EP2850318A1 - Pompe à haute pression - Google Patents

Pompe à haute pression

Info

Publication number
EP2850318A1
EP2850318A1 EP13714617.1A EP13714617A EP2850318A1 EP 2850318 A1 EP2850318 A1 EP 2850318A1 EP 13714617 A EP13714617 A EP 13714617A EP 2850318 A1 EP2850318 A1 EP 2850318A1
Authority
EP
European Patent Office
Prior art keywords
drive shaft
pressure pump
cavity
fuel
piston
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP13714617.1A
Other languages
German (de)
English (en)
Other versions
EP2850318B1 (fr
Inventor
Sascha Ambrock
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP2850318A1 publication Critical patent/EP2850318A1/fr
Application granted granted Critical
Publication of EP2850318B1 publication Critical patent/EP2850318B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • 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
    • 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
    • F04B1/0439—Supporting or guiding means for the pistons

Definitions

  • the present invention relates to a high-pressure pump according to the preamble of claim 1 and a high-pressure injection system according to the preamble of claim 10.
  • a high-pressure pump permanently ensures the maintenance of the pressure in the
  • 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 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 stands with the roller rolling surface on a shaft rolling surface as the surface of the drive shaft with the at least one cam in contact with the drive shaft.
  • the roller is mounted by means of a sliding bearing in the roller shoe.
  • the drive shaft with the at least one cam is generally made of steel, on the one hand to have sufficient rigidity and on the other hand to withstand the mechanical loads due to the roller, which rolls on the drive roller can withstand.
  • the drive shaft has a large mass and, when the high-pressure pump is used in a motor vehicle, a large mass of the high-pressure pump also leads to a greater fuel consumption of the motor vehicle in a disadvantageous manner.
  • 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
  • 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, wherein the at least one piston indirectly by means of at least one roller on the drive shaft is supported by the at least one cam, so that from the at least one piston a translational movement due to a
  • Rotary movement of the drive shaft is executable, wherein the at least one drive shaft is formed with the at least one cam as a hollow shaft with at least one cavity to the mass of at least one
  • the at least one drive shaft has at least one cavity, which is machined, for example, as an axial bore machined into the at least one drive shaft.
  • the cavity is closed in a fluid-tight manner with the at least one sealing plug so that no fuel can flow into the at least one cavity.
  • the high pressure pump has a
  • Lubrication space is the roller and the drive shaft arranged. If the fuel flows into the cavity, additional mass would thereby be arranged in the drive shaft due to the fuel.
  • the closure plug is arranged at one or more axial ends of the one drive shaft, so that thereby the cavity is not filled with fuel, but for example, filled with air, so that thereby the drive shaft has a lower mass.
  • at least one stiffening part is arranged in the at least one cavity.
  • the drive shaft may not have sufficient rigidity.
  • a stiffening part is arranged within the cavity, so that characterized the drive shaft has sufficient rigidity. This is necessary because a compressive force is applied to the drive shaft perpendicular to the longitudinal axis of the roller.
  • Stiffening member and / or the at least one sealing plug a lower density, preferably at least 10%, 30% or 50% lower density than the at least one drive shaft.
  • Sealing plugs have a lower density than the drive shaft, thereby reducing mass on the drive shaft.
  • the at least one drive shaft preferably consists at least partially, in particular completely, of metal, in particular steel or aluminum, and the at least one stiffening part and / or the at least one
  • Closure plug is at least partially, in particular completely, made of titanium and / or carbon.
  • the drive shaft is generally made of steel, since on the outside of the drive shaft, the roller rolls off and thereby a considerable mechanical stress on the outside of a shaft rolling surface of the drive shaft is present. This generally requires steel.
  • the stiffening member and / or the sealing plug have titanium with a low density and thus mass to keep one hand, the mass of the drive shaft with stiffening and / or sealing plug low, and on the other hand, titanium and / or carbon also ensures sufficient rigidity.
  • the at least one stiffening part and / or the at least one sealing plug force and / or cohesive, z. B. by means of a press fit, connected to the at least one drive shaft.
  • the at least one stiffening part and / or the at least one sealing plug can also be connected to the at least one drive shaft by means of a screw connection.
  • Volumes of the cavities of a drive shaft at least 10%, 30%, 50% or 70% of the total volume of the drive shaft with the at least one
  • the volume of the cavity and / or the sum of the volumes of the Cavities of the drive shaft have a significant share of
  • the volume of a cavity or the sum of the volumes of the cavities of a drive shaft is or are filled to at least 10%, 30%, 50%, 70%, 90% or 98% with the at least one stiffening part. If the volume of the cavity is filled to a substantial extent by the stiffening part and the stiffening part is also sufficiently connected to the drive shaft, can thereby with the stiffening the
  • Stiffness of the drive shaft can be increased to a significant extent.
