EP1759115B1 - Hochdruckpumpe für eine kraftstoffeinspritzeinrichtung einer brennkraftmaschine - Google Patents

Hochdruckpumpe für eine kraftstoffeinspritzeinrichtung einer brennkraftmaschine Download PDF

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Publication number
EP1759115B1
EP1759115B1 EP05726501A EP05726501A EP1759115B1 EP 1759115 B1 EP1759115 B1 EP 1759115B1 EP 05726501 A EP05726501 A EP 05726501A EP 05726501 A EP05726501 A EP 05726501A EP 1759115 B1 EP1759115 B1 EP 1759115B1
Authority
EP
European Patent Office
Prior art keywords
cone angle
valve member
pump
sealing surface
valve
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
EP05726501A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP1759115A1 (de
Inventor
Achim Koehler
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 EP1759115A1 publication Critical patent/EP1759115A1/de
Application granted granted Critical
Publication of EP1759115B1 publication Critical patent/EP1759115B1/de
Not-in-force 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
    • F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
    • F02M59/46—Valves
    • F02M59/462—Delivery valves
    • 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
    • F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
    • F02M59/46—Valves
    • 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
    • F02M63/02—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively
    • F02M63/0225—Fuel-injection apparatus having a common rail feeding several injectors ; Means for varying pressure in common rails; Pumps feeding common rails

