EP2850318B1 - Pompe haute pression - Google Patents

Pompe haute pression Download PDF

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Publication number
EP2850318B1
EP2850318B1 EP13714617.1A EP13714617A EP2850318B1 EP 2850318 B1 EP2850318 B1 EP 2850318B1 EP 13714617 A EP13714617 A EP 13714617A EP 2850318 B1 EP2850318 B1 EP 2850318B1
Authority
EP
European Patent Office
Prior art keywords
drive shaft
pressure pump
cavity
fuel
roller
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
EP13714617.1A
Other languages
German (de)
English (en)
Other versions
EP2850318A1 (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

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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
    • 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 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 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.
  • the DE 10 2006 045 933 A1 shows a high-pressure pump for high-pressure fuel delivery according to the preamble of claim 1.
  • 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.
  • a high-pressure pump according to the invention is defined in claim 1.
  • the drive shaft has a cavity, which is machined, for example as an axial bore machined into the drive shaft.
  • the mass of the drive shaft can be reduced in an advantageous manner, thereby reducing the fuel consumption of the motor vehicle when the high-pressure pump is used in a motor vehicle.
  • as at least one cavity of the at least one drive shaft is also considered a space which is at least partially filled by a stiffening member and / or a sealing plug.
  • the cavity is closed with at least one sealing plug in the region of an axial end of 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 lubricant space through which fuel flows and within this lubrication space, the roller and the drive shaft is arranged. If the fuel flows into the cavity, additional mass would thereby be arranged in the drive shaft due to the fuel.
  • the sealing plug is arranged at an axial end of the 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 cavity.
  • the drive shaft In a large formation of the cavity, ie, that in a section perpendicular to a longitudinal axis of the drive shaft, the cavity occupies a large proportion, the drive shaft may not have sufficient rigidity.
  • a stiffening member is disposed 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.
  • the at least one stiffening member and / or the sealing plug has a lower density, preferably at least 10%, 30% or 50% lower density, than the drive shaft.
  • the stiffening member and / or the sealing plug have a lower density than the drive shaft, thereby reducing mass on the drive shaft.
  • the drive shaft is at least partially made of metal and the at least one stiffening part and / or the sealing plug is at least partially 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 closure plug force and / or cohesive, z. B. by means of a press fit, connected to the 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.
  • the volume of the cavity of the drive shaft is at least 10%, 30%, 50% or 70% of the total volume of the drive shaft.
  • the volume of the cavity the drive shaft has a substantial portion of the total volume of the drive shaft, thereby substantially reducing the mass of the drive shaft by means of the cavity.
  • the volume of the cavity of the drive shaft to at least 10%, 30%, 50%, 70%, 90% or 98% filled 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, the rigidity of the drive shaft can be increased to a significant extent with the stiffening part.
  • a contact surface between the roller and the drive shaft is lubricated by means of fuel.
  • the at least one roller is mounted in at least one roller shoe by means of at least one sliding bearing or a plain bearing.
  • 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 fuel from a fuel tank to the high pressure pump, wherein the high pressure pump is designed as a high pressure pump described in this patent application.
  • the high-pressure injection system has a metering unit which controls or regulates the quantity of fuel delivered per unit time by the prefeed 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 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 rotation axis 26.
  • the axis of rotation 26, which also represents a longitudinal axis 26 of the drive shaft 2 lies in the plane of the drawing Fig. 1 and is perpendicular to the plane of Fig. 2 .
  • a piston 5 is mounted in a cylinder 6 as a piston guide 7, which is formed by a housing 8.
  • 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. Through the inlet channel 22, the fuel flows into the working space 29 and through the outlet channel 24, the fuel flows out of the working space 29 under high pressure.
  • 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 lies and perpendicular to the plane of Fig. 2 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 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.
  • a spring 27 or spiral spring 27 as an elastic 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 11 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.
  • a drive shaft 2 is shown in a longitudinal section.
  • the drive shaft 2 made of steel two cavities 17 are incorporated as an axial bore 38. Because of these two cavities 17 thus has the drive shaft 2 a significantly reduced mass and on the other hand, the rigidity of the drive shaft 2 made of steel is still sufficiently large, since the holes 38 in cross section still leave a sufficiently large proportion of the drive shaft 2 made of steel.
  • Two axial ends 40 of the drive shaft 2 are arranged outside of a not shown lubrication chamber of the high-pressure pump 1, so that thereby no fuel located within the lubricant space can flow into the two bores 38.
  • a first embodiment of the drive shaft 2 is shown.
  • the drive shaft 2 has an axial bore 38 as a cavity 17 and at an in Fig. 5 On the left axial end 40 shown, the cavity 17 is closed fluid-tight by a closure plug 16 made of titanium or carbon.
  • the closure plug 16 has the effect that no fuel can flow into the cavity 17 from a lubricant space of the high-pressure pump 1. 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.
  • a second embodiment of the drive shaft 2 is shown.
  • 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. By means of the stiffening member 15 made of titanium, 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 can withstand the mechanical stresses due to the rolling of the roller 10 on the shaft rolling surface 4 in the long term.
  • a third embodiment of the drive shaft 2 is shown.
  • the stiffening member 15 is formed as a sleeve with a stiffening member cavity 14 and at an axial end 40 of the drive shaft 2 shown in Figure left this stiffening member cavity 14 of the stiffening member 15 is closed by a sealing plug 16. As a result, no fuel can flow from the lubricant space of the high-pressure pump 1, which is not shown, into the stiffening part cavity 14.
  • the stiffening part 15 made of titanium has a lower rigidity than the stiffening part 15 in FIG Fig. 6 on, since the stiffening part 15 in Fig.
  • stiffening member 15 is formed as a sleeve with a stiffening member cavity 14.
  • the stiffening part 15 in Fig. 7 can thereby provide only a smaller increase in the rigidity of the drive shaft 2 available as in Fig. 6 shown stiffening part 15. This is sufficient because in the in Fig. 7 illustrated third embodiment of the drive shaft 2, the drive shaft 2 either requires less rigidity and / or due to the formation of the bore 38 with a smaller diameter, the drive shaft 2 itself has sufficient rigidity and this only slightly with the stiffening member 15 as a sleeve as shown in FIG Fig. 7 must be increased to meet the requirements for the rigidity of the drive shaft 2.
  • FIG. 3 is a highly schematic representation of the high-pressure injection system 36 for a motor vehicle (not shown) imaged with a high-pressure rail 30 or a fuel rail 31.
  • the fuel is injected by means of valves (not shown) in the combustion chamber of the engine 39.
  • 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.
  • the fuel not required by the high-pressure pump 1 is thereby returned to the fuel tank 32 through a 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).
  • 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.

