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WO1998048169A1 - High-pressure fuel pump - Google Patents

High-pressure fuel pump Download PDF

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Publication number
WO1998048169A1
WO1998048169A1 PCT/DE1998/000299 DE9800299W WO9848169A1 WO 1998048169 A1 WO1998048169 A1 WO 1998048169A1 DE 9800299 W DE9800299 W DE 9800299W WO 9848169 A1 WO9848169 A1 WO 9848169A1
Authority
WO
WIPO (PCT)
Prior art keywords
pressure
pump
drive shaft
fuel pump
pressure fuel
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.)
Ceased
Application number
PCT/DE1998/000299
Other languages
German (de)
French (fr)
Inventor
Josef Guentert
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
Priority to EP98909323A priority Critical patent/EP0931219A1/en
Priority to JP10544652A priority patent/JP2000512715A/en
Publication of WO1998048169A1 publication Critical patent/WO1998048169A1/en
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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
    • 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
    • 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
    • F04B1/053—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement with actuating or actuated elements at the inner ends of the cylinders
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16L—PIPES; JOINTS OR FITTINGS FOR PIPES; SUPPORTS FOR PIPES, CABLES OR PROTECTIVE TUBING; MEANS FOR THERMAL INSULATION IN GENERAL
    • F16L41/00—Branching pipes; Joining pipes to walls
    • F16L41/08—Joining pipes to walls or pipes, the joined pipe axis being perpendicular to the plane of a wall or to the axis of another pipe
    • F16L41/10—Joining pipes to walls or pipes, the joined pipe axis being perpendicular to the plane of a wall or to the axis of another pipe the extremity of the pipe being screwed into the wall

Definitions

  • the invention is based on a high-pressure radial piston type fuel pump according to the features of the preamble of claim 1.
  • a high-pressure fuel pump known from the document US Pat. No. 4,952,121 has a plurality of pump pistons which are arranged at an angular distance from one another about a central drive shaft and which, by means of prestressed springs, bear with their radially inner ends on the circumferential surface of the drive shaft and which are each axially displaceable in a guide bore .
  • the pump pistons with their end faces facing away from the drive shaft, each delimit a pump work chamber in the guide bore, which can alternately be connected to a fuel-filled low pressure chamber and to a high pressure delivery line.
  • High fuel pressures of up to 2000 bar are built up in the pump workspace during the high-pressure delivery phase, so that the requirements placed on the sealing points and bores under high pressure are very high with regard to reliable sealing.
  • the known high-pressure fuel pump has the disadvantage that the high-pressure channels are characterized by a large number of Components of the high pressure pump extend, which considerably increases the effort with regard to a high pressure seal.
  • the large number of components on the known high-pressure fuel pump causes increased construction and assembly costs.
  • the high-pressure fuel pump according to the invention with the characterizing features of claim 1 has the advantage over the fact that all channels and sealing points subjected to high pressure are arranged in a single common, one-piece pump housing. In this way, in a structurally simple manner, the sealing points necessary on the additional components used are eliminated, which in addition to a reduction in the sealing points also results in a reduction in the construction work.
  • the pump pistons of the individual pump elements are axially movably guided in a simple manner in a guide bore, which is worked directly into the pump housing, so that additional
  • Cylinder liners can be dispensed with.
  • the sealing points required when closing the high-pressure lines in the pump housing and at a connection of a pressure port on the pump housing are also advantageously designed as “biting edges”, for which purpose the pair of sealing surfaces each have a flat sealing surface on a first component and a sharp sealing edge interacting with this on a second component When the components are braced against one another, a slight plastic deformation is achieved at the contact line between the sealing edge and the flat sealing surface, which ensures a very secure seal even at very high internal fuel pressures.
  • a further advantage of the high-pressure fuel pump according to the invention is provided by the exclusive loan Guiding the high pressure ducts within the pump housing ses one, so that additional, conductive components and seals on these components can be dispensed with.
  • the pressure valve on the pump work rooms that is necessary for the function and opens in the direction of the pressure port is completely in the respective high-pressure channel within the
  • Integrated pump housing Integrated pump housing.
  • the individual high-pressure ducts leading away from the respective pump work spaces lead via a common high-pressure manifold within the pump housing to the pressure connection nozzle, to which a high-pressure delivery line can be connected, which preferably opens into a high-pressure storage space, from which in turn injection lines to the injection valves projecting into the combustion chamber of the internal combustion engine dissipate (common rail).
  • Screw connections, fuel channels and pump pistons are arranged in a common pump housing, it is possible to decouple all high-pressure sealing points from one another and thus design them statically exact.
  • the common pump housing (mono block) is preferably designed as a one-piece steel part. This common pump housing enables not only a high level of tightness due to the reduction in the number of components, but also a very compact design, so that the entire pump space required can be reduced.
  • the high-pressure fuel pump according to the invention can optionally be closed with a cover and preferably has a receiving device for a mounting flange, via which it can be attached to the respective engine housing.
  • the modular and modular design of the high-pressure fuel pump enables the attachment of various flange shapes, so that it can be easily adapted to different installation requirements.
  • This modular design is made possible by the provision of a steel housing monoblock in which all high-pressure-carrying parts are integrated. On This monoblock can now be fitted with various additional components, such as adapters, pre-feed pumps, etc., preferably made of aluminum, as required.
  • the drive shaft of the high-pressure fuel pump according to the invention is advantageously designed as an eccentric shaft, but there are also other drive shaft shapes, e.g. Camshafts possible.
  • FIG. 1 shows a longitudinal section through the high-pressure fuel pump according to the invention and
  • FIG. 2 shows a cross section of the high-pressure fuel pump according to FIG. 1 along the section line II.
  • the exemplary embodiment of the high-pressure fuel pump according to the invention shown in FIGS. 1 and 2 in two sectional views has an approximately triangular pump housing 1.
  • this pump housing 1 which is preferably made of steel, an annular central recess 3 is provided, which is open in one axial direction and closed by an inner housing end face 5 in a second axial direction.
  • a central axial through hole 7 is provided, which serves as a bearing bush of a central drive shaft 9.
  • the drive shaft 9 is rotatably guided with an end piece 11 in the through bore 7 and has, at its portion protruding into the recess 3 of the pump housing 1, an eccentric shaft part 13 forming a drive cam. This with its axis from the axis of the drive shaft 9 displaced eccentric shaft part 13 has on its circumference a drain ring 15 made of hardened material.
  • the pump housing 3 has guide bores 17 running radially to the drive shaft 9, which are arranged at the same angular distance from one another around the central drive shaft 9 and in each of which a pump piston 19 is slidably guided.
  • the pump pistons 19 At their ends facing away from the pump working spaces 21 and protruding from the respective guide bore 17, the pump pistons 19 each have a slide shoe 23, the pump pistons 19 thereby are formed in one piece in the form of a valve lifter.
  • the slide shoe 23, which is enlarged in cross section with respect to the pump piston 19, is held in contact with the end ring 15 of the eccentric shaft part 13 of the drive shaft 9 by means of a spring 25 with its end face remote from the pump work space.
  • the spring 25 engages on the ring end face of the slide shoe 23 facing the pump work space and, on the other hand, is supported on the ring end face of the pump housing 1 which delimits the recess 3. It is advantageous to arrange the spring 25 coaxially with the pump piston 19 and to guide it in a corresponding ring opening 27 in the pump housing 1.
  • the guide bores 17 receiving the pump pistons 19 are closed radially outward by a closure piece 29 which is screwed into the pump housing 1 and which, with its inside face of the pump, presses a spacer disk 31 axially against a housing shoulder formed on the guide bore 17.
  • the spacer disk 31, with its end face facing the pump piston 19, delimits the pump working space 21 and also forms with this end face a valve seat surface for a disk-shaped valve member 33 which is held in contact with the spacer disk 31 by means of a leaf spring 35.
  • the spacer 31 has an axial through-bore 37, from which a radial bore 39 leads, which opens into a fuel supply line 41, which, on the other hand, originates from a fuel-filled low-pressure chamber, not shown.
  • Flow cross section from the fuel supply line 41 in the pump work chamber 21 is kept closed by the disc-shaped valve member 33 by the leaf spring 35.
  • the leaf spring 35 is supported on a cranked spring plate 43, which is clamped with its upper edge between the housing shoulder and the spacer 31.
  • a radial high-pressure bore 45 leads from the guide bore 17 of each pump piston 19 in the area of the pump work chamber 21, which opens into a high-pressure duct 47, the individual high-pressure ducts 47 via a common manifold (not shown in detail) inside the pump housing 1 to one into the pump housing 1 screwed discharge nozzle 49 open.
  • a high-pressure delivery line can be connected to this pressure connection 49, which on the other hand opens into a high-pressure storage space (common rail), from which in turn discharge the individual injection lines to the injection valves (not shown) which project into the combustion chamber of the internal combustion engine to be supplied.
  • a pressure valve 51 which opens in the direction of the pressure connection 49, is inserted into each high-pressure bore 45 and, in the exemplary embodiment, is designed as a check valve with a spherical valve member 53.
  • This valve ball 53 is held on a conical valve seat by means of a spring plate 55 and a valve spring 57, the valve spring 57 being supported on a counter stop 59 that can be screwed into the pump housing 1.
  • the sealing surfaces on the counter stop 59 and on the end face of the pressure connection 49 screwed into the housing 1 are designed as so-called biting edges, in which a flat sealing surface on a first component interacts with a sharp-edged sealing edge (cutting edge) on a second component, whereby when the components are braced against each other, a sealing plastic deformation along the line of contact of the flat and sharp-edged sealing surface is set.
  • the pump housing 1 also has, at its open end facing away from the end piece 11 of the drive shaft 9, an axially projecting tube extension 61 which forms a receptacle for a fastening flange 63 which forms a pump cover.
  • This mounting flange 63 is pushed with a corresponding inner recess in a sealing manner onto the tubular extension 61 and is axially fastened to the latter.
  • the fastening flange 63 is centered on the tube extension 61 and is preferably clamped to the pump housing 1 by means of fastening screws which are screwed into corresponding holes 71 in the pump housing 1 which form screw holes.
  • the mounting flange 63 has an axial through opening through which the free end of the drive shaft 9 projects and is sealingly guided there. There are also 63 mounting holes on the mounting flange 65 provided with which the high-pressure fuel pump can be attached to an engine housing. In addition, a cone 67 is provided at the free end of the drive shaft 9, via which a motor-side drive part can be attached to the drive shaft 9 in a rotationally locking manner. At its end facing away from the free end of the drive shaft 9, the through bore 7 in the pump housing 1 receiving the drive shaft 9 is sealed by a cover 69.
  • the high-pressure fuel pump works in the following manner.
  • a prefeed pump (not shown) delivers fuel from a low-pressure chamber, preferably a fuel storage tank, to the valve member 33 via the fuel supply line 41 and the bores 39, 37 in the spacer disk 31, this valve working as a suction valve.
  • the pump pistons 19 resting on the eccentric shaft part 13 are shifted up and down alternately.
  • the fuel located in the pump work chamber 21 is compressed to a very high fuel pressure of up to 2000 bar and thereby opens the pressure valve 51 arranged in the high-pressure bore 45, so that the fuel under high pressure passes through the high-pressure channel 47 and the common manifold to the pressure port 49 can flow. From there, the high-pressure fuel reaches the common high-pressure storage space (common rail) via the high-pressure delivery line, where it is stored to supply the injection lines to the injection valves. After passing through top dead center
  • the pump piston 19 is again displaced radially inward, the pressure in the pump working space 21 drops below a certain opening pressure and the pressure valve 51 closes again.
  • the high-pressure bore 45 open into the guide bore 17 in such a way that the pump piston 19 closes the inlet opening of the high-pressure bore 45 with its lateral surface from a certain piston stroke position.
  • the fuel pressure in the pump work chamber 21 drops again below the fuel pressure in the supply line 41, so that the valve member 33 of the suction valve lifts again from its seat and fuel is fed via the leaf spring 35 and the spring plate 43 into the Pump work space 21 can flow.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Reciprocating Pumps (AREA)

