EP2673495B1 - Pompe haute pression et methode de fonctionnement de celle-ci - Google Patents

Pompe haute pression et methode de fonctionnement de celle-ci Download PDF

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Publication number
EP2673495B1
EP2673495B1 EP11805885.8A EP11805885A EP2673495B1 EP 2673495 B1 EP2673495 B1 EP 2673495B1 EP 11805885 A EP11805885 A EP 11805885A EP 2673495 B1 EP2673495 B1 EP 2673495B1
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EP
European Patent Office
Prior art keywords
roller
axial
bearing arrangement
plain
blades
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Not-in-force
Application number
EP11805885.8A
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German (de)
English (en)
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EP2673495A1 (fr
Inventor
Andreas Dutt
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
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Robert Bosch GmbH
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Filing date
Publication date
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Publication of EP2673495A1 publication Critical patent/EP2673495A1/fr
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Publication of EP2673495B1 publication Critical patent/EP2673495B1/fr
Not-in-force legal-status Critical Current
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Classifications

    • 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
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0001—Fuel-injection apparatus with specially arranged lubricating system, e.g. by fuel oil
    • 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
    • F04B1/0417—Cams consisting of two or more cylindrical elements, e.g. rollers
    • 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 present invention relates to a high-pressure pump according to the preamble of claim 1 and a method for operating a high-pressure pump according to the preamble of claim 10.
  • a high-pressure pump continuously ensures the maintenance of the pressure in the high-pressure accumulator of the common-rail injection system.
  • the high-pressure pump can be driven, for example, by a camshaft of the internal combustion engine by means of a drive shaft.
  • Vor detailpumpen, z. B. a gear or rotary vane pump used, which are connected upstream of the high-pressure pump.
  • the prefeed pump delivers the fuel from a fuel tank through a fuel line to the high pressure pump.
  • piston pumps are used as high-pressure pumps.
  • a drive shaft is mounted. Radially to pistons are arranged in a cylinder.
  • a roller with a roller rolling surface On the drive shaft with at least one cam is a roller with a roller rolling surface, which is mounted in a roller shoe.
  • the roller shoe is connected to the piston, so that the piston is forced to oscillate translational motion.
  • a spring applies to the roller shoe a radially directed to the drive shaft force, so that the roller is in constant contact with the drive shaft.
  • the roller is mounted by means of a sliding bearing in the roller shoe.
  • the roller In the axial direction with respect to a rotational axis of the roller, the roller is mounted with an axial sliding bearing and in the radial direction, d. H. perpendicular to the axis of rotation of the roller, mounted with a radial sliding bearing on the roller shoe.
  • the plain bearing is doing with a lubricant, eg. As fuel or lubricating oil, lubricated.
  • a bearing neck is arranged at both ends and with this axial bearing neck the roller is mounted axially.
  • the bearing neck can occur at its axial end in direct contact with the roller shoe. This results in the axial slide bearing at the end of the bearing neck and the corresponding portion of the roller shoe.
  • the lubricant is conveyed away at the end or at the front-side contact point of the bearing neck radially outward or thrown so that at the end or at the frontal contact point of the bearing neck, a lack of lubricant.
  • increased wear and unnecessary consumption of mechanical energy arise at the high-pressure pump at this axial plain bearing.
  • the DE 10 2006 045 933 A1 shows a high-pressure pump for high-pressure fuel delivery.
  • the high-pressure pump has a drive shaft with cams. Cylindrical rollers are supported by roller shoes and rest on the cams. The roller shoes are mounted by means of a plunger assembly in a bore of a part of the housing. The pump elements are attached to the plunger assembly. A coil spring presses the plunger assembly onto the cams.
