EP2663772B1 - High-pressure pump - Google Patents

High-pressure pump Download PDF

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Publication number
EP2663772B1
EP2663772B1 EP11805064.0A EP11805064A EP2663772B1 EP 2663772 B1 EP2663772 B1 EP 2663772B1 EP 11805064 A EP11805064 A EP 11805064A EP 2663772 B1 EP2663772 B1 EP 2663772B1
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EP
European Patent Office
Prior art keywords
pump
section
cam
cross
flow
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EP11805064.0A
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German (de)
French (fr)
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EP2663772A1 (en
Inventor
Andreas Dutt
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Robert Bosch GmbH
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Robert Bosch GmbH
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
    • F04B9/02—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical
    • F04B9/04—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical the means being cams, eccentrics or pin-and-slot mechanisms
    • F04B9/042—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical the means being cams, eccentrics or pin-and-slot mechanisms the means being cams
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/02—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type
    • F02M59/04—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by special arrangement of cylinders with respect to piston-driving shaft, e.g. arranged parallel to that shaft or swash-plate type pumps
    • F02M59/06—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by special arrangement of cylinders with respect to piston-driving shaft, e.g. arranged parallel to that shaft or swash-plate type pumps with cylinders arranged radially to driving shaft, e.g. in V or star arrangement
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/02—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type
    • F02M59/10—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by the piston-drive
    • F02M59/102—Mechanical drive, e.g. tappets or cams
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/0404—Details or component parts
    • F04B1/0413—Cams
    • 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
    • F04B1/047—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 outer ends of the cylinders
    • 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
    • F04B53/18—Lubricating