Abstract

The invention relates to a high-pressure fuel pump with several pump pistons (19) separated from each other at different angles around an axle drive shaft (9). By means of prestressed springs, the radially inward facing ends of these pistons rest against the peripheral surface of the axle drive shaft (9), and each piston is fitted in a guide bore hole in such a way as to be axially displaceable. With the side facing away from the axle drive shaft (9), the respective pump pistons (19) define a pump working area (21) in the guide bore hole (17), which area can be alternately connected to a fuel-filled low-pressure area and to a high-pressure delivery line. To improve high-pressure tightness, the guide bore holes (17) of the pump pistons (19) and the high-pressure lines (45, 47) are arranged directly in a common, one-piece pump case (1).

Description

KraftstoffhochdruckpumpeHigh pressure fuel pump

Stand der TechnikState of the art

Die Erfindung geht von einer Kraftstoffhochdruckpumpe der Radialkolbenbauart gemäß den Merkmalen des Oberbegriffs des Patentanspruchs 1 aus. Eine derartige aus der Schrift US-PS 4,952,121 bekannte Kraftstoffhochdruckpumpe weist mehrere, im Winkelabstand zueinander um eine zentrale Antriebswelle angeordnete Pumpenkolben auf, die mittels vorgespannter Federn mit ihren radial innenliegenden Enden an der Umfangsflache der Antriebswelle anliegen und die dabei jeweils in einer Führungsbohrung axial verschiebbar sind. Die Pumpenkolben begrenzen dabei mit ihren der Antriebswelle abgewandten Stirnflächen jeweils einen Pumpen- arbeitsraum in der Führungsbohrung, der alternierend mit einem kraftstoffgefüllten Niederdruckraum und mit einer Hochdruckförderleitung verbindbar ist.The invention is based on a high-pressure radial piston type fuel pump according to the features of the preamble of claim 1. Such a high-pressure fuel pump known from the document US Pat. No. 4,952,121 has a plurality of pump pistons which are arranged at an angular distance from one another about a central drive shaft and which, by means of prestressed springs, bear with their radially inner ends on the circumferential surface of the drive shaft and which are each axially displaceable in a guide bore . The pump pistons, with their end faces facing away from the drive shaft, each delimit a pump work chamber in the guide bore, which can alternately be connected to a fuel-filled low pressure chamber and to a high pressure delivery line.

