EP2809943B1 - Hochdruckpumpe - Google Patents

Hochdruckpumpe Download PDF

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Publication number
EP2809943B1
EP2809943B1 EP13700229.1A EP13700229A EP2809943B1 EP 2809943 B1 EP2809943 B1 EP 2809943B1 EP 13700229 A EP13700229 A EP 13700229A EP 2809943 B1 EP2809943 B1 EP 2809943B1
Authority
EP
European Patent Office
Prior art keywords
roller
pressure pump
roller shoe
shoe
contact surface
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.)
Active
Application number
EP13700229.1A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP2809943A1 (de
Inventor
Sascha ARMBROCK
Frank Zehnder
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 EP2809943A1 publication Critical patent/EP2809943A1/de
Application granted granted Critical
Publication of EP2809943B1 publication Critical patent/EP2809943B1/de
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • 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
    • F04B1/0426—Arrangements for pressing the pistons against the actuated cam; Arrangements for connecting the pistons to the actuated cam
    • 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 12.
  • 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 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.
  • the DE 10 2009 028 378 A1 is considered to be the closest prior art and discloses a friction-reduced coated roller shoe having a widening gap between roller and roller shoe over the operating contact surface. A cover prevents the ingress of dirt into the gap.
  • 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, a roller shoe with a mounted in the roller shoe with a sliding bearing Roller and the piston indirectly with the roller shoe on the drive shaft with the at least one cam is supported, so that from the at least one piston a translational movement due to a rotational movement of the drive shaft executable, wherein the sliding bearing on the roller shoe outside an operating contact surface of the slide bearing at least one recess has at least one axial groove and the at least one axial groove is formed completely in the axial direction of a rotation axis of the roller on the roller shoe.
  • the at least one recess is formed as at least one axial groove and preferably the roller shoe has two axial grooves and / or there is at the at least one recess, in particular the at least one axial groove, no contact between the roller and the roller shoe.
  • An axial groove on the roller shoe allows the clamping to be prevented over a larger area of the roller shoe in the direction of the axis of rotation of the roller.
  • the at least one axial groove is formed in the tangential direction between the operating contact surface and an assembly aid of the plain bearing.
  • the roller shoe is pressed by a spring onto the drive shaft.
  • a compressive force occurs in the direction of the translational movement of the roller shoe between the plain bearing of the roller shoe and the roller.
  • This pressure force is transmitted to the roller substantially at the operating contact surface of the roller shoe, so that in general no or only very small forces are to be transmitted from the roller shoe to the roller outside of the operating contact surface.
  • the mounting aid is essentially required only that during the assembly of the high-pressure pump, the roller is attached to the roller shoe and possibly used during operation of the high-pressure pump only that in case of disturbances or vibrations, the roller is still held on the roller shoe. However, generally occurs at the Assembly aid in normal operation of the high pressure pump no contact between the roller and the mounting aid of the sliding bearing on.
  • the at least one axial groove interrupts the sliding bearing in the tangential direction between the operating contact surface and the mounting aid of the plain bearing and / or the at least one axial groove is formed completely in the axial direction of a rotation axis of the roller on the roller shoe.
  • the axial groove is formed completely continuously in the direction of the axis of rotation of the roller on the roller shoe. It is expedient for the at least one axial groove to have a spacing of at least 0.5, 1, 2, 3 or 5 mm between the roller shoe and the roller rolling surface of the roller.
  • the mounting aid of the plain bearing in the direction of the translational movement of the roller shoe is at least partially formed between the axis of rotation of the roller and a side of the roller shoe in the direction of the drive shaft.
  • the operating contact surface comprises an angular range in a fictitious plane perpendicular to the axis of rotation of the caster, each beginning at opposite angles on a fictitious half-line intersecting the location of the operating contact surface with a minimum distance to the piston and the axis of rotation of the caster of less than 80 ° , 60 °, 40 °, 30 °, 15 °, 10 ° or 5 ° and / or of at least 5 °, 10 ° or 15 °.