  • Inventive high-pressure pump in particular for a motor vehicle, for conveying a fluid, in particular fuel, for. B. diesel, comprising a drive shaft with at least one cam, at least one piston, at least one cylinder for supporting the at least one piston, at least one roller, wherein the at least one piston indirectly by means of at least one roller on the drive shaft with the at least one cam at least one roller shoe, each with a sliding bearing, which is lubricated with lubricant, for the at least one roller, so that from the at least one roller a rotational movement about one Rotation axis is executable, wherein the at least one roller is provided at least one axial end portion with blades as a turbomachine, so that the at least one roller forms a rotor for the blades for conveying the lubricant to an axial sliding bearing at least one en roller on the at least one roller shoe.
  • the at least one roller is provided with blades, which form a turbomachine.
  • the geometry of the blades is designed such that they are able to promote the lubricant, for example fuel, especially diesel or gasoline, or lubricating oil, to the axial sliding bearing for the at least one roller on the roller shoe.
  • a lack of lubricant on the axial slide bearing of the at least one roller can be reduced or eliminated.
  • the wear of the axial sliding bearing on the at least one roller and the respective associated roller shoe significantly reduced and the consumption of mechanical energy to the axial sliding bearing can be substantially reduced.
  • the lubricant can be conveyed by the blades radially in the direction of the axis of rotation of the at least one roller.
  • the blades are formed in their geometry to the extent that they are able to promote the lubricant radially towards the axis of rotation of the at least one roller.
  • the blades have a curvature in a section perpendicular to the axis of rotation of the roller, and preferably the radius of curvature increases or decreases from outside to inside in the direction of the axis of rotation.
  • the at least one roller each with an axial and radial sliding bearing mounted on the at least one roller shoe.
  • the axial sliding bearing is only partially formed on the at least one axial end section in that the maximum radius of the axial sliding bearing is smaller than the maximum or outside radius of the at least one roller with this axial plain bearing.
  • the axial plain bearing can for example be formed by the fact that at each of the end portions and the axial end of the roller, a bearing neck is present and the axial end distances are parallel to the axis of rotation of the bearing nozzle larger than outside of the bearing neck, so that in an axial movement of the Roller at the end or the frontal contact point of the bearing stub enters into contact between the roller and the roller shoe and outside the bearing neck no contact between the axial end of the roller and the roller shoe occurs.
  • a bearing neck can also be formed on the roller shoe.
  • the axial sliding bearing is circular in a section perpendicular to the axis of rotation of the at least one roller and the maximum radius of the axial sliding bearing is less than 70%, 50%, 20% or 10% of the radius of the roller. If the radius of the axial plain bearing or the radius of the bearing neck is, for example, 10% of the radius of the roller, the radius of the bearing neck or the radius of the axial plain bearing is 1 mm for a radius of the roller of 10 mm.
  • the blades are formed only radially outside the axial sliding bearing, so that the blades, in particular exclusively, a greater distance from the axis of rotation than the axial sliding bearing.
  • the axial distance between two axial sliding bearings per roller shoe is greater than the axial distance of the axial sliding bearing of the associated roller, so that the roller is mounted axially with an axial clearance on the roller shoe.
  • a contact surface between a roller rolling surface of the roller and a shaft rolling surface of the drive shaft occur at the contact surface in the axial direction, d. H. in the direction of the axis of rotation of the roller, different forces. This results in that the roller performs a reciprocating motion or an oscillating movement in the axial direction and thereby a direct contact between the axial sliding bearing on the at least one roller and the axial sliding bearing on the roller shoe occurs, d. H.
  • the axial extent of the blades decreases in radial direction towards the axis of rotation of the at least one roller.
  • the flow cross-sectional area of a flow space between two blades decreases in the radial direction in the direction of the axis of rotation of the at least one roller.