Definitions

  • the invention relates to a high-pressure pump, comprising a fluid-filled pump interior in a pump housing in which a pump camshaft is rotatably mounted with at least one cam, and at least one pump cylinder in which a pump plunger translationally for conveying fluid by means of a rolling on the cam track of the pump camshaft roller Roller plunger is movable, and being formed by the at least one circumferential cam and the roller tappet and changing volume in the pump interior via a flow cross section for a Fluidaustauch.
  • Such a high pressure pump is from the DE 10 2008 043 430 A1 known.
  • the subject of claim 1 is delimited in two-part form against this document.
  • the pump camshaft with axial clearance between two fixed housing side stop surfaces is arranged.
  • a cam of the pump camshaft arranged on the pump camshaft Axialfederelement is arranged in the form of a spring washer.
  • a circumferential annular groove in the region of the interaction of the cam with the roller of a roller tappet is arranged in the pump housing.
  • the invention has for its object to optimize the compensating flow between the rotating cam and the roller tappet in the pump interior formed increasing and decreasing volume.
  • a roller which is guided in a roller shoe, and rolls on the cam track, thus converting the rotational rotational movement of the pump camshaft in a translational (up and down) movement of the roller tappet or actuated by this pump tappet , Due to the very high roller speed, the fluid acting as a lubricant medium is drawn into the gap between the roller and the roller shoe due to the drag effect on the inlet gap, thus creating a wear-free hydrodynamic sliding bearing, which transmits the high axial forces from the pump plunger to the pump camshaft.
  • the flow cross section is a flow cross section extending radially above the cam in the pump housing and at least one connecting cross section extending axially laterally of the cam in the pump housing.
  • At least two pump cylinders are provided on the high-pressure pump, and the flow cross-section and the at least one connecting cross-section connects the pump cylinders to one another by the shortest path. If, for example, two pump cylinders are arranged at an angle of 90 °, the flow cross-section and the connection cross-section extend over this angular range encompassing in each case the area around the two pump cylinders. Through this Design is achieved that the compensation flow must be performed only in a narrow range between two pump cylinders through the flow cross-section in the pump housing.
  • the fluid deflection device is a laterally adjacent to the cam in the pump housing incorporated Umlenknase.
  • Umlenknase can be easily implemented, for example, in the cast production of the pump housing by appropriate design of the mold.
  • the circulation nose extends along the Umströmungsqueritess and the connecting cross-section through it and again in a further embodiment, at least approximately parallel to the pump cylinder axis.
  • a sealing gap is formed in the area outside the flow cross-section between the cams and the pump housing.
  • This sealing gap is designed so that on the one hand, the rotational movement of the pump camshaft is not hindered by fluid friction, on the other hand, the flowing through the sealing gap fluid amount is low.
  • the high-pressure pump is a high-pressure fuel pump of an injection system for an internal combustion engine.
  • the invention is particularly useful when the fluid is fuel, useful and advantageous.
  • the high pressure pump shown in the figures is designed for the injection system of an internal combustion engine.
  • fuel is conveyed up to a pressure of about 3,000 bar in a high-pressure accumulator, from which the fuel is taken from, for example, solenoid valve controlled fuel injectors for injection into the associated combustion chambers of the internal combustion engine.
  • the in the Fig. 1 Exhaust pump shown in detail has a pump housing 1 with a pump interior 2.
  • a pump camshaft 3 in bearings 4a, 4b ( Fig. 3 ) rotatably mounted.
  • the pump camshaft 3 has two cams 5a, 5b in the exemplary embodiment.
  • the cams 5a, 5b cooperate with rollers 6 of two roller tappets 7.
  • the roller tappet 7 each have a roller shoe 8, in which a cylindrical recess 9 is incorporated. In this cylindrical recess 9 each have a roller 6 is inserted captive.
  • 2 different volumes are formed in the pump interior, which constantly change due to the interaction of the cams 5a, 5b with the roller tappets 7 during a rotary movement of the pump camshaft 1 and indeed increase and decrease.
  • the volume V 1 decreases while the volume V 3 and V 4 in particular increase.
  • a compensating flow between these volumes V 1 , V 3 and V 4 takes place via a flow cross-section 10, which is inserted radially above the cams 5 a, 5 b into the pump housing 1 and via a connecting cross-section 11, which is axially laterally of the cams 5 a, 5 b in FIG the pump housing 1 ( Fig. 3 ) is admitted.
  • Fig. 2 shows in contrast to Fig. 1 the pump camshaft 3 in two other rotational positions, which after a further rotation of the pump camshaft 1 by about 120 ° opposite Fig. 1 result.
  • the volume V 1 and V 3 decreases during the change in position from the position shown in dashed lines to the extended position of the pump camshaft 3 , while the volume V 4 is also increased here.
  • Fig. 3 shown longitudinal section along S 1 -S 1 according to Fig. 2 shows the arrangement and configuration of the Umströmungsqueritess 10 and arranged on both sides of the cams 5a, 5b connecting cross-section 11 in the pump housing 1.
  • the flow connection of the volume D 1 , V 3 and V 4 so in that, during the rotational movement of the pump camshaft 3, a compensation flow takes place between the volumes V 1 , V 3 and V 4 .
  • a sealing gap 12 formed in the area of the volume V 5 (see Fig. 1 and 2 ) is between the pump camshaft 3 and the cam 5a, 5b and the pump housing 1, a sealing gap 12 formed. Along this sealing gap 12, no appreciable flow compensation takes place.
  • Fig. 4 shows a sectional view S 2 according to Fig. 2 , It is shown that in each case a Umlenknase 13 projects into the Umströmungsquerites 10 and arranged on both sides of the pump housing 1 connecting cross-section 11. Arranged are the two Umlenknasen 13 each just behind the cylindrical recess 9 and the roller 6 and are formed by the pump housing 1.
  • the two Umlenknasen 13 cause the flow deflection shown by the arrows of the compensating flow of the fluid from the volume V 1 in the volume V 3rd
  • the fluid is selectively guided in front of the inlet gap E 1 of the roller 6.
  • fluid is thus deliberately built up to build up a wear-free hydrostatic sliding bearing between the roller 6 and the cylindrical recess 9.

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

Description

Stand der TechnikState of the art

Die Erfindung betrifft eine Hochdruckpumpe, aufweisend einen fluidgefüllten Pumpeninnenraum in einem Pumpengehäuse, in dem eine Pumpennockenwelle mit zumindest einem Nocken drehbar gelagert ist, und zumindest einem Pumpenzylinder, in dem ein Pumpenstößel translatorisch zur Förderung von Fluid mittels eines auf der Nockenlaufbahn der Pumpennockenwelle abrollenden Laufrolle eines Rollenstößels bewegbar ist, und wobei von dem zumindest einen umlaufenden Nocken und dem Rollenstößel gebildete und sich ändernde Volumen in dem Pumpeninnenraum über einen Strömungsquerschnitt für eine Fluidaustauch verbunden sind.The invention relates to a high-pressure pump, comprising a fluid-filled pump interior in a pump housing in which a pump camshaft is rotatably mounted with at least one cam, and at least one pump cylinder in which a pump plunger translationally for conveying fluid by means of a rolling on the cam track of the pump camshaft roller Roller plunger is movable, and being formed by the at least one circumferential cam and the roller tappet and changing volume in the pump interior via a flow cross section for a Fluidaustauch.

