EP1682771B1 - Soupape de pompe a injection de carburant - Google Patents

Soupape de pompe a injection de carburant Download PDF

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Publication number
EP1682771B1
EP1682771B1 EP04786716A EP04786716A EP1682771B1 EP 1682771 B1 EP1682771 B1 EP 1682771B1 EP 04786716 A EP04786716 A EP 04786716A EP 04786716 A EP04786716 A EP 04786716A EP 1682771 B1 EP1682771 B1 EP 1682771B1
Authority
EP
European Patent Office
Prior art keywords
valve
cross
hollow groove
fuel
valve member
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.)
Expired - Lifetime
Application number
EP04786716A
Other languages
German (de)
English (en)
Other versions
EP1682771A1 (fr
Inventor
Stefan Schuerg
Wolfgang Stoecklein
Holger Rapp
Violaine Chassagnoux
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 EP1682771A1 publication Critical patent/EP1682771A1/fr
Application granted granted Critical
Publication of EP1682771B1 publication Critical patent/EP1682771B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • F02M59/20—Varying fuel delivery in quantity or timing
    • F02M59/36—Varying fuel delivery in quantity or timing by variably-timed valves controlling fuel passages to pumping elements or overflow passages
    • 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
    • F02M59/20—Varying fuel delivery in quantity or timing
    • F02M59/36—Varying fuel delivery in quantity or timing by variably-timed valves controlling fuel passages to pumping elements or overflow passages
    • F02M59/366—Valves being actuated electrically
    • 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
    • F02M59/466—Electrically operated valves, e.g. using electromagnetic or piezoelectric operating means
    • 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
    • F02M63/0012—Valves
    • F02M63/007—Details not provided for in, or of interest apart from, the apparatus of the groups F02M63/0014 - F02M63/0059
    • F02M63/0077—Valve seat details
    • 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
    • F02M63/0012—Valves
    • F02M63/007—Details not provided for in, or of interest apart from, the apparatus of the groups F02M63/0014 - F02M63/0059
    • F02M63/0078—Valve member details, e.g. special shape, hollow or fuel passages in the valve member
    • 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
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/04—Fuel-injection apparatus having means for avoiding effect of cavitation, e.g. erosion

