EP1727983A1 - 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

Info

Publication number
EP1727983A1
EP1727983A1 EP05707796A EP05707796A EP1727983A1 EP 1727983 A1 EP1727983 A1 EP 1727983A1 EP 05707796 A EP05707796 A EP 05707796A EP 05707796 A EP05707796 A EP 05707796A EP 1727983 A1 EP1727983 A1 EP 1727983A1
Authority
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.)
Granted
Application number
EP05707796A
Other languages
German (de)
French (fr)
Other versions
EP1727983B1 (en
Inventor
Andreas Dutt
Jochen Aleker
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP1727983A1 publication Critical patent/EP1727983A1/en
Application granted granted Critical
Publication of EP1727983B1 publication Critical patent/EP1727983B1/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

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

  • High-pressure pump in particular for a fuel injection device of an internal combustion engine
  • the invention is based on 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 known from DE 197 29 790 AI.
  • This high-pressure pump has at least one pump element, with a pump piston which is displaceably guided in a cylinder bore of a housing part of the high-pressure pump and is driven in a stroke movement.
  • the pump piston limits one in the cylinder bore
  • the inlet valve has a piston-shaped valve member which is displaceably guided in a valve housing connected to the housing part of the high-pressure pump.
  • the valve member has a sealing surface with which it interacts with a valve seat formed on the valve housing for controlling a connection of the pump work space to a fuel inlet.
  • the valve member is acted upon by a closing spring arranged in the valve housing and by the pressure prevailing in the pump work space in the closing direction towards the valve seat and acted upon by the pressure prevailing in the fuel supply in the opening direction.
  • the fuel inlet opens into the valve housing, the valve housing, together with the valve member and the closing spring, forming a preassembled structural unit, which in the housing part of the high pressure pump is used. Due to the separate valve housing, the high-pressure pump is complex to manufacture and thus expensive. In addition, the valve housing of the pump work space is covered, so that between the
  • the high-pressure pump according to the invention with the features according to claim 1 has the advantage that no separate valve housing and therefore no sealing to the high pressure in the pump work space is required for the inlet valve.
  • the valve member is inserted from the inside of the cylinder bore with its stem ahead, and the closing spring is attached from the outside of the housing part opposite the cylinder bore and connected to the stem of the valve member.
  • the embodiment according to claim 2 enables an easy to manufacture course of the fuel feed.
  • the embodiment according to claim 4 enables the valve member to be guided and thus a reliable sealing effect of the inlet valve and low wear of the sealing surface and the valve seat.
  • the embodiment according to claim 5 enables a secure sealing effect of the inlet valve even without guiding the valve member.
  • FIG. 1 shows a high-pressure pump for a fuel injection device
  • FIG. 2 shows a section of the high-pressure pump, designated II in FIG. 1, with an inlet valve in an enlarged representation according to a first exemplary embodiment
  • FIG. 3 shows section II with an inlet valve according to a second exemplary embodiment.
  • the high-pressure pump has a multi-part 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 mounted in a base body 14 of the housing 10 via two bearing points spaced apart in the direction of the axis of rotation 13 of the drive shaft 12.
  • the base body 14 of the housing 10 can in turn be formed in several parts and the bearing points can be arranged in different parts of the base body 14.
  • the base body 14 consists of a material with the strength required for the mounting of the drive shaft 12, in particular of light metal such as aluminum or an aluminum alloy.
  • the drive shaft 12 has at least one section 16 eccentric to its axis of rotation 13 or a cam, the cam 16 also being a multiple cam can be trained.
  • the high-pressure pump has at least one or more pump elements 18 arranged in the pump housing 10, each with a pump piston 20, which is driven by the eccentric section 16 or the cam of the drive shaft 12 in a stroke movement in at least approximately radial direction to the axis of rotation 13 of the drive shaft 12.
  • a housing part 22 which is connected to the base body 14 and is designed as a cylinder head.
  • the housing part 22 has a flange 24 which bears on an outer side of the base body 14 and an approximately cylindrical projection 26 which projects through an opening 15 in the base body 14 towards the drive shaft 12 and has a smaller diameter than the flange 24.
  • the pump piston 20 is guided such that it can be moved in a sealed manner in a cylinder bore 28 formed in the housing part 22 and, with its end face remote from the drive shaft 12, limits one in the cylinder bore 28
  • the pump chamber 30 is disposed of the housing part 22 in the '' ⁇ portion of the flange 24 and the bore 28 extends up to the of the drive shaft 12 facing the end of the projection 26 of the housing part 22.
  • the pump chamber 30 has extending over a in the pump housing 10
  • Fuel inlet channel 32 has a connection to a fuel inlet, for example a feed pump.
  • At the mouth of the fuel inlet channel 32 into the pump work chamber 30 there is an inlet valve 34 which opens into the pump work chamber 30.
  • the pump work chamber 30 also has an outlet valve 34 in the pump housing 10
  • Fuel drain channel 36 has a connection to an outlet, which is connected, for example, to a high-pressure accumulator 110.
  • a high-pressure accumulator 110 With the high-pressure accumulator 110, one or preferably more are on the cylinders of the Internal combustion engine arranged injectors 120 connected through which fuel is injected into the cylinders of the internal combustion engine.
  • injectors 120 At the mouth of the
  • the housing part 22 consists of a material with high strength, since there is high pressure in the pump working chamber 30 during the delivery stroke of the pump piston 20.
  • the housing part 22 can be made of steel or cast iron, for example.