Dabei werden im Pumpenarbeitsraum während der Hochdruckför- derphase sehr hohe Kraftstoffdrücke von bis zu 2000 bar aufgebaut, so daß die Anforderungen an die mit Hochdruck beaufschlagen Dichtstellen und Bohrungen hinsichtlich eines sicheren Abdichtens sehr hoch sind. Dabei weist die bekannte Kraftstoffhochdruckpumpe jedoch den Nachteil auf, daß sich die hochdruckführenden Kanäle durch eine Vielzahl von Bauteilen der Hochdruckpumpe erstrecken, was den Aufwand hinsichtlich einer Hochdruckabdichtung erheblich vergrößert. Zudem verursacht die hohe Anzahl von Bauteilen an der bekannten Kraftstoffhochdruckpumpe einen erhöhten Bau- und Montageaufwand.Very high fuel pressures of up to 2000 bar are built up in the pump workspace during the high-pressure delivery phase, so that the requirements placed on the sealing points and bores under high pressure are very high with regard to reliable sealing. However, the known high-pressure fuel pump has the disadvantage that the high-pressure channels are characterized by a large number of Components of the high pressure pump extend, which considerably increases the effort with regard to a high pressure seal. In addition, the large number of components on the known high-pressure fuel pump causes increased construction and assembly costs.

Vorteile der ErfindungAdvantages of the invention

Die erfindungsgemäße Kraftstoffhochdruckpumpe mit den kenn- zeichnenden Merkmalen des Patentanspruchs 1 hat dem gegenüber den Vorteil, daß sämtliche mit Hochdruck beaufschlagten Kanäle und Dichtstellen in einem einzigen gemeinsamen, einstückigen Pumpengehäuse angeordnet sind. Auf diese Weise entfallen in konstruktiv einfacher Weise die an den zusätz- lieh eingesetzten Bauteilen notwendigen Dichtstellen, was neben einer Reduzierung der Dichtstellen auch eine Reduzierung des Bauaufwandes zur Folge hat . Die Pumpenkolben der einzelnen Pumpenelemente sind dabei in einfacher Weise in einer Führungsbohrung axial beweglich geführt, die direkt in das Pumpengehäuse eingearbeitet wird, so daß auf zusätzlicheThe high-pressure fuel pump according to the invention with the characterizing features of claim 1 has the advantage over the fact that all channels and sealing points subjected to high pressure are arranged in a single common, one-piece pump housing. In this way, in a structurally simple manner, the sealing points necessary on the additional components used are eliminated, which in addition to a reduction in the sealing points also results in a reduction in the construction work. The pump pistons of the individual pump elements are axially movably guided in a simple manner in a guide bore, which is worked directly into the pump housing, so that additional

Zylinderbüchsen verzichtet werden kann. Die beim Verschließen der Hochdruckleitungen im Pumpengehäuse und an einem Anschluß eines Druckstutzens am Pumpengehäuse notwendigen Dichtstellen sind desweiteren in vorteilhafter Weise als „Beißkanten" ausgebildet, wozu die Dichtflächenpaarungen jeweils eine plane Dichtfläche an einem ersten Bauteil und eine mit dieser zusammenwirkende scharfe Dichtkante an einem zweiten Bauteil aufweisen. Dabei wird beim Verspannen der Bauteile gegeneinander an der Berührungslinie zwischen der Dichtkante und der planen Dichtfläche eine geringfügige plastische Verformung erreicht, die eine sehr sichere Abdichtung auch bei sehr hohen Kraftstoffinnendrücken gewährleistet. Ein weiterer Vorteil der erfindungsgemäßen Kraftstoffhochdruckpumpe stellt sich durch das ausschließ- liehe Führen der Hochdruckkanäle innerhalb des Pumpengehäu- ses ein, so daß auf zusätzliche, leitungsführende Bauteile und Abdichtungen an diesen Bauteilen verzichtet werden kann. Dabei ist auch das für die Funktion notwendige, in Richtung Druckstutzen öffnende Druckventil an den Pumpenarbeitsräumen vollständig in den jeweiligen Hochdruckkanal innerhalb desCylinder liners can be dispensed with. The sealing points required when closing the high-pressure lines in the pump housing and at a connection of a pressure port on the pump housing are also advantageously designed as “biting edges”, for which purpose the pair of sealing surfaces each have a flat sealing surface on a first component and a sharp sealing edge interacting with this on a second component When the components are braced against one another, a slight plastic deformation is achieved at the contact line between the sealing edge and the flat sealing surface, which ensures a very secure seal even at very high internal fuel pressures. A further advantage of the high-pressure fuel pump according to the invention is provided by the exclusive loan Guiding the high pressure ducts within the pump housing ses one, so that additional, conductive components and seals on these components can be dispensed with. In this case, the pressure valve on the pump work rooms that is necessary for the function and opens in the direction of the pressure port is completely in the respective high-pressure channel within the

Pumpengehäuses integriert. Die einzelnen, von den jeweiligen Pumpenarbeitsräumen abführenden Hochdruckkanäle führen dabei über eine gemeinsame Hochdrucksammelleitung innerhalb des Pumpengehäuses zum Druckanschlußstutzen, an den eine Hoch- druckförderleitung anschließbar ist, die vorzugsweise in einen Hochdruckspeicherraum mündet, von dem seinerseits Einspritzleitungen zu den in den Brennraum der Brennkraftmaschine ragenden Einspritzventilen abführen (Common Rail) .Integrated pump housing. The individual high-pressure ducts leading away from the respective pump work spaces lead via a common high-pressure manifold within the pump housing to the pressure connection nozzle, to which a high-pressure delivery line can be connected, which preferably opens into a high-pressure storage space, from which in turn injection lines to the injection valves projecting into the combustion chamber of the internal combustion engine dissipate (common rail).

