a feed pump. 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.
  • a high-pressure accumulator 110 are one or preferably more on the cylinders of the Internal combustion engine arranged injectors 120 connected by the fuel is injected into the cylinders of the internal combustion engine.
  • injectors 120 connected by the 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.
  • the housing part 22 is made of a material with high strength, since there is 20 high pressure in the pump working chamber 30 during the delivery stroke of the pump piston.
  • the housing part 22 may for example consist of steel or gray cast iron.
  • a support member may be arranged in the form of a plunger 40, via which the pump piston 20 is at least indirectly supported on the cam 16.
  • the pump piston 20 is coupled to the plunger 40 in a manner not shown in the direction of its longitudinal axis 21.
  • the plunger 40 may be supported directly on the eccentric portion 16 or cam.
  • a ring 42 can be rotatably mounted on the section 16 of the drive shaft 12, against which the plunger 40 rests.
  • the ring 42 has a flattening 44 for each pump element 18 against which the plunger 40 rests.
  • the plunger 40 is slidably mounted in the base body 14 of the pump housing 10 or on the housing part 22 and takes in the implementation of the rotational movement of the drive shaft 12 in the lifting movement of the pump piston 20 occurring transverse forces, so that they do not act on the pump piston 20.
  • a prestressed return spring 48 At the plunger 40 engages a prestressed return spring 48, through which the plunger 40 and the associated pump piston 20 are pressed to the section 16 through. The following is based on the FIG. 2 the intake valve 34 described according to a non-inventive embodiment.
  • a valve seat 52 is formed, which is for example at least approximately frusto-conical.
  • a further bore 54 with a much larger diameter.
  • the inlet valve 34 has a piston-shaped valve member 56, which has a head 58 which is arranged in the pump working chamber 30 and thus in the cylinder bore 28.
  • a sealing surface 60 is formed, which is preferably formed convex.
  • the sealing surface 60 may be formed at least approximately spherical segment-shaped.
  • the head 58 of the valve member 56 is adjoined by a shaft 62, which has a smaller diameter than the head 58 and projects through the bore 50 into the further bore 54, which forms a region of the housing part 22 facing away from the pump working space 30.
  • a prestressed closing spring 64 is arranged, which is designed as a helical compression spring.
  • the closing spring 64 is supported, on the one hand, on an annular shoulder 55 on the housing part 22 formed at the transition of the bore 50 into the further bore 54 and, on the other hand, via a spring plate 66 connected to the shaft 62 on the valve member 56.
  • valve member 56 By the closing spring 64, the valve member 56 is thus acted upon in the closing direction, wherein the valve member 56 rests in its closed position with its sealing surface 60 on the valve seat 52.
  • the diameter of the shaft 62 of the valve member 56 is smaller than the diameter of the bore 50, so that between the shaft 62 and the bore 50, a flow cross-section in the form of an annular gap 63 remains.
  • the further bore 54 is sealed to the outside of the housing part 22 by means of a closure element 68, which is inserted into the bore 54.
  • the closure element 68 may, for example, as in FIG. 2 shown formed as a screw plug, which has an external thread with which it is screwed into an internal thread of the bore 54.
  • the closure element 68 can also be connected in a different way to the housing part 22, for example, be pressed into the bore 54 or be welded to the housing part 22.
  • an elastic sealing element 70 for example in the form of an O-ring, is clamped for sealing purposes.
  • the closure element 68 has on its side facing the valve member 56 a recess 69, for example in the form of a blind bore, in which the shaft 62 of the valve member 56 and the surrounding closing spring 64 are arranged.
  • the closure element 68 does not extend completely to the annular shoulder at the transition from the further bore 54 to the bore 50, so that in the further bore 54 by the closure member 68, a space 72 is limited.
  • In the space 72 opens the fuel inlet channel 32, which is in communication with the annular gap 63 between the bore 50 and the valve member 56.
  • space 72 there is an increased inlet pressure, which acts on the disposed within the valve seat 52 face of the head 58 of the valve member 56 and generates a force in the opening direction on the valve member 56. Due to the pressure prevailing in the pump working chamber 30, which acts on the end face of the head 58 of the valve member 56 facing away from the valve seat 52, a force is generated in the closing direction on the valve member 56.
  • the bores 50, 54 and the valve seat 52 can be produced on the housing part 22 in a simple manner, since the valve seat 52 is accessible to the assembly of the housing part 22 with the base body 14 from the inside of the cylinder bore 28 for processing.
  • the valve member 56 is inserted before the assembly of the housing part 22 with the base body 14 from the inside of the cylinder bore 28 with its shaft 62 ahead so that it protrudes through the bore 50 to the outside, then the closing spring 64 and the spring plate 66 are mounted and finally the closure element 68 is inserted.
  • the inlet valve 34 is shown according to an embodiment of the invention, compared to the embodiment according to FIG. 2 is modified such that one is modified, that a guide for the valve member 56 is provided.
  • the cylinder bore 28 closes as in the embodiment according to FIG. 2 the bore 50 with a smaller diameter, but here has a opening into the cylinder bore 28 first portion 150 and an opening into the further bore 54 second portion 250 with respect to the first portion 150 of smaller diameter.
  • the transition from the cylinder bore 28 into the first bore portion 150 of the valve seat 52 is arranged, which is for example at least approximately frusto-conical.
  • the transition from the first bore portion 150 to the second bore portion 250 may be at least approximately frusto-conical.
  • the bore portions 150, 250 are arranged in a projection 74 of the housing part 22, which projects into a recess 76 formed on the outside of the housing part 22.
  • the first bore section 150 is connected to the recess 76 via at least one, preferably a plurality of bores 78 in the projection 74 of the housing part 22.
  • the valve member 56 has arranged in the pump working chamber 30 head 58 with the sealing surface 60, which may for example be convexly curved, in particular at least approximately spherical segment-shaped, or at least approximately frusto-conical.
  • the smaller diameter shaft 62 of the valve member 56 connects, wherein the shaft 62 in the second Bore portion 250 is slidably guided with little play and between the first bore portion 150 and the shaft 62, a flow cross-section in the form of an annular gap 63 is present.
  • the recess 76 is sealed to the outside by means of a closure member 68, wherein the closure member 68 may be screwed to the housing part 22, pressed or welded.
  • a space 72 is limited in the recess 76, in which the fuel inlet 32 opens, the space 72 is connected via the holes 78 with the shaft 62 of the valve member 56 surrounding the annular gap 63.
  • the inlet valve 34 When the inlet valve 34 is open, fuel flows out of the recess 76 via the holes 78 into the annular gap 63 and out of this into the pump working space 30.
  • the valve member 56 is guided with its shaft 62 in the second bore section 250.