  • a contact surface between the roller and the drive shaft is lubricated by means of fuel.
  • the at least one roller by means of at least one
  • the at least one roller in a section perpendicular to a longitudinal axis as the axis of rotation, surrounds the plain bearing to more than 50% of the at least one roller.
  • the plain bearing by means of fuel, for.
  • fuel for.
  • 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 designed as a high pressure pump described in this patent application.
  • the high-pressure injection system has a
  • Metering unit that controls or regulates the amount of fuel delivered per unit time by the precharge pump to the high pressure pump.
  • 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 shows a cross section of a high-pressure pump in a first
  • FIG. 2 shows a section A-A of FIG. 1 a roller with roller shoe and a drive shaft
  • FIG. 3 is a highly schematic view of a high-pressure injection system
  • Fig. 4 is a longitudinal section of the drive shaft in one
  • Fig. 5 is a longitudinal section of the drive shaft in one
  • Fig. 6 is a longitudinal section of the drive shaft in one
  • Fig. 7 is a longitudinal section of the drive shaft in one
  • 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 rotation axis 26.
  • a piston 5 is mounted in a cylinder 6 as a piston guide 7, which is formed by a housing 8.
  • a working space 29 is from the cylinder 6, the
  • In the working space 29 opens an inlet channel 22 with an inlet valve 19 and an outlet channel 24 with a
  • Working space 29 can flow and the exhaust valve 20, z. B. a
  • 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.
  • Roller 10 can perform a rotational movement
  • Rotation axis 25 lies in the plane of FIG. 1 and is perpendicular to the plane of Fig. 2.
  • 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 1 1.
  • roller tread 1 1 of the roller 10 rolls on a contact surface 12 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.
  • Element 28 which is clamped between the housing 8 and the roller shoe 9 is, brings on the roller shoe 9 a compressive force, so that the roller rolling surface 1 1 of the roller 10 is in constant contact with the shaft rolling surface 4 of the drive shaft 2.
  • the roller shoe 9 and the piston 5 thus carry out together an oscillating stroke movement.
  • Fig. 4 is a first embodiment of the drive shaft 2 in one
  • High pressure pump 1 arranged so that thereby no within the
  • Lubricating space located fuel can flow into the two holes 38.
  • a second embodiment of the drive shaft 2 is shown.
  • the drive shaft 2 has an axial bore 38 as a cavity 17 and at an axial end 40 shown on the left in Fig. 5, the cavity 17 is closed fluid-tight by a closure plug 16 made of titanium or carbon.
  • Closure plug 16 causes that no fuel from a lubricant chamber of the high-pressure pump 1 can flow into the cavity 17. As a result, 16 air is disposed within the cavity 17 apart from the sealing plug and the drive shaft 2 thereby has a low mass.
  • the drive shaft 2 made of steel has an axial bore 38 as a cavity 17 and this cavity 17 is substantially filled with a stiffening member 15 made of titanium.
  • the axial bore 38 is machined, z. B. by means of drilling, incorporated and then the closure plug 16 inserted into this bore 38 and thereby positively connected by means of a press fit with the drive shaft 2 made of steel. Due to the size of the bore 38, the drive shaft 2 without the stiffening part 5 made of titanium does not have sufficient rigidity.
  • the rigidity of the drive shaft. 2 be increased significantly.
  • titanium advantageously has on the one hand a low mass and on the other hand also a sufficiently high rigidity in order to increase the rigidity of the drive shaft 2.
  • the drive shaft 2 in particular on the shaft rolling surface 4 for supporting the roller 10, made of steel, so that thereby the drive shaft 2, the mechanical
  • a fourth embodiment of the drive shaft 2 is shown. In the following, essentially only the differences to the third
  • the stiffening part 15 is formed as a sleeve with a stiffening part cavity 14 and at an axial end 40 of the drive shaft 2 shown in Figure on the left is this
  • Closing plug 16 closed This can be done in the
  • the stiffening member 15 made of titanium has a lower rigidity than the stiffening member 15 in Fig. 6, since the stiffening member 15 in Fig. 6 consists of a solid material and the stiffening member 15 used in Fig. 7 in the fourth embodiment as a sleeve with a stiffening member cavity 14 is formed.
  • the stiffening member 15 in Fig. 7 can thereby only a smaller increase in the rigidity of
  • FIG. 3 is a highly schematic representation of the high-pressure injection system 36 for a motor vehicle (not shown) 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
  • a prefeed pump 35 delivers fuel from a fuel tank 32 through a fuel line 33 to the
  • High-pressure pump 1 according to the above embodiment.
  • High-pressure pump 1 and the feed pump 35 are thereby of the
  • a metering unit 37 controls and / or controls the
  • High-pressure pump 1 supplied amount of fuel, so that can be dispensed in a further embodiment, the fuel return line 34 (not shown).
  • the drive shaft 2 made of steel has a bore 38 as a cavity 17, so that thereby the drive shaft 2 has a reduced mass.
  • a stiffening member 15, z To increase the rigidity of the drive shaft 2 can within the cavity 17, a stiffening member 15, z.
  • Example of titanium to thereby increase the one hand, the rigidity of the drive shaft 2, at a low mass of the drive shaft 2 due to the low density of the stiffening member 15, and on the other hand on the shaft rolling surface 4, a sufficient mechanical wear resistance for rolling the To get roller 10.

