EP0220207A1 - Injecteur de carburant pour moteurs a combustion interne. - Google Patents

Injecteur de carburant pour moteurs a combustion interne.

Info

Publication number
EP0220207A1
EP0220207A1 EP86901817A EP86901817A EP0220207A1 EP 0220207 A1 EP0220207 A1 EP 0220207A1 EP 86901817 A EP86901817 A EP 86901817A EP 86901817 A EP86901817 A EP 86901817A EP 0220207 A1 EP0220207 A1 EP 0220207A1
Authority
EP
European Patent Office
Prior art keywords
piston
cap
valve needle
fuel
injection nozzle
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
Application number
EP86901817A
Other languages
German (de)
English (en)
Other versions
EP0220207B1 (fr
Inventor
Kurt Seifert
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 EP0220207A1 publication Critical patent/EP0220207A1/fr
Application granted granted Critical
Publication of EP0220207B1 publication Critical patent/EP0220207B1/fr
Expired legal-status Critical Current

Links

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
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/04—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series
    • F02M61/08—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series the valves opening in direction of fuel flow
    • 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
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/20—Closing valves mechanically, e.g. arrangements of springs or weights or permanent magnets; Damping of valve lift
    • F02M61/205—Means specially adapted for varying the spring tension or assisting the spring force to close the injection-valve, e.g. with damping of valve lift