Eine derartige Hochdruckpumpe ist aus der DE 10 2008 043 430 A1 bekannt. Der Gegenstand des Patentanspruchs 1 ist in zweiteiliger Form gegenüber dieser Druckschrift abgegrenzt. Bei dieser Hochdruckpumpe ist die Pumpennockenwelle mit Axialspiel zwischen zwei gehäuseseitig fixierten Anschlagflächen angeordnet. Zwischen den Anschlagflächen und einem Nocken der Pumpennockenwelle ist ein auf der Pumpennockenwelle angeordnetes Axialfederelement in Form einer Federscheibe angeordnet. Weiterhin ist in das Pumpengehäuse eine umlaufende Ringnut im Bereich des Zusammenwirkens des Nockens mit der Laufrolle eines Rollenstößels angeordnet. Entlang der Federscheibe bzw. des von dieser nur teilweise ausgefüllten Freiraums zwischen der Pumpennockenwelle und den Anschlagflächen sowie durch die umlaufende Ringnut kann von dem Nocken bei dessen Umlaufbewegung verdrängtes Fluid, mit dem der Pumpeninnenraum gefüllt ist, mehr oder weniger unkontrolliert und unbeeinflusst in den von den umlaufenden Nocken und dem Rollenstößel gebildeten und sich ständig ändernden Volumen strömen. Hierdurch können insbesondere im Nahbereich des Rollenstößels bzw. dem Zulaufbereich für die Lagerschmierung der Laufrolle in den Rollenschuh Unterdruck und Kavitationsblasen entstehen, die zu einer Mangelschmierung der Laufrolle in dem Rollenschuh führen.Such a high pressure pump is from the DE 10 2008 043 430 A1 known. The subject of claim 1 is delimited in two-part form against this document. In this high-pressure pump, the pump camshaft with axial clearance between two fixed housing side stop surfaces is arranged. Between the stop surfaces and a cam of the pump camshaft arranged on the pump camshaft Axialfederelement is arranged in the form of a spring washer. Furthermore, a circumferential annular groove in the region of the interaction of the cam with the roller of a roller tappet is arranged in the pump housing. Along the spring washer or of this only partially filled space between the pump camshaft and the stop surfaces and by the circumferential annular groove of the cam in its orbital displacement displaced fluid with which the pump interior is filled, more or less uncontrolled and uninfluenced in the of the circulating cam and the roller tappet formed and constantly changing volume flow. As a result, in particular in the vicinity of the roller tappet or the inlet region for the bearing lubrication of the roller in the roller shoe negative pressure and cavitation bubbles arise, which lead to a lack of lubrication of the roller in the roller shoe.

Der Erfindung liegt die Aufgabe zugrunde, die Ausgleichsströmung zwischen dem umlaufenden Nocken und dem Rollenstößel in dem Pumpeninnenraum gebildeten sich vergrößernden sowie verkleinernden Volumen zu optimieren.The invention has for its object to optimize the compensating flow between the rotating cam and the roller tappet in the pump interior formed increasing and decreasing volume.

Offenbarung der ErfindungDisclosure of the invention Vorteile der ErfindungAdvantages of the invention

Diese Aufgabe wird dadurch gelöst, dass in Drehrichtung des Nockens im Bereich hinter der Laufrolle eine Fluidumlenkvorrichtung in den Strömungsquerschnitt angeordnet ist. Diese Fluidumlenkvorrichtung ist - wie nachfolgend noch ausgeführt wird - so angeordnet und ausgebildet, dass eine Fluidströmung in Richtung zu dem Einlaufspalt zwischen der Laufrolle und dem Rollenschuh ausgerichtet ist. Hierbei ist zu berücksichtigen, dass eine Laufrolle, die in einem Rollenschuh geführt ist, und sich auf der Nockenbahn abwälzt, somit die rotatorische Drehbewegung der Pumpennockenwelle in eine translatorische (Auf- und Ab-) Bewegung des Rollenstößels bzw. eines von diesem betätigten Pumpenstößels umwandelt. Durch die sehr hohe Laufrollendrehzahl wird das als Schmiermedium wirkende Fluid aufgrund der Schleppwirkung über den Einlaufspalt in den Spalt zwischen der Laufrolle und dem Rollenschuh eingezogen, es entsteht somit eine verschleißfreie hydrodynamische Gleitlagerung, welche die hohen Axialkräfte von dem Pumpenstößel auf die Pumpennockenwelle überträgt.This object is achieved in that in the direction of rotation of the cam in the region behind the roller a Fluidumlenkvorrichtung is arranged in the flow cross-section. This Fluidumlenkvorrichtung is - as will be explained below - arranged and designed so that a fluid flow is aligned in the direction of the inlet gap between the roller and the roller shoe. It should be noted that a roller, which is guided in a roller shoe, and rolls on the cam track, thus converting the rotational rotational movement of the pump camshaft in a translational (up and down) movement of the roller tappet or actuated by this pump tappet , Due to the very high roller speed, the fluid acting as a lubricant medium is drawn into the gap between the roller and the roller shoe due to the drag effect on the inlet gap, thus creating a wear-free hydrodynamic sliding bearing, which transmits the high axial forces from the pump plunger to the pump camshaft.

