WO2012107151A1 - Pompe à haute pression - Google Patents

Pompe à haute pression Download PDF

Info

Publication number
WO2012107151A1
WO2012107151A1 PCT/EP2011/074287 EP2011074287W WO2012107151A1 WO 2012107151 A1 WO2012107151 A1 WO 2012107151A1 EP 2011074287 W EP2011074287 W EP 2011074287W WO 2012107151 A1 WO2012107151 A1 WO 2012107151A1
Authority
WO
WIPO (PCT)
Prior art keywords
roller
axial
pressure pump
blades
sliding bearing
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/EP2011/074287
Other languages
German (de)
English (en)
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
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 CN201180066853XA priority Critical patent/CN103348122A/zh
Priority to EP11805885.8A priority patent/EP2673495B1/fr
Publication of WO2012107151A1 publication Critical patent/WO2012107151A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

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, a method for operating a high-pressure pump according to the preamble of claim 10, a high-pressure injection system according to the preamble of claim 13 and an internal combustion engine according to the preamble of claim 14.
  • High pressure accumulator of the common rail injection system can be driven, for example, by a camshaft of the internal combustion engine by means of a drive shaft.
  • Rotary vane pump used, which are 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 brings on the
  • Roller shoe a force directed radially to the drive shaft, 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 occur at the high-pressure pump at this axial plain bearing.
  • 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 at the
  • High-pressure pump in particular for a motor vehicle, for
  • 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 is supported, so that of the at least one piston
  • Translational movement due to a rotational movement of the drive shaft is executable, at least one roller shoe, each with a sliding bearing, which is lubricated with lubricant for the at least one roller, so that at least one roller a rotational movement about an axis of rotation is executable, wherein the at least one roller at least one axial end portion is provided 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 of the at least one roller on the at least one roller shoe.
  • the at least one roller is provided with blades, the one
  • the geometry of the blades is designed such that they are capable of the lubricant, for.
  • As fuel especially diesel or gasoline, or lubricating oil, to promote 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 respectively associated roller shoe can be significantly reduced and the
  • 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 in such a way that they are capable of the lubricant radially to promote in the direction of 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 in a section perpendicular to the
  • Rotary axis of the at least one roller formed circular 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.
  • 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.
  • Rotary axis 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, so that the roller is a rotational movement about an axis of rotation of the roller is performed and by an associated with the roller shoe piston an oscillating rotational movement is performed Conveying a fluid
  • roller shoe with a lubricant eg. As fuel or lubricating oil, with blades on the roller, 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 is temporarily formed a gap between the axial sliding bearing of the roller and the axial sliding bearing of the
  • the at least one roller Longitudinal axis as a rotation axis, the at least one roller, the sliding bearing to more than 50%, 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.
  • Inventive high-pressure injection system for an internal combustion engine in particular for a motor vehicle, comprising a high-pressure pump, a
  • High-pressure rail preferably a prefeed pump for conveying a
  • High-pressure pump is formed and / or from the high-pressure injection system described in this patent application process is executable.
  • the high-pressure injection system has a
  • 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.
  • High-pressure injection system in particular for a motor vehicle, comprises a high-pressure injection system described in this patent application and / or a high-pressure pump described in this patent application.
  • a motor vehicle according to the invention comprises one in this
  • Patent application described high-pressure pump and / or a high-pressure injection system described in this patent application and / or an internal combustion engine described in this patent application.
  • 1 is a cross section of a high-pressure pump
  • FIG. 2 shows an enlarged cross section of a roller and a roller shoe of the high-pressure pump according to FIG. 1,
  • FIG. 3 is a side view of the roller according to FIG. 2,
  • FIG. 4 shows a section A-A according to FIG. 1 of the roller with roller shoe and a drive shaft
  • Fig. 5 is a highly schematic view of a high-pressure injection system and Fig. 6 is a view of a motor vehicle.
  • Fig. 1 is a cross section of a high-pressure pump 1 for a
  • 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 drawing plane of FIG. 1 and is perpendicular to the plane of the drawing 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.
  • As a check valve is designed to the effect that only fuel can flow into the working space 29 and the exhaust valve 20, z.
  • Check valve is designed so that only fuel can flow out of the working chamber 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
  • Rotation axis 25 lies in the plane of the drawing of FIG. 1 and 2 and is perpendicular to the plane of Fig. 3 and 4.
  • 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 tread 1 1 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. Further, in the section of FIG. 4, the roller 10 is more than 50% in contact with the sliding bearing 13 formed by the roller shoe 9.
  • the sliding bearing 13 is lubricated by means of fuel.
  • 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
  • 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 is used for
  • a bearing stub 40 (FIGS. 1 and 2) is formed integrally with the rest of the roller 10.
  • the radius of the bearing stub 40 is for example 10% of the radius of the rest of the roller 10 at the
  • roller rolling surface 11 At the location stub 40 is the axial extent of the
  • Roller 10 is larger than outside the bearing stub 40. Radially outside of the bearing stub 40, the roller 10 is provided with blades 16 (FIGS. 2 and 3) at both axial end portions 18. 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 entrance angle ⁇ 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 corresponds to the distance of the radial end of the blade 16 to the center or the rotation axis 25.
  • the radius of this circle corresponds to the radius of the roller 10 at the
  • the roller 10 is mounted with an axial play on the roller shoe 9, because the axial distance between two axial sliding bearings of the roller, d. H. the axial distance of the end-side contact points of the bearing stub 40, is smaller than the axial distance of the axial sliding bearing 14 on the roller shoe 9, on soft the bearing stub 40 can rest.
  • Such axial play is required to reduce manufacturing inaccuracies and thermal issues
  • Rotation axis 25 different forces, so that the roller 10 performs an axial oscillating movement and thereby on the front side
  • roller shoe 9 each 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 sleeve 40, ie on the blades 16, only on the bearing stub 40 of the direct axial contact between the roller 10th and the roller shoe 9.
  • the fuel is used as a lubricant in the radial direction, i. H. toward the axis of rotation 25 from outside to inside to the
  • Supported spigot 40 In the axial direction is a conveyor or
  • the roller shoe 9 has an inflow channel 43.
  • 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. Due to the oscillating movement of the roller 10 in the direction of the axis of rotation 25 occurs temporarily to each of the
  • 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. From the high-pressure rail 30, the fuel by means of valves (not shown) in the combustion chamber of the engine
  • a prefeed pump 35 delivers fuel from one Fuel tank 32 through a fuel line 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.
  • the fuel not required by the high pressure pump 1 is thereby returned to the fuel return line 34
  • 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).
  • Overall, significant advantages are associated with the high-pressure pump 1 according to the invention. With the blades 16 on the roller 10 can be promoted to the axial sliding bearing 14 of the roller 10 on the roller shoe 9 in a simple manner, so that thereby the lubrication of the axial sliding bearing 14 is substantially improved.