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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)
  • Details Of Reciprocating Pumps (AREA)

Abstract

A high-pressure pump has at least one pump element, with a pump piston which is guided displaceably in a cylinder bore of a housing part of the high-pressure pump and is driven in a reciprocating motion and defines a pump work chamber in the cylinder bore, into which chamber fuel is aspirated via an inlet valve in the intake stroke of the pump piston. The inlet valve has a pistonlike valve member, which with a sealing face cooperates with a valve seat for controlling the communication of the pump work chamber with the fuel inlet. The valve member is disposed with a head, on which the sealing face is embodied, in the pump work chamber and protrudes out of the pump work chamber with a shaft adjoining the head. The valve seat is formed in the housing part at a transition from the cylinder bore to a bore of smaller diameter adjoining the cylinder bore. With its shaft, the valve member protrudes through the bore into a region of the housing part remote from the pump work chamber, in which region a closing spring is disposed that engages the shaft of the valve member.

Description

Die Erfindung betrifft eine Hochdruckpumpe, insbesondere für eine Kraftstoffeinspritzeinrichtung einer Brennkraftmaschine, nach dem Oberbegriff 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 in Form eines Kompressors ist durch die US 1 445 073 A bekannt. Diese Hochdruckpumpe weist ein Pumpenelement auf, mit einem in einer Zylinderbohrung eines Gehäuseteils der Hochdruckpumpe verschiebbar geführten, in einer Hubbewegung angetriebenen Pumpenkolben. Der Pumpenkolben begrenzt in der Zylinderbohrung einen Pumpenarbeitsraum, in den beim Saughub des Pumpenkolbens über ein Einlassventil ein Medium angesaugt wird und aus dem beim Förderhub des Pumpenkolbens Medium verdrängt wird. Das Einlassventil weist ein kolbenförmiges Ventilglied auf, das mit einer Dichtfläche mit einem Ventilsitz zur Steuerung der Verbindung des Pumpenarbeitsraums mit einem Zulauf zusammenwirkt. Das Ventilglied ist durch eine Schließfeder und durch den im Zulauf herrschenden Druck in Öffnungsrichtung und durch den im Pumpenarbeitsraum herrschenden Druck in Schließrichtung beaufschlagt. Das Ventilglied ist mit einem Kopf, an dem die Dichtfläche ausgebildet ist, im Pumpenarbeitsraum angeordnet und ragt mit einem an den Kopf anschließenden Schaft aus dem Pumpenarbeitsraum heraus. Die Schließfeder ist außerhalb des Pumpenarbeitsraums angeordnet und greift am Schaft an. Der Ventilsitz ist am Gehäuseteil am Übergang der Zylinderbohrung zu einer an diese anschließenden, im Durchmesser kleineren Bohrung gebildet, wobei das Ventilglied mit seinem Schaft durch die Bohrung in einen dem Pumpenarbeitsraum abgewandten Bereich des Gehäuseteils hindurchragt und die Schließfeder in diesem Bereich des Gehäuseteils angeordnet ist. Der Bereich des Gehäuseteils, in dem die Schließfeder angeordnet ist, ist zur Außenseite des Gehäuseteils mittels eines Verschlusselements dicht verschlossen und in diesen Bereich mündet der Zulauf. Nachteilig bei dieser Hochdruckpumpe ist, dass das Ventilglied nicht geführt ist und somit die Funktion des Einlassventils nicht dauerhaft sichergestellt ist.Such a high pressure pump in the form of a compressor is through the US 1 445 073 A known. This high-pressure pump has a pump element, with a pump piston guided displaceably in a cylinder bore of a housing part of the high-pressure pump and driven in a stroke movement. In the cylinder bore, the pump piston delimits a pump working space into which a medium is sucked in via an inlet valve during the suction stroke of the pump piston and from which medium is displaced during the delivery stroke of the pump piston. The inlet valve has a piston-shaped valve member which cooperates with a sealing surface with a valve seat for controlling the connection of the pump working space with an inlet. The valve member is acted upon by a closing spring and by the pressure prevailing in the inlet in the opening direction and by the pressure prevailing in the pump working chamber in the closing direction. The valve member is arranged in the pump working space with a head on which the sealing surface is formed, and protrudes out of the pump working space with a shaft adjoining the head. The closing spring is arranged outside the pump working space and engages the shaft. The valve seat is formed on the housing part at the transition of the cylinder bore to a subsequent, smaller diameter bore, wherein the valve member protrudes with its shaft through the bore in a pump working space remote from the housing part and the closing spring is disposed in this region of the housing part. The region of the housing part in which the closing spring is arranged is sealed to the outside of the housing part by means of a closure element, and the inlet opens into this area. A disadvantage of this high pressure pump is that the valve member is not guided and thus the function of the inlet valve is not permanently ensured.