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

Claims (9)

  1. Pompe à haute pression (1) pour refouler un fluide, en particulier du carburant, par exemple du carburant diesel, comprenant :
    - un arbre d'entraînement (2) avec au moins une came (3),
    - au moins un piston (5),
    - au moins un cylindre (6) pour supporter l'au moins un piston (5),
    - l'au moins un piston (5) s'appuyant de manière indirecte au moyen d'au moins un galet de roulement (10) sur l'arbre d'entraînement (2) avec l'au moins une came (3), de telle sorte qu'un mouvement de translation puisse être effectué par l'au moins un piston (5) sur la base d'un mouvement de rotation de l'arbre d'entraînement (2),
    caractérisée en ce que
    l'arbre d'entraînement (2) avec l'au moins une came (3) est réalisé sous forme d'arbre creux (2) avec une cavité (17), afin de réduire la masse de l'arbre d'entraînement (2) et au moins une partie de rigidification (15) est disposée dans la cavité (17) afin d'accroître la rigidité de l'arbre d'entraînement (2).
  2. Pompe à haute pression selon la revendication 1, caractérisée en ce que
    la cavité (17) est fermée avec un bouchon de fermeture (16) dans la région d'une extrémité axiale (40) de l'arbre d'entraînement (2).
  3. Pompe à haute pression selon la revendication 1 ou 2,
    caractérisée en ce que
    l'au moins une partie de rigidification (15) et/ou le bouchon de fermeture (16) présente une plus faible densité, de préférence une densité d'au moins 10 %, 30 % ou 50 % plus faible que celle de l'arbre d'entraînement (2).
  4. Pompe à haute pression selon l'une quelconque ou plusieurs des revendications précédentes,
    caractérisée en ce que
    l'arbre d'entraînement (2) se compose au moins en partie de métal, et l'au moins une partie de rigidification (15) et/ou le bouchon de fermeture (16) se composent au moins en partie de titane et/ou de carbone.
  5. Pompe à haute pression selon l'une quelconque ou plusieurs des revendications précédentes,
    caractérisée en ce que
    l'au moins une partie de rigidification (15) et/ou le bouchon de fermeture (16) sont raccordés par engagement par force et/ou par liaison de matière à l'arbre d'entraînement (2).
  6. Pompe à haute pression selon l'une quelconque ou plusieurs des revendications précédentes,
    caractérisée en ce que
    le volume de la cavité (17) de l'arbre d'entraînement (2) vaut au moins 10 %, 30 %, 50 % ou 70 % du volume total de l'arbre d'entraînement (2).
  7. Pompe à haute pression selon l'une quelconque ou plusieurs des revendications précédentes,
    caractérisée en ce que
    le volume de la cavité (17) de l'arbre d'entraînement (2) est rempli à raison d'au moins 10 %, 30 %, 50 %, 70 %, 90 % ou 98 % avec l'au moins une partie de rigidification (15).
  8. Pompe à haute pression selon l'une quelconque ou plusieurs des revendications précédentes,
    caractérisée en ce que
    une surface de contact entre le galet de roulement (10) et l'arbre d'entraînement (2) est lubrifiée avec du carburant.
  9. Système d'injection à haute pression (36) pour un moteur à combustion interne (39),
    comprenant
    - une pompe à haute pression (1),
    - un rail à haute pression (30),
    - une pompe de pré-refoulement (35) pour refouler un carburant depuis un réservoir de carburant (32) jusqu'à la pompe à haute pression (1), caractérisé en ce que
    la pompe à haute pression (1) est réalisée selon l'une quelconque ou plusieurs des revendications précédentes.
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 EP2850318A1 (fr) 2015-03-25
EP2850318B1 true 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
AU4390396A (en) * 1995-01-05 1996-07-24 Linear Anstalt Pump for conveying a medium
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
None *

Also Published As

Publication number Publication date
EP2850318A1 (fr) 2015-03-25
CN104285061B (zh) 2018-10-12
DE102012208189A1 (de) 2013-11-21
CN104285061A (zh) 2015-01-14
IN2014DN06883A (fr) 2015-05-22
WO2013170997A1 (fr) 2013-11-21

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