EP1759115A1 - Hochdruckpumpe für eine kraftstoffeinspritzeinrichtung einer brennkraftmaschine - Google Patents
Hochdruckpumpe für eine kraftstoffeinspritzeinrichtung einer brennkraftmaschineInfo
- Publication number
- EP1759115A1 EP1759115A1 EP05726501A EP05726501A EP1759115A1 EP 1759115 A1 EP1759115 A1 EP 1759115A1 EP 05726501 A EP05726501 A EP 05726501A EP 05726501 A EP05726501 A EP 05726501A EP 1759115 A1 EP1759115 A1 EP 1759115A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- cone angle
- valve member
- pump
- sealing surface
- section
- 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
Links
- 239000000446 fuel Substances 0.000 title claims abstract description 36
- 238000002485 combustion reaction Methods 0.000 title claims description 8
- 238000002347 injection Methods 0.000 title claims description 6
- 239000007924 injection Substances 0.000 title claims description 6
- 238000007789 sealing Methods 0.000 claims abstract description 35
- 230000007704 transition Effects 0.000 claims abstract description 6
- 230000001419 dependent effect Effects 0.000 description 1
- 238000011161 development Methods 0.000 description 1
- 230000018109 developmental process Effects 0.000 description 1
- 230000001771 impaired effect Effects 0.000 description 1
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
-
- 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
- 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 relates to 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 known from DE 198 60 672 AI.
- This high-pressure pump has at least one pump element with a pump piston which is driven in a lifting movement and delimits a pump working space.
- fuel is drawn in from a fuel inlet via an inlet valve, and during the delivery stroke of the pump piston, fuel is displaced from the pump work space into a high-pressure region via an outlet valve.
- the inlet valve has a valve member with a sealing surface with which it interacts with a valve seat for controlling the connection of the pump work space to the fuel inlet.
- the sealing surface and the seat surface of the valve seat are each frustoconical, but have different cone angles.
- the valve member is acted upon by the pressure prevailing in the pump work chamber in the closing direction and by the pressure prevailing in the fuel inlet in the opening direction.
- the high-pressure pump according to the invention with the features according to claim 1 has the advantage that the opening pressure of the inlet valve changes only slightly over the operating time of the high-pressure pump, so that the delivery characteristic of the high-pressure pump remains at least substantially the same over the operating time.
- FIG. 1 shows a high-pressure pump for a fuel injection device
- Figure 2 is an intake valve
- Figure 3 shows the inlet valve according to a second
- Description of the embodiments 1 shows a high-pressure pump 10 for a fuel injection device of an internal combustion engine, which is preferably a self-igniting internal combustion engine.
- the high-pressure pump 10 delivers fuel under high pressure into a reservoir 12, from which fuel is taken for injection at the internal combustion engine.
- the high-pressure pump 10 is supplied with fuel by a feed pump 14.
- the high-pressure pump 10 has at least one pump element 16 which has a pump piston 20 which is driven at least indirectly by a drive shaft 18 of the high-pressure pump 10 in a stroke movement.
- the pump piston 20 is tightly guided in a cylinder bore 22 that extends at least approximately radially to the drive shaft 18 and delimits a pump work chamber 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 that is eccentric to its axis of rotation 19 , via which the stroke movement of the pump piston 20 is effected during the rotary movement of the drive shaft 18.
- the pump work chamber 24 can be connected to a fuel inlet from the feed pump 14 via an inlet valve 30 which opens into the pump work chamber 24 and is designed as a check valve.
- the pump work chamber 24 can also be connected to a fuel outlet to the reservoir 12 via an outlet valve 32 that opens out of the pump work chamber 24 and is designed as a check valve.
- the pump piston 20 moves radially inward in the cylinder bore 22, so that the volume of the pump working space 24 is increased.
- the inlet valve 30 is opened because of the existing pressure difference, since the feed pump 14 generates a higher pressure than the pressure prevailing in the pump work chamber 24, so that fuel delivered by the feed pump 14 is sucked into the pump work chamber 24.
- the outlet valve 32 is at the suction stroke of the Pump piston 20 closed, since there is a higher pressure in the reservoir 12 than in the pump work space 24.