Voraussetzung für die Entstehung eines solches hydrodynamischen Gleitlagers ist es, das genügend Fluid an der Einzugskante der Laufrolle und dem Rollenschuh vorhanden ist. Diese Forderung wird durch die erfindungsgemäße Fluidumlenkvorrichtung in Verbindung mit der Anordnung des Strömungsquerschnitts erfüllt. Dabei wird durch die spezielle Anordnung des den Strömungsquerschnitt bildenden Umströmungsquerschnitts und des Verbindungsquerschnitts die Kavitationsbildung soweit verhindert, dass kein schädlicher Einfluss auf die Schmierung bzw. die den Aufbau der hydrodynamischen Lagerung besteht.Prerequisite for the emergence of such a hydrodynamic sliding bearing is that there is enough fluid at the feed edge of the roller and the roller shoe. This requirement is met by the fluid deflection device according to the invention in conjunction with the arrangement of the flow cross section. The cavitation formation is prevented by the special arrangement of the Umströmungsquerschnitts forming the flow cross-section and the connecting cross-section so far that there is no harmful effect on the lubrication or the structure of the hydrodynamic bearing.

In Weiterbildung der Erfindung ist der Strömungsquerschnitt ein sich radial oberhalb des Nockens in dem Pumpengehäuse erstreckender Umströmungsquerschnitt und zumindest ein axial seitlich des Nockens in dem Pumpengehäuse erstreckender Verbindungsquerschnitt. Diese Ausgestaltung ermöglicht eine besonders gezielte Beeinflussung der Ausgleichsströmung zwischen den sich verändernden Volumen insbesondere dahingehend, dass kein Unterdruck und keine Kavitationsblasen in diesem Bereich auftreten. Allein durch diese Ausgestaltung wird eine durch Unterdruck und Kavitationsblasen verursachte Mangelschmierung im Lagerbereich der Laufrolle in dem Rollenschuh vermieden.In a development of the invention, the flow cross section is a flow cross section extending radially above the cam in the pump housing and at least one connecting cross section extending axially laterally of the cam in the pump housing. This embodiment enables a particularly targeted influencing of the compensation flow between the changing volumes, in particular to the effect that no negative pressure and no cavitation bubbles occur in this area. Alone by this design, a lack of lubrication caused by negative pressure and cavitation bubbles in the storage area of the roller in the roller shoe is avoided.

In weiterer Ausgestaltung der Erfindung sind an der Hochdruckpumpe zumindest zwei Pumpenzylinder vorgesehen und der Umströmungsquerschnitt und der zumindest eine Verbindungsquerschnitt verbindet die Pumpenzylinder auf kürzestem Weg miteinander. Wenn beispielsweise zwei Pumpenzylinder in einem Winkel von 90° angeordnet sind, erstrecken sich der Umströmungsquerschnitt und der Verbindungsquerschnitt über diesen Winkelbereich umfassend jeweils den Bereich um die beiden Pumpenzylinder. Durch diese Ausgestaltung wird erreicht, dass die Ausgleichsströmung nur in einem engen Bereich zwischen zwei Pumpenzylindern durch den Strömungsquerschnitt in dem Pumpengehäuse geführt werden muss.In a further embodiment of the invention, at least two pump cylinders are provided on the high-pressure pump, and the flow cross-section and the at least one connecting cross-section connects the pump cylinders to one another by the shortest path. If, for example, two pump cylinders are arranged at an angle of 90 °, the flow cross-section and the connection cross-section extend over this angular range encompassing in each case the area around the two pump cylinders. Through this Design is achieved that the compensation flow must be performed only in a narrow range between two pump cylinders through the flow cross-section in the pump housing.

In Weiterbildung der Erfindung ist die Fluidumlenkvorrichtung eine seitlich neben dem Nocken in das Pumpengehäuse eingearbeitete Umlenknase. Eine solche Umlenknase kann beispielsweise bei der Gussfertigung des Pumpengehäuses durch entsprechende Ausbildung der Gießform einfach umgesetzt werden.In a further development of the invention, the fluid deflection device is a laterally adjacent to the cam in the pump housing incorporated Umlenknase. Such Umlenknase can be easily implemented, for example, in the cast production of the pump housing by appropriate design of the mold.