Definitions

  • the invention relates to a valve for a fuel injection system of an internal combustion engine having the features specified in the preamble of claim 1, in particular for an injector of a common rail injection system.
  • Common rail injection systems have a plurality of injectors, which are supplied with fuel under the control of an electronic engine control by a high-pressure pump from a designated as common rail central high-pressure accumulator and inject the fuel via a valve in the combustion chambers of the cylinders of the internal combustion engine.
  • a valve is among others from the DE 199 40 296 A1 Known by the applicant and is used depending on the valve position to connect a high-pressure region of an injector of the injection system with a low pressure region or to separate from this, when fuel is injected through the valve into the combustion chamber of a cylinder or the supply of fuel to be interrupted.
  • a valve of the aforementioned type in which a circumferential groove arranged in the flow direction directly behind a sealing surface of the valve member is delimited together with a circumferential cross-sectional thickening of the valve member and with the valve housing an annular space. Between the groove and the cross-sectional thickening, the valve member has a circumferential edge against which contiguous outer peripheral surface portions of the groove and cross-sectional thickening meet at an angle of 270 °, with a peripheral surface portion adjacent the edge on the side of the groove at an angle of 90 degrees is aligned with the central axis of the valve member.
  • cavitation damage could be prevented with good success, because the fuel flow behind the valve seat is not simply deflected in the axial direction. Instead, as it flows through the groove, it receives a velocity component in a direction pointing away from the central axis of the valve member so that, after exiting the groove, it impinges on an opposite region of an inner wall of an outlet bore of the valve housing. On impact, part of the fuel flow is directed along the inner wall back toward the valve gap, leaving immediately behind the opposite wall portion of the inner wall forms a vortex.
  • a hollow groove is understood to mean a concave annular groove in the circumference of the valve member, while cross-sectional thickening means an adjacent part of the valve member in the direction of flow whose diameter is greater than the diameter in the region of the annular groove.
  • a particularly good vortex formation in the enlarged annular space behind the valve gap is achieved in a preferred embodiment of the invention in that between the groove and the cross-sectional thickening an undercut circumferential trailing edge is arranged on the both sides of this edge adjacent outer peripheral surface portions of the groove and the cross-sectional enlargement under a blunt Angle meet.
  • While the outer peripheral surface portion adjacent to the edge on the side of the cross-sectional thickening is preferably aligned substantially parallel to a central axis of the valve member is opposite to the flow direction at an angle between 20 and 80 degrees, preferably between 30 and 60 degrees, inclined to the central axis of the valve member, so that the two peripheral surface portions at an angle between 200 and 260 degrees, preferably between 190 and 240 degrees.
  • a particularly simple and cost-effective production of the spoiler lip is in accordance with a further preferred embodiment of the invention possible in that one abrades the outer peripheral surface at least in the region of the valve seat opposite sealing surface and the groove to the final diameter during the finishing of the valve member, but not in the Area of cross-sectional thickening, so that the material remaining there automatically leads to the formation of the spoiler edge.
  • the cross-section of the valve member tapers in the flow direction behind the cross-sectional thickening, but this need not necessarily be the case.
  • the concave groove expediently has a radius of curvature which is preferably at least 0.2 mm and is expedient over the entire width of the groove uniformly large.
  • sondem one of the groove substantially opposite inner wall portion of the outflow to install in this section a step or slope which helps to redirect part of the fuel flow in the direction of the valve gap.
  • valve 2 shown only partially in the drawing is part of an injector of a common rail injection system of an internal combustion engine, which serves to fuel from a common rail inject central high-pressure accumulator into the combustion chambers of the cylinders of the internal combustion engine.
  • the valve 2 consists essentially of a valve housing 4, in which a rotationally symmetrical valve pin 6 (see. FIG. 1 ) is used axially movable.
  • the valve pin 6 has a conical, tapered in the flow direction sealing surface 8, which bears sealingly against a complementary conical valve seat 10 of the housing 4 when the valve 2 is closed. How best in the FIGS. 2 to 4 shown limited at the valve 2 open the sealing surface 8 together with the valve seat 10 surrounding the valve pin 6 valve gap 12 in the form of an annular flow channel through which the fuel to be injected flows from the high pressure side 14 of the valve 2 to the low pressure side 16.
  • the valve pin 6 further comprises a circumferentially disposed in the direction of flow immediately behind the sealing surface 8 in its outer circumference circumferential groove 18, that is a concave recess in longitudinal section or groove over the axial width of the diameter of the valve pin 6 is smaller than before or behind, where the valve pin 6 is provided with an adjacent to the groove 18 cross-sectional thickening 20.
  • the groove 18 serves to deflect at least a portion of the fuel flow discharged substantially behind the valve seat 10 in the axial direction such that it has a velocity component directed away from a central axis 22 of the valve pin 6 and, after its exit from the groove 18, against an opposite region the inner wall 24 of an outflow bore 26 of the valve housing 4 rebounds. How best in FIG. 2 . 3 and 4 represented by arrows, while dividing the fuel flow into two partial streams, of which the larger is directed after the impact along the inner wall 24 of the discharge hole 26 in the downstream part of the bore 26, while the smaller against the flow direction to the valve gap 12 directed back out becomes.
  • valve housing 4 in the area immediately behind the valve seat 10th protects against erosion caused by cavitation, so that the valve seat 10 remains undamaged even over a long period of operation.
  • the angle of inclination of the fuel flow emerging from the groove 18 with respect to the central axis 22 of the valve pin 6 must not be too small, since otherwise the entire fuel is directed directly into the outflow bore 26. Therefore, on the one hand, the groove 18 should not be formed too flat, but with respect to the subsequent cross-sectional thickening a certain minimum depth T (FIG. FIG. 1 ), which at a diameter of the valve pin 6 in the middle of Sealing surface of 1.35 mm should preferably be greater than 0.04 mm. On the other hand, the groove 18 should not be rounded at the transition to the cross-sectional thickening, because thereby the inclination angle of the emerging from the groove 18 fuel flow with respect to the central axis 22 is also smaller.
  • a circumferential edge 34 is provided between the groove 18 and the cross-sectional thickening 20, at the adjoining outer peripheral surface portions 36, 38 of the groove 18 and the cross-sectional thickening 20 has a superficial angle ⁇ (FIG. FIG. 1 ), which should be at least 200 degrees and preferably between 220 degrees and 240 degrees. Unlike a rounded transition at such an edge 34, the flow of fuel from the peripheral surface of the valve pin 6 breaks off, but this has no cavitation due to the hardened surface of the valve pin 6 result.
  • the stall at the edge 34 causes the fuel to exit the fillet 18 at an angle of inclination to the central axis 22 that substantially corresponds to the angle of inclination ⁇ of the peripheral surface portion 36 adjacent the edge 34 within the fillet 18.
  • this angle of inclination is selected, more or less fuel is directed back in the direction of the valve gap 12 upon impact of the fuel flow on the opposite region of the inner wall 24 of the discharge bore 26.
  • this angle of inclination which is preferably between 20 and 60 degrees, therefore, the proportion of the returning fuel can be adjusted to such a value that on the one hand vortex formation avoids cavitation damage immediately behind the valve seat 10, on the other hand, the vortex formation the flow of fuel after its exit from the valve gap 12 is not affected.
  • the fuel flowing back along the inner wall 24 protects the latter from cavitation-related damage, which might otherwise be caused by a pressure drop in the fuel as it exits the valve gap 12 into the annulus 30, just past the valve gap 12.
  • FIG. 2 a valve pin 6, wherein the within the groove 18 adjacent to the edge 34 peripheral surface portion 36 is aligned at an inclination angle ⁇ of about 60 degrees to the central axis 22 of the valve pin 6, the fuel therefore bounces quite steeply on the inner wall 24 of the discharge bore 26 and thus relatively much fuel is directed back in the direction of the valve gap 28, show the Figures 3 and 4 two valve bolts 6, in which this inclination angle ⁇ is about 35 degrees or about 20 degrees, and therefore correspondingly less fuel is directed back toward the valve gap 28 to form a vortex 34.
  • the concave boundary of the groove 18 is circular in all embodiments, wherein the radius of curvature should not fall below 0.2 mm in order to allow cost-effective mass production of the valve pin 6.
  • the groove 18 preferably transitions seamlessly into the sealing surface 8, as shown in all exemplary embodiments.
  • the sharp tear-off edge 34 on the other side of the groove 18 can be inexpensively produced in a series production of the valve pin 6, that the valve pin 6 is ground at its final diameter on both sides of the cross-sectional thickening 20, but not in the region of the cross-sectional thickening 20, so that there existing in front of the abrasive finishing of the valve pin 6 existing diameter is maintained, which automatically leads to the formation of the tear-off edge 34 at the transition to the groove 18.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Electromagnetism (AREA)
  • Fuel-Injection Apparatus (AREA)