Da dabei alle mit Hochdruck beaufschlagten Dichtstellen,Since all the sealing points that are exposed to high pressure,

Verschraubungen, Kraftstoffkanäle und Pumpenkolben in einem gemeinsamen Pumpengehäuse angeordnet sind ist es möglich, sämtliche Hochdruckdichtstellen voneinander zu entkoppeln und somit statisch exakt auszulegen. Dabei ist das gemein- same Pumpengehäuse (Mono-Block) vorzugsweise als einteiliges Stahlteil ausgebildet. Dieses gemeinsame Pumpengehäuse ermöglicht dabei neben einer hohen Dichtheit aufgrund der Reduzierung der Bauteile auch eine sehr kompakte Bauweise, so daß sich der gesamte benötigte Pumpenbauraum verringern läßt. Die erfindungsgemäße Kraftstoffhochdruckpumpe läßt sich dabei wahlweise mit einem Deckel verschließen und weist vorzugsweise eine Aufnahmevorrichtung für einen Befestigungsflansch auf, über den sie an das jeweilige Motorengehäuse anbringbar ist. Dabei ermöglicht die modulare und baukastengerechte Bauweise der Kraftstoffhochdruckpumpe die Befestigung verschiedener Flanschformen, so daß sie in einfacher Weise an verschiedene Einbauanforderungen anpaßbar ist . Diese modulare Bauweise wird dabei durch das Vorsehen eines Gehäusemonoblocks aus Stahl ermöglicht, in den sämtliche Hochdruck-führenden Teile integriert sind. An diesen Monoblock können nun je nach Bedarf verschiedenste Zusatzbauteile wie Adapter, Vorförderpumpen u.a., vorzugsweise aus Aluminium angebracht werden.Screw connections, fuel channels and pump pistons are arranged in a common pump housing, it is possible to decouple all high-pressure sealing points from one another and thus design them statically exact. The common pump housing (mono block) is preferably designed as a one-piece steel part. This common pump housing enables not only a high level of tightness due to the reduction in the number of components, but also a very compact design, so that the entire pump space required can be reduced. The high-pressure fuel pump according to the invention can optionally be closed with a cover and preferably has a receiving device for a mounting flange, via which it can be attached to the respective engine housing. The modular and modular design of the high-pressure fuel pump enables the attachment of various flange shapes, so that it can be easily adapted to different installation requirements. This modular design is made possible by the provision of a steel housing monoblock in which all high-pressure-carrying parts are integrated. On This monoblock can now be fitted with various additional components, such as adapters, pre-feed pumps, etc., preferably made of aluminum, as required.

Die Antriebswelle der erfindungsgemäßen Kraftstoffhochdruckpumpe ist in vorteilhafter Weise als Exzenterwelle ausgebildet, es sind jedoch auch andere Antriebswellenformen, z.B. Nockenwellen möglich. Zudem sind verschiedene Formen von Stößeln am Pumpenkolben wie z.B. Tassenstössel oder Rollen- stössel alternativ möglich.The drive shaft of the high-pressure fuel pump according to the invention is advantageously designed as an eccentric shaft, but there are also other drive shaft shapes, e.g. Camshafts possible. In addition, various forms of plungers on the pump piston, such as Cup tappet or roller tappet alternatively possible.

Weitere Vorteile und vorteilhafte Ausgestaltungen des Gegenstandes der Erfindung sind der Beschreibung, der Zeichnung und den Patentansprüchen entnehmbar.Further advantages and advantageous configurations of the subject matter of the invention can be gathered from the description, the drawing and the patent claims.

Zeichnungdrawing

Ein Ausführungsbeispiel der erfindungsgemäßen Kraftstoffhochdruckpumpe ist in der Zeichnung dargestellt und wird in der folgenden Beschreibung näher erläutert. Es zeigen dieAn embodiment of the high-pressure fuel pump according to the invention is shown in the drawing and is explained in more detail in the following description. They show

Figur 1 einen Längsschnitt durch die erfindungsgemäße Kraftstoffhochdruckpumpe und die Figur 2 einen Querschnitt der Kraftstoffhochdruckpumpe gemäß Figur 1 entlang der Schnittlinie II.1 shows a longitudinal section through the high-pressure fuel pump according to the invention and FIG. 2 shows a cross section of the high-pressure fuel pump according to FIG. 1 along the section line II.

Beschreibung des AusführungsbeispielsDescription of the embodiment

Das in den Figuren 1 und 2 in zwei Schnittansichten dargestellte Ausführungsbeispiel der erfindungsgemäßen Kraft- stoffhochdruckpumpe weist ein in etwa dreieckförmiges Pumpengehäuse 1 auf. In diesem, vorzugsweise aus Stahl gefertigtem Pumpengehäuse 1 ist eine kreisringförmige zentrische Ausnehmung 3 vorgesehen, die in eine Achsrichtung offen und in einer zweiten Achsrichtung durch eine innere Gehäusestirnfläche 5 verschlossen ist. In dieser Gehäusestirnfläche 5 ist eine zentrale axiale Durchgangsbohrung 7 vorgesehen, die als Lagerbuchse einer zentralen Antriebswelle 9 dient. Die Antriebswelle 9 ist dabei mit einem Endstück 11 drehbar in der Durchgangsbohrung 7 geführt und weist an ihrem in die Ausnehmung 3 des Pumpengehäuses 1 ragenden Abschnitt einen, einen Antriebsnocken bildenden Exzenterwellenteil 13 auf. Dieser mit seiner Achse aus der Achse der Antriebswelle 9 verschobene Exzenterwellenteil 13 weist an seinem Umfang einen Ablaufring 15 aus gehärtetem Material auf.The exemplary embodiment of the high-pressure fuel pump according to the invention shown in FIGS. 1 and 2 in two sectional views has an approximately triangular pump housing 1. In this pump housing 1, which is preferably made of steel, an annular central recess 3 is provided, which is open in one axial direction and closed by an inner housing end face 5 in a second axial direction. In this Housing end face 5, a central axial through hole 7 is provided, which serves as a bearing bush of a central drive shaft 9. The drive shaft 9 is rotatably guided with an end piece 11 in the through bore 7 and has, at its portion protruding into the recess 3 of the pump housing 1, an eccentric shaft part 13 forming a drive cam. This with its axis from the axis of the drive shaft 9 displaced eccentric shaft part 13 has on its circumference a drain ring 15 made of hardened material.