- the inlet valve 30 is described in more detail below with reference to FIG. 2, in which the inlet valve 30 is shown according to a first exemplary embodiment.
- the inlet valve 30 is inserted, for example, into a bore 34 of a housing part 36 of the high-pressure pump 10 that adjoins the cylinder bore 22 radially outward.
- the bore 34 is larger in diameter than the cylinder bore 22.
- the housing part 36 can be, for example, 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 also mounted.
- a fuel feed channel 38 which is connected to the feed pump 14, opens into the bore 34 near its end region facing the cylinder bore 22, for example approximately radially to the axis of the bore 34.
- the inlet valve 30 has a valve housing 40 in which there is a bore 42 with a graduated diameter.
- the bore 42 has a section 43 with a small diameter, a section 44 with a larger diameter adjoining the section 43 to the pump work chamber 24 and a section 45 adjoining the section 44 with the pump work chamber 24.
- the inlet valve 30 has a piston-shaped valve member 46, which is displaceably guided in the bore section 43 by a cylindrical shaft 47.
- the valve member 46 also has a head 48 adjoining the stem 47 and enlarged in diameter compared to the stem 47, a sealing surface 49, 50 being arranged on the valve member 46 at the transition from the head 48 to the stem 47.
- the sealing surface has two sections 49, 50 arranged one after the other in the direction of the longitudinal axis 51 of the valve member 44, each of which is, however, at least approximately conical have different cone angles.
- the first section 49 of the sealing surface facing away from the pump working chamber 24 has a cone angle ⁇ 1 and the second section 50 of the sealing surface adjoining the pump working chamber 24 has a cone angle ⁇ 2 which is smaller than the cone angle ⁇ l.
- the head 48 of the valve member 46 faces the pump work space 24.
- the end 47 of the valve member -46 protrudes from the bore section 43 with its end facing away from the head 48 and a prestressed closing spring 52 engages it.
- At least one inlet channel 53 is introduced in the valve housing 40 and opens into the bore section 44.
- several, for example three, are evenly distributed over the circumference of the valve housing 40
- Inlet channels 53 are provided.
- the bore section 45 is designed in such a way that its diameter widens away from the bore section 44 toward the pump working space 24.
- the lateral surface of the bore section 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 larger than the cone angle ⁇ 2 but smaller than the cone angle ⁇ l.
- Valve member 46 an edge 54 protruding toward the seat surface 45 is formed, with which the valve member 46 comes into contact with the seat surface 45 in its closed position and thereby the pump working chamber 24 is separated from the fuel inlet with the inlet channels 53.
- the two sections 49, 50 of the sealing surface of the valve member 46 form an obtuse angle between them.
- the difference ⁇ between the cone angle ⁇ 1 of the section 49 of the sealing surface on the valve member 46 and the cone angle ⁇ 3 of the seat surface 45 is preferably between approximately 0.1 ° and 20 °.
- the difference ⁇ between the cone angle ⁇ 2 of the Section 50 of the sealing surface on the valve member 46 and the cone angle ⁇ 3 of the seat surface 45 is preferably between approximately 0.1 ° and 90 °.
- the angle ⁇ between the second section 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 surface of the first section 49 of the sealing surface of the valve member 46 arranged within the edge 54 is acted upon by the pressure prevailing in the fuel inlet 38, 53, by which a force in the opening direction is generated on the valve member 46.
- the end face of the head 48 of the valve member 46 facing the pump work chamber 24 is acted upon by the pressure prevailing in the pump work chamber 24, by means of which a force is generated on the valve member 46 in the closing direction.
- the closing spring 52 generates a force in the closing direction on the valve member 46.
- the pressure exerted on the fuel inflow area of the first section 49 of the sealing surface of the valve member 46 is slightly reduced, so that the opening pressure, that is the pressure difference between the pressure prevailing in the fuel inflow and the pressure prevailing in the pump work chamber 24 at which the inlet valve 30 opens, increases slightly.
- the inlet valve 30 opens when the pressure generated in the fuel inlet 38, 51, which acts on the section 49 of the sealing surface of the valve member 46, is greater than the sum of the force generated by the valve member 46 in the opening direction pressure prevailing in the pump working chamber 24 on the valve member 46 and the force generated by the closing spring 52.