  • a support element in the form of a tappet 40 can be arranged between the pump piston 20 and the eccentric section 16 or cam of the drive shaft 12, via which the pump piston 20 is supported at least indirectly on the cam 16.
  • the pump piston 20 is coupled to the tappet 40 in a manner not shown in the direction of its longitudinal axis 21.
  • the tappet 40 can be supported directly on the eccentric section 16 or cam.
  • a ring 42 on which the tappet 40 bears can be rotatably mounted on the section 16 of the drive shaft 12.
  • Ring 42 has a flattened area 44 for each pump element 18, on which the plunger 40 bears.
  • the pump piston 20 is driven in a stroke movement via the ring 42 and the tappet 40, the ring 42 not rotating with the drive shaft 12, but being stationary.
  • the tappet 40 is displaceably mounted in the base body 14 of the pump housing 10 or on the housing part 22 and absorbs transverse forces that occur when the rotary movement of the drive shaft 12 is converted into the stroke movement of the pump piston 20, so that these do not act on the pump piston 20.
  • a preloaded return spring 48 acts on the plunger 40, by means of which the plunger 40 and the pump piston 20 connected to it are pressed toward the section 16.
  • the inlet valve 34 according to a first exemplary embodiment is described below with reference to FIG. 2.
  • a bore 50 adjoins the cylinder bore 28 of the housing part 22 toward the outside of the housing part 22 facing away from the drive shaft 12 and has a smaller diameter than the cylinder bore 28.
  • An annular shoulder is formed at the transition from the cylinder bore 28 to the bore 50 which is formed a valve seat 52 which, for example, is at least approximately frustoconical.
  • a further hole 54 with a substantially larger diameter adjoins the hole 50.
  • the inlet valve 34 has a piston-shaped valve member 56 which has a head 58 which is arranged in the pump work chamber 30 and thus in the cylinder bore 28.
  • a sealing surface 60 is formed, which is preferably convex.
  • the sealing surface 60 can be at least approximately spherical.
  • At the head 58 of the valve member 56 closes in
  • Shaft 62 smaller in diameter than head 58, which projects through bore 50 into further bore 54, which forms a region of housing part 22 facing away from pump working space 30.
  • a prestressed closing spring 64 which is designed as a helical compression spring, is arranged in the further bore 54.
  • the closing spring 64 is supported on the one hand on an annular shoulder 55 formed at the transition of the bore 50 into the further bore 54 on the housing part 22 and on the other hand via a connection to the shaft 62
  • valve member 56 is thus acted upon in the closing direction by the closing spring 64, the valve member 56 resting in its closed position with its sealing surface 60 on the valve seat 52.
  • the diameter of the stem 62 of the valve member 56 is smaller than the diameter of the bore 50, so that A flow cross section in the form of an annular gap 63 remains between the shaft 62 and the bore 50.
  • the further bore 54 is sealed off from 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 can be designed as a closure screw, for example, which has an external thread with which it engages
  • closure element 68 can also be connected in another way to the housing part 22, for example pressed into the bore 54 or welded to the housing part 22.
  • An elastic sealing element 70 for example in the form of an O-ring, is clamped between the closure element 68 and the bore 54 for sealing.
  • 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 stem 62 of the
  • the closure element 68 does not extend all the way to the annular shoulder at the transition from the further bore 54 to the bore 50, so that a space 72 is delimited in the further bore 54 by the closure element 68.
  • the room opens into room 72
  • Fuel inlet channel 32 which communicates with the annular gap 63 between the bore 50 and 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 before the assembly of the housing part 22 with the base body 14 from the inside of the
  • Cylinder bore 28 is accessible 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 stem 62 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 inserted.
  • FIG. 3 shows the inlet valve 34 according to a second exemplary embodiment, which is modified compared to the first exemplary embodiment in such a way that a guide for the valve member 56 is provided.
  • the cylinder bore 28 is followed by the bore 50 with a smaller diameter, but here has a first section 150 opening into the cylinder bore 28 and a second section 250 opening into the further bore 54 with a smaller diameter than the first section 150 ,
  • the valve seat 52 is arranged, which for example is at least approximately frustoconical.
  • the transition from the first bore section 150 to the second bore section 250 can run at least approximately in the shape of a truncated cone.
  • the bore sections 150, 250 are arranged in a shoulder 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 extension 74 of the housing part 22.
  • the valve member 56 has the head 58 arranged in the pump work chamber 30 with the sealing surface 60, which, for example, is convexly curved, in particular at least approximately spherical, or at least approximately frustoconical.
  • the head 62 is followed by the smaller-diameter stem 62 of the valve member 56, the stem 62 in the second Bore section 250 is slidably guided and a flow cross-section in the form of an annular gap 63 is present between the first bore section 150 and the shaft 62.
  • the spring plate 66 is connected to the end region of the stem 62 of the valve member 56 protruding from the bore section 250, between which and the bottom of the recess 76 the closing spring 64 is clamped.
  • the recess 76 is outwardly by means of a
  • Closure element 68 tightly closed, wherein the closure element 68 can be screwed, pressed or welded to the housing part 22.
  • the closure element 68 delimits a space 72 in the recess 76 into which the fuel inlet 32 opens, the space 72 being connected via the bores 78 to the annular gap 63 surrounding the stem 62 of the valve member 56.
  • fuel flows out of the recess 76 through the bores 78 into the annular gap 63 and out of this into the pump work chamber 30
  • valve member 56 Opening and closing movement, the valve member 56 with • - • out its shank 62 in the second bore portion 250th