  • the operating contact surface is thus formed at a portion of the sliding bearing in the direction of the piston, that is, the operating contact surface has a smaller distance to the piston than the rest of sliding bearing.
  • the rest of the sliding bearing of the roller shoe comprises only the mounting aid of the plain bearing or the sliding bearing on the mounting aid.
  • the distance between the axis of rotation of the roller and the sliding bearing of the roller shoe on the mounting aid is greater than on the operating contact surface.
  • the distance between the axis of rotation and the mounting aid is at least 1, 3, 5, 10, 20 or 30% greater than the distance between the axis of rotation and the operating contact surface.
  • the plain bearing in particular the operating contact surface
  • the plain bearing is provided with a coating, in particular carbon coating, for reducing the friction between the roller and the plain bearing.
  • the coating reduces the friction between the roller and the slide bearing on the operating contact surface and is also abrasion resistant, so that the high pressure pump has only a very small and negligible removal of the coating by the roller in permanent and long-term operation on the coating.
  • the roller shoe is provided with at least one lubrication channel, which opens into the at least one recess, in particular into the at least one axial groove. By means of the lubricating channel, fuel can additionally be conducted as lubricant to the slide bearing, in particular to the operating contact surface.
  • the temperature of the sliding bearing of the roller shoe is reduced due to the friction occurring because heat is dissipated by the fuel.
  • the formation of deposits and deposits on the slide bearing, in particular on the operating contact surface can be substantially reduced in an advantageous manner.
  • the at least one lubrication channel is designed in the direction of the translational movement of the roller shoe, and preferably the at least one lubrication channel terminates on one side of the roller shoe in the direction of the drive shaft.
  • the roller shoe is arranged within a lubricant space with fuel and in a translational movement of the piston from a top dead center to a bottom dead center thereby flows fuel into the lubrication channel and is then passed through the lubrication channel to the at least one axial groove, thereby lubricating the plain bearing of the roller shoe with fuel is substantially increased.
  • a sliding bearing between the roller shoe and the roller is lubricated by means of fuel.
  • the high-pressure pump comprises a lubricating space and fuel is conveyed through the lubricating space for lubricating the high-pressure pump and within the lubricating space the roller shoe with the roller and preferably the drive shaft and partially preferably the piston is arranged.
  • 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.
  • An internal combustion engine according to the invention with a high-pressure injection system comprises a high-pressure injection system described in this patent application and / or a high-pressure pump described in this patent application.
  • 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.
  • Fig. 2 is a known from the prior art roller shoe 9 shown.
  • 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 lies in the plane of Fig. 1 and is perpendicular to the plane of Fig. 2 ,
  • a piston 5 is mounted in a cylinder 6, 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.
  • a check valve is designed such that only fuel in the Working space 29 can flow 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 lies and perpendicular to the plane of Fig. 2 . 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 on a contact surface 12 from.
  • the roller shoe 9 is mounted in a roller shoe bearing formed by the housing 8 as a slide bearing 13.
  • Fig. 2 is a well-known from the prior art slide bearing 13 is shown.
  • 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.
  • FIG. 6 is a highly schematic representation of the high-pressure injection system 36 shown for a motor vehicle 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.
  • Fuel is returned through a fuel return line 34 back into the fuel tank 32.
  • 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).
  • a first embodiment of the roller shoe 9 is shown with the roller 10 for a high-pressure pump 1 according to the invention.
  • the sliding bearing 13 of the roller shoe 9 comprises an operating contact surface 14 and an assembly aid 15. Only on the operating contact surface 14 is a carbon coating 41 formed as a coating 40 is present. Outside the carbon coating 41, the roller shoe 9 is made of metal, for example steel, such as the roller 10. At the mounting aid 15, the sliding bearing 13 no carbon coating 41 on. In a tangential direction 18 of the sliding bearing 13, a cross-sectionally semicircular axial groove 17 is incorporated in the roller shoe 9 made of steel between the operating contact surface 14 and the carbon coating 41 and the two mounting aids.