Vorteile der ErfindungAdvantages of the invention

Die erfindungsgemäße Hochdruckpumpe mit den Merkmalen des Anspruchs 1 hat demgegenüber den Vorteil, dass das Ventilglied geführt ist, wodurch eine sichere Dichtwirkung des Einlassventils sowie ein geringer Verschleiß der Dichtfläche sowie des Ventilsitzes ermöglicht ist.The high pressure pump according to the invention with the features of claim 1 has the advantage that the valve member is guided, whereby a secure sealing action of the inlet valve and a low wear of the sealing surface and the valve seat is made possible.

Die Ausbildung der Dichtfläche gemäß Anspruch 2 ermöglicht eine weitere Verbesserung der Dichtwirkung des Einlassventils. das Gehäuseteil der Hochdruckpumpe eingesetzt wird.The design of the sealing surface according to claim 2 allows a further improvement of the sealing effect of the inlet valve. the housing part of the high pressure pump is used.

Aufgrund des separaten Ventilgehäuses ist die Hochdruckpumpe in der Fertigung und Herstellung aufwendig und somit teuer. Außerdem wird durch das Ventilgehäuse der Pumpenarbeitsraum abgedeckt, so dass zwischen dem Gehäuseteil der Hochdruckpumpe und dem Ventilgehäuse eine aufwendige Abdichtung gegen den Hochdruck im Pumpenarbeitsraum erforderlich ist.Due to the separate valve housing, the high-pressure pump is expensive to manufacture and manufacture and therefore expensive. In addition, the pump housing is covered by the valve housing, so that between the housing part of the high pressure pump and the valve housing a complex seal against the high pressure in the pump working space is required.

Vorteile der ErfindungAdvantages of the invention

Die erfindungsgemäße Hochdruckpumpe mit den Merkmalen gemäß Anspruch 1 hat demgegenüber den Vorteil, dass für das Einlassventil kein separates Ventilgehäuse und damit auch keine Abdichtung zum Hochdruck im Pumpenarbeitsraum erforderlich ist. Am Gehäuseteil braucht dabei zusätzlich nur der Ventilsitz hergestellt zu werden, der auf einfache Weise von der Innenseite der Zylinderbohrung her bearbeitet werden kann. Das Ventilglied wird dabei von der Innenseite der Zylinderbohrung her mit seinem Schaft voraus eingeführt und von der der Zylinderbohrung gegenüberliegenden Außenseite des Gehäuseteils her wird die Schließfeder aufgesetzt und mit dem Schaft des Ventilglieds verbunden.The high pressure pump according to the invention with the features of claim 1 has the advantage that no separate valve housing and thus no seal to the high pressure in the pump working space is required for the inlet valve. In addition, only the valve seat needs to be manufactured on the housing part, which can be processed in a simple manner from the inside of the cylinder bore. The valve member is thereby introduced from the inside of the cylinder bore with its shaft ahead and from the cylinder bore opposite the outside of the housing part forth the closing spring is placed and connected to the shaft of the valve member.

In den abhängigen Ansprüchen sind vorteilhafte Ausgestaltungen und Weiterbildungen der erfindungsgemäßen Hochdruckpumpe angegeben. Die Ausführung gemäß Anspruch 2 ermöglicht einen einfach zu fertigenden Verlauf des Kraftstoffzulaufs. Die Ausbildung gemäß Anspruch 4 ermöglicht eine Führung des Ventilglieds und damit eine sichere Dichtwirkung des Einlassventils sowie einen geringen Verschleiß der Dichtfläche sowie des Ventilsitzes. Die Ausbildung gemäß Anspruch 5 ermöglicht auch ohne Führung des Ventilglieds eine sichere Dichtwirkung des Einlassventils.In the dependent claims advantageous refinements and developments of the high pressure pump according to the invention are given. The embodiment according to claim 2 allows an easy-to-manufacture course of the fuel inlet. The embodiment according to claim 4 allows a guide of the valve member and thus a secure sealing action of the inlet valve and a low wear of the sealing surface and the valve seat. The embodiment according to claim 5 allows a safe sealing effect of the inlet valve even without guiding the valve member.

Zeichnungdrawing

Ein Ausführungsbeispiel der Erfindung ist 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 mit einem Einlassventil in vergrößerter Darstellung gemäß einer nicht erfindungsgemäßen Ausführung und Figur 3 den Ausschnitt II mit einem Einlassventil gemäß einem Ausführungsbeispiel der Erfindung.An embodiment of the invention is 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 with an inlet valve in an enlarged view according to a non-inventive embodiment and FIG. 3 the detail II with an inlet valve according to an embodiment of the invention.

Beschreibung der AusführungsbeispieleDescription of the embodiments

In den Figuren 1 bis 3 ist eine Hochdruckpumpe für eine Kraftstoffeinspritzeinrichtung einer Brennkraftmaschine dargestellt. Die Hochdruckpumpe weist ein mehrteiliges Pumpengehäuse 10 auf, in dem eine durch die Brennkraftmaschine rotierend antreibbare Antriebswelle 12 drehbar gelagert ist. Die Antriebswelle 12 ist in einem Grundkörper 14 des Gehäuses 10 über zwei in Richtung der Drehachse 13 der Antriebswelle 12 voneinander beabstandete Lagerstellen drehbar gelagert. Der Grundkörper 14 des Gehäuses 10 kann wiederum mehrteilig ausgebildet sein und die Lagerstellen können in verschiedenen Teilen des Grundkörpers 14 angeordnet sein. Der Grundkörper 14 besteht aus einem Werkstoff mit der für die Lagerung der Antriebswelle 12 erforderlichen Festigkeit, insbesondere aus Leichtmetall wie Aluminium oder einer Aluminiumlegierung.In the FIGS. 1 to 3 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, which can be driven in rotation by the internal combustion engine, is rotatably mounted. The drive shaft 12 is rotatably supported in a base body 14 of the housing 10 via two spaced apart in the direction of the axis of rotation 13 of the drive shaft 12 bearings. The main body 14 of the housing 10 may in turn be designed in several parts and the bearings may be arranged in different parts of the main body 14. The main body 14 is made of a material with the required for the storage of the drive shaft 12 strength, in particular of light metal such as aluminum or an aluminum alloy.