Landscapes

  • 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

Hochdruckpumpe, insbesondere für eine Kraftstoffeinspritzeinrichtung einer BrennkraftmaschineHigh-pressure pump, in particular for a fuel injection device of an internal combustion engine
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 is based on 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 197 29 790 AI bekannt. Diese Hochdruckpumpe weist wenigstens ein Pumpenelement auf, mit einem in einer Zylinderbohrung eines Gehäuseteils der Hochdruckpumpe verschiebbar geführten, in einer Hubbewegung angetriebenen Pumpenkolben auf. Der Pumpenkolben begrenzt in der Zylinderbohrung einenSuch a high pressure pump is known from DE 197 29 790 AI. This high-pressure pump has at least one pump element, with a pump piston which is displaceably guided in a cylinder bore of a housing part of the high-pressure pump and is driven in a stroke movement. The pump piston limits one in the cylinder bore
Pumpenarbeitsraum, in den der Pumpenkolben bei dessen Saughub Kraftstoff über ein Einlassventil ansaugt und aus dem der Pumpenkolben bei dessen Förderhub Kraftstoff verdrängt. Das Einlassventil weist ein kolbenförmiges Ventilglied auf, das in einem mit dem Gehäuseteil der Hochdruckpumpe verbundenen Ventilgehäuse verschiebbar geführt ist. Das Ventilglied weist eine Dichtfläche auf, mit der es mit einem am Ventilgehäuse ausgebildeten Ventilsitz zur Steuerung einer Verbindung des Pumpenarbeitsraums mit einem Kraftstoffzulauf zusammenwirkt. Das Ventilglied ist durch eine im Ventilgehäuse angeordnete Schließfeder und durch den im Pumpenarbeitsraum herrschenden Druck in Schließrichtung zum Ventilsitz hin beaufschlagt und durch den im Kraftstoffzulauf herrschenden Druck in Öffnungsrichtung beaufschlagt. Der Kraftstoffzulauf mündet im Ventilgehäuse, wobei das Ventilgehäuse mit dem Ventilglied und der Schließfeder eine vormontierte Baueinheit bildet, die in das Gehäuseteil der Hochdruckpumpe eingesetzt wird. 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 demPump work space into which the pump piston sucks fuel via an inlet valve during its suction stroke and from which the pump piston displaces fuel during its delivery stroke. The inlet valve has a piston-shaped valve member which is displaceably guided in a valve housing connected to the housing part of the high-pressure pump. The valve member has a sealing surface with which it interacts with a valve seat formed on the valve housing for controlling a connection of the pump work space to a fuel inlet. The valve member is acted upon by a closing spring arranged in the valve housing and by the pressure prevailing in the pump work space in the closing direction towards the valve seat and acted upon by the pressure prevailing in the fuel supply in the opening direction. The fuel inlet opens into the valve housing, the valve housing, together with the valve member and the closing spring, forming a preassembled structural unit, which in the housing part of the high pressure pump is used. Due to the separate valve housing, the high-pressure pump is complex to manufacture and thus expensive. In addition, the valve housing of the pump work space is covered, so that between the
Gehäuseteil der Hochdruckpumpe und dem Ventilgehäuse eine aufwendige Abdichtung gegen den Hochdruck im Pumpenarbeitsraum erforderlich ist.Housing part of the high pressure pump and the valve housing requires a complex seal against the high pressure in the pump work space.
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 according to claim 1 has the advantage that no separate valve housing and therefore no sealing to the high pressure in the pump work space is required for the inlet valve. In addition, only the valve seat, which can be machined from the inside of the cylinder bore, needs to be produced on the housing part. The valve member is inserted from the inside of the cylinder bore with its stem ahead, and the closing spring is attached from the outside of the housing part opposite the cylinder bore and connected to the stem of the valve member.
In den abhängigen Ansprüchen sind vorteilhafteIn the dependent claims are advantageous
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. ZeichnungRefinements and developments of the high-pressure pump according to the invention are specified. The embodiment according to claim 2 enables an easy to manufacture course of the fuel feed. The embodiment according to claim 4 enables the valve member to be guided and thus a reliable sealing effect of the inlet valve and low wear of the sealing surface and the valve seat. The embodiment according to claim 5 enables a secure sealing effect of the inlet valve even without guiding the valve member. drawing
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 einerTwo embodiments of the invention are shown in the drawing and explained in more detail in the following description. FIG. 1 shows a high-pressure pump for a fuel injection device
Brennkraftmaschine in einem Längsschnitt, Figur 2 einen in Figur 1 mit II bezeichneten Ausschnitt der Hochdruckpumpe mit einem Einlassventil in vergrößerter Darstellung gemäß einem ersten Ausführungsbeispiel und Figur 3 den Ausschnitt II mit einem Einlassventil gemäß einem zweiten Ausführungsbeispiel .Internal combustion engine in a longitudinal section, FIG. 2 shows a section of the high-pressure pump, designated II in FIG. 1, with an inlet valve in an enlarged representation according to a first exemplary embodiment, and FIG. 3 shows section II with an inlet valve according to a second exemplary embodiment.
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.1 to 3 show a high-pressure pump for a fuel injection device of an internal combustion engine. The high-pressure pump has a multi-part 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 mounted in a base body 14 of the housing 10 via two bearing points spaced apart in the direction of the axis of rotation 13 of the drive shaft 12. The base body 14 of the housing 10 can in turn be formed in several parts and the bearing points can be arranged in different parts of the base body 14. The base body 14 consists of a material with the strength required for the mounting of the drive shaft 12, 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 zylinderför igen Ansatz 26 mit gegenüber dem Flansch 24 kleinerem Durchmesser auf.In an area lying between the two bearing points, the drive shaft 12 has at least one section 16 eccentric to its axis of rotation 13 or a cam, the cam 16 also being a multiple cam can be trained. The high-pressure pump has at least one or more pump elements 18 arranged in the pump housing 10, each with a pump piston 20, which is driven by the eccentric section 16 or the cam of the drive shaft 12 in a stroke movement in at least approximately radial direction to the axis of rotation 13 of the drive shaft 12. In the area of each pump element 18 there is a housing part 22 which is connected to the base body 14 and is designed as a cylinder head. The housing part 22 has a flange 24 which bears on an outer side of the base body 14 and an approximately cylindrical projection 26 which projects through an opening 15 in the base body 14 towards the drive shaft 12 and has a smaller diameter than the flange 24.