  • Method for operating a high-pressure pump comprising the steps of rotating a drive shaft with at least one cam about an axis of rotation of the drive shaft, supporting a roller on a shaft rolling surface of the drive shaft, sliding bearings of the roller with a roller shoe, such that from the roller a rotational movement about an axis of rotation of the roller is executed and carried out by a piston connected to the roller shoe, an oscillating rotational movement for conveying a fluid, lubricating an axial and radial sliding bearing for the roller on the roller shoe with a lubricant, for.
  • the lubricant is conveyed radially in the direction of the axis of rotation to the axial sliding bearing of the roller.
  • the lubricant is conveyed by the blades in the radial direction to the axis of rotation and then due to an oscillating axial movement of the roller temporarily forms a gap between the axial sliding bearing of the roller and the axial sliding bearing of the roller shoe and in this temporary gap is the initiated by the blades funded fluid.
  • the at least one roller in a section perpendicular to a longitudinal axis as the axis of rotation, surrounds the plain bearing for more than 50% of the at least one roller.
  • the sliding bearing by means of fuel, for. As gasoline or diesel lubricated.
  • a contact surface between the roller rolling surface and the shaft rolling surface is lubricated by means of fuel.
  • an eccentric shaft is considered as a drive shaft with at least one cam.
  • the producible by the high-pressure pump pressure in the high-pressure rail is, for example, in the range of 1000 to 3000 bar z. B. for diesel engines or between 40 bar and 400 bar z. B. for gasoline engines.
  • Fig. 1 a cross section of a high pressure pump 1 for a high pressure injection system 36 is shown.
  • the high-pressure pump 1 serves to fuel, z. As gasoline or diesel, to promote an internal combustion engine 39 under high pressure.
  • the pressure which can be generated by the high-pressure pump 1 is, for example, in a range between 1000 and 3000 bar.
  • the high-pressure pump 1 has a drive shaft 2 with two cams 3, which performs a rotational movement about a shaft rotation axis 26.
  • the shaft rotation axis 26 lies in the plane of Fig. 1 and gets upright the drawing plane of Fig. 4 ,
  • a piston 5 is mounted in a cylinder 6, which is formed by a housing 8 ( Fig. 1 ).
  • a working chamber 29 is bounded by the cylinder 6, the housing 8 and the piston 5.
  • Into the working space 29 opens an inlet channel 22 with an inlet valve 19 and an outlet channel 24 with an outlet valve 20.
  • a check valve is designed to the effect that only fuel can flow into the working space 29 and the exhaust valve 20, z.
  • a check valve is designed to the effect that only fuel can flow out of the working space 29.
  • the volume of the working chamber 29 is changed due to an oscillating stroke movement of the piston 5.
  • the piston 5 is indirectly supported on the drive shaft 2 from.
  • a roller shoe 9 is attached to a roller 10.
  • the roller 10 can perform a rotational movement, the axis of rotation 25 in the plane according to Fig. 1 and 2 lies and perpendicular to the plane of Fig. 3 and 4 stands.
  • the drive shaft 2 with the at least one cam 3 has a shaft rolling surface 4 and the roller 10 has a roller rolling surface 11.
  • the roller-running surface 11 of the roller 10 rolls on the shaft rolling surface 4 of the drive shaft 2 with the two cams 3 from.
  • the roller shoe 9 is mounted in a roller shoe bearing formed by the housing 8 as a sliding bearing.
  • roller 10 to more than 50% in contact with the sliding bearing 13, which is formed by the roller shoe 9.
  • the sliding bearing 13 is lubricated by means of fuel.
  • Rolling surface 4 of the drive shaft 2 is.
  • the roller shoe 9 and the piston 5 thus carry out together an oscillating stroke movement.
  • the sliding bearing 13 in this case comprises an axial slide bearing 14 and a radial slide bearing 15.
  • the space on the roller shoe 9, the roller 10 and the drive shaft 2 in the shaft rolling surface 4 is completely filled with fuel as a lubricant.
  • From a prefeed pump 35 is Fuel constantly transported in this room. This causes a lubrication by means of fuel as a lubricant of the sliding bearing 13 as well as a cooling of the slide bearing 13.
  • the space is completed here and has only an inlet opening for supplying the fuel and an outlet opening (not shown) for discharging the fuel and is preferably always with the fuel is flowing through.
  • the radial sliding bearing 15 serves to receive radial forces on the roller 10. In the in Figure 4 illustrated section perpendicular to the axis of rotation 25 of the roller 10 and perpendicular to the shaft rotation axis 26 of the drive shaft 2, the radial slide bearing 15 is clearly visible.