In einem zwischen den beiden Lagerstellen liegenden Bereich weist die Antriebswelle 12 wenigstens einen zu ihrer Drehachse 13 exzentrischen Abschnitt 16 oder einen Nocken auf, wobei der Nocken 16 auch als Mehrfachnocken ausgebildet sein kann. Die Hochdruckpumpe weist wenigstens ein oder mehrere im Pumpengehäuse 10 angeordnete Pumpenelemente 18 mit jeweils einem Pumpenkolben 20 auf, der durch den exzentrischen Abschnitt 16 oder den Nocken der Antriebswelle 12 in einer Hubbewegung in zumindest annähernd radialer Richtung zur Drehachse 13 der Antriebswelle 12 angetrieben wird. Im Bereich jedes Pumpenelements 18 ist ein mit dem Grundkörper 14 verbundenes Gehäuseteil 22 vorgesehen, das als Zylinderkopf ausgebildet ist. Das Gehäuseteil 22 weist einen an einer Außenseite des Grundkörpers 14 anliegenden Flansch 24 und einen durch eine Öffnung 15 im Grundkörper 14 zur Antriebswelle 12 hin durchragenden, etwa zylinderförmigen Ansatz 26 mit gegenüber dem Flansch 24 kleinerem Durchmesser auf.In a lying between the two bearing areas, the drive shaft 12 at least one eccentric to its axis of rotation 13 section 16 or a cam, wherein the cam 16 as a multiple cam can be trained. The high-pressure pump has at least one or more pump elements 10 arranged in the pump housing 18, each with a pump piston 20 which is driven by the eccentric portion 16 or the cam 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 housing part 22 connected to the main body 14 is provided, which is designed as a cylinder head. The housing part 22 has a voltage applied to an outer side of the base body 14 and a flange 24 through an opening 15 in the base body 14 to the drive shaft 12 through projecting approximately cylindrical projection 26 with respect to the flange 24 of smaller diameter.

Der Pumpenkolben 20 ist in einer im Gehäuseteil 22 ausgebildeten Zylinderbohrung 28 dicht verschiebbar geführt und begrenzt mit seiner der Antriebswelle 12 abgewandten Stirnseite in der Zylinderbohrung 28 einen Pumpenarbeitsraum 30. Der Pumpenarbeitsraum 30 ist im Bereich des Flansches 24 des Gehäuseteils 22 angeordnet und die Zylinderbohrung 28 verläuft bis zu dem der Antriebswelle 12 zugewandten Ende des Ansatzes 26 des Gehäuseteils 22. 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. Das Gehäuseteil 22 besteht aus einem Werkstoff mit hoher Festigkeit, da im Pumpenarbeitsraum 30 beim Förderhub des Pumpenkolbens 20 Hochdruck herrscht. Das Gehäuseteil 22 kann beispielsweise aus Stahl oder Grauguss bestehen.The pump piston 20 is guided in a displaceable manner in a cylinder bore 28 formed in the housing part 22 and limited with its end facing away from the drive shaft 12 in the cylinder bore 28 a pump chamber 30. The pump chamber 30 is disposed in the region of the flange 24 of the housing part 22 and the cylinder bore 28 extends up to the drive shaft 12 facing the end of the projection 26 of the housing part 22. The pump working chamber 30 has a running in the pump housing 10 fuel inlet channel 32 is in communication with a fuel inlet, for example a feed pump. 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. With the high-pressure accumulator 110 are one or preferably more on the cylinders of the Internal combustion engine arranged injectors 120 connected by the 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. The housing part 22 is made of a material with high strength, since there is 20 high pressure in the pump working chamber 30 during the delivery stroke of the pump piston. The housing part 22 may for example consist of steel or gray cast iron.