Landscapes

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

Abstract

L'invention concerne une pompe à haute pression (1) destinée à refouler un fluide, en particulier un carburant, par exemple du diesel. La pompe comprend un arbre d'entraînement (2) doté au moins d'une came (3), au moins un piston (5), au moins un cylindre (6) destiné au montage du ou des pistons (5). Le ou les pistons (5) s'appuient indirectement, au moyen d'au moins un galet de roulement (10), sur l'arbre d'entraînement (2) doté de la ou des cames (3), de sorte qu'un déplacement en translation peut être mis en œuvre par le ou les pistons (5) du fait d'un déplacement en rotation de l'arbre d'entraînement (2). Le ou les arbres d'entraînement (2) dotés de la ou des cames (3) sont réalisés sous la forme d'un arbre creux (2) pourvu d'au moins une cavité, afin de réduire la masse de l'arbre ou des arbres d'entraînement (2).
EP13714617.1A 2012-05-16 2013-04-02 Pompe haute pression Not-in-force EP2850318B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102012208189A DE102012208189A1 (de) 2012-05-16 2012-05-16 Hochdruckpumpe
PCT/EP2013/056859 WO2013170997A1 (fr) 2012-05-16 2013-04-02 Pompe à haute pression

Publications (2)

Publication Number Publication Date
EP2850318A1 true EP2850318A1 (fr) 2015-03-25
EP2850318B1 EP2850318B1 (fr) 2017-09-20

Family

ID=48049998

Family Applications (1)

Application Number Title Priority Date Filing Date
EP13714617.1A Not-in-force EP2850318B1 (fr) 2012-05-16 2013-04-02 Pompe haute pression

Country Status (5)

Country Link
EP (1) EP2850318B1 (fr)
CN (1) CN104285061B (fr)
DE (1) DE102012208189A1 (fr)
IN (1) IN2014DN06883A (fr)
WO (1) WO2013170997A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102015220870A1 (de) 2015-10-26 2017-04-27 Robert Bosch Gmbh Hochdruckpumpe

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1097759B (de) * 1956-07-10 1961-01-19 Mono Cam Ltd Kraftstoffeinspritzpumpe
AT233903B (de) * 1959-12-10 1964-06-10 Pierre Etienne Bessiere Vorrichtung zur selbsttätigen Änderung der Voreilung der Brennstoffeinspritzung in Motoren
AT236168B (de) * 1962-06-14 1964-10-12 Friedmann & Maier Ag Einspritzpumpe für Brennkraftmaschinen
WO1996021107A1 (fr) * 1995-01-05 1996-07-11 Linear Anstalt Pompe permettant de refouler un milieu
DE19529041B4 (de) * 1995-08-08 2006-07-27 Schaeffler Kg Kipp- oder Schlepphebelanordnung
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

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2013170997A1 *

Also Published As

Publication number Publication date
CN104285061B (zh) 2018-10-12
DE102012208189A1 (de) 2013-11-21
IN2014DN06883A (fr) 2015-05-22
WO2013170997A1 (fr) 2013-11-21
EP2850318B1 (fr) 2017-09-20
CN104285061A (zh) 2015-01-14

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