In weiterer Ausgestaltung der Erfindung erstreckt sich die Umlaufnase entlang des Umströmungsquerschnitts und des Verbindungsquerschnitts durch diese hindurch und wiederum in weiterer Ausgestaltung zumindest angenähert parallel zu der Pumpenzylinderachse. Diese Ausgestaltung ist herstellungstechnisch einfach zu realisieren und ermöglicht andererseits eine optimale Führung der Ausgleichsströmung einerseits zwischen dem sich verändernden Volumen und andererseits hinsichtlich des Einlaufs in den Zulauf zu den jeweiligen hydrodynamischen Gleitlagern.In a further embodiment of the invention, the circulation nose extends along the Umströmungsquerschnitts and the connecting cross-section through it and again in a further embodiment, at least approximately parallel to the pump cylinder axis. This embodiment is easy to realize manufacturing technology and on the other hand allows optimal management of the equalizing flow on the one hand between the changing volume and on the other hand with respect to the inlet to the inlet to the respective hydrodynamic sliding bearings.

In Weiterbildung der Erfindung ist im Bereich außerhalb des Strömungsquerschnitts zwischen den Nocken und dem Pumpengehäuse ein Dichtspalt gebildet. Dieser Dichtspalt ist so ausgelegt, dass einerseits die Drehbewegung der Pumpennockenwelle durch Fluidreibung nicht behindert wird, andererseits die durch den Dichtspalt hindurch strömende Fluidmenge gering ist.In a further development of the invention, a sealing gap is formed in the area outside the flow cross-section between the cams and the pump housing. This sealing gap is designed so that on the one hand, the rotational movement of the pump camshaft is not hindered by fluid friction, on the other hand, the flowing through the sealing gap fluid amount is low.

In weiterer Ausgestaltung der Erfindung ist die Hochdruckpumpe eine Kraftstoffhochdruckpumpe eines Einspritzsystems für eine Brennkraftmaschine. Insbesondere bei einer solchen Kraftstoffhochdruckpumpe ist die Erfindung insbesondere dann, wenn das Fluid Kraftstoff ist, sinnvoll und vorteilhaft umsetzbar.In a further embodiment of the invention, the high-pressure pump is a high-pressure fuel pump of an injection system for an internal combustion engine. In particular, in such a high-pressure fuel pump, the invention is particularly useful when the fluid is fuel, useful and advantageous.

Weitere vorteilhafte Ausgestaltungen der Erfindung sind der Zeichnungsbeschreibung zu entnehmen, in der ein in den Fig. dargestelltes Ausführungsbeispiel der Erfindung näher beschrieben ist.Further advantageous embodiments of the invention are described in the drawing, in which an illustrated in FIGS. Embodiment of the invention is described in more detail.

Kurze Beschreibung der ZeichnungenBrief description of the drawings

Es zeigen:

Fig. 1
einen Querschnitt durch einen Teilbereich eines Pumpengehäuses einer Hochdruckpumpe mit zwei in einem Winkel von 90° angeordneten Pumpenzylindern,
Fig. 2
einen identischen Schnitt wie Fig. 1 mit zwei anderen Drehstellungen einer Pumpennockenwelle,
Fig. 3
einen Längsschnitt durch die Hochdruckpumpe gemäß S1-S1 aus Fig. 2 und
Fig. 4
eine Schnittansicht der Hochdruckpumpe gemäß S2 aus Fig. 2.
Show it:
Fig. 1
a cross section through a portion of a pump housing of a high-pressure pump with two arranged at an angle of 90 ° pump cylinders,
Fig. 2
an identical cut like Fig. 1 with two other rotational positions of a pump camshaft,
Fig. 3
a longitudinal section through the high pressure pump according to S1-S1 Fig. 2 and
Fig. 4
a sectional view of the high-pressure pump according to S2 Fig. 2 ,

Ausführungsform der ErfindungEmbodiment of the invention

Die in den Figuren dargestellte Hochdruckpumpe ist für das Einspritzsystem einer Brennkraftmaschine ausgelegt. Mittels der Hochdruckpumpe wird Kraftstoff bis zu einem Druck von ca. 3.000 bar in einen Hochdruckspeicher gefördert, aus dem der Kraftstoff von beispielsweise magnetventilgesteuerten Kraftstoffinjektoren zur Einspritzung in zugeordnete Brennräume der Brennkraftmaschine entnommen wird.The high pressure pump shown in the figures is designed for the injection system of an internal combustion engine. By means of the high pressure pump fuel is conveyed up to a pressure of about 3,000 bar in a high-pressure accumulator, from which the fuel is taken from, for example, solenoid valve controlled fuel injectors for injection into the associated combustion chambers of the internal combustion engine.