  • the two axial grooves 17 between the operating contact surface 14 and the two mounting aids 15 thus form a recess 16 on the sliding bearing 13, so that no contact between the roller shoe 9 and the roller 10 can occur at the two axial grooves 17.
  • the roller shoe 9 with the roller 10 performs an oscillating translatory movement in one direction 43.
  • a compressive force in the direction of the drive shaft 2 is applied by the spring 27 on the roller shoe 9, so that from the roller shoe 9 on the roller 10, a compressive force is transmitted and this is exclusively or substantially at the operating contact surface 14 of the roller shoe on the Transfer roller 10.
  • the two assembly aids 15 as part of the sliding bearing 13 are required only during assembly of the high pressure pump 1 to hold the roller 10 in the roller shoe 9 can.
  • vibrations of the high pressure pump 1 may also occur during normal operation of the high pressure pump 1, which could cause falling out of the roller 10 in very unfavorable circumstances.
  • the two mounting aids 15 the slide bearing 13 is required in order to be able to hold the roller 10 securely against the roller shoe 9 even with vibrations in this operating state of the high-pressure pump 1.
  • the operating contact surface 14 or the sliding bearing 13 has in the section in Fig. 3 a location 38 with a minimum distance to the piston 5 on and in the section in FIG Fig. 3 is the point 38 to a point, but due to the expansion of the roller shoe 9 and the roller 10 perpendicular to the plane of Fig. 3 the point 38 is a line or a straight line.
  • a first leg of the angle ⁇ is a fictitious half-line 45, beginning with the axis of rotation 25 in the section in FIG Fig. 3 and this half-line also intersects the point 38.
  • the two angles ⁇ are bounded in two opposite directions by the fictitious half-line 45.
  • the two angles ⁇ are in Fig.
  • the roller shoe 9 has a total of four lubrication channels 42 (FIG. Fig. 5 ) on. These lubrication channels 42 begin at the side 44 and respectively end and guide into the two axial grooves 17. In each case two lubrication channels 42 open into each of the two axial grooves 17.
  • the lubricating passages 42 guide fuel to the axial grooves 17 and thereby the operating contact surface 14 is lubricated with additional fuel so that thereby the temperature of the operating contact surface 14 is reduced due to the cooling effect of the fuel and thus form less deposits on the operating contact surface 14 as well as on the mounting aid 15.
  • the roller shoe 9 may be executed without the lubrication channels 42.
  • the two axial grooves 17 in the first embodiment of the roller shoe 9 according to Fig. 3 and 5 have significant advantages for the high pressure pump 1.
  • there is also a deposit or deposit in this area because generally no deposits are formed on the operating contact surface 14 due to the permanent contact between the roller 10 and the operating contact surface 14.
  • the mounting aid 15 since it is not required in normal operation for the sliding bearing of the roller 10, formed with a significantly greater distance of the rotation axis 25 of the roller 9, so that between the roller 10 and the roller rolling surface 11 and Mounting aid 15 is a very large distance or a very big game and this distance and this game is chosen so constructive that even with unfavorable and larger deposits on the mounting aid 15 no clamping of the roller 10 occurs in the roller shoe 9.
  • no or substantially no deposits occur on the operating contact surface 14, and because of the axial groove 17, movement due to deposits of the roller 10 relative to the roller shoe 9 in the direction of the drive shaft 2 is precluded.
  • the axial grooves 17 thus prevent a relative movement of the roller 10 relative to the roller shoe 9 in the direction of the drive shaft second
  • a second embodiment of the roller shoe 9 is shown.
  • the two axial grooves 17 are in the section in Fig. 4 formed substantially rectangular and not semicircular. Otherwise, the roller shoe 9 corresponds to Fig. 4 the in Fig. 3 and 5 shown first embodiment of the roller shoe. 9
  • the two axial grooves 17 prevent as simple and inexpensive constructive feature a relative movement of the roller 10 relative to the roller shoe 9 in the direction of the drive shaft 2, thereby clamping the roller 10 can be prevented in the roller shoe 9, because between the two mounting aids 15 and the roller 10 constructively a large Distance and a big game exists.
  • possibly occurring deposits or deposits on the mounting aid 15 as part of the sliding bearing 13 does not lead to a clamping of the roller 10, because constructively between the roller 10 and the mounting aid 15, a sufficiently large distance or a sufficiently large game exists, for example between 0.2 and 2 mm at a contact of the roller 10 with the operating contact surface fourteenth