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 einenThe pump piston 20 is guided such that it can be moved in a sealed manner in a cylinder bore 28 formed in the housing part 22 and, with its end face remote from the drive shaft 12, limits one in the cylinder bore 28
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 verlaufendenPump chamber 30. The pump chamber 30 is disposed of the housing part 22 in the '' <■ portion of the flange 24 and the bore 28 extends up to the of the drive shaft 12 facing the end of the projection 26 of the housing part 22. The pump chamber 30 has extending over a in the pump housing 10 Fuel inlet channel 32 has a connection to a fuel inlet, for example a feed pump. At the mouth of the fuel inlet channel 32 into the pump work chamber 30 there is an inlet valve 34 which opens into the pump work chamber 30. The pump work chamber 30 also has an outlet valve 34 in the pump housing 10
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 desFuel drain channel 36 has a connection to an outlet, which is connected, for example, to a high-pressure accumulator 110. With the high-pressure accumulator 110, one or preferably more are on the cylinders of the Internal combustion engine arranged injectors 120 connected through which fuel is injected into the cylinders of the internal combustion engine. At the mouth of the
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.An outlet valve 38 opening out of the pump work chamber 30 is arranged in the fuel work channel 36 in the pump work chamber 30. The housing part 22 consists of a material with high strength, since there is high pressure in the pump working chamber 30 during the delivery stroke of the pump piston 20. The housing part 22 can be made of steel or cast iron, for example.
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. DerA support element in the form of a tappet 40 can be arranged between the pump piston 20 and the eccentric section 16 or cam of the drive shaft 12, via which the pump piston 20 is supported at least indirectly on the cam 16. The pump piston 20 is coupled to the tappet 40 in a manner not shown in the direction of its longitudinal axis 21. The tappet 40 can be supported directly on the eccentric section 16 or cam. A ring 42 on which the tappet 40 bears can be rotatably mounted on the section 16 of the drive shaft 12. The
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 einem ersten Ausführungsbeispiel 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 kegelstumpfför ig 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 imRing 42 has a flattened area 44 for each pump element 18, on which the plunger 40 bears. When the drive shaft 12 rotates about its axis of rotation 13, the pump piston 20 is driven in a stroke movement via the ring 42 and the tappet 40, the ring 42 not rotating with the drive shaft 12, but being stationary. The tappet 40 is displaceably mounted in the base body 14 of the pump housing 10 or on the housing part 22 and absorbs transverse forces that occur when the rotary movement of the drive shaft 12 is converted into the stroke movement of the pump piston 20, so that these do not act on the pump piston 20. A preloaded return spring 48 acts on the plunger 40, by means of which the plunger 40 and the pump piston 20 connected to it are pressed toward the section 16. The inlet valve 34 according to a first exemplary embodiment is described below with reference to FIG. 2. A bore 50 adjoins the cylinder bore 28 of the housing part 22 toward the outside of the housing part 22 facing away from the drive shaft 12 and has a smaller diameter than the cylinder bore 28. An annular shoulder is formed at the transition from the cylinder bore 28 to the bore 50 which is formed a valve seat 52 which, for example, is at least approximately frustoconical. To the outside of the housing part 22, a further hole 54 with a substantially larger diameter adjoins the hole 50. The inlet valve 34 has a piston-shaped valve member 56 which has a head 58 which is arranged in the pump work chamber 30 and thus in the cylinder bore 28. On the side of the head 58 of the valve member 56 facing the valve seat 52, a sealing surface 60 is formed, which is preferably convex. The sealing surface 60 can be at least approximately spherical. At the head 58 of the valve member 56 closes in
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 verbundenenShaft 62 smaller in diameter than head 58, which projects through bore 50 into further bore 54, which forms a region of housing part 22 facing away from pump working space 30. A prestressed closing spring 64, which is designed as a helical compression spring, is arranged in the further bore 54. The closing spring 64 is supported on the one hand on an annular shoulder 55 formed at the transition of the bore 50 into the further bore 54 on the housing part 22 and on the other hand via a connection to the shaft 62
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 .Spring plate 66 on the valve member 56. The valve member 56 is thus acted upon in the closing direction by the closing spring 64, the valve member 56 resting in its closed position with its sealing surface 60 on the valve seat 52. The diameter of the stem 62 of the valve member 56 is smaller than the diameter of the bore 50, so that A flow cross section in the form of an annular gap 63 remains between the shaft 62 and the bore 50.
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 einThe further bore 54 is sealed off from the outside of the housing part 22 by means of a closure element 68 which is inserted into the bore 54. As shown in FIG. 2, the closure element 68 can be designed as a closure screw, for example, which has an external thread with which it engages