Landscapes

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

Abstract

Pompe à haute pression (1), notamment pour véhicule automobile, permettant de refouler un fluide, en particulier un carburant, par ex. du gazole, comprenant un arbre d'entraînement (2) doté d'au moins une came (3), d'au moins un piston (5), d'au moins un cylindre (6) servant de logement audit au moins un piston (5), d'au moins un galet de roulement (10), le piston (5) prenant indirectement appui sur l'arbre d'entraînement (2) doté de la came (3) au moyen du galet de roulement (10) de sorte que le piston (5) puisse exécuter un mouvement de translation engendré par le mouvement de rotation de l'arbre d'entraînement (2), au moins un coussinet à rouleaux (9) respectivement doté d'un palier lisse lubrifié avec un lubrifiant, pour le galet de roulement (10) de sorte que le galet de roulement (10) puisse exécuter un mouvement de rotation autour d'un axe de rotation (25), le galet de roulement (10) étant muni d'ailettes (16) sur au moins une section finale axiale de manière que le galet de roulement (10) forme un rotor pour les ailettes (16) afin de refouler le lubrifiant vers un palier lisse axial du galet de roulement (10) sur le coussinet à rouleaux (9).
PCT/EP2011/074287 2011-02-07 2011-12-30 Pompe à haute pression Ceased WO2012107151A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
CN201180066853XA CN103348122A (zh) 2011-02-07 2011-12-30 高压泵
EP11805885.8A EP2673495B1 (fr) 2011-02-07 2011-12-30 Pompe haute pression et methode de fonctionnement de celle-ci

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE201110003678 DE102011003678A1 (de) 2011-02-07 2011-02-07 Hochdruckpumpe
DE102011003678.4 2011-02-07

Publications (1)

Publication Number Publication Date
WO2012107151A1 true WO2012107151A1 (fr) 2012-08-16

Family

ID=45464572

Family Applications (1)

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

Country Status (4)

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

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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

Families Citing this family (2)

* 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

Citations (7)