Die in der Fig. 1 ausschnittsweise dargestellte Hochdruckpumpe weist ein Pumpengehäuse 1 mit einem Pumpeninnenraum 2 auf. In dem Pumpengehäuse 1 ist eine Pumpennockenwelle 3 in Lagern 4a, 4b (Fig. 3) drehbar gelagert. Die Pumpennockenwelle 3 weist in dem Ausführungsbeispiel zwei Nocken 5a, 5b auf. Die Nocken 5a, 5b wirken mit Laufrollen 6 von zwei Rollenstößeln 7 zusammen. Die Rollenstößel 7 weisen jeweils einen Rollenschuh 8 auf, in den eine zylinderförmige Ausnehmung 9 eingearbeitet ist. In diese zylinderförmige Ausnehmung 9 ist jeweils eine Laufrolle 6 verliersicher eingesetzt.The in the Fig. 1 Exhaust pump shown in detail has a pump housing 1 with a pump interior 2. In the pump housing 1 is a pump camshaft 3 in bearings 4a, 4b ( Fig. 3 ) rotatably mounted. The pump camshaft 3 has two cams 5a, 5b in the exemplary embodiment. The cams 5a, 5b cooperate with rollers 6 of two roller tappets 7. The roller tappet 7 each have a roller shoe 8, in which a cylindrical recess 9 is incorporated. In this cylindrical recess 9 each have a roller 6 is inserted captive.

Die Pumpennockenwelle 3 füllt mit den Nocken 5a, 5b den Pumpeninnenraum 2 im Bereich der Nocken 5a, 5b quasi vollständig aus, während die Pumpennockenwelle 3 sich im Bereich zwischen den Nocken 5a, 5b kontinuierlich bis zu deren Lagerdurchmesser verjüngt. Dadurch werden in dem Pumpeninnenraum 2 verschiedene Volumen gebildet, die sich durch das Zusammenwirken der Nocken 5a, 5b mit den Rollenstößeln 7 bei einer Drehbewegung der Pumpennockenwelle 1 ständig ändern und zwar vergrößern und verkleinern. Bei der in Fig. 1 dargestellten Drehbewegung der Pumpennockenwelle 3 in Drehpfeilrichtung von der strichliniert dargestellten Position in die ausgezogenen dargestellte Position verringert sich das Volumen V1 während sich die Volumen V3 und insbesondere V4 vergrößern. Eine Ausgleichsströmung zwischen diesen Volumen V1, V3 und V4 erfolgt über einen Umströmungsquerschnitt 10, der radial ober-halb der Nocken 5a, 5b in das Pumpengehäuse 1 eingelassen ist und über einen Verbindungsquerschnitt 11, der axial seitlich der Nocken 5a, 5b in das Pumpengehäuse 1 (Fig. 3) eingelassen ist.The pump camshaft 3, with the cams 5a, 5b, almost completely fills the pump interior 2 in the region of the cams 5a, 5b, while the pump camshaft 3 tapers continuously in the region between the cams 5a, 5b up to their bearing diameter. As a result, 2 different volumes are formed in the pump interior, which constantly change due to the interaction of the cams 5a, 5b with the roller tappets 7 during a rotary movement of the pump camshaft 1 and indeed increase and decrease. At the in Fig. 1 shown rotational movement of the pump camshaft 3 in the rotational direction of the arrow from the position shown in dashed lines to the solid position shown, the volume V 1 decreases while the volume V 3 and V 4 in particular increase. A compensating flow between these volumes V 1 , V 3 and V 4 takes place via a flow cross-section 10, which is inserted radially above the cams 5 a, 5 b into the pump housing 1 and via a connecting cross-section 11, which is axially laterally of the cams 5 a, 5 b in FIG the pump housing 1 ( Fig. 3 ) is admitted.

Fig. 2 zeigt im Unterschied zu Fig. 1 die Pumpennockenwelle 3 in zwei anderen Drehpositionen, die sich nach einer Weiterdrehung der Pumpennockenwelle 1 um ca. 120° gegenüber Fig. 1 ergeben. Hierbei verringert sich bei der Positionsänderung von der strichliniert dargestellten Stellung in die ausgezogen dargestellte Stellung der Pumpennockenwelle 3 das Volumen V1 und V3, während sich das Volumen V4 auch hier vergrößert. Fig. 2 shows in contrast to Fig. 1 the pump camshaft 3 in two other rotational positions, which after a further rotation of the pump camshaft 1 by about 120 ° opposite Fig. 1 result. In this case, the volume V 1 and V 3 decreases during the change in position from the position shown in dashed lines to the extended position of the pump camshaft 3 , while the volume V 4 is also increased here.