  • a bearing neck 40 (FIG. Fig. 1 and 2 ) formed integrally with the rest of the roller 10.
  • the radius of the bearing neck 40 is, for example, 10% of the radius of the other roller 10 on the roller rolling surface 11.
  • the axial extent of the roller 10 is greater than outside of the bearing neck 40.
  • Radially outside of the bearing neck 40 is at both axial End sections 18, the roller 10 with blades 16 (FIG. Fig.2 and 3 ) Mistake.
  • the blades 16 thereby form a turbomachine and thereby the roller 10 also represents a rotor 17 for the blades 16.
  • the blades 16 have an entry angle ⁇ at their radial end.
  • the angle of entry ⁇ is the angle between a tangent to the blade 16 at the radial end of the blade 16 and a circle with the center of the axis of rotation 25 of the roller 10, wherein the radius of the circle the distance of the radial end of the blade 16 to the center or the axis of rotation 25 corresponds.
  • the radius of this circle corresponds to the radius of the roller 10 on the roller roller surface eleventh
  • the frontal contact point of the bearing stub 40 and the axial end of the blades 16 is convex. Correspondingly complementary to the roller shoe 9 is concave at this area. In this way, both the axial bearing gap 41 and the axial blade gap 42 in its axial extent the same size at a constant axial position of the roller 10. Notwithstanding this (not shown), the frontal contact point of the bearing stub 40, ie the axial sliding bearing 14 of caster 10 and the axial sliding bearing 14 on the roller shoe 9 also be flat.
  • the roller 10 is supported with an axial play on the roller shoe 9, because the axial distance between two axial sliding bearings of the roller, i. the axial distance between the frontal contact points of the bearing stub 40, is smaller than the axial distance of the axial slide bearing 14 on the roller shoe 9, on which the bearing stub 40 can rest.
  • Such axial clearance is required to compensate for manufacturing inaccuracies and thermally induced shape changes.
  • an axial blade gap 42 between the blades 16 and the roller shoe 9 are each provided in the axial direction.
  • the axial blade gap 42 is constantly present and changes its extent in the axial direction only in its size due to the oscillating movement of the roller 10 in the axial direction. It thus occurs due to the geometry of the roller 10, because in the axial direction, the extension of the roller 10 on the bearing neck 40 is greater than outside the bearing neck 40, i. on the blades 16, only on the bearing neck 40 of the direct axial contact between the roller 10 and the roller shoe 9.
  • the blades 16 of the fuel as a lubricant in the radial direction ie, in the direction of the rotation axis 25 is conveyed from the outside inwards to the bearing neck 40.
  • the roller shoe 9 has a Inflow channel 43 on.
  • the inflow channel 43 is formed completely in the tangential direction. Since the space around the roller 10 is completely filled with the fuel as a lubricant (not shown), the vanes 16 may deliver the fuel radially inwardly into flow spaces 44 between the blades 16.
  • an axial bearing gap 41 occurs temporarily on the bearing support 40.
  • the lubricant conveyed by the blades 16 in the direction of the axial slide bearing 14 can flow as fuel into the axial bearing gap 41 and thereby lubricate the axial sliding bearing 14, ie the front contact point of the bearing neck 40 and the corresponding axial slide bearing 14 on the roller shoe 9, are executed.
  • the lubrication of the axial sliding bearing 14 is thereby substantially improved, so that the outflow due to centrifugal forces of lubricant on the axial sliding bearing 14 can be substantially compensated.
  • FIG 5 is a highly schematic representation of the high-pressure injection system 36 for a motor vehicle 38 shown with a high-pressure rail 30 or a fuel rail 31.
  • a prefeed pump 35 delivers fuel from a fuel tank 32 through a fuel pipe 33 to the high-pressure pump 1 according to the above embodiment.
  • the high-pressure pump 1 and the prefeed pump 35 are driven by the drive shaft 2.
  • the drive shaft 2 is coupled to a crankshaft of the engine 39.
  • the high pressure rail 30 serves - as already described - to inject the fuel into the combustion chamber of the internal combustion engine 39.
  • the funded by the feed pump 35 fuel is passed through the fuel line 33 to the high-pressure pump 1.
  • a metering unit 37 controls and / or regulates the quantity of fuel supplied to the high-pressure pump 1, so that the fuel return line 34 can be dispensed with in a further embodiment (not shown).