Desweiteren weist das Pumpengehäuse 3 radial zur Antriebswelle 9 verlaufende Führungsbohrungen 17 auf, die im gleichen Winkelabstand zueinander um die zentrale Antriebs- welle 9 angeordnet sind und in denen jeweils ein Pumpenkolben 19 gleitverschiebbar geführt ist. Dabei begrenzen die Pumpenkolben 19 mit ihren der Antriebswelle 9 abgewandten Stirnflächen jeweils einen Pumpenarbeitsraum 21 in der Führungsbohrung 17. An ihren den Pumpenarbeitsräumen 21 abgewandten, aus der jeweiligen Führungsbohrung 17 herausragenden Enden weisen die Pumpenkolben 19 jeweils einen Gleitschuh 23 auf, wobei die Pumpenkolben 19 dabei in Form eines Ventilstößels einteilig ausgebildet sind. Der im Querschnitt gegenüber dem Pumpenkolben 19 vergrößerte Gleitschuh 23 wird dabei mit seiner pumpenarbeitsraumfernen Stirnfläche mittels einer Feder 25 in Anlage am Ablaufring 15 des Exzenterwellenteils 13 der Antriebswelle 9 gehalten. Dazu greift die Feder 25 an der pumpenarbeitsraumzugewandten Ringstirnfläche des Gleitschuhs 23 an und stützt sich andererseits an der die Ausnehmung 3 begrenzenden Ringstirnfläche des Pumpengehäuses 1 ab. Dabei ist es vorteilhaft, die Feder 25 koaxial zum Pumpenkolben 19 anzuordnen und in einer entsprechenden Ringöffnung 27 im Pumpengehäuse 1 zu führen . Die die Pumpenkolben 19 aufnehmenden Führungsbohrungen 17 sind radial auswärts durch ein in das Pumpengehäuse 1 eingeschraubtes Verschlußstück 29 verschlossen, das mit seiner pumpeninneren Stirnfläche eine Distanzscheibe 31 axial gegen einen an der Führungsbohrung 17 gebildeten Gehäuseabsatz preßt. Dabei begrenzt die Distanzscheibe 31 mit ihrer dem Pumpenkolben 19 zugewandten Stirnfläche den Pumpenarbeits- raum 21 und bildet zudem mit dieser Stirnfläche eine Ventilsitzfläche für ein scheibenförmiges Ventilglied 33, das mittels einer Blattfeder 35 in Anlage an der Distanzscheibe 31 gehalten wird. Dabei weist die Distanzscheibe 31 eine axiale Durchgangsbohrung 37 auf, von der eine Radialbohrung 39 abführt die an eine KraftstoffZuführungsleitung 41 mündet, die andererseits von einem nicht gezeigten kraft- stoffgefüllten Niederdruckraum ausgeht. Dabei wird derFurthermore, the pump housing 3 has guide bores 17 running radially to the drive shaft 9, which are arranged at the same angular distance from one another around the central drive shaft 9 and in each of which a pump piston 19 is slidably guided. The pump pistons 19, with their end faces facing away from the drive shaft 9, each delimit a pump working space 21 in the guide bore 17. At their ends facing away from the pump working spaces 21 and protruding from the respective guide bore 17, the pump pistons 19 each have a slide shoe 23, the pump pistons 19 thereby are formed in one piece in the form of a valve lifter. The slide shoe 23, which is enlarged in cross section with respect to the pump piston 19, is held in contact with the end ring 15 of the eccentric shaft part 13 of the drive shaft 9 by means of a spring 25 with its end face remote from the pump work space. For this purpose, the spring 25 engages on the ring end face of the slide shoe 23 facing the pump work space and, on the other hand, is supported on the ring end face of the pump housing 1 which delimits the recess 3. It is advantageous to arrange the spring 25 coaxially with the pump piston 19 and to guide it in a corresponding ring opening 27 in the pump housing 1. The guide bores 17 receiving the pump pistons 19 are closed radially outward by a closure piece 29 which is screwed into the pump housing 1 and which, with its inside face of the pump, presses a spacer disk 31 axially against a housing shoulder formed on the guide bore 17. In this case, the spacer disk 31, with its end face facing the pump piston 19, delimits the pump working space 21 and also forms with this end face a valve seat surface for a disk-shaped valve member 33 which is held in contact with the spacer disk 31 by means of a leaf spring 35. The spacer 31 has an axial through-bore 37, from which a radial bore 39 leads, which opens into a fuel supply line 41, which, on the other hand, originates from a fuel-filled low-pressure chamber, not shown. The

Durchflußquerschnitt von der KraftstoffZuführungsleitung 41 in den Pumpenarbeitsraum 21 vom scheibenförmigen Ventilglied 33 durch die Blattfeder 35 verschlossen gehalten. Die Blattfeder 35 stützt sich dabei an einem gekröpften Federteller 43 ab, der mit seinem oberen Rand zwischen Gehäuseabsatz und Distanzscheibe 31 eingespannt ist.Flow cross section from the fuel supply line 41 in the pump work chamber 21 is kept closed by the disc-shaped valve member 33 by the leaf spring 35. The leaf spring 35 is supported on a cranked spring plate 43, which is clamped with its upper edge between the housing shoulder and the spacer 31.

Von der Führungsbohrung 17 jedes Pumpenkolbens 19 führt weiterhin im Bereich des Pumpenarbeitsraumes 21 eine radiale Hochdruckbohrung 45 ab, die in einen Hochdruckkanal 47 mündet, wobei die einzelnen Hochdruckkanäle 47 über eine gemeinsame, nicht näher gezeigte Sammelleitung innerhalb des Pumpengehäuses 1 an einen in das Pumpengehäuse 1 eingeschraubten Druckstutzen 49 münden. An diesen Druckstutzen 49 ist eine Hochdruckförderleitung anschließbar, die anderseits in einen Hochdruckspeicherraum (Common Rail) mündet, von dem seinerseits die einzelnen Einspritzleitungen zu den nicht gezeigten, in den Brennraum der zu versorgende Brennkraftmaschine ragenden Einspritzventilen abführen. Dabei ist in jede Hochdruckbohrung 45 ein in Richtung Druckstutzen 49 öffnendes Druckventil 51 eingesetzt, das im Ausführungsbeispiel als Rückschlagventil mit einem kugelför- migen Ventilglied 53 ausgebildet ist. Diese Ventilkugel 53 wird dabei über einen Federteller 55 und eine Ventilfeder 57 an einem konischen Ventilsitz gehalten, wobei sich die Ventilfeder 57 an einem in das Pumpengehäuse 1 einschraubbaren Gegenanschlag 59 abstützt. Die dichtenden Flächen am Gegenanschlag 59 sowie an der in das Gehäuse 1 eingeschraubten Stirnfläche des Druckstutzens 49 sind dabei als sogenannte Beißkanten ausgebildet, bei denen jeweils eine plane Dichtfläche an einem ersten Bauteil mit einer scharfkantigen Dichtkante (Schneide) an einem zweiten Bauteil zusammenwirkt, wobei sich beim Verspannen der Bauteile gegeneinander eine dichtende plastische Verformung entlang der Berührungslinie der planen und scharfkantigen Dichtfläche einstellt.A radial high-pressure bore 45 leads from the guide bore 17 of each pump piston 19 in the area of the pump work chamber 21, which opens into a high-pressure duct 47, the individual high-pressure ducts 47 via a common manifold (not shown in detail) inside the pump housing 1 to one into the pump housing 1 screwed discharge nozzle 49 open. A high-pressure delivery line can be connected to this pressure connection 49, which on the other hand opens into a high-pressure storage space (common rail), from which in turn discharge the individual injection lines to the injection valves (not shown) which project into the combustion chamber of the internal combustion engine to be supplied. A pressure valve 51, which opens in the direction of the pressure connection 49, is inserted into each high-pressure bore 45 and, in the exemplary embodiment, is designed as a check valve with a spherical valve member 53. This valve ball 53 is held on a conical valve seat by means of a spring plate 55 and a valve spring 57, the valve spring 57 being supported on a counter stop 59 that can be screwed into the pump housing 1. The sealing surfaces on the counter stop 59 and on the end face of the pressure connection 49 screwed into the housing 1 are designed as so-called biting edges, in which a flat sealing surface on a first component interacts with a sharp-edged sealing edge (cutting edge) on a second component, whereby when the components are braced against each other, a sealing plastic deformation along the line of contact of the flat and sharp-edged sealing surface is set.