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 desInternal thread of the bore 54 is screwed. Alternatively, the closure element 68 can also be connected in another way to the housing part 22, for example pressed into the bore 54 or welded to the housing part 22. An elastic sealing element 70, for example in the form of an O-ring, is clamped between the closure element 68 and the bore 54 for sealing. 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 stem 62 of the
Ventilglieds 56-vund 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 derValve member 56-v and the closing spring 64 surrounding them. The closure element 68 does not extend all the way to the annular shoulder at the transition from the further bore 54 to the bore 50, so that a space 72 is delimited in the further bore 54 by the closure element 68. The room opens into room 72
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. 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 derFuel inlet channel 32, which communicates with the annular gap 63 between the bore 50 and the valve member 56. In the space 72 there is an increased inlet pressure, which acts on the end face of the head 58 of the valve member 56 arranged within the valve seat 52 and generates a force in the opening direction on the valve member 56. The pressure prevailing in the pump work chamber 30, which acts on the end face of the head 58 of the valve member 56 facing away from the valve seat 52, generates a force 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 before the assembly of the housing part 22 with the base body 14 from the inside of the
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.Cylinder bore 28 is accessible 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 stem 62 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 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 Kraftstof zulauf 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 Pumpenarbeitsräum 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.During the suction stroke of the pump piston 20, during which it moves together with the tappet 40, caused by the return spring 48, to move radially inward, there is a low pressure in the pump working chamber 30, so that the inlet valve 34 opens by the valve member 56 with its sealing surface 60 from the valve seat 52 lifts off, since a greater force in the opening direction is generated by the pressure prevailing in the fuel inlet 32 than the sum of the force of the closing spring 64 and the force generated by the pressure prevailing in the pump work chamber 30. When the inlet valve 34 is open, fuel flows from the space 72 through the annular gap 63 into the pump work space 30. At low pressure in the pump work space 30 while it is being filled, the outlet valve 38 is closed. During the delivery stroke of the pump piston 20, in which it moves radially outwards together with the tappet 40, fuel is compressed by the pump piston 20 in the pump work chamber 30, so that the inlet valve 34 closes as a result of the increased pressure in the pump work chamber 30 while fuel is under high pressure is conveyed through the fuel outlet channel 36 to the high-pressure accumulator 110 with the outlet valve 38 open. The valve member 56 of the inlet valve 34 is not guided, with its convexly curved sealing surface 60 and the frustoconical valve seat 52 resulting in centering during the closing movement of the valve member 56, so that the sealing surface 60 seals the valve seat 52 securely and the pump working chamber 30 is separated from the fuel inlet 32.
In Figur 3 ist das Einlassventil 34 gemäß einem zweiten Ausführungsbeispiel dargestellt, das gegenüber dem ersten Ausführungsbeispiel dahingehend modifiziert ist, dass eine Führung für das Ventilglied 56 vorgesehen ist. An die Zylinderbohrung 28 schließt sich wie beim ersten Ausführungsbeispiel 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.FIG. 3 shows the inlet valve 34 according to a second exemplary embodiment, which is modified compared to the first exemplary embodiment in such a way that a guide for the valve member 56 is provided. As in the first exemplary embodiment, the cylinder bore 28 is followed by the bore 50 with a smaller diameter, but here has a first section 150 opening into the cylinder bore 28 and a second section 250 opening into the further bore 54 with a smaller diameter than the first section 150 , At the transition from the cylinder bore 28 into the first bore section 150, the valve seat 52 is arranged, which for example is at least approximately frustoconical. The transition from the first bore section 150 to the second bore section 250 can run at least approximately in the shape of a truncated cone. The bore sections 150, 250 are arranged in a shoulder 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 extension 74 of the housing part 22. The valve member 56 has the head 58 arranged in the pump work chamber 30 with the sealing surface 60, which, for example, is convexly curved, in particular at least approximately spherical, or at least approximately frustoconical. The head 62 is followed by the smaller-diameter stem 62 of the valve member 56, the stem 62 in the second Bore section 250 is slidably guided and a flow cross-section in the form of an annular gap 63 is present between the first bore section 150 and the shaft 62. The spring plate 66 is connected to the end region of the stem 62 of the valve member 56 protruding from the bore section 250, between which and the bottom of the recess 76 the closing spring 64 is clamped.
Die Vertiefung 76 ist nach außen mittels einesThe recess 76 is outwardly by means of a
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 seinerClosure element 68 tightly closed, wherein the closure element 68 can be screwed, pressed or welded to the housing part 22. The closure element 68 delimits a space 72 in the recess 76 into which the fuel inlet 32 opens, the space 72 being connected via the bores 78 to the annular gap 63 surrounding the stem 62 of the valve member 56. When the inlet valve 34 is open, fuel flows out of the recess 76 through the bores 78 into the annular gap 63 and out of this into the pump work chamber 30
Öffnungs- und Schließbewegung ist das Ventilglied 56 mit •--• seinem Schaft 62 im zweiten Bohrungsabschnitt 250 geführt. Opening and closing movement, the valve member 56 with • - • out its shank 62 in the second bore portion 250th