Definitions

  • the invention is based on a high-pressure pump for a fuel injection device of an internal combustion engine according to the preamble of claim 1.
  • Such a high-pressure pump is through the DE 198 60 672 A1 known.
  • This high-pressure pump has at least one pump element with a pump piston driven in a stroke movement, which delimits a pump working space.
  • fuel is drawn in from a fuel feed via an inlet valve, and during the delivery stroke of the pump piston, fuel is expelled from the pump working space into a high-pressure region via an outlet valve.
  • the inlet valve has a valve member with a sealing surface with which it cooperates with a valve seat to control the connection of the pump working space to the fuel inlet.
  • the sealing surface and the seat surface of the valve seat are each frusto-conical, but have different cone angles.
  • the valve member is acted upon by the pressure prevailing in the pump working chamber in the closing direction and by the pressure prevailing in the fuel inlet in the opening direction. It results in the known high-pressure pump line contact between the sealing surface of the valve member and the seat surface of the valve seat, which during the operating time of the high pressure pump due to wear the Position of the line contact changes, resulting in a change of the opening pressure of the intake valve, since it changes the size of the pressure applied to the fuel inlet surface of the valve member. As a result, the filling of the pump working space is deteriorated with fuel, so that the delivery characteristic of the high-pressure pump is impaired.
  • a high-pressure pump which comprises an inlet valve, the valve member having a frusto-conical portion and a cylindrical portion, whereby a protruding edge is formed, which rests against a sealing surface of a valve seat with a frusto-conical portion of the valve member different cone angle.
  • the edge is formed at an acute angle and there is also a change in the opening pressure of the inlet valve and thus an impairment of the delivery characteristics of the high-pressure pump during the operating life of the high pressure pump due to wear.
  • the high-pressure pump according to the invention with the features of claim 1 has the advantage that the opening pressure of the inlet valve changes only slightly over the service life of the high-pressure pump, so that the delivery characteristics of the high-pressure pump remains at least substantially the same over the operating period.
  • FIG. 1 a high-pressure pump for a fuel injection device of an internal combustion engine
  • FIG. 2 an inlet valve of the high pressure pump in an enlarged view in a longitudinal section according to a first embodiment
  • FIG. 3 the inlet valve according to a second embodiment.
  • a high pressure pump 10 is shown for a fuel injector of an internal combustion engine, which is preferably a self-igniting internal combustion engine.
  • fuel is conveyed under high pressure in a memory 12, is taken from the fuel for injection to the internal combustion engine.
  • the high-pressure pump 10 is supplied by a feed pump 14 fuel.
  • the high-pressure pump 10 has at least one pump element 16 which has a pump piston 20 driven at least indirectly by a drive shaft 18 of the high-pressure pump 10 in a lifting movement.
  • the pump piston 20 is tightly guided in a cylinder bore 22 extending at least approximately radially to the drive shaft 18 and delimits a pump working space 24 in the outer end region of the cylinder bore 22 facing away from the drive shaft 18.
  • the drive shaft 18 has a cam or a shaft section 26 eccentric to its axis of rotation 19 , via which during the rotational movement of the drive shaft 18, the lifting movement of the pump piston 20 is effected.
  • the pump working chamber 24 can be connected to the inlet pump 30, which opens into the pump working chamber 24 and is designed as a check valve, with a fuel feed from the feed pump 14.
  • the pump working chamber 24 can also be connected to the accumulator 12 via a discharge valve 32, which opens out of the pump working chamber 24 and is designed as a check valve, with a fuel outlet.
  • the pump piston 20 in the cylinder bore 22 moves radially inwards, so that the volume of the pump working chamber 24 is increased.
  • the inlet valve 30 is inserted, for example, into a bore 34 of a housing part 36 of the high-pressure pump 10 which adjoins the cylinder bore 22 radially outward.
  • the bore 34 is formed larger in diameter relative to the cylinder bore 22.
  • the housing part 36 may for example be a cylinder head, which is connected to another housing part in which the drive shaft 18 is mounted, or a housing part, in which the drive shaft 18 is mounted.
  • In the bore 34 opens near the cylinder bore 22 facing end portion, for example, approximately radially to the axis of the bore 34, a fuel inlet channel 38 which is connected to the feed pump 14.
  • the inlet valve 30 has a valve housing 40 in which a diameter-stepped bore 42 is present.
  • the bore 42 has a small-diameter portion 43, a section 44 which adjoins the section 43 to the pump working chamber 24 with a larger diameter and a section 45 adjoining the section 44 to the pump working chamber 24.
  • the inlet valve 30 has a piston-shaped valve member 46, which is displaceably guided in the bore section 43 with a cylindrical shaft 47.
  • the valve member 46 also has an adjoining the shaft 47, enlarged in diameter relative to the shaft 47 head 48, wherein at the transition from the head 48 to the shaft 47, a sealing surface 49,50 on the valve member 46 is arranged.
  • the sealing surface has two successively arranged in the direction of the longitudinal axis 51 of the valve member 44 sections 49,50, each of which may be at least approximately conical, however have different cone angles.