Das Pumpengehäuse 1 weist weiterhin an seinem dem Endstück 11 der Antriebswelle 9 abgewandten offenen Ende einen axial vorstehenden Rohransatz 61 auf, der eine Aufnahme für einen, einen Pumpendeckel bildenden Befestigungsflansch 63 bildet. Dabei ist dieser Befestigungsflansch 63 mit einer entsprechenden Innenausnehmung dichtend auf den Rohransatz 61 aufgeschoben und axial an diesem befestigt. Dazu ist der Befestigungsflansch 63 auf dem Rohransatz 61 zentriert und wird vorzugsweise mittels Befestigungsschrauben, die in entsprechende, Schraublöcher bildende Bohrungen 71 im Pumpengehäuse 1 eingeschraubt werden, am Pumpengehäuse 1 verspannt. Der Befestigungsflansch 63 weist eine axiale Durchgangsöffnung auf, durch die das freie Ende der Antriebswelle 9 ragt und dort dichtend geführt ist. Desweiteren sind am Befestigungsflansch 63 Aufnahmebohrungen 65 vorgesehen, mit denen die Kraftstoffhochdruckpumpe an einem Motorgehäuse befestigbar ist . Zudem ist am freien Ende der Antriebswelle 9 ein Konus 67 vorgesehen, über den sich ein motorseitiges Antriebsteil auf der Antriebswelle 9 drehschlüssig befestigen läßt. An ihrem dem freien Ende der Antriebswelle 9 abgewandten Ende ist die die Antriebswelle 9 aufnehmende Durchgangsbohrung 7 im Pumpengehäuse 1 durch einen Deckel 69 dichtend verschlossen.The pump housing 1 also has, at its open end facing away from the end piece 11 of the drive shaft 9, an axially projecting tube extension 61 which forms a receptacle for a fastening flange 63 which forms a pump cover. This mounting flange 63 is pushed with a corresponding inner recess in a sealing manner onto the tubular extension 61 and is axially fastened to the latter. For this purpose, the fastening flange 63 is centered on the tube extension 61 and is preferably clamped to the pump housing 1 by means of fastening screws which are screwed into corresponding holes 71 in the pump housing 1 which form screw holes. The mounting flange 63 has an axial through opening through which the free end of the drive shaft 9 projects and is sealingly guided there. There are also 63 mounting holes on the mounting flange 65 provided with which the high-pressure fuel pump can be attached to an engine housing. In addition, a cone 67 is provided at the free end of the drive shaft 9, via which a motor-side drive part can be attached to the drive shaft 9 in a rotationally locking manner. At its end facing away from the free end of the drive shaft 9, the through bore 7 in the pump housing 1 receiving the drive shaft 9 is sealed by a cover 69.

Die erfindungsgemäße Kraftstoffhochdruckpumpe arbeitet in folgender Weise. Zunächst wird durch eine nicht gezeigte Vorförderpumpe Kraftstoff aus einem Niederdruckraum, vorzugsweise einem Kraftstoffvorratstank über die KraftstoffZuführungsleitung 41 und die Bohrungen 39, 37 in der Distanzscheibe 31 an das Ventilglied 33 gefördert, wobei dieses Ventil als Saugventil arbeitet. Beim rotierenden Antrieb der Antriebswelle 9 werden die am Exzenterwellenteil 13 anliegenden Pumpenkolben 19 alternierend nach oben und unten verschoben. Dabei entsteht bei der radial nach innen gerichteten Saughubbewegung des Pumpenkolbens 19 ein Unterdruck im Pumpenarbeitsraum 21, so daß der am Ventilglied 33 des Saugventils anstehende Kraftstoffdruck ausreicht das Ventilglied 33 vom Ventilsitz an der Distanzscheibe 31 abzuheben und so den Kraftstoffdurchtrittsquerschnitt aus der Zuführungsleitung 41 in den Pumpenarbeitsraum 21 aufzusteuern. Nach Durchlaufen des unteren Totpunktes wird der Pumpenkolben 19 anschließend radial auswärts in Richtung oberer Totpunkt verschoben, wobei diese Pumpenkolbenhubbewegung dem Förderhub entspricht . Der im Pumpenarbeitsraum 21 befindliche Kraftstoff wird dabei auf einen sehr hohen Kraftstoffdruck von bis zu 2000 bar komprimiert und öffnet dabei das in der Hochdruckbohrung 45 angeordnete Druckventil 51, so daß der unter hohem Druck stehende Kraftstoff über den Hochdruckkanal 47 und die gemeinsame Sammelleitung zum Druckstutzen 49 strömen kann. Von dort gelangt der KraftStoffhochdruck über die Hochdruckförderleitung in den gemeinsamen Hochdruckspeicherraum (Common Rail) , wo er zur Versorgung der Einspritzleitungen zu den Einspritzventilen gespeichert wird. Nach Durchlaufen des oberen Totpunktes derThe high-pressure fuel pump according to the invention works in the following manner. First, a prefeed pump (not shown) delivers fuel from a low-pressure chamber, preferably a fuel storage tank, to the valve member 33 via the fuel supply line 41 and the bores 39, 37 in the spacer disk 31, this valve working as a suction valve. When the drive shaft 9 is driven in rotation, the pump pistons 19 resting on the eccentric shaft part 13 are shifted up and down alternately. This creates a vacuum in the pump work chamber 21 during the radially inward suction stroke movement of the pump piston 19, so that the fuel pressure present at the valve member 33 of the suction valve is sufficient to lift the valve member 33 from the valve seat on the spacer disk 31 and thus the fuel passage cross section from the supply line 41 into the pump work chamber 21 to tax. After passing through the bottom dead center, the pump piston 19 is then displaced radially outward in the direction of the top dead center, this pump piston stroke movement corresponding to the delivery stroke. The fuel located in the pump work chamber 21 is compressed to a very high fuel pressure of up to 2000 bar and thereby opens the pressure valve 51 arranged in the high-pressure bore 45, so that the fuel under high pressure passes through the high-pressure channel 47 and the common manifold to the pressure port 49 can flow. From there, the high-pressure fuel reaches the common high-pressure storage space (common rail) via the high-pressure delivery line, where it is stored to supply the injection lines to the injection valves. After passing through top dead center

Pumpenkolbenbewegung wird der Pumpenkolben 19 erneut radial einwärts verschoben, der Druck im Pumpenarbeitsraum 21 sinkt unter einen bestimmten Öffnungsdruck und das Druckventil 51 schließt erneut. Es ist jedoch alternativ auch möglich, die Hochdruckbohrung 45 so in die Führungsbohrung 17 münden zu lassen, daß der Pumpenkolben 19 die Eintrittsöffnung der Hochdruckbohrung 45 ab einer bestimmten Kolbenhublage mit seiner Mantelfläche verschließt. Beim sich anschließenden Saughub des Pumpenkolbens 19 in Richtung unterer Totpunkt sinkt der Kraftstoffdruck im Pumpenarbeitsraum 21 erneut unter den Kraftstoffdruck in der Zuführungsleitung 41, so daß das Ventilglied 33 des Saugventils erneut von seinem Sitz abhebt und Kraftstoff über die Blattfeder 35 und den Federteller 43 in den Pumpenarbeitsraum 21 einströmen kann.Pump piston movement, the pump piston 19 is again displaced radially inward, the pressure in the pump working space 21 drops below a certain opening pressure and the pressure valve 51 closes again. However, it is alternatively also possible to have the high-pressure bore 45 open into the guide bore 17 in such a way that the pump piston 19 closes the inlet opening of the high-pressure bore 45 with its lateral surface from a certain piston stroke position. During the subsequent suction stroke of the pump piston 19 in the direction of the bottom dead center, the fuel pressure in the pump work chamber 21 drops again below the fuel pressure in the supply line 41, so that the valve member 33 of the suction valve lifts again from its seat and fuel is fed via the leaf spring 35 and the spring plate 43 into the Pump work space 21 can flow.