Claims

Ansprüche Expectations
1. Hochdruckpumpe, insbesondere für eine Kraftstoffeinspritzeinrichtung einer Brennkraftmaschine, mit wenigstens einem Pumpenelement (18) , das einen in einer Zylinderbohrung (28) eines Gehäuseteils (22) der Hochdruckpumpe verschiebbar geführten, in einer Hubbewegung angetriebenen Pumpenkolben (20) aufweist, der in der Zylinderbohrung (28) einen Pumpenarbeitsraum (30) begrenzt, in den beim Saughub des Pumpenkolbens (20) über ein Einlassventil (34) Kraftstoff angesaugt wird und aus dem beim Förderhub des Pumpenkolbens (20) Kraftstoff verdrängt wird, wobei das Einlassventil (34) ein kolbenförmiges Ventilglied (56) aufweist, das mit einer Dichtfläche (60) mit einem Ventilsitz (52) zur Steuerung der Verbindung des 'T- Pumpenarbeitsraums (30) mit dem Kraftstoffzulauf (32) zusammenwirkt, wobei das Ventilglied (56) durch eine Schließfeder (64) und durch den im Pumpenarbeitsraum (30) herrschenden Druck in Schließrichtung und durch den im Kraftstoffzulauf (32) herrschenden Druck in Öffnungsrichtung beaufschlagt ist, wobei das Ventilglied (56) mit einem Kopf (58), an dem die Dichtfläche (60) ausgebildet ist, im Pumpenarbeitsraum (30) angeordnet ist und mit einem an den Kopf (58) anschließenden Schaft (62) aus dem Pumpenarbeitsraum (30) herausragt, wobei die Schließfeder (64) außerhalb des Pumpenarbeitsraums (30) angeordnet ist und am Schaft (62) angreift, dadurch gekennzeichnet, dass der Ventilsitz (52) am Gehäuseteil (22) an einem Übergang der Zylinderbohrung (28) zu einer an diese anschließenden, im Durchmesser kleineren Bohrung (50;150) gebildet ist, dass das Ventilglied (56) mit seinem Schaft (62) durch die Bohrung (50) in einen dem Pumpenarbeitsraum (30) abgewandten Bereich (72) des Gehäuseteils (22) hindurchragt und dass die Schließfeder (64) in diesem Bereich (72) des Gehäuseteils (22) angeordnet ist .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 displaceably guided in a cylinder bore (28) of a housing part (22) of the high pressure pump and which is driven in a stroke movement Cylinder bore (28) delimits a pump work chamber (30) into which fuel is sucked in via an inlet valve (34) during the suction stroke of the pump piston (20) and from which fuel is displaced during the delivery stroke of the pump piston (20), the inlet valve (34) entering has a piston-shaped valve member (56) which cooperates with a sealing surface (60) with a valve seat (52) for controlling the connection of the 'T pump work chamber (30) to the fuel inlet (32), the valve member (56) being actuated by a closing spring ( 64) and by the pressure in the closing direction in the pump work chamber (30) and by the pressure in Ö in the fuel inlet (32) Opening direction is acted upon, wherein the valve member (56) with a head (58), on which the sealing surface (60) is formed, is arranged in the pump work space (30) and with a stem (62) adjoining the head (58) Pump working space (30) protrudes, the closing spring (64) being arranged outside the pump working space (30) and engaging on the shaft (62), characterized in that the valve seat (52) on the housing part (22) at a transition of the cylinder bore (28) to form a bore (50; 150) which is smaller in diameter and adjoins the valve member (56) with its Shaft (62) projects through the bore (50) into a region (72) of the housing part (22) facing away from the pump working space (30) and that the closing spring (64) is arranged in this region (72) of the housing part (22).
2. Hochdruckpumpe nach Anspruch 1, dadurch gekennzeichnet, dass der Bereich (72) des Gehäuseteils (22) , in dem die Schließfeder (64) angeordnet ist, zur Außenseite des Gehäuseteils (22) mittels eines Verschlusselements (68) dicht verschlossen ist und dass in diesen Bereich (72) der Kraftstoffzulauf (32) mündet.2. High-pressure pump according to claim 1, characterized in that the area (72) of the housing part (22), in which the closing spring (64) is arranged, is tightly closed to the outside of the housing part (22) by means of a closure element (68) and that the fuel inlet (32) opens into this area (72).
3. Hochdruckpumpe nach Anspruch 2, dadurch gekennzeichnet, dass zwischen dem Schaft (62) des Ventilglieds (56) und der3. High-pressure pump according to claim 2, characterized in that between the shaft (62) of the valve member (56) and the
Bohrung (50) ein freier Durchflussquerschnitt (63) vorhanden, durch den in geöffnetem Zustand des Ventilglieds (56) Kraftstoff aus dem Bereich (72) in den Pumpenarbei sräum (30) strömt.Bore (50) has a free flow cross-section (63) through which fuel flows from the area (72) into the pump working area (30) when the valve member (56) is open.
4. Hochdruckpumpe nach Anspruch 2, dadurch gekennzeichnet', dass die Bohrung (50) einen ersten, in den Pumpenarbeitsraum (30) mündenden Abschnitt (150) aufweist, zwischen dem und dem Schaft (62) des Ventilglieds (56) ein Durchflussquerschnitt (63) freigegeben ist, dass die4. High-pressure pump according to claim 2, characterized in that the bore (50) has a first section (150) opening into the pump working chamber (30), a flow cross-section (63) between and the stem (62) of the valve member (56) ) is released that the
Bohrung (50) einen in den Bereich (72) mündenden zweiten Abschnitt (250) aufweist, in dem der Schaft (62) des Ventilglieds (56) verschiebbar geführt ist und dass der erste Abschnitt (150) der Bohrung (50) mit dem Bereich (72) verbunden ist.Bore (50) has a second section (250) opening into the area (72), in which the stem (62) of the valve member (56) is slidably guided and that the first section (150) of the bore (50) with the area (72) is connected.
5. Hochdruckpumpe nach einem der vorstehenden Ansprüche, dadurch gekennzeichnet, dass die Dichtfläche (60) des Ventilglieds (56) zum Ventilsitz (52) hin konvex gewölbt, insbesondere zumindest annähernd kugelabschnittförmig, ausgebildet ist. 5. High-pressure pump according to one of the preceding claims, characterized in that the sealing surface (60) of the valve member (56) towards the valve seat (52) is convexly curved, in particular at least approximately spherical.
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)