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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)

Claims (11)

  1. Pompe haute pression (1), en particulier pour un véhicule automobile (38), pour refouler un fluide, en particulier du carburant, par exemple du diesel, comprenant
    - un arbre d'entraînement (2) comprenant au moins une came (3),
    - au moins un piston (5),
    - au moins un cylindre (6) pour le support de l'au moins un piston (5),
    - au moins un galet de roulement (10),
    - l'au moins un piston (5) s'appuyant de manière indirecte au moyen de l'au moins un galet de roulement (10) sur l'arbre d'entraînement (2) par l'au moins une came (3), de telle sorte qu'un mouvement de translation sur la base d'un mouvement de rotation de l'arbre d'entraînement (2) puisse être réalisé par l'au moins un piston (5),
    - au moins un patin (9) présentant à chaque fois un palier lisse (13) qui est lubrifié avec du lubrifiant, pour l'au moins un galet de roulement (10), de telle sorte qu'un mouvement de rotation autour d'un axe de rotation (25) puisse être effectué par l'au moins un galet de roulement (10),
    l'au moins un galet de roulement (10) étant pourvu de pales (16) au niveau d'au moins une portion d'extrémité axiale (18), de telle sorte que l'au moins un galet de roulement (10) constitue un rotor (17) pour les pales (16) afin de refouler le lubrifiant vers un palier lisse axial (14) de l'au moins un galet de roulement (10) au niveau de l'au moins un patin (9),
    caractérisée en ce que
    le lubrifiant peut être refoulé par les pales (16) radialement dans la direction de l'axe de rotation (25) de l'au moins un galet de roulement (10).
  2. Pompe haute pression selon la revendication 1,
    caractérisée en ce que
    l'au moins un galet de roulement (10) est supporté par un palier lisse axial et radial (14, 15) sur l'au moins un patin (9).
  3. Pompe haute pression selon la revendication 2,
    caractérisée en ce que
    le palier lisse axial (14) est réalisé seulement en partie au niveau de l'au moins une portion d'extrémité axiale (18), par le fait que le rayon maximal du palier lisse axial (14) est inférieur au rayon de l'au moins un galet de roulement (10) comprenant ce palier lisse axial (14).
  4. Pompe haute pression selon la revendication 3,
    caractérisée en ce que
    le palier lisse axial (14) est réalisé sous forme circulaire en coupe perpendiculairement à l'axe de rotation (25) de l'au moins un galet de roulement (10) et le rayon maximal du palier lisse axial (14) est inférieur à 70 %, 50 %, 20 % ou 10 % du rayon du galet de roulement (10).
  5. Pompe haute pression selon la revendication 3 ou 4,
    caractérisée en ce que
    les pales (16) sont réalisées seulement radialement à l'extérieur du palier lisse axial (14) de telle sorte que les pales (16) présentent en particulier exclusivement une plus grande distance à l'axe de rotation (25) que le palier lisse axial (14).
  6. Pompe haute pression selon l'une quelconque ou plusieurs des revendications 3 à 5,
    caractérisée en ce que
    la distance axiale de deux paliers lisses axiaux (14) pour chaque patin (9) est supérieure à la distance axiale du palier lisse axial (14) du galet de roulement associé (10), de telle sorte que le galet de roulement (10) soit supporté axialement avec un jeu axial sur le patin (9).
  7. Pompe haute pression selon l'une quelconque ou plusieurs des revendications précédentes,
    caractérisée en ce que
    l'étendue axiale des pales (16) diminue dans la direction radiale dans la direction de l'axe de rotation (25) de l'au moins un galet de roulement (10).
  8. Pompe haute pression selon l'une quelconque ou plusieurs des revendications précédentes,
    caractérisée en ce que
    la surface en section transversale d'écoulement d'un espace d'écoulement (44) entre deux pales (16) diminue dans la direction radiale dans la direction de l'axe de rotation (25) de l'au moins un galet de roulement (10).
  9. Procédé pour faire fonctionner une pompe haute pression (1), en particulier une pompe haute pression (1) selon l'une quelconque ou plusieurs des revendications précédentes, comprenant les étapes suivantes :
    - rotation d'un arbre d'entraînement (2) avec au moins une came (3) autour d'un axe de rotation (25) de l'arbre d'entraînement (2),
    - support d'un galet de roulement (10) sur une surface de roulement d'arbre (4) de l'arbre d'entraînement (2),
    - support sur palier lisse du galet de roulement (10) avec un patin (9),
    - de telle sorte qu'un mouvement de rotation autour d'un axe de rotation (25) du galet de roulement (10) soit réalisé par le galet de roulement (10) et
    - un mouvement de translation oscillant étant réalisé par un piston (5) connecté au patin (9) pour refouler un fluide,
    - et lubrification d'un palier lisse axial et radial (14, 15) pour le galet de roulement (10) sur le patin (9) avec un lubrifiant, par exemple du carburant ou de l'huile de lubrification,
    caractérisé en ce que
    le lubrifiant est refoulé avec des pales (16) au niveau du galet de roulement (10) radialement dans la direction de l'axe de rotation (25) au niveau du palier lisse axial (14) du galet de roulement (10).
  10. Procédé selon la revendication 9, caractérisé en ce que le lubrifiant est refoulé par les pales (16) dans la direction radiale vers l'axe de rotation (25) et ensuite, sur la base d'un déplacement axial oscillant du galet de roulement (10), il se forme temporairement une fente (41) entre le palier lisse axial (14) du galet de roulement (10) et le palier lisse axial (14) du patin (9), et du fluide refoulé par les pales (16) est introduit dans cette fente temporaire (41).
  11. Procédé selon la revendication 10,
    caractérisé en ce que
    les forces hydrauliques axiales produites du fait de la pression de refoulement du lubrifiant lors du refoulement du lubrifiant dans la direction du palier lisse axial (14) sont supérieures aux forces axiales nécessaires pour le support axial (14) du galet de roulement (10) sur le patin (9), de sorte qu'aucun contact direct entre le palier lisse axial (14) du galet de roulement (10) et le palier lisse axial (14) sur le patin (9) ne se produise.
EP11805885.8A 2011-02-07 2011-12-30 Pompe haute pression et methode de fonctionnement de celle-ci Not-in-force EP2673495B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE201110003678 DE102011003678A1 (de) 2011-02-07 2011-02-07 Hochdruckpumpe
PCT/EP2011/074287 WO2012107151A1 (fr) 2011-02-07 2011-12-30 Pompe à haute pression