Claims (8)

  1. Soupape (2) pour un système d'injection de carburant, comprenant un siège de soupape (10) réalisé dans un boîtier de soupape (4) et un organe de soupape (6) déplaçable dans le boîtier de soupape (4), qui présente une surface d'étanchéité (8) s'appliquant hermétiquement contre le siège de soupape (10) lorsque la soupape (2) est fermée, laquelle surface d'étanchéité, lorsque la soupape (2) est ouverte, délimite avec le siège de soupape (10) une fente de soupape (12) parcourue par le carburant, l'organe de soupape (6) présentant une goulotte (18) périphérique disposée dans le sens de l'écoulement directement derrière la surface d'étanchéité (8), à laquelle goulotte (18) se raccorde un épaississement de section transversale périphérique (20) de l'organe de soupape (6), et une arête périphérique (34) étant disposée entre la goulotte (18) et l'épaississement de section transversale (20), au niveau de laquelle arête des portions de surface périphérique extérieures adjacentes (36, 38) de la goulotte (18) et de l'épaississement de section transversale (20) se rejoignent en formant un angle rentrant (β), caractérisée en ce que la portion de surface périphérique (36) adjacente à l'arête (34) du côté de la goulotte (18) est inclinée suivant un angle (α) compris entre 20 et 80 degrés par rapport à un axe médian (22) de l'organe de soupape (6).
  2. Soupape selon la revendication 1, caractérisée en ce que la portion de surface périphérique (36) adjacente à l'arête (34) du côté de la goulotte (18) est inclinée suivant un angle (α) compris entre 20 et 60 degrés par rapport à un axe médian (22) de l'organe de soupape (6).
  3. Soupape selon la revendication 1 ou 2, caractérisée en ce que la portion de surface périphérique extérieure (38) adjacente à l'arête (34) du côté de l'épaississement de section transversale (20) est orientée essentiellement parallèlement à un axe médian (22) de l'organe de soupape (6).
  4. Soupape selon l'une quelconque des revendications précédentes, caractérisée en ce qu'un rayon de courbure de la goulotte (18) est supérieur à 0,2 mm.
  5. Soupape selon l'une quelconque des revendications précédentes, caractérisée en ce que la goulotte (18) et la surface d'étanchéité (8) se prolongent l'une dans l'autre sans transition.
  6. Soupape selon l'une quelconque des revendications précédentes, caractérisée en ce que la section transversale de l'organe de soupape (6) se rétrécit dans le sens de l'écoulement derrière l'épaississement de section transversale (20).
  7. Soupape selon l'une quelconque des revendications précédentes, caractérisée en ce qu'une surface périphérique extérieure de l'organe de soupape (6) est poncée au moins dans la région de la surface d'étanchéité (8) et de la goulotte (18), mais pas dans la région de l'épaississement de section transversale (20).
  8. Pompe d'injection de carburant, caractérisée par une soupape selon l'une quelconque des revendications précédentes.
EP04786716A 2003-11-05 2004-09-06 Soupape de pompe a injection de carburant Expired - Lifetime EP1682771B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10351680A DE10351680A1 (de) 2003-11-05 2003-11-05 Ventil für eine Kraftstoffeinspritzpumpe
PCT/DE2004/001994 WO2005045228A1 (fr) 2003-11-05 2004-09-06 Soupape de pompe a injection de carburant