Definitions

  • the invention relates to a fuel injection nozzle according to the preamble of the main claim.
  • Injection nozzles of this type have the advantage that the opening stroke of the valve needle is damped.
  • the pressure piece slidably mounted in the base of the cap transmits the fuel pressure directly to the piston and via this to the valve needle during a preliminary stroke. It is thereby achieved that at the beginning of each injection process, a pre-jet is sprayed with a sufficiently large amount of fuel.
  • the pressure piece has the same diameter as the piston connected to the valve needle.
  • This version can be Process the hole in the cap slightly, but the pre-stroke of the valve needle runs practically completely undamped. In some cases, this can have an undesirable effect on the damping effect of the subsequent partial stroke or, in certain areas of the operating map, can lead to an unfavorable ratio of the pre-injection quantity to the main injection quantity.
  • the arrangement according to the invention with the characterizing features of the main claim has the advantage that the preliminary stroke of the valve needle is partially damped at least in the lower speed and load range.
  • the preliminary stroke of the valve needle is partially damped at least in the lower speed and load range.
  • FIG. 1 shows the first embodiment in longitudinal section and FIG. 2 shows a partial longitudinal section through the second embodiment.
  • FIGS. 3, 4 and 5 show functional diagrams of the injection nozzles according to FIGS. 1 and 2.
  • the injection nozzle according to FIG. 1 has a nozzle body 10 which is clamped to a nozzle holder 14 by a union nut 12.
  • a sleeve 16 Arranged between the nozzle body 10 and the nozzle holder 14 is a sleeve 16 which has an inwardly directed collar 18 which divides a chamber 20 from a chamber 22.
  • a valve seat 24 is formed in the nozzle body 10 and a valve needle 26 is displaceably mounted, the sealing cone 27 of which is pressed against the valve seat 24 by a closing spring 28.
  • the closing spring 28 is supported on the nozzle body 10 and engages via a flange part 30 on a support disk 32, which in turn is supported on a shoulder 34 of the valve needle 26.
  • the nozzle holder 14 contains an inlet bore 36 which opens into the chamber 20, which is connected to the chamber 22 via bores 38, 39 in the collar 18. From this, a bore 4o leads in the nozzle body 10 into an annular space 42, which is formed between the central bore wall of the nozzle body 10 and the circumference of a section 44 of the valve needle 26 which is weakened in diameter and immediately bar up to the valve seat 24. Between the flange part 30 and the nozzle body 10 there is a distance h g in the closed position shown, which corresponds to the total stroke of the valve needle 26. The valve needle 26 is displaced outward in the opening direction by the fuel pressure against the force of the closing spring 28 until the flange part 30 strikes the nozzle body 10. When the valve closes, the closing spring 28 returns the valve needle 26 inward to the closed position shown.
  • a piston 46 which passes through the collar 18 and projects into the chamber 20, is integrally formed on the valve needle 26 above the shoulder 34.
  • the diameter of the piston 46 corresponds to the guide diameter of the valve needle 26.
  • a cap 48 with a predetermined radial clearance is fitted on the piston 46, which has a flange 50 and is pressed against the collar 18 by a return spring 52.
  • the return spring 52 is supported on an annular shoulder 54 of the nozzle holder 14, which is formed at the transition from the chamber 20 to an enlarged section 56 of the inlet bore 36.
  • the cap 48 has a bottom 58, in which a pressure piece 60 is slidably mounted, which has a smaller diameter than the piston 46.
  • a fuel-filled damping space 62 is formed in the cap 48 between the end face of the piston 46 and the base 58 and is connected to the chambers 20, 22 and therefore to the flow path of the fuel via the bearing clearances of the piston 46 and the pressure piece 60.
  • the pressure piece 60 projects into the damping space 62 at the bottom and has an annular collar 64 at the top, on which a return spring 66 engages, which is supported on an annular shoulder 68 of the nozzle holder 14. In the starting position shown, the pressure piece 60 bears against the piston 46, its collar 64 being a distance h v from the upper end face of the cap 46.
  • the distance h v corresponds to a preliminary stroke of the valve needle, at which the valve needle is to experience a weaker damping in a certain area of the operating characteristic map than with the remaining stroke.
  • the parts assume the position shown in FIG. 1, in which the damping space 62 has its smallest volume.
  • the increasing fuel pressure now acts in full via the pressure piece 60 and throttled on the annular surface of the piston 46 not covered by the pressure piece 60.
  • the valve needle 26 is thereby displaced in the opening direction until after the advance stroke h v the pressure piece 60 comes to rest on the cap 48.
  • this process is represented by the partial distance a. Because the damping space 62 increases in this process, the movement of the valve needle 26 takes place more slowly than in the known arrangement in which the pressure piece 60 has the same diameter as the piston 46 and the damping space 60 does not enlarge during the preliminary stroke.
  • the closing spring 28 returns the valve needle 26 upwards into the closed position, whereby the cap 48 together with the pressure piece 60 also lifts and then through its return spring 52 in accordance with the throttling in the bearing gaps of the piston 46 and pressure piece 60 in the illustrated Starting position is reduced.
  • the valve needle 26 can advantageously only perform the preliminary stroke h v , as is shown in the diagram in FIG. 4.
  • the injection nozzle according to FIG. 2 differs from that according to FIG. 1 in that a cap 70 fitted onto the piston 46 is supported on the collar 18 fixed to the housing by means of a prestressed support spring 72, the annular shoulder 54 of the nozzle holder 1 4 catching the cap 70 upwards .
  • the pressure piece 60 acts, as in the above-described embodiment, directly on the piston 46 during a preliminary stroke h v and then comes to bear against the cap 70.
  • the pressure difference between the damping space 62 and the chamber 20 increases because the cap 70 initially cannot follow the movement of the valve needle 26 due to the action of the prestressed support spring 72.
  • the support spring 72 is designed so that its bias is not overcome in idle and in the medium speed range, so that the damping is effective over the entire needle stroke. In the upper speed and load range, the pressure difference between the chamber 20 and the damping chamber 62 increases to such an extent that the pretension of the support spring 72 is overcome.