  • the pump chamber 24 facing away from the first portion 49 of the sealing surface has a cone angle ⁇ 1 and adjoining the pump working chamber 24 second portion 50 of the sealing surface has a cone angle ⁇ 2, which is smaller than the cone angle ⁇ 1.
  • the head 48 of the valve member 46 faces the pump working chamber 24.
  • the shaft 47 of the valve member 46 protrudes with its end facing away from the head 48 out of the bore portion 43 and at this engages a prestressed closing spring 52.
  • At least one inlet channel 53 is introduced, which opens into the bore portion 44.
  • a plurality, for example, three over the circumference of the valve housing 40 evenly distributed feed channels 53 are provided.
  • the bore portion 45 is formed such that its diameter widens away from the bore portion 44 toward the pump working space 24.
  • the lateral surface of the bore portion 45 forms a seat surface of a valve seat, is at least approximately conical and has a constant cone angle ⁇ 3.
  • the cone angle ⁇ 3 is greater than the cone angle ⁇ 2 but smaller than the cone angle ⁇ 1.
  • the two sections 49,50 of the sealing surface of the valve member 46 include an obtuse angle between them.
  • the difference ⁇ between the cone angle ⁇ 1 of the portion 49 of the sealing surface on the valve member 46 and the cone angle ⁇ 3 of the seat surface 45 is preferably between about 0.1 ° and 20 °.
  • the difference ⁇ between the cone angle ⁇ 2 of Section 50 of the sealing surface on the valve member 46 and the cone angle ⁇ 3 of the seat surface 45 is preferably between about 0.1 ° and 90 °.
  • the angle ⁇ between the second portion 50 of the sealing surface of the valve member 46 and the longitudinal axis 51 of the valve member 46 is greater than 0 ° and less than 90 °.
  • the arranged within the edge 54 of the first portion 49 of the sealing surface of the valve member 46 is acted upon by the pressure prevailing in the fuel inlet 38,53 pressure, by which a force in the opening direction is generated on the valve member 46.
  • the pump chamber 24 facing the end face of the head 48 of the valve member 46 is acted upon by the pressure prevailing in the pump working chamber 24, by which a force in the closing direction is generated on the valve member 46.
  • a force in the closing direction is generated on the valve member 46 by the closing spring 52.
  • the edge 54 is pressed slightly flat as a result of wear, whereby the pressure applied to the pressure prevailing in the fuel inlet surface of the first portion 49 of the sealing surface of the valve member 46 is slightly reduced, so that the opening pressure, which is the pressure difference between the in the fuel inlet prevailing pressure and the pressure prevailing in the pump working chamber 24 at which the inlet valve 30 opens slightly increases.
  • the inlet valve 30 opens when the force prevailing in the fuel inlet 38,51 pressure acting on the portion 49 of the sealing surface of the valve member 46 in the opening direction on the valve member 46 generated force is greater than the sum of the through in the pump working chamber 24 prevailing pressure on the valve member 46 generated force and the force generated by the closing spring 52 is.
  • the pump piston 20 is generated by this in the pump working chamber 24, an increased pressure through which the inlet valve 30 is closed.
  • the intake valve 30 is shown according to a second embodiment.
  • the inlet valve 30 in this case has the valve housing 40, in which the bore 42 is formed with the sections 43,44 and 45.
  • the bore section 45 forming the seating surface of the valve seat does not have a constant cone angle, but has a first section 45a with a cone angle ⁇ 4 and a second section 45b with a cone angle ⁇ 5.
  • the cone angle ⁇ 5 of the second portion 45b is greater than the cone angle ⁇ 4 of the first portion 45a.
  • the valve member 46 has the shaft 47 guided in the section 43 of the bore 42 and the pump working chamber 24 facing head 48, wherein at the transition from the shaft 47 to the head 48, the conical sealing surface 49 is arranged, which has a constant cone angle ⁇ 6.
  • the cone angle ⁇ 4 of the first portion 45a of the seat is smaller than the cone angle ⁇ 6 of the sealing surface 49 of the valve member 46 and the cone angle ⁇ 5 of the second portion 45b of the seat is greater than the cone angle ⁇ 6 of the sealing surface 49 of the valve member 46.
  • the difference ⁇ between the cone angle ⁇ 4 of the first portion 45a of the seat and the cone angle ⁇ 6 of the sealing surface 49 of the valve member 46 is preferably between about 0.1 ° and 90 °.
  • the difference ⁇ between the cone angle ⁇ 5 of the second portion 45b of the seat surface and the cone angle ⁇ 6 of the sealing surface 49 of the valve member 46 is preferably between about 0.1 ° and 20 °.
  • the angle ⁇ between the second portion 45b of the seating surface and the longitudinal axis 51 of the valve member 46 is greater than 0 ° and less than 90 °.
  • a protruding Edge 54 formed at which the valve member 46 comes into abutment with its sealing surface 49 in its closed position.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Details Of Reciprocating Pumps (AREA)
EP05726501A 2004-06-16 2005-04-18 Hochdruckpumpe für eine kraftstoffeinspritzeinrichtung einer brennkraftmaschine Not-in-force EP1759115B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102004028998A DE102004028998A1 (de) 2004-06-16 2004-06-16 Hochdruckpumpe für eine Kraftstoffeinspritzeinrichtung einer Brennkraftmaschine
PCT/EP2005/051692 WO2005124146A1 (de) 2004-06-16 2005-04-18 Hochdruckpumpe für eine kraftstoffeinspritzeinrichtung einer brennkraftmaschine