Dabei ermöglicht die Anordnung sämtlicher mit Hochdruck beaufschlagter Dichtstellen, Verschraubungen, Bohrungen zur Kraftstoffzusammenführung und der einzelnen Pumpenelemente in einem gemeinsamen einstückigen Pumpengehäuse eine sehr hohe Dichtwirkung gegenüber hohen Kraftstoffdrücken und somit eine hohe Funktionssicherheit der erfindungsgemäßen Kraftstoffhochdruckpumpe . The arrangement of all the high-pressure sealing points, screw connections, bores for fuel assembly and the individual pump elements in a common one-piece pump housing enables a very high sealing effect against high fuel pressures and thus a high level of functional reliability of the high-pressure fuel pump according to the invention.

Claims

Ansprüche Expectations 1. Kraftstoffhochdruckpumpe mit mehreren, im Winkelabstand zueinander um eine zentrale Antriebswelle (9) angeordneten Pumpenkolben (19) , die mittels vorgespannter Federn (25) mit ihren radial innen liegenden Enden an der Umfangsfläche der Antriebswelle (9) anliegen und die jeweils in einer Führungsbohrung (17) axial verschiebbar geführt sind, wobei die Pumpenkolben (19) mit ihren der Antriebswelle (9) abge- wandten Stirnflächen jeweils einen Pumpenarbeitsraum (21) in der Führungsbohrung (17) begrenzen, der mit einem kraftstoffgefüllten Niederdruckraum und mit einer Hochdruckförderleitung verbindbar ist, dadurch gekennzeichnet, daß die Führungsbohrungen sämtlicher Pumpenkolben (19) direkt in einem gemeinsamen, einstückigen Pumpengehäuse (1) angeordnet sind.1. High-pressure fuel pump with a plurality of pump pistons (19) arranged at an angular distance from one another around a central drive shaft (9), which by means of preloaded springs (25) rest with their radially inner ends on the peripheral surface of the drive shaft (9) and each in a guide bore (17) are axially displaceable, the pump pistons (19), with their end faces facing away from the drive shaft (9), each delimiting a pump work chamber (21) in the guide bore (17), which can be connected to a fuel-filled low pressure chamber and to a high pressure delivery line , characterized in that the guide bores of all pump pistons (19) are arranged directly in a common, one-piece pump housing (1). 2. Kraftstoffhochdruckpumpe nach Anspruch 1, dadurch gekennzeichnet, daß die Hochdruckförderleitung an einem am Pumpengehäuse (1) vorgesehenen Druckstutzen (49) befestigbar ist und daß die Pumpenarbeitsräume (21) über Hochdruckkanäle (45, 47) mit dem Druckstutzen (49) verbunden sind, wobei die Hochdruckkanäle (45, 47) ausschließlich innerhalb des Pumpengehäuses verlaufen.2. High-pressure fuel pump according to Claim 1, characterized in that the high-pressure delivery line can be fastened to a pressure port (49) provided on the pump housing (1) and that the pump work spaces (21) are connected to the pressure port (49) via high-pressure channels (45, 47), the high-pressure channels (45, 47) running exclusively within the pump housing. 3. Kraftstoffhochdruckpumpe nach Anspruch 2, dadurch gekennzeichnet, daß jeweils ein in Richtung Druckstutzen (49) öffnendes Druckventil (51) an jedem Pumpenarbeitsraum (21) in den jeweiligen Hochdruckkanal (45, 47) eingesetzt ist, wobei das Druckventil (51) vollständig in das Pumpengehäuse (1) eingesetzt ist.3. High-pressure fuel pump according to claim 2, characterized in that in each case one in the direction of the pressure port (49) opening pressure valve (51) is used on each pump work chamber (21) in the respective high pressure channel (45, 47) is, wherein the pressure valve (51) is completely inserted into the pump housing (1). 4. Kraftstoffhochdruckpumpe nach Anspruch 1, dadurch gekennzeichnet, daß die Dichtflächenpaarungen an den kraftstoffführenden Bauteilen jeweils eine plane Dichtfläche an einem ersten Bauteil und eine mit dieser zusammenwirkende scharfe Dichtkante an einem zweiten Bauteil aufweisen, wobei sich beim Verspannen der Bauteile gegeneinander eine dichtende plastische Verformung an der Berührungslinie zwischen der scharfkantigen Dichtkante und der planen Dichtfläche einstellt.4. High-pressure fuel pump according to claim 1, characterized in that the sealing surface pairings on the fuel-carrying components each have a flat sealing surface on a first component and a cooperating sharp sealing edge on a second component, wherein when the components are clamped together, a sealing plastic deformation occurs the line of contact between the sharp-edged sealing edge and the flat sealing surface. 5. Kraftstoffhochdruckpumpe nach Anspruch 1, dadurch gekennzeichnet, daß eine Stirnseite des Pumpengehäuses (1) eine Aufnahme für einen Befestigungsflansch (63) aufweist, mit dem die Kraftstoffhochdruckpumpe an einem Gehäuse einer zu versorgenden Brennkraftmaschine befestigbar ist.5. High-pressure fuel pump according to claim 1, characterized in that an end face of the pump housing (1) has a receptacle for a mounting flange (63) with which the high-pressure fuel pump can be fastened to a housing of an internal combustion engine to be supplied. 6. Kraftstoffhochdruckpumpe nach Anspruch 5, dadurch gekennzeichnet, daß die Aufnahme als axial vorstehender Rohransatz (61) ausgebildet ist, auf den der Befestigungsflansch (63) aufgesteckt ist.6. High-pressure fuel pump according to claim 5, characterized in that the receptacle is designed as an axially projecting tube extension (61) onto which the fastening flange (63) is attached. 7. Kraftstoffhochdruckpumpe nach Anspruch 6, dadurch gekennzeichnet, daß der Befestigungsflansch (63) mit dem Pumpengehäuse (1) verschraubt ist.7. High-pressure fuel pump according to claim 6, characterized in that the mounting flange (63) is screwed to the pump housing (1). 8. Kraftstoffhochdruckpumpe nach Anspruch 1, dadurch gekennzeichnet, daß die Antriebswelle (9) wenigstens im Bereich der Überdeckung mit den Pumpenkolben (19) als Exzenterwelle (13) ausgebildet ist.8. High-pressure fuel pump according to claim 1, characterized in that the drive shaft (9) is formed at least in the region of overlap with the pump piston (19) as an eccentric shaft (13). 9. Kraftstoffhochdruckpumpe nach Anspruch 1, dadurch gekennzeichnet, daß die Pumpenkolben (19) symmetrisch zueinander versetzt um die Antriebswelle (9) angeordnet sind.9. High-pressure fuel pump according to claim 1, characterized in that the pump piston (19) symmetrical are arranged offset to one another around the drive shaft (9). 10. Kraftstoffhochdruckpumpe nach Anspruch 1, dadurch gekennzeichnet, daß die Hochdruckförderleitung in einen Hochdruckspeicherraum mündet, von dem Einspritzleitungen zu in den Brennraum einer Brennkraftmaschine ragenden Einspritzventilen abführen. 10. High-pressure fuel pump according to claim 1, characterized in that the high-pressure delivery line opens into a high-pressure storage chamber, from the injection lines to the injection valves projecting into the combustion chamber of an internal combustion engine.
PCT/DE1998/000299 1997-04-18 1998-02-03 High-pressure fuel pump Ceased WO1998048169A1 (en)