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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)
  • Transmission Devices (AREA)
EP13700229.1A 2012-01-31 2013-01-15 Hochdruckpumpe Active EP2809943B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE201210201302 DE102012201302A1 (de) 2012-01-31 2012-01-31 Hochdruckpumpe
PCT/EP2013/050629 WO2013113544A1 (de) 2012-01-31 2013-01-15 Hochdruckpumpe

Publications (2)

Publication Number Publication Date
EP2809943A1 EP2809943A1 (de) 2014-12-10
EP2809943B1 true EP2809943B1 (de) 2017-12-20

Family

ID=47557166

Family Applications (1)

Application Number Title Priority Date Filing Date
EP13700229.1A Active EP2809943B1 (de) 2012-01-31 2013-01-15 Hochdruckpumpe

Country Status (4)

Country Link
EP (1) EP2809943B1 (zh)
CN (1) CN104081038B (zh)
DE (1) DE102012201302A1 (zh)
WO (1) WO2013113544A1 (zh)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102013218260A1 (de) 2013-09-12 2015-03-12 Continental Automotive Gmbh Rollenstößel
GB2577677B (en) * 2018-09-21 2021-06-23 Delphi Tech Ip Ltd High pressure pump shoe
GB2593934B (en) * 2020-04-10 2022-08-03 Delphi Tech Ip Ltd Drive assembly for a fuel pump

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102009028378A1 (de) * 2009-08-10 2011-02-17 Robert Bosch Gmbh Hochdruckpumpe
DE102009029297A1 (de) * 2009-09-09 2011-03-10 Robert Bosch Gmbh Kolbenpumpe mit kavitationsfreiem Rollenschuh/Laufrollen-Verband
DE102011086703A1 (de) * 2011-11-21 2013-05-23 Robert Bosch Gmbh Hochdruckpumpe

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10115168C1 (de) * 2001-03-27 2002-08-22 Orange Gmbh Kraftstoff-Hochdruckpumpe, insbesondere für Einspritzsysteme von Brennkraftmaschinen
CN2576989Y (zh) * 2002-10-22 2003-10-01 陈振鹏 柴油机用喷油泵
DE10355027A1 (de) * 2003-11-25 2005-06-23 Robert Bosch Gmbh Hochdruckpumpe, insbesondere für eine Kraftstoffeinspritzeinrichtung einer Brennkraftmaschine
DE10356262A1 (de) 2003-12-03 2005-06-30 Robert Bosch Gmbh Radialkolbenpumpe, insbesondere für Kraftstoffeinspritzsysteme
DE102004023541A1 (de) * 2004-05-13 2005-12-01 Robert Bosch Gmbh Hochdruckpumpe 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
DE102010031359A1 (de) * 2010-07-15 2012-01-19 Robert Bosch Gmbh Hochdruckgeschmiertes hydrostatisches Gleitlager einer Hochdruckpumpe
DE102010042025A1 (de) * 2010-10-06 2012-04-12 Robert Bosch Gmbh Lagerelement mit darin drehbar gelagerter Rolle, insbesondere im Antrieb eines Pumpenkolbens einer Kraftstoffhochdruckpumpe

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102009028378A1 (de) * 2009-08-10 2011-02-17 Robert Bosch Gmbh Hochdruckpumpe
DE102009029297A1 (de) * 2009-09-09 2011-03-10 Robert Bosch Gmbh Kolbenpumpe mit kavitationsfreiem Rollenschuh/Laufrollen-Verband
DE102011086703A1 (de) * 2011-11-21 2013-05-23 Robert Bosch Gmbh Hochdruckpumpe

Also Published As

Publication number Publication date
EP2809943A1 (de) 2014-12-10
CN104081038A (zh) 2014-10-01
WO2013113544A1 (de) 2013-08-08
DE102012201302A1 (de) 2013-08-01
CN104081038B (zh) 2017-04-12

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