Zwischen dem Pumpenkolben 20 und dem exzentrischen Abschnitt 16 oder Nocken der Antriebswelle 12 kann ein Stützelement in Form eines Stößels 40 angeordnet sein, über den sich der Pumpenkolben 20 zumindest mittelbar am Nocken 16 abstützt. Der Pumpenkolben 20 ist dabei mit dem Stößel 40 in nicht näher dargestellter Weise in Richtung seiner Längsachse 21 gekoppelt. Der Stößel 40 kann sich direkt am exzentrischen Abschnitt 16 oder Nocken abstützen. Auf dem Abschnitt 16 der Antriebswelle 12 kann dabei ein Ring 42 drehbar gelagert sein, an dem der Stößel 40 anliegt. Der Ring 42 weist für jedes Pumpenelement 18 eine Abflachung 44 auf, an der der Stößel 40 anliegt. Bei der Drehbewegung der Antriebswelle 12 um ihre Drehachse 13 wird der Pumpenkolben 20 über den Ring 42 und den Stößel 40 in einer Hubbewegung angetrieben, wobei sich der Ring 42 nicht mit der Antriebswelle 12 dreht, sondern ortsfest ist. Der Stößel 40 ist im Grundkörper 14 des Pumpengehäuses 10 oder am Gehäuseteil 22 verschiebbar gelagert und nimmt bei der Umsetzung der Drehbewegung der Antriebswelle 12 in die Hubbewegung des Pumpenkolbens 20 auftretende Querkräfte auf, so dass diese nicht auf den Pumpenkolben 20 wirken. Am Stößel 40 greift eine vorgespannte Rückstellfeder 48 an, durch die der Stößel 40 und der mit diesem verbundene Pumpenkolben 20 zum Abschnitt 16 hin gedrückt werden. Nachfolgend wird anhand der Figur 2 das Einlassventil 34 gemäß einer nicht erfindungsgemäßen Ausführung beschrieben. An die Zylinderbohrung 28 des Gehäuseteils 22 schließt sich zu der der Antriebswelle 12 abgewandten Außenseite des Gehäuseteils 22 hin eine Bohrung 50 an, die einen kleineren Durchmesser aufweist als die Zylinderbohrung 28. Am Übergang von der Zylinderbohrung 28 zur Bohrung 50 ist eine Ringschulter gebildet, an der ein Ventilsitz 52 ausgebildet ist, der beispielsweise zumindest annähernd kegelstumpfförmig ist. Zur Außenseite des Gehäuseteils 22 schließt sich an die Bohrung 50 eine weitere Bohrung 54 mit wesentlich größerem Durchmesser an. Das Einlassventil 34 weist ein kolbenförmiges Ventilglied 56 auf, das einen Kopf 58 aufweist, der im Pumpenarbeitsraum 30 und damit in der Zylinderbohrung 28 angeordnet ist. An der dem Ventilsitz 52 zugewandten Seite des Kopfs 58 des Ventilglieds 56 ist eine Dichtfläche 60 ausgebildet, die vorzugsweise konvex gewölbt ausgebildet ist. Die Dichtfläche 60 kann zumindest annähernd kugelabschnittförmig ausgebildet sein. An den Kopf 58 des Ventilglieds 56 schließt sich ein im Durchmesser gegenüber dem Kopf 58 kleinerer Schaft 62 an, der durch die Bohrung 50 hindurch bis in die weitere Bohrung 54 ragt, die einen dem Pumpenarbeitsraum 30 abgewandten Bereich des Gehäuseteils 22 bildet. In der weiteren Bohrung 54 ist eine vorgespannte Schließfeder 64 angeordnet, die als Schraubendruckfeder ausgebildet ist. Die Schließfeder 64 stützt sich einerseits an einer am Übergang der Bohrung 50 in die weitere Bohrung 54 gebildeten Ringschulter 55 am Gehäuseteil 22 und andererseits über einen mit dem Schaft 62 verbundenen Federteller 66 am Ventilglied 56 ab. Durch die Schließfeder 64 wird das Ventilglied 56 somit in Schließrichtung beaufschlagt, wobei das Ventilglied 56 in seiner Schließstellung mit seiner Dichtfläche 60 am Ventilsitz 52 anliegt. Der Durchmesser des Schafts 62 des Ventilglieds 56 ist kleiner als der Durchmesser der Bohrung 50, so dass zwischen dem Schaft 62 und der Bohrung 50 ein Durchflussquerschnitt in Form eines Ringspalts 63 verbleibt.Between the pump piston 20 and the eccentric portion 16 or cam of the drive shaft 12, a support member may be arranged in the form of a plunger 40, via which the pump piston 20 is at least indirectly supported on the cam 16. The pump piston 20 is coupled to the plunger 40 in a manner not shown in the direction of its longitudinal axis 21. The plunger 40 may be supported directly on the eccentric portion 16 or cam. In this case, a ring 42 can be rotatably mounted on the section 16 of the drive shaft 12, against which the plunger 40 rests. The ring 42 has a flattening 44 for each pump element 18 against which the plunger 40 rests. During the rotational movement of the drive shaft 12 about its axis of rotation 13 of the pump piston 20 is driven via the ring 42 and the plunger 40 in a lifting movement, wherein the ring 42 does not rotate with the drive shaft 12, but is stationary. The plunger 40 is slidably mounted in the base body 14 of the pump housing 10 or on the housing part 22 and takes in the implementation of the rotational movement of the drive shaft 12 in the lifting movement of the pump piston 20 occurring transverse forces, so that they do not act on the pump piston 20. At the plunger 40 engages a prestressed return spring 48, through which the plunger 40 and the associated pump piston 20 are pressed to the section 16 through. The following is based on the FIG. 2 the intake valve 34 described according to a non-inventive embodiment. To the cylinder bore 28 of the housing part 22 connects to the drive shaft 12 facing away from the outside of the housing part 22 toward a bore 50, which has a smaller diameter than the cylinder bore 28. At the transition from the cylinder bore 28 to the bore 50 an annular shoulder is formed on a valve seat 52 is formed, which is for example at least approximately frusto-conical. To the outside of the housing part 22 connects to the bore 50, a further bore 54 with a much larger diameter. The inlet valve 34 has a piston-shaped valve member 56, which has a head 58 which is arranged in the pump working chamber 30 and thus in the cylinder bore 28. At the valve seat 52 side facing the head 58 of the valve member 56, a sealing surface 60 is formed, which is preferably formed convex. The sealing surface 60 may be formed at least approximately spherical segment-shaped. The head 58 of the valve member 56 is adjoined by a shaft 62, which has a smaller diameter than the head 58 and projects through the bore 50 into the further bore 54, which forms a region of the housing part 22 facing away from the pump working space 30. In the further bore 54, a prestressed closing spring 64 is arranged, which is designed as a helical compression spring. The closing spring 64 is supported, on the one hand, on an annular shoulder 55 on the housing part 22 formed at the transition of the bore 50 into the further bore 54 and, on the other hand, via a spring plate 66 connected to the shaft 62 on the valve member 56. By the closing spring 64, the valve member 56 is thus acted upon in the closing direction, wherein the valve member 56 rests in its closed position with its sealing surface 60 on the valve seat 52. The diameter of the shaft 62 of the valve member 56 is smaller than the diameter of the bore 50, so that between the shaft 62 and the bore 50, a flow cross-section in the form of an annular gap 63 remains.