* 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
EP1544462A2 (fr) * 2003-12-15 2005-06-22 Denso Corporation Pompe à carburant avec rainure de lubrification
DE10356262A1 (de) 2003-12-03 2005-06-30 Robert Bosch Gmbh Radialkolbenpumpe, insbesondere für Kraftstoffeinspritzsysteme
DE102006045933A1 (de) 2006-09-28 2008-04-03 Robert Bosch Gmbh Stößelbaugruppe für eine Hochdruckpumpe und Hochdruckpumpe mit wenigstens einer Stößelbaugruppe
WO2008113625A1 (fr) * 2007-03-16 2008-09-25 Robert Bosch Gmbh Pompe haute pression destinée au transport de carburant avec une meilleure amenée de lubrifiant dans le palier d'arbre à cames
DE102007034036A1 (de) * 2007-07-20 2009-01-22 Robert Bosch Gmbh Kraftstoffhochdruckpumpe mit Rollenstößel
DE102009029297A1 (de) * 2009-09-09 2011-03-10 Robert Bosch Gmbh Kolbenpumpe mit kavitationsfreiem Rollenschuh/Laufrollen-Verband

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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
DE102009001631A1 (de) * 2009-03-18 2010-09-23 Robert Bosch Gmbh Hochdruckpumpe und Stößelbaugruppe
DE102010063351A1 (de) * 2010-12-17 2012-06-21 Robert Bosch Gmbh Hochdruckpumpe

Patent Citations (7)

* 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
EP1544462A2 (fr) * 2003-12-15 2005-06-22 Denso Corporation Pompe à carburant avec rainure de lubrification
DE102006045933A1 (de) 2006-09-28 2008-04-03 Robert Bosch Gmbh Stößelbaugruppe für eine Hochdruckpumpe und Hochdruckpumpe mit wenigstens einer Stößelbaugruppe
WO2008113625A1 (fr) * 2007-03-16 2008-09-25 Robert Bosch Gmbh Pompe haute pression destinée au transport de carburant avec une meilleure amenée de lubrifiant dans le palier d'arbre à cames
DE102007034036A1 (de) * 2007-07-20 2009-01-22 Robert Bosch Gmbh Kraftstoffhochdruckpumpe mit Rollenstößel
DE102009029297A1 (de) * 2009-09-09 2011-03-10 Robert Bosch Gmbh Kolbenpumpe mit kavitationsfreiem Rollenschuh/Laufrollen-Verband

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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

Also Published As

Publication number Publication date
EP2673495A1 (fr) 2013-12-18
DE102011003678A1 (de) 2012-08-09
CN103348122A (zh) 2013-10-09
EP2673495B1 (fr) 2016-09-14

Similar Documents

Publication Publication Date Title
WO2013124103A1 (fr) Pompe haute pression
DE102009026596A1 (de) Hochdruckpumpe
EP2954192B1 (fr) Pompe haute pression
EP2673495B1 (fr) Pompe haute pression et methode de fonctionnement de celle-ci
EP2935857B1 (fr) Systeme d'injection de carburant a haute pression
EP3011164B1 (fr) Pompe haute pression
EP2809943B1 (fr) Pompe haute pression
EP3368764A1 (fr) Pompe à haute pression
WO2012072294A1 (fr) Pompe haute pression
EP2850318B1 (fr) Pompe haute pression
DE102012212154A1 (de) Hochdruckpumpe
EP2872771B1 (fr) Pompe haute pression
DE102009026740A1 (de) Hochdruckpumpe
DE102012202717A1 (de) Hochdruckpumpe
DE102011076063A1 (de) System zum Fördern eines Fluides
DE102012201308A1 (de) Hochdruckpumpe
DE102011076057A1 (de) Hochdruckeinspritzsystem
DE102024200265A1 (de) Rollenstößel
DE102009026610A1 (de) Hochdruckpumpe
DE102011076060A1 (de) System zum Fördern eines Fluides
DE102009027156A1 (de) Hochdruckpumpe
DE102012202718A1 (de) Ventil
DE102012208187A1 (de) Hochdruckpumpe
DE102011086690A1 (de) System für ein Hochdruckeinspritzsystem mit einem Überströmventil und einer Zumesseinheit
DE102009026603A1 (de) Hochdruckpumpe

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 11805885

Country of ref document: EP

Kind code of ref document: A1

REEP Request for entry into the european phase

Ref document number: 2011805885

Country of ref document: EP

WWE Wipo information: entry into national phase

Ref document number: 2011805885

Country of ref document: EP