Priority Applications (2)

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EP98909323A EP0931219A1 (en) 1997-04-18 1998-02-03 High-pressure fuel pump
JP10544652A JP2000512715A (en) 1997-04-18 1998-02-03 Fuel high pressure pump

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DE1997116242 DE19716242A1 (en) 1997-04-18 1997-04-18 High pressure fuel pump
DE19716242.8 1997-04-18

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JP (1) JP2000512715A (en)
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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1028252A3 (en) * 1999-02-11 2001-01-24 Delphi Technologies, Inc. Radial piston pump
WO2009059835A2 (en) 2007-11-06 2009-05-14 Robert Bosch Gmbh Radial piston pump comprising a prismatic base body for a fuel injection system

Families Citing this family (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19858861A1 (en) * 1998-12-19 2000-06-29 Bosch Gmbh Robert Common-rail system for IC engines has minimum contact faces between high pressure pump and e.g. engine block
DE19859188B4 (en) * 1998-12-21 2013-11-21 Continental Automotive Gmbh high pressure pump
DE19946842C2 (en) 1999-09-30 2001-08-23 Bosch Gmbh Robert high pressure pump
IT248791Y1 (en) * 1999-11-30 2003-02-20 Elasis Sistema Ricerca Fiat RADIAL PISTON PUMP FOR HIGH PRESSURE FUEL SUPPLY FOR AN INTERNAL COMBUSTION ENGINE.
US6520755B1 (en) * 2000-10-10 2003-02-18 Beckman Coulter, Inc. Fluid-moving device with integrated valve
DE10247142A1 (en) * 2002-10-09 2004-04-22 Robert Bosch Gmbh High pressure pump for fuel injection device has pump housing with body and cap to cover each pump element
US7134846B2 (en) * 2004-05-28 2006-11-14 Stanadyne Corporation Radial piston pump with eccentrically driven rolling actuation ring
DE102008041536A1 (en) 2008-08-26 2010-03-04 Robert Bosch Gmbh High pressure pump for fuel injection system of internal combustion engine, particularly for common-rail-injection system of vehicle, has housing and pump element arranged in guide bore of housing
DE102011119519A1 (en) 2011-06-30 2013-01-03 Arens GmbH Metallbau- und Bauschlosserei Fuel pump for high pressure compaction of fuel for direct injection two-stroke internal combustion engine, has eccentric cam chamber partially filled with lubricant, and eccentric cam received in chamber for driving compaction pistons
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EP2726716B1 (en) 2011-06-30 2016-11-02 Arens GmbH Metallbau & Bauschlosserei Fuel distributor block

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2678005A (en) * 1949-12-13 1954-05-11 Frank G Campbell High-pressure pump
US2679808A (en) * 1949-04-22 1954-06-01 Bernard M Thun Fluid pressure generator
US3434428A (en) * 1967-06-05 1969-03-25 White Motor Corp Intake control for multiple piston pump
US3578879A (en) * 1969-01-22 1971-05-18 Gillett Tool Co Spring actuated fuel pump for fuel injection systems
DE2243138A1 (en) * 1972-09-01 1974-03-07 Langen & Co RADIAL PISTON PUMP
DE2845072A1 (en) * 1978-10-16 1980-04-30 Heinrichs & Co Kg Schrauben Un Screw plug with sealing flanges - has head with annular groove below head and concentric ring-form sealing ridges
DE3713677A1 (en) * 1987-04-24 1988-11-17 Teves Gmbh Alfred Screw connection with a screw, a nut and a seal
EP0304750A1 (en) * 1987-08-25 1989-03-01 WEBER S.r.l. A radial piston pump, particularly a fuel injection pump for diesel engines
US4952121A (en) 1987-08-25 1990-08-28 Weber S.R.L. Radial piston pump with means preventing ovalization of piston chamber

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2679808A (en) * 1949-04-22 1954-06-01 Bernard M Thun Fluid pressure generator
US2678005A (en) * 1949-12-13 1954-05-11 Frank G Campbell High-pressure pump
US3434428A (en) * 1967-06-05 1969-03-25 White Motor Corp Intake control for multiple piston pump
US3578879A (en) * 1969-01-22 1971-05-18 Gillett Tool Co Spring actuated fuel pump for fuel injection systems
DE2243138A1 (en) * 1972-09-01 1974-03-07 Langen & Co RADIAL PISTON PUMP
DE2845072A1 (en) * 1978-10-16 1980-04-30 Heinrichs & Co Kg Schrauben Un Screw plug with sealing flanges - has head with annular groove below head and concentric ring-form sealing ridges
DE3713677A1 (en) * 1987-04-24 1988-11-17 Teves Gmbh Alfred Screw connection with a screw, a nut and a seal
EP0304750A1 (en) * 1987-08-25 1989-03-01 WEBER S.r.l. A radial piston pump, particularly a fuel injection pump for diesel engines
US4952121A (en) 1987-08-25 1990-08-28 Weber S.R.L. Radial piston pump with means preventing ovalization of piston chamber

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1028252A3 (en) * 1999-02-11 2001-01-24 Delphi Technologies, Inc. Radial piston pump
US6302659B1 (en) 1999-02-11 2001-10-16 Stephen Michael Parker Multi-chamber positive displacement pump
WO2009059835A2 (en) 2007-11-06 2009-05-14 Robert Bosch Gmbh Radial piston pump comprising a prismatic base body for a fuel injection system
WO2009059835A3 (en) * 2007-11-06 2009-06-25 Bosch Gmbh Robert Radial piston pump comprising a prismatic base body for a fuel injection system

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JP2000512715A (en) 2000-09-26
DE19716242A1 (en) 1998-10-22
EP0931219A1 (en) 1999-07-28

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