Der in Fig. 3 dargestellte Längsschnitt entlang S1-S1 gemäß Fig. 2 zeigt die Anordnung und Ausgestaltung des Umströmungsquerschnitts 10 und des auf beiden Seiten der Nocken 5a, 5b angeordneten Verbindungsquerschnitts 11 in dem Pumpengehäuse 1. Über den Umströmungsquerschnitt 10 und die beiden Verbindungsquerschnitte 11 erfolgt die Strömungsverbindung der Volumen D1, V3 und V4, so, dass bei der Drehbewegung der Pumpennockenwelle 3 eine Ausgleichsströmung zwischen den Volumen V1, V3 und V4 erfolgt. Im Bereich des Volumens V5 (siehe Fig. 1 und 2) ist zwischen der Pumpennockenwelle 3 bzw. den Nocken 5a, 5b und dem Pumpengehäuse 1 ein Dichtspalt 12 gebildet. Entlang dieses Dichtspaltes 12 erfolgt kein nennenswerter Strömungsausgleich.The in Fig. 3 shown longitudinal section along S 1 -S 1 according to Fig. 2 shows the arrangement and configuration of the Umströmungsquerschnitts 10 and arranged on both sides of the cams 5a, 5b connecting cross-section 11 in the pump housing 1. About the flow cross-section 10 and the two connecting sections 11, the flow connection of the volume D 1 , V 3 and V 4 , so in that, during the rotational movement of the pump camshaft 3, a compensation flow takes place between the volumes V 1 , V 3 and V 4 . In the area of the volume V 5 (see Fig. 1 and 2 ) is between the pump camshaft 3 and the cam 5a, 5b and the pump housing 1, a sealing gap 12 formed. Along this sealing gap 12, no appreciable flow compensation takes place.

Fig. 4 zeigt eine Schnittansicht S2 gemäß Fig. 2. Dargestellt ist, dass jeweils eine Umlenknase 13 in den Umströmungsquerschnitt 10 bzw. den auf beiden Seiten des Pumpengehäuses 1 angeordneten Verbindungsquerschnitts 11 hineinragt. Angeordnet sind die beiden Umlenknasen 13 jeweils kurz hinter der zylinderförmigen Ausnehmung 9 bzw. der Laufrolle 6 und werden von dem Pumpengehäuse 1 gebildet. Die beiden Umlenknasen 13 bewirken die durch die Pfeile dargestellte Strömungsumlenkung der Ausgleichsströmung des Fluides von dem Volumen V1 in das Volumen V3. Durch diese Strömungsumkehr wird das Fluid gezielt vor dem Einlaufspalt E1 der Laufrolle 6 geführt. Bei der Drehbewegung der Laufrolle 6 während des Abrollvorgangs auf der Nockenlaufbahn der Pumpennockenwelle 3 wird folglich gezielt Fluid zum Aufbau einer verschleißfreien hydrostatischen Gleitlagerung zwischen der Laufrolle 6 und der zylinderförmigen Ausnehmung 9 aufgebaut. Fig. 4 shows a sectional view S 2 according to Fig. 2 , It is shown that in each case a Umlenknase 13 projects into the Umströmungsquerschnitt 10 and arranged on both sides of the pump housing 1 connecting cross-section 11. Arranged are the two Umlenknasen 13 each just behind the cylindrical recess 9 and the roller 6 and are formed by the pump housing 1. The two Umlenknasen 13 cause the flow deflection shown by the arrows of the compensating flow of the fluid from the volume V 1 in the volume V 3rd By this flow reversal, the fluid is selectively guided in front of the inlet gap E 1 of the roller 6. As a result of the rotational movement of the roller 6 during the rolling process on the cam track of the pump camshaft 3, fluid is thus deliberately built up to build up a wear-free hydrostatic sliding bearing between the roller 6 and the cylindrical recess 9.