Publications (2)

Publication Number Publication Date
EP2673495A1 EP2673495A1 (fr) 2013-12-18
EP2673495B1 true EP2673495B1 (fr) 2016-09-14

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EP11805885.8A Not-in-force EP2673495B1 (fr) 2011-02-07 2011-12-30 Pompe haute pression et methode de fonctionnement de celle-ci

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Country Link
EP (1) EP2673495B1 (fr)
CN (1) CN103348122A (fr)
DE (1) DE102011003678A1 (fr)
WO (1) WO2012107151A1 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102013212047A1 (de) * 2013-06-25 2015-01-08 Robert Bosch Gmbh Pumpvorrichtung, insbesondere Kraftstoffhochdruckpumpvorrichtung für eine Kraftstoffeinspritzeinrichtung
DE102014218489A1 (de) 2014-09-15 2016-03-17 Robert Bosch Gmbh Kolbenpumpe
CN107489757A (zh) * 2017-08-30 2017-12-19 湘电风能有限公司 一种开式齿轮润滑装置

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2012080330A1 (fr) * 2010-12-17 2012-06-21 Robert Bosch Gmbh Pompe haute pression

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0849619A (ja) * 1994-08-04 1996-02-20 Toyota Motor Corp 燃料噴射ポンプ
DE10356262A1 (de) 2003-12-03 2005-06-30 Robert Bosch Gmbh Radialkolbenpumpe, insbesondere für Kraftstoffeinspritzsysteme
JP4134896B2 (ja) * 2003-12-15 2008-08-20 株式会社デンソー 燃料供給ポンプ
JP4453028B2 (ja) * 2005-03-30 2010-04-21 株式会社デンソー 高圧燃料ポンプ
DE102006041673A1 (de) * 2006-02-20 2007-08-23 Robert Bosch Gmbh Hochdruckpumpe, insbesondere für eine Kraftstoffeinspritzeinrichtung einer Brennkraftmaschine
DE102006045933A1 (de) * 2006-09-28 2008-04-03 Robert Bosch Gmbh Stößelbaugruppe für eine Hochdruckpumpe und Hochdruckpumpe mit wenigstens einer Stößelbaugruppe
DE102007012707A1 (de) * 2007-03-16 2008-09-18 Robert Bosch Gmbh Hochdruckpumpe zur Förderung von Kraftstoff mit einer verbesserten Schmiermittelzufuhr in der Nockenwellenlagerung
DE102007034036A1 (de) * 2007-07-20 2009-01-22 Robert Bosch Gmbh Kraftstoffhochdruckpumpe mit Rollenstößel
DE102009001631A1 (de) * 2009-03-18 2010-09-23 Robert Bosch Gmbh Hochdruckpumpe und Stößelbaugruppe
DE102009029297A1 (de) * 2009-09-09 2011-03-10 Robert Bosch Gmbh Kolbenpumpe mit kavitationsfreiem Rollenschuh/Laufrollen-Verband

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2012080330A1 (fr) * 2010-12-17 2012-06-21 Robert Bosch Gmbh Pompe haute pression

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WO2012107151A1 (fr) 2012-08-16
EP2673495A1 (fr) 2013-12-18
DE102011003678A1 (de) 2012-08-09

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