EP0282480A1 - Injecteur de carburant pour moteurs a combustion interne. - Google Patents

Injecteur de carburant pour moteurs a combustion interne.

Info

Publication number
EP0282480A1
EP0282480A1 EP86906291A EP86906291A EP0282480A1 EP 0282480 A1 EP0282480 A1 EP 0282480A1 EP 86906291 A EP86906291 A EP 86906291A EP 86906291 A EP86906291 A EP 86906291A EP 0282480 A1 EP0282480 A1 EP 0282480A1
Authority
EP
European Patent Office
Prior art keywords
valve needle
stroke
shoulder
nozzle body
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
EP86906291A
Other languages
German (de)
English (en)
Other versions
EP0282480B1 (fr
Inventor
Max Straubel
Ewald Eblen
Paul Fussner
Gunter Kapolke
Edgar Schneider
Klaus Wolf
Werner Wagner
Karl Hofmann
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 EP0282480A1 publication Critical patent/EP0282480A1/fr
Application granted granted Critical
Publication of EP0282480B1 publication Critical patent/EP0282480B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • F02M45/00—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship
    • F02M45/02—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts
    • F02M45/04—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts with a small initial part, e.g. initial part for partial load and initial and main part for full load
    • F02M45/08—Injectors peculiar thereto
    • F02M45/083—Having two or more closing springs acting on injection-valve
    • 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
    • F02M2200/80—Fuel injection apparatus manufacture, repair or assembly
    • F02M2200/8015—Provisions for assembly of fuel injection apparatus in a certain orientation, e.g. markings, notches or specially shaped sleeves other than a clip

Definitions

  • the invention relates to a fuel injection nozzle according to the preamble of the main claim.
  • the shoulders limiting the forward stroke of the valve needle are formed on the pressure pin of the first closing spring and on the pressure piece of the second closing spring.
  • the tolerance range of the advance stroke is determined by manufacturing tolerances on the nozzle body and the valve needle, as well as on the pressure pin and the intermediate washer, so that it is necessary to adjust the advance stroke by adjusting the pressure pin. Due to the large number of individual manufacturing tolerances and deformation during assembly, the pre-stroke tolerance can, however, only be achieved in a relatively large range, e.g. B. 0.05 mm, which is too large for some applications. In the case of very small forward strokes, as are required for direct-injection engines, the tolerance range of the forward stroke must be significantly smaller than the fourth specified above, for example. Advantages of the invention
  • the arrangement according to the invention with the characterizing features of the main claim has the advantage that the tolerance range of the advance stroke is determined solely by manufacturing tolerances on the nozzle body and the nozzle needle.
  • the forward stroke can therefore be measured precisely and adjusted by grinding the valve needle.
  • dimensional tolerances or changes in other parts that occur during operation or during assembly no longer affect the size of the forward stroke.
  • the total stroke of the valve needle can be easily adjusted if the intermediate disk is formed from two individual disks, of which the one lying against the nozzle body has a larger diameter 3 hole than the other, and if the shoulder formed on the intermediate disk to limit the total stroke of the valve needle that not covered by a single pane
  • the total stroke is determined by the wall thickness of the individual disc determined, so that only a single disc of appropriate wall thickness must be provided to obtain the desired total stroke.
  • the intermediate bushing can expediently be guided on a pressure socket of the valve needle, which also results in guidance of the pressure bolt of the first closing spring.
  • it can also be advantageous to design the valve needle without a pressure plug and to guide the intermediate bushing in the intermediate disk. With this arrangement, the end face of the valve needle can be machined particularly easily and, furthermore, pressure pin breaks on the valve needle are avoided.
  • the injection nozzle according to FIG. 1 has a nozzle body it, which, together with an intermediate disk 12, is clamped to a holding body 10 by a union nut 14.
  • a valve needle 1S is slidably mounted in the nozzle body 10 and cooperates with a valve seat in the nozzle body 10 which is turned inward and which is arranged in front of a plurality of spray openings 20.
  • the leading The bore of the valve needle 18 is, as usual, expanded at one point to a pressure chamber, in the area of which the valve needle 18 has a pressure shoulder and which is connected via a channel 22 to a connecting piece 24 on the holding body 16 for connecting a fuel delivery line.
  • the fuel engaging the pressure shoulder of the valve needle 18 pushes the valve needle 18 upward against the graduated force curve of a closing spring arrangement described below, the fuel being sprayed out through the injection openings 20 in a pre-injection phase and a main injection phase.
  • a first chamber 26 is formed for receiving a first closing spring 28, which is supported by a washer 30 on the bottom of the chamber 26 and acts continuously on the valve needle 18 via a pressure piece 32 and a pressure pin 34.
  • the chamber 26 merges at a housing shoulder 36 into a second chamber 38, in which a second closing spring 40 is arranged, which surrounds the pressure bolt 34.
  • the closing spring 40 is supported on the housing shoulder 36 by means of disks 42, 44 and engages on a pressure piece 46 which is slidably mounted on the pressure pin 34.
  • the pressure piece 46 is supported via an intermediate bushing 48, which is designed as a separate part, on an area 50 (FIG. 2) of the upper end face 52 of the nozzle body 10 which is not covered by the intermediate disk 12.
  • the chambers 26 and 38 are connected via a channel 56 to a connection nipple 58 for a leak oil line.
  • the valve needle 18 guides one during the injection process
  • Valve needle 18 together with intermediate bush 48 moved in the opening direction until it has completed its entire stroke. This is limited and determined by annular shoulders 64, 66 on the intermediate bush 48 and the intermediate disk 12. On the annular shoulder 6h, a section 68 of the intermediate bush 48 with a larger diameter merges into a section 70 with a smaller diameter, which is guided in the intermediate disk 12 and in turn leads the central pressure pin 34.
  • the preliminary stroke h v can easily be measured. This is only the valve needle
  • the desired amount of the preliminary stroke h v can also be produced very precisely. No changes in the preliminary stroke h v occur during assembly and operation of the injection nozzle.
  • a pressure pin 72 is formed on the valve needle 18 ', on which the intermediate bush 48 is guided and via ien the force of the first closing spring 28 on the valve needle 18 'is transmitted.
  • the intermediate disc 12 ' is formed from two individual discs 74, 76, of which the lower one has a larger inner diameter than the upper one.
  • the shoulder for limiting the total stroke of the valve needle 18 ' is formed by the area 66' of the upper individual disk 76 which is not covered by the lower individual disk 74.
  • the overall stroke can also be easily adjusted to the desired value by appropriate selection of the wall thickness of the individual disk 74 become.