Publications (2)

Publication Number Publication Date
EP1682771A1 EP1682771A1 (fr) 2006-07-26
EP1682771B1 true EP1682771B1 (fr) 2012-11-14

Family

ID=34559352

Family Applications (1)

Application Number Title Priority Date Filing Date
EP04786716A Expired - Lifetime EP1682771B1 (fr) 2003-11-05 2004-09-06 Soupape de pompe a injection de carburant

Country Status (7)

Country Link
US (1) US20070119991A1 (fr)
EP (1) EP1682771B1 (fr)
JP (1) JP2006526729A (fr)
KR (1) KR101100973B1 (fr)
CN (1) CN1875184B (fr)
DE (1) DE10351680A1 (fr)
WO (1) WO2005045228A1 (fr)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4720724B2 (ja) * 2006-11-13 2011-07-13 トヨタ自動車株式会社 燃料噴射弁
DE102010043360A1 (de) * 2010-11-04 2012-05-10 Robert Bosch Gmbh Kraftstoffinjektor
DE102011004993A1 (de) * 2011-03-02 2012-09-06 Robert Bosch Gmbh Ventileinrichtung zum Schalten oder Zumessen eines Fluids
DE102012218667B4 (de) * 2012-10-12 2014-06-05 Continental Automotive Gmbh Magnetventil
JP6224415B2 (ja) * 2013-10-29 2017-11-01 日立オートモティブシステムズ株式会社 高圧燃料供給ポンプ
JP6781661B2 (ja) * 2017-04-20 2020-11-04 ボッシュ株式会社 燃料噴射装置

Family Cites Families (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1952816A (en) * 1931-04-04 1934-03-27 Bendix Res Corp Fuel injector
US4503884A (en) * 1982-06-22 1985-03-12 Spils Richard W Angle globe valve
ATE59434T1 (de) * 1984-09-14 1991-01-15 Bosch Gmbh Robert Elektrisch gesteuerte kraftstoffeinspritzpumpe fuer brennkraftmaschinen.
US4941508A (en) * 1989-12-28 1990-07-17 Dana Corporation Force balanced hydraulic spool valve
DE19619523A1 (de) 1996-05-15 1997-11-20 Bosch Gmbh Robert Kraftstoffeinspritzventil für Hochdruckeinspritzung
DE19940296A1 (de) 1999-08-25 2001-03-01 Bosch Gmbh Robert Ventil
DE10000501A1 (de) * 2000-01-08 2001-07-19 Bosch Gmbh Robert Kraftstoffeinspritzventil für Brennkraftmaschinen
EP1118765A3 (fr) * 2000-01-19 2003-11-19 CRT Common Rail Technologies AG Injecteur de combustible pour moteur à combustion interne
DE10008554A1 (de) 2000-02-24 2001-08-30 Bosch Gmbh Robert Kraftstoffeinspritzventil für Brennkraftmaschinen
DE10031264A1 (de) * 2000-06-27 2002-01-17 Bosch Gmbh Robert Kraftstoffeinspritzventil für Brennkraftmaschinen
JP2002039031A (ja) * 2000-07-10 2002-02-06 Robert Bosch Gmbh 後置された圧力制御エレメントを備えた、燃料を噴射するためのインジェクタ
DE10134526B4 (de) * 2001-07-16 2007-10-11 Robert Bosch Gmbh Schaltventil für Kraftstoffeinspritzsystem

Also Published As

Publication number Publication date
CN1875184A (zh) 2006-12-06
EP1682771A1 (fr) 2006-07-26
KR20060108655A (ko) 2006-10-18
WO2005045228A1 (fr) 2005-05-19
CN1875184B (zh) 2011-04-06
DE10351680A1 (de) 2005-06-09
US20070119991A1 (en) 2007-05-31
KR101100973B1 (ko) 2011-12-29
JP2006526729A (ja) 2006-11-24

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