Publications (2)

Publication Number Publication Date
EP1759115A1 EP1759115A1 (de) 2007-03-07
EP1759115B1 true EP1759115B1 (de) 2009-11-04

Family

ID=34967363

Family Applications (1)

Application Number Title Priority Date Filing Date
EP05726501A Not-in-force EP1759115B1 (de) 2004-06-16 2005-04-18 Hochdruckpumpe für eine kraftstoffeinspritzeinrichtung einer brennkraftmaschine

Country Status (8)

Country Link
US (1) US20070221162A1 (es)
EP (1) EP1759115B1 (es)
JP (1) JP2006523806A (es)
KR (1) KR20070020074A (es)
CN (1) CN100473822C (es)
DE (2) DE102004028998A1 (es)
ES (1) ES2333344T3 (es)
WO (1) WO2005124146A1 (es)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4163706B2 (ja) * 2005-09-07 2008-10-08 三菱電機株式会社 燃料噴射装置
DE102007044357A1 (de) * 2007-06-21 2008-12-24 Robert Bosch Gmbh Steuerventil für ein Kraftstoffeinspritzventil
DE102008043217A1 (de) * 2008-10-28 2010-04-29 Robert Bosch Gmbh Kraftstoff-Hochdruckpumpe für eine Brennkraftmaschine

Family Cites Families (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US596607A (en) * 1898-01-04 Sample-exhibiting book
US5419587A (en) * 1993-07-14 1995-05-30 Wallace Computer Services, Inc. Personalized envelope assembly for printed publication and method
US5566979A (en) * 1994-12-05 1996-10-22 Ong; Bon S. Document holder insert
US5661895A (en) * 1995-07-25 1997-09-02 Outboard Marine Corporatin Method of controlling the magnetic gap length and the initial stroke length of a pressure surge fuel pump
JP2807214B2 (ja) * 1996-07-30 1998-10-08 忠男 宇野 パスポートにおける偽造防止構造とその製法
US6135503A (en) * 1997-11-21 2000-10-24 Giesecke & Devrient Gmbh Identification document
EP0999360A1 (de) * 1998-11-05 2000-05-10 Siemens Aktiengesellschaft Steuerventil für Dosiervorrichtung für Fluid
GB2352780A (en) * 1999-03-23 2001-02-07 Nachi Fujikoshi Corp High pressure plunger pump
JP3685317B2 (ja) * 2000-02-18 2005-08-17 株式会社デンソー 燃料噴射ポンプ
DE10139054C1 (de) * 2001-08-08 2003-01-30 Bosch Gmbh Robert Verfahren, Computerprogramm, Steuer- und/oder Regelgerät sowie Kraftstoffsystem für eine Brennkraftmaschine, insbesondere mit Direkteinspritzung
DE10233452B4 (de) * 2002-07-24 2006-08-17 Ovd Kinegram Ag Individualisiertes Sicherheitsdokument
DE10242591A1 (de) * 2002-09-13 2004-03-25 Robert Bosch Gmbh Kraftstoffeinspritzanlage für Brennkraftmaschinen
DE102004008840A1 (de) * 2004-02-20 2005-09-01 Bundesdruckerei Gmbh Verfahren zur Herstellung eines buchartigen Wertdokuments sowie ein buchartiges Wertdokument
US7040981B2 (en) * 2004-03-11 2006-05-09 Canadian Bank Note Company, Limited Laminate sheet for security booklets and method for making same
US7296782B2 (en) * 2004-10-01 2007-11-20 Halkey-Roberts Corporation Dome check valve
DE102004055495A1 (de) * 2004-11-17 2006-05-24 Bundesdruckerei Gmbh Personaldokument in Heftform

Also Published As

Publication number Publication date
WO2005124146A1 (de) 2005-12-29
EP1759115A1 (de) 2007-03-07
CN100473822C (zh) 2009-04-01
US20070221162A1 (en) 2007-09-27
CN1969124A (zh) 2007-05-23
JP2006523806A (ja) 2006-10-19
DE502005008446D1 (de) 2009-12-17
KR20070020074A (ko) 2007-02-16
ES2333344T3 (es) 2010-02-19
DE102004028998A1 (de) 2006-01-05

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