- the inlet valve 30 is shown according to a second embodiment.
- the inlet valve 30 has the valve housing 40 in which the bore 42 with the sections 43, 44 and 45 is formed.
- the bore section 45 forming the seat surface of the valve seat does not have a constant cone angle, but rather 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 section 45b is larger than the cone angle ⁇ 4 of the first section 45a.
- the valve member 46 has the shaft 47 guided in the section 43 of the bore 42 and the head 48 pointing to the pump work chamber 24, the conical sealing surface 49 having a constant cone angle ⁇ 6 being arranged at the transition from the shaft 47 to the head 48.
- the cone angle ⁇ 4 of the first ⁇ portion 45a of the seat surface 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 surface is larger than the cone angle of the sealing surface ⁇ 6 49 of the valve member 46.
- the difference ⁇ between the Cone angle ⁇ 4 of the first section 45a of the seat surface and the cone angle ⁇ 6 of the sealing surface 49 of the valve member 46 is preferably between approximately 0.1 ° and 90 °.
- the difference ⁇ between the cone angle ⁇ 5 of the second section 45b of the seat surface and the cone angle ⁇ 6 of the sealing surface 49 of the valve member 46 is preferably between approximately 0.1 ° and 20 °.
- the angle ⁇ between the second section 45b of the seat surface and the longitudinal axis 51 of the valve member 46 is greater than 0 ° and less than 90 °.
- a protruding one Edge 54 is formed, on which the valve member 46 comes into contact with its sealing surface 49 in its closed position.
Abstract
Description
Claims
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 true EP1759115A1 (de) | 2007-03-07 |
EP1759115B1 EP1759115B1 (de) | 2009-11-04 |
Family
ID=34967363
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP05726501A Expired - Fee Related EP1759115B1 (de) | 2004-06-16 | 2005-04-18 | Hochdruckpumpe für eine kraftstoffeinspritzeinrichtung einer brennkraftmaschine |
Country Status (8)
Country | Link |
---|---|
US (1) | US20070221162A1 (de) |
EP (1) | EP1759115B1 (de) |
JP (1) | JP2006523806A (de) |
KR (1) | KR20070020074A (de) |
CN (1) | CN100473822C (de) |
DE (2) | DE102004028998A1 (de) |
ES (1) | ES2333344T3 (de) |
WO (1) | WO2005124146A1 (de) |
Families Citing this family (3)
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)
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 |
-
2004
- 2004-06-16 DE DE102004028998A patent/DE102004028998A1/de not_active Withdrawn
-
2005
- 2005-04-18 ES ES05726501T patent/ES2333344T3/es active Active
- 2005-04-18 KR KR1020067026394A patent/KR20070020074A/ko not_active Application Discontinuation
- 2005-04-18 WO PCT/EP2005/051692 patent/WO2005124146A1/de active Application Filing
- 2005-04-18 US US11/597,326 patent/US20070221162A1/en not_active Abandoned
- 2005-04-18 DE DE502005008446T patent/DE502005008446D1/de active Active
- 2005-04-18 EP EP05726501A patent/EP1759115B1/de not_active Expired - Fee Related
- 2005-04-18 CN CNB2005800198098A patent/CN100473822C/zh not_active Expired - Fee Related
- 2005-04-18 JP JP2006520844A patent/JP2006523806A/ja active Pending
Non-Patent Citations (1)
Title |
---|
See references of WO2005124146A1 * |
Also Published As
Publication number | Publication date |
---|---|
DE502005008446D1 (de) | 2009-12-17 |
EP1759115B1 (de) | 2009-11-04 |
US20070221162A1 (en) | 2007-09-27 |
CN100473822C (zh) | 2009-04-01 |
CN1969124A (zh) | 2007-05-23 |
KR20070020074A (ko) | 2007-02-16 |
ES2333344T3 (es) | 2010-02-19 |
DE102004028998A1 (de) | 2006-01-05 |
JP2006523806A (ja) | 2006-10-19 |
WO2005124146A1 (de) | 2005-12-29 |
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