Claims (9)

  1. High-pressure pump, having a fluid-filled pump inner space (2) in a pump casing (1), in which a pump camshaft (3) with at least one cam (5a, 5b) is mounted rotatably, and at least one pump cylinder, in which a pump tappet is movable in translation for the conveyance of fluid by means of a running roller (6), rolling on the cam track of the pump camshaft (3), of a roller tappet (7), changing volumes (V1, V3) in the pump inner space (2), which are formed by the rotating cam (5a, 5b) and the roller tappet (7), being connected for fluid exchange via a flow cross section (10, 11), and the flow cross section, which extends into the pump casing (1) in the region of the roller tappet (7), being arranged adjacently to the pump inner space (2), characterized in that a fluid deflection device (13) projects into the flow cross section in the region behind the running roller (6) in the direction of rotation of the cam (5a, 5b).
  2. High-pressure pump according to Claim 1, characterized in that the flow cross section is a flow-around cross section (10) extending radially above the cam (5a, 5b) in the pump casing (1) and at least one connecting cross section (11) extending axially, laterally to the cam (5a, 5b), in the pump casing (1).
  3. High-pressure pump according to Claim 2, characterized in that at least two pump cylinders are provided, and the flow-around cross section (10) and the at least one connecting cross section (11) are introduced into the pump casing so as to connect the pump cylinders to one another at the shortest possible distance.
  4. High-pressure pump according to one of Claims 1 to 3, characterized in that the fluid deflection device is at least one deflection nose (13) incorporated into the pump casing (1) laterally next to the cam (5a, 5b).
  5. High-pressure pump according to Claim 4, characterized in that the deflection nose (13) extends along the flow-around cross section (10) and the connecting cross section (11) and through these.
  6. High-pressure pump according to Claim 5, characterized in that the deflection nose (13) extends at least approximately parallel to the pump cylinder axis.
  7. High-pressure pump according to one of the preceding claims, characterized in that a sealing gap (12) is formed in the region outside the flow cross section, between the cam (5a, 5b), the pump camshaft (3) and the pump casing (1).
  8. High-pressure pump according to one of the preceding claims, characterized in that the high-pressure pump is a high-pressure fuel pump of an injection system for an internal combustion engine.
  9. High-pressure pump according to one of the preceding claims, characterized in that the fluid is fuel.
EP11805064.0A 2011-01-14 2011-12-30 High-pressure pump Active EP2663772B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE201110002701 DE102011002701A1 (en) 2011-01-14 2011-01-14 high pressure pump
PCT/EP2011/074294 WO2012095270A1 (en) 2011-01-14 2011-12-30 High-pressure pump

Publications (2)

Publication Number Publication Date
EP2663772A1 EP2663772A1 (en) 2013-11-20
EP2663772B1 true EP2663772B1 (en) 2014-11-12

Family

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Application Number Title Priority Date Filing Date
EP11805064.0A Active EP2663772B1 (en) 2011-01-14 2011-12-30 High-pressure pump

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EP (1) EP2663772B1 (en)
CN (1) CN103299072B (en)
DE (1) DE102011002701A1 (en)
WO (1) WO2012095270A1 (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9835123B2 (en) 2015-01-13 2017-12-05 Roller Bearing Company Of America, Inc. Roller for a fuel pump actuator

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104047838B (en) * 2014-06-13 2016-08-24 江苏盈科汽车空调有限公司 A kind of change discharge capacity compressor of air conditioner
CN104929885A (en) * 2015-07-07 2015-09-23 中国航天科技集团公司烽火机械厂 Radial plunger pump
KR101745118B1 (en) * 2015-07-29 2017-06-08 현대자동차 유럽기술연구소 High pressure pump
WO2022066505A1 (en) * 2020-09-24 2022-03-31 Cummins Inc. Pump housing with relief cut for lobe clearance

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102004048711B4 (en) * 2004-10-06 2006-09-14 Siemens Ag Radial piston pump with roller tappet
JP2008163816A (en) * 2006-12-27 2008-07-17 Denso Corp Cam mechanism mounting device
DE102007060772A1 (en) * 2007-12-17 2009-06-18 Robert Bosch Gmbh Pump, in particular high-pressure fuel pump
DE102008043430A1 (en) 2008-11-04 2010-05-06 Robert Bosch Gmbh Piston pump i.e. high-pressure pump, for fuel-injection device of internal-combustion engine of motor vehicle, has axial spring element that is arranged on drive shaft and provided between one of axial abutment surfaces and cam

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9835123B2 (en) 2015-01-13 2017-12-05 Roller Bearing Company Of America, Inc. Roller for a fuel pump actuator

Also Published As

Publication number Publication date
DE102011002701A1 (en) 2012-07-19
CN103299072A (en) 2013-09-11
WO2012095270A1 (en) 2012-07-19
EP2663772A1 (en) 2013-11-20
CN103299072B (en) 2016-03-30

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