Die weitere Bohrung 54 ist zur Außenseite des Gehäuseteils 22 hin mittels eines Verschlusselements 68 dicht verschlossen, das in die Bohrung 54 eingesetzt ist. Das Verschlusselement 68 kann beispielsweise wie in Figur 2 dargestellt als Verschlussschraube ausgebildet sein, wobei diese ein Außengewinde aufweist, mit dem diese in ein Innengewinde der Bohrung 54 eingeschraubt ist. Alternativ kann das Verschlusselement 68 auch in anderer Weise mit dem Gehäuseteil 22 verbunden sein, beispielsweise in die Bohrung 54 eingepresst sein oder mit dem Gehäuseteil 22 verschweißt sein. Zwischen dem Verschlusselement 68 und der Bohrung 54 ist zur Abdichtung ein elastisches Dichtelement 70, beispielsweise in Form eines O-Rings, eingespannt. Das Verschlusselement 68 weist auf seiner dem Ventilglied 56 zugewandten Seite eine Ausnehmung 69 auf, beispielsweise in Form einer Sackbohrung, in der der Schaft 62 des Ventilglieds 56 und die diesen umgebende Schließfeder 64 angeordnet sind. Das Verschlusselement 68 erstreckt sich nicht ganz bis zur Ringschulter am Übergang von der weiteren Bohrung 54 zur Bohrung 50, so dass in der weiteren Bohrung 54 durch das Verschlusselement 68 ein Raum 72 begrenzt wird. In den Raum 72 mündet der Kraftstoffzulaufkanal 32, der mit dem Ringspalt 63 zwischen der Bohrung 50 und dem Ventilglied 56 in Verbindung steht. Im Raum 72 herrscht ein erhöhter Zulaufdruck, der auf die innerhalb des Ventilsitzes 52 angeordnete Stirnfläche des Kopfes 58 des Ventilglieds 56 wirkt und eine Kraft in Öffnungsrichtung auf das Ventilglied 56 erzeugt. Durch den im Pumpenarbeitsraum 30 herrschenden Druck, der auf die dem Ventilsitz 52 abgewandte Stirnseite des Kopfes 58 des Ventilglieds 56 wirkt, wird eine Kraft in Schließrichtung auf das Ventilglied 56 erzeugt.The further bore 54 is sealed to the outside of the housing part 22 by means of a closure element 68, which is inserted into the bore 54. The closure element 68 may, for example, as in FIG. 2 shown formed as a screw plug, which has an external thread with which it is screwed into an internal thread of the bore 54. Alternatively, the closure element 68 can also be connected in a different way to the housing part 22, for example, be pressed into the bore 54 or be welded to the housing part 22. Between the closure element 68 and the bore 54, an elastic sealing element 70, for example in the form of an O-ring, is clamped for sealing purposes. The closure element 68 has on its side facing the valve member 56 a recess 69, for example in the form of a blind bore, in which the shaft 62 of the valve member 56 and the surrounding closing spring 64 are arranged. The closure element 68 does not extend completely to the annular shoulder at the transition from the further bore 54 to the bore 50, so that in the further bore 54 by the closure member 68, a space 72 is limited. In the space 72 opens the fuel inlet channel 32, which is in communication with the annular gap 63 between the bore 50 and the valve member 56. In space 72 there is an increased inlet pressure, which acts on the disposed within the valve seat 52 face of the head 58 of the valve member 56 and generates a force in the opening direction on the valve member 56. Due to the pressure prevailing in the pump working chamber 30, which acts on the end face of the head 58 of the valve member 56 facing away from the valve seat 52, a force is generated in the closing direction on the valve member 56.

Die Bohrungen 50, 54 sowie der Ventilsitz 52 können am Gehäuseteil 22 auf einfache Weise hergestellt werden, da der Ventilsitz 52 vor dem Zusammenbau des Gehäuseteils 22 mit dem Grundkörper 14 von der Innenseite der Zylinderbohrung 28 her zur Bearbeitung zugänglich ist. Das Ventilglied 56 wird vor dem Zusammenbau des Gehäuseteils 22 mit dem Grundkörper 14 von der Innenseite der Zylinderbohrung 28 mit seinem Schaft 62 voraus eingeführt, so dass dieser durch die Bohrung 50 nach außen hindurchragt, anschließend werden die Schließfeder 64 und der Federteller 66 montiert und schließlich das Verschlusselement 68 eingesetzt.The bores 50, 54 and the valve seat 52 can be produced on the housing part 22 in a simple manner, since the valve seat 52 is accessible to the assembly of the housing part 22 with the base body 14 from the inside of the cylinder bore 28 for processing. The valve member 56 is inserted before the assembly of the housing part 22 with the base body 14 from the inside of the cylinder bore 28 with its shaft 62 ahead so that it protrudes through the bore 50 to the outside, then the closing spring 64 and the spring plate 66 are mounted and finally the closure element 68 is inserted.