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

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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)

Families Citing this family (30)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2008111396A (en) * 2006-10-31 2008-05-15 Denso Corp Manufacturing method of high-pressure fuel pump
WO2009043798A1 (en) * 2007-09-28 2009-04-09 ESV Werkzeuge und Zubehör für die elektrische Stromverteilung GmbH Mobile hydraulic pump for hydraulically operated tools
DE102007047417A1 (en) * 2007-10-04 2009-04-09 Robert Bosch Gmbh Piston pump for conveying a fluid and associated brake system
DE102008009226A1 (en) 2008-02-05 2009-12-17 Vladimir Volchkov High-pressure pump for fuel injection, has housing and base body which is formed from flange part connected with housing and consisting of guide component
DE102008000824A1 (en) * 2008-03-26 2009-10-01 Robert Bosch Gmbh Pump, in particular high-pressure fuel pump
GB0812888D0 (en) * 2008-07-15 2008-08-20 Delphi Tech Inc Improvements relating to fuel pumps
DE102008050657A1 (en) 2008-09-22 2010-03-25 Vladimir Volchkov Driving gear for reciprocating piston engines, particularly for fuel injecting high-pressure pumps, has return spring component, where each pair has two springs with left- and right rotation points
DE102008057089A1 (en) * 2008-11-13 2010-05-20 Continental Mechanical Components Germany Gmbh Pump unit for a high-pressure pump
DE102009001440A1 (en) 2009-03-10 2010-09-16 Robert Bosch Gmbh High-pressure pump, particularly for fuel injection device of internal combustion engine, has pump element which has pump piston axially guided in cylindrical bore of housing part formed as cylinder head
DE102009001463A1 (en) 2009-03-11 2010-09-16 Robert Bosch Gmbh High-pressure pump for fuel injection device of internal combustion engine, has high-pressure bore limited by internal wall surface of housing part, where counterbore of high-pressure bore causes counter-pressure to adjacent fuel pressure
EP2278163A1 (en) * 2009-07-20 2011-01-26 Delphi Technologies Holding S.à.r.l. Pump assembly
DE102010027745A1 (en) * 2010-04-14 2011-10-20 Robert Bosch Gmbh high pressure pump
DE102010031390B4 (en) * 2010-07-15 2018-08-09 Man Diesel & Turbo Se Suction valve of a fuel supply system of an internal combustion engine
DE102010046929A1 (en) * 2010-09-29 2012-03-29 Robert Bosch Gmbh Sealing bush arrangement and hydraulic device
CN102454574B (en) * 2010-10-17 2014-08-27 向英 Alcohol group fuel transportation method and alcohol group fuel burning machine special pump
IT1402403B1 (en) * 2010-10-21 2013-09-04 Bosch Gmbh Robert PUMPING GROUP FOR FUEL SUPPLEMENTATION, PREFERABLY GASOIL, TO AN INTERNAL COMBUSTION ENGINE.
CN103403333B (en) * 2011-02-10 2015-10-21 本田技研工业株式会社 The sealing configuration of fuel tank and possess the vehicle of sealing configuration of this fuel tank
DE102011103387A1 (en) * 2011-06-04 2012-12-06 Robert Bosch Gmbh Pre-assembled housing and preassembly procedure
ITMI20120243A1 (en) * 2012-02-17 2013-08-18 Bosch Gmbh Robert INTAKE VALVE AND PUMPING GROUP FOR FUEL SUPPLEMENT, PREFERIBLY GASOIL, TO AN INTERNAL COMBUSTION ENGINE