Landscapes

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

Abstract

Un injecteur de carburant pour moteurs à combustion interne possédant un pointeau de soupape (26) s'ouvrant vers l'extérieur relié à un piston (46) qui délimite un espace d'amortissement (62) rempli de carburant, qui, pendant le cycle d'ouverture n'est relié à la trajectoire d'écoulement du carburant que par un passage d'étranglement. L'espace d'amortissement (62) est formé d'un capuchon (48) monté sur le piston (46). A la base (58) du capuchon (48) se trouve un élément de transmission de pression (60) commandé par le carburant qui presse directement sur le piston (46) pendant la course préliminaire (hv), puis vient reposer sur le capuchon (48). L'élément de transmission de pression (60) possède un diamètre plus petit que le piston (46), de sorte que la course préliminaire (hv) du pointeau (26) de la soupape est plus ou moins amortie au moins dans la faible gamme de t/m et de charge.
EP86901817A 1985-05-02 1986-03-26 Injecteur de carburant pour moteurs a combustion interne Expired EP0220207B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3515723 1985-05-02
DE19853515723 DE3515723A1 (de) 1985-05-02 1985-05-02 Kraftstoff-einspritzduese fuer brennkraftmaschinen

Publications (2)

Publication Number Publication Date
EP0220207A1 true EP0220207A1 (fr) 1987-05-06
EP0220207B1 EP0220207B1 (fr) 1988-06-08

Family

ID=6269597

Family Applications (1)

Application Number Title Priority Date Filing Date
EP86901817A Expired EP0220207B1 (fr) 1985-05-02 1986-03-26 Injecteur de carburant pour moteurs a combustion interne

Country Status (5)

Country Link
US (1) US4730785A (fr)
EP (1) EP0220207B1 (fr)
JP (1) JPS62502699A (fr)
DE (2) DE3515723A1 (fr)
WO (1) WO1986006441A1 (fr)

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DK65592D0 (da) * 1992-05-19 1992-05-19 Dysekompagniet I S V Svend End Forstoeverdyse
GB9301793D0 (en) * 1993-01-29 1993-03-17 Lucas Ind Plc Fuel injection nozzle
US5836521A (en) * 1995-03-09 1998-11-17 Dysekompagniet I/S Valve device with impact member and solenoid for atomizing a liquid
DE19546033A1 (de) * 1995-12-09 1997-06-12 Bosch Gmbh Robert Kraftstoffeinspritzventil für Brennkraftmaschinen
GB9802061D0 (en) * 1998-01-31 1998-03-25 Lucas Ind Plc Spring assembly
DE19940558C2 (de) * 1998-09-16 2003-11-20 Siemens Ag Vorrichtung zum Verzögern des Auslenkens der Düsennadel eines Kraftstoffeinspritzventils
US6042028A (en) * 1999-02-18 2000-03-28 General Motors Corporation Direct injection fuel injector spray nozzle and method

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2451462A1 (de) * 1974-10-30 1976-05-06 Maschf Augsburg Nuernberg Ag Einspritzventil fuer hubkolbenbrennkraftmaschinen
DE2825982A1 (de) * 1978-06-14 1980-01-03 Bosch Gmbh Robert Kraftstoffeinspritzduese fuer brennkraftmaschinen
DE3120060A1 (de) * 1981-05-20 1982-12-09 Robert Bosch Gmbh, 7000 Stuttgart Kraftstoff-einspritzduese fuer brennkraftmaschinen
DE3220398A1 (de) * 1982-01-26 1983-07-28 Robert Bosch Gmbh, 7000 Stuttgart Kraftstoff-einspritzduese fuer brennkraftmaschinen
DE3246916A1 (de) * 1982-12-18 1984-06-20 Robert Bosch Gmbh, 7000 Stuttgart Kraftstoff-einspritzduese fuer brennkraftmaschinen
DE3307671A1 (de) * 1983-03-04 1984-09-06 Robert Bosch Gmbh, 7000 Stuttgart Kraftstoff-einspritzduese fuer brennkraftmaschinen

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO8606441A1 *

Also Published As

Publication number Publication date
DE3660290D1 (en) 1988-07-14
EP0220207B1 (fr) 1988-06-08
US4730785A (en) 1988-03-15
JPS62502699A (ja) 1987-10-15
DE3515723A1 (de) 1986-11-06
WO1986006441A1 (fr) 1986-11-06

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