Beim Saughub des Pumpenkolbens 20, bei dem sich dieser zusammen mit dem Stößel 40 bewirkt durch die Rückstellfeder 48 radial nach innen bewegt, herrscht im Pumpenarbeitsraum 30 ein geringer Druck, so dass das Einlassventil 34 öffnet, indem dessen Ventilglied 56 mit seiner Dichtfläche 60 vom Ventilsitz 52 abhebt, da durch den im Kraftstoffzulauf 32 herrschenden Druck eine größere Kraft in Öffnungsrichtung erzeugt wird als die Summe der Kraft der Schließfeder 64 und der durch den im Pumpenarbeitsraum 30 herrschenden Druck erzeugten Kraft. Aus dem Raum 72 strömt bei geöffnetem Einlassventil 34 Kraftstoff durch den Ringspalt 63 in den Pumpenarbeitsraum 30. Bei geringem Druck im Pumpenarbeitsraum 30 während dessen Befüllung ist das Auslassventil 38 geschlossen. Beim Förderhub des Pumpenkolbens 20, bei dem sich dieser zusammen mit dem Stößel 40 radial nach aussen bewegt, wird durch den Pumpenkolben 20 Kraftstoff im Pumpenarbeitsraum 30 verdichtet, so dass das Einlassventil 34 infolge des erhöhten Drucks im Pumpenarbeitsraum 30 schließt, während unter Hochdruck stehender Kraftstoff durch den Kraftstoffablaufkanal 36 bei geöffnetem Auslassventil 38 zum Hochdruckspeicher 110 gefördert wird. Das Ventilglied 56 des Einlassventils 34 ist nicht geführt, wobei durch dessen konvex gewölbte Dichtfläche 60 und den kegelstumpfförmigen Ventilsitz 52 eine Zentrierung bei der Schließbewegung des Ventilglieds 56 ergibt, so dass die Dichtfläche 60 den Ventilsitz 52 sicher abdichtet und der Pumpenarbeitsraum 30 vom Kraftstoffzulauf 32 getrennt ist.In the suction stroke of the pump piston 20, in which this moves together with the plunger 40 caused by the return spring 48 radially inward, prevails in the pump working chamber 30, a low pressure, so that the inlet valve 34 opens by the valve member 56 with its sealing surface 60 from the valve seat 52 lifts, since a larger force in the opening direction is generated by the pressure prevailing in the fuel inlet 32 as the sum of the force of the closing spring 64 and the force generated by the pressure prevailing in the pump working chamber 30 force. From the space 72 fuel flows through the annular gap 63 into the pump working chamber 30 when the inlet valve 34 is open. At low pressure in the pump working chamber 30 during its filling, the outlet valve 38 is closed. During the delivery stroke of the pump piston 20, in which it moves radially outwards together with the plunger 40, fuel is compressed in the pump working chamber 30 by the pump piston 20, so that the inlet valve 34 closes due to the increased pressure in the pump working space 30, while under high pressure fuel is conveyed through the fuel drain passage 36 with the exhaust valve 38 open to the high-pressure accumulator 110. The valve member 56 of the inlet valve 34 is not guided, whereby by its convex curved sealing surface 60 and the frusto-conical valve seat 52 results in a centering during the closing movement of the valve member 56 so that the sealing surface 60 the valve seat 52 securely seals and the pump chamber 30 is separated from the fuel inlet 32.

In Figur 3 ist das Einlassventil 34 gemäß einem erfindungsgemäßen Ausführungsbeispiel dargestellt, das gegenüber der Ausführung gemäß Figur 2 dahingehend modifiziert ist, dass eine modifiziert ist, dass eine Führung für das Ventilglied 56 vorgesehen ist. An die Zylinderbohrung 28 schließt sich wie bei der Ausführung gemäß Figur 2 die Bohrung 50 mit kleinerem Durchmesser an, die hier jedoch einen in die Zylinderbohrung 28 mündenden ersten Abschnitt 150 und einen in die weitere Bohrung 54 mündenden zweiten Abschnitt 250 mit gegenüber dem ersten Abschnitt 150 kleinerem Durchmesser aufweist. Am Übergang von der Zylinderbohrung 28 in den ersten Bohrungsabschnitt 150 ist der Ventilsitz 52 angeordnet, der beispielsweise zumindest annähernd kegelstumpfförmig ausgebildet ist. Der Übergang vom ersten Bohrungsabschnitt 150 zum zweiten Bohrungsabschnitt 250 kann zumindest annähernd kegelstumpfförmig verlaufen. Die Bohrungsabschnitte 150,250 sind in einem Ansatz 74 des Gehäuseteils 22 angeordnet, der in eine auf der Außenseite des Gehäuseteils 22 gebildete Vertiefung 76 hineinragt. Der erste Bohrungsabschnitt 150 ist über wenigstens eine, vorzugsweise mehrere Bohrungen 78 im Ansatz 74 des Gehäuseteils 22 mit der Vertiefung 76 verbunden. Das Ventilglied 56 weist den im Pumpenarbeitsraum 30 angeordneten Kopf 58 mit der Dichtfläche 60 auf, die beispielsweise konvex gewölbt, insbesondere zumindest annähernd kugelabschnittförmig, oder zumindest annähernd kegelstumpfförmig ausgebildet sein kann. An den Kopf 58 schließt sich der im Durchmesser kleinere Schaft 62 des Ventilglieds 56 an, wobei der Schaft 62 im zweiten Bohrungsabschnitt 250 mit geringem Spiel verschiebbar geführt ist und zwischen dem ersten Bohrungsabschnitt 150 und dem Schaft 62 ein Durchflussquerschnitt in Form eines Ringspalts 63 vorhanden ist. Mit dem aus dem Bohrungsabschnitt 250 ragenden Endbereich des Schafts 62 des Ventilglieds 56 ist der Federteller 66 verbunden, zwischen dem und dem Boden der Vertiefung 76 die Schließfeder 64 eingespannt ist.In FIG. 3 the inlet valve 34 is shown according to an embodiment of the invention, compared to the embodiment according to FIG. 2 is modified such that one is modified, that a guide for the valve member 56 is provided. At the cylinder bore 28 closes as in the embodiment according to FIG. 2 the bore 50 with a smaller diameter, but here has a opening into the cylinder bore 28 first portion 150 and an opening into the further bore 54 second portion 250 with respect to the first portion 150 of smaller diameter. At the transition from the cylinder bore 28 into the first bore portion 150 of the valve seat 52 is arranged, which is for example at least approximately frusto-conical. The transition from the first bore portion 150 to the second bore portion 250 may be at least approximately frusto-conical. The bore portions 150, 250 are arranged in a projection 74 of the housing part 22, which projects into a recess 76 formed on the outside of the housing part 22. The first bore section 150 is connected to the recess 76 via at least one, preferably a plurality of bores 78 in the projection 74 of the housing part 22. The valve member 56 has arranged in the pump working chamber 30 head 58 with the sealing surface 60, which may for example be convexly curved, in particular at least approximately spherical segment-shaped, or at least approximately frusto-conical. To the head 58, the smaller diameter shaft 62 of the valve member 56 connects, wherein the shaft 62 in the second Bore portion 250 is slidably guided with little play and between the first bore portion 150 and the shaft 62, a flow cross-section in the form of an annular gap 63 is present. With the protruding from the bore portion 250 end portion of the shaft 62 of the valve member 56 of the spring plate 66 is connected, between which and the bottom of the recess 76, the closing spring 64 is clamped.