DE102013210861A1 (en) * 2013-06-11 2014-12-11 Robert Bosch Gmbh pump
DE102013212479A1 (en) 2013-06-27 2014-12-31 Robert Bosch Gmbh Inlet valve for one pump and pump with inlet valve
DE102013218895A1 (en) 2013-09-20 2015-03-26 Robert Bosch Gmbh Inlet valve for one pump and pump with inlet valve
DE102013220247A1 (en) 2013-10-08 2015-04-09 Robert Bosch Gmbh Pump, in particular high-pressure fuel pump
JP6533290B2 (en) * 2014-12-24 2019-06-19 ロベルト・ボッシュ・ゲゼルシャフト・ミト・ベシュレンクテル・ハフツングＲｏｂｅｒｔ Ｂｏｓｃｈ Ｇｍｂｈ Pump unit for supplying fuel, preferably diesel fuel, to an internal combustion engine
GB201501282D0 (en) * 2015-01-27 2015-03-11 Delphi International Operations Luxembourg S.�.R.L. Plunger assembly
DE102015203345A1 (en) 2015-02-25 2016-08-25 Robert Bosch Gmbh Pump, in particular high-pressure fuel pump
ITUB20159778A1 (en) * 2015-12-30 2017-06-30 Bosch Gmbh Robert PUMP FOR POWERING HIGH-PRESSURE FUEL TO AN INTERNAL COMBUSTION ENGINE
DE102016201600B4 (en) * 2016-02-03 2017-10-12 Continental Automotive Gmbh High-pressure fuel pump and fuel injection system
DE102016220360A1 (en) 2016-10-18 2018-04-19 Robert Bosch Gmbh Pump, in particular high-pressure fuel pump
US11692521B2 (en) 2021-09-08 2023-07-04 Robert Bosch Gmbh Fitting connection assembly for a fluid delivery system

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US302978A (en) * 1884-08-05 Air-compressor
US1445073A (en) * 1919-10-25 1923-02-13 Corpl Domenico Portable compressor
DE3505229A1 (en) * 1985-02-05 1986-08-07 Gebrüder Sulzer AG, Winterthur Device for the injection of a fine particulate, solid fuel suspended in a liquid into the combustion chamber of a reciprocating piston internal combustion engine
US5230613A (en) * 1990-07-16 1993-07-27 Diesel Technology Company Common rail fuel injection system
US5133645A (en) * 1990-07-16 1992-07-28 Diesel Technology Corporation Common rail fuel injection system
DE4323683A1 (en) * 1993-07-15 1995-01-19 Bosch Gmbh Robert Fuel injection pump
DE19717494A1 (en) * 1997-04-25 1998-10-29 Bosch Gmbh Robert Distributor type fuel injection pump
DE19729790C2 (en) * 1997-07-11 2002-08-29 Bosch Gmbh Robert Radial piston pump for high-pressure fuel supply
EP1379784B1 (en) * 2001-04-06 2008-03-05 Robert Bosch Gmbh Single-plunger injection pump for a common rail fuel injection system
DE10221305A1 (en) * 2002-05-14 2003-11-27 Bosch Gmbh Robert Radial piston pump for fuel injection system with improved high pressure resistance
ITBO20020498A1 (en) * 2002-07-30 2004-01-30 Magneti Marelli Powertrain Spa COMMON RAIL FUEL INJECTION SYSTEM WITH VARIABLE FLOW PUMP

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2005090790A1 *

Also Published As

Publication number Publication date
JP2007529675A (en) 2007-10-25
US20070215113A1 (en) 2007-09-20
ATE449260T1 (en) 2009-12-15
US7363913B2 (en) 2008-04-29
EP1727983B1 (en) 2009-11-18
DE102004013244A1 (en) 2005-10-06
JP4395534B2 (en) 2010-01-13
DE502005008539D1 (en) 2009-12-31
CN1934357A (en) 2007-03-21
WO2005090790A1 (en) 2005-09-29
CN100417814C (en) 2008-09-10

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