Die Vertiefung 76 ist nach außen mittels eines Verschlusselements 68 dicht verschlossen, wobei das Verschlusselement 68 mit dem Gehäuseteil 22 verschraubt, verpresst oder verschweißt sein kann. Durch das Verschlusselement 68 wird in der Vertiefung 76 ein Raum 72 begrenzt, in den der Kraftstoffzulauf 32 mündet, wobei der Raum 72 über die Bohrungen 78 mit dem den Schaft 62 des Ventilglieds 56 umgebenden Ringspalt 63 verbunden ist. Bei geöffnetem Einlassventil 34 strömt Kraftstoff aus der Vertiefung 76 über die Bohrungen 78 in den Ringspalt 63 und aus diesem in den Pumpenarbeitsraum 30. Bei seiner Öffnungs- und Schließbewegung ist das Ventilglied 56 mit seinem Schaft 62 im zweiten Bohrungsabschnitt 250 geführt.The recess 76 is sealed to the outside by means of a closure member 68, wherein the closure member 68 may be screwed to the housing part 22, pressed or welded. By the closure member 68, a space 72 is limited in the recess 76, in which the fuel inlet 32 opens, the space 72 is connected via the holes 78 with the shaft 62 of the valve member 56 surrounding the annular gap 63. When the inlet valve 34 is open, fuel flows out of the recess 76 via the holes 78 into the annular gap 63 and out of this into the pump working space 30. During its opening and closing movement, the valve member 56 is guided with its shaft 62 in the second bore section 250.

Claims (2)

  1. High-pressure pump, in particular for a fuel injection device of an internal combustion engine, with at least one pump element (18) which has a pump piston (20) which is guided displaceably in a cylinder bore (28) of a housing part (22) of the high-pressure pump and is driven in a lifting movement and which delimits in the cylinder bore (28) a pumping working space (30), into which fuel is sucked via an inlet valve (34) during the suction stroke of the pump piston (20) and out of which fuel is displaced during the feed stroke of the pump piston (20), the inlet valve (34) having a piston-shaped valve member (56) which co-operates by means of a sealing surface (60) with a valve seat (52) for controlling the connection of the pump working space (30) to a fuel inflow (32), the valve member (56) being acted upon in the opening direction by a closing spring (64) and by the pressure prevailing in the fuel inflow (32) and in the closing direction by the pressure prevailing in the pump working space (30), the valve member (56) being arranged with a head (58), on which the sealing surface (60) is formed, in the pump working space (30) and projecting, with a shank (62) adjoining the head (58), out of the pump working space (30), the closing spring (64) being arranged outside the pump working space (30) and acting on the shank (62), the valve seat (52) being formed on the housing part (22) at the transition of the cylinder bore (28) to a bore (150, 250) adjoining the latter and having a smaller diameter, the valve member (56) projecting with its shank (62) through the bore (150, 250) into a region (72), facing away from the pump working space (30), of the housing part (22), and the closing spring (64) being arranged in this region (72) of the housing part (22), that region (72) of the housing part (22) in which the closing spring (64) is arranged being sealingly closed with respect to the outside of the housing part (22) by means of a closing element (68), and the fuel inflow (32) issuing into this region (72), characterized in that the bore (150, 250) has a first portion (150) which issues into the pump working space (30) and between which and the shank (62) of the valve member (56) a throughflow cross section (63) is released, in that the bore (150, 250) has a second portion (250) which issues into the region (72) and in which the shank (62) of the valve member (56) is guided displaceably, and in that the first portion (150) of the bore (150, 250) is connected to the region (72).
  2. High-pressure pump according to Claim 1, characterized in that the sealing surface (60) of the valve member (56) is designed to be curved convexly towards the valve seat (52), in particular, at least approximately, in the form of a spherical segment.
EP05707796A 2004-03-18 2005-01-18 High-pressure pump, in particular for a fuel-injection device in an internal combustion engine Active EP1727983B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102004013244A DE102004013244A1 (en) 2004-03-18 2004-03-18 High-pressure pump, in particular for a fuel injection device of an internal combustion engine
PCT/EP2005/050193 WO2005090790A1 (en) 2004-03-18 2005-01-18 High-pressure pump, in particular for a fuel-injection device in an internal combustion engine

Publications (2)

Publication Number Publication Date
EP1727983A1 EP1727983A1 (en) 2006-12-06
EP1727983B1 true EP1727983B1 (en) 2009-11-18

Family

ID=34960413

Family Applications (1)

Application Number Title Priority Date Filing Date
EP05707796A Active EP1727983B1 (en) 2004-03-18 2005-01-18 High-pressure pump, in particular for a fuel-injection device in an internal combustion engine

Country Status (7)

Country Link
US (1) US7363913B2 (en)
EP (1) EP1727983B1 (en)
JP (1) JP4395534B2 (en)
CN (1) CN100417814C (en)
AT (1) ATE449260T1 (en)
DE (2) DE102004013244A1 (en)
WO (1) WO2005090790A1 (en)

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Also Published As

Publication number Publication date
WO2005090790A1 (en) 2005-09-29
DE502005008539D1 (en) 2009-12-31
EP1727983A1 (en) 2006-12-06
CN1934357A (en) 2007-03-21
JP2007529675A (en) 2007-10-25
DE102004013244A1 (en) 2005-10-06
JP4395534B2 (en) 2010-01-13
CN100417814C (en) 2008-09-10
US20070215113A1 (en) 2007-09-20
US7363913B2 (en) 2008-04-29
ATE449260T1 (en) 2009-12-15

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