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

Injecteur avec une configuration spécifique d'injection. Un premier ressort de fermeture (28) agit constamment sur l'aiguille (18) de soupape par l'intermédiaire d'un axe de pression central (34), et après exécution d'une course préliminaire (hv), un deuxième ressort (40) de fermeture agit au moyen d'un élément de pression (46). Celui-ci est supporté pendant une course préliminaire (hv) au moyen d'un manchon intermédiaire (48) sur le corps (10) d'injecteur. La course préliminaire (hv) est limitée par des épaulements (60, 62) sur l'aiguille de soupape (18) et par le manchon intermédiaire (48). Par contre, la course totale est limitée par des épaulements (64, 66) sur le manchon intermédiaire (48) et le disque intermédiaire (12). De cette manière, la course préliminaire (hv) peut être réglée de façon très précise à une valeur choisie en usinant l'aiguille (18) de soupape et ne change pas lors du montage de l'injecteur.
EP86906291A 1985-11-21 1986-11-07 Injecteur de carburant pour moteurs a combustion interne Expired - Lifetime EP0282480B1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE3541131 1985-11-21
DE3541131 1985-11-21
DE19863610658 DE3610658A1 (de) 1985-11-21 1986-03-29 Kraftstoff-einspritzduese fuer brennkraftmaschinen
DE3610658 1986-03-29

Publications (2)

Publication Number Publication Date
EP0282480A1 true EP0282480A1 (fr) 1988-09-21
EP0282480B1 EP0282480B1 (fr) 1990-02-07

Family

ID=25838027

Family Applications (1)

Application Number Title Priority Date Filing Date
EP86906291A Expired - Lifetime EP0282480B1 (fr) 1985-11-21 1986-11-07 Injecteur de carburant pour moteurs a combustion interne

Country Status (5)

Country Link
US (1) US4768719A (fr)
EP (1) EP0282480B1 (fr)
JP (1) JP2545523B2 (fr)
DE (2) DE3610658A1 (fr)
WO (1) WO1987003339A1 (fr)

Families Citing this family (31)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0288207A3 (fr) * 1987-04-24 1989-08-09 LUCAS INDUSTRIES public limited company Buse d'injection de combustible
GB8711188D0 (en) * 1987-05-12 1987-06-17 Lucas Ind Plc Fuel injection nozzles
JPH081160B2 (ja) * 1988-09-19 1996-01-10 株式会社ゼクセル 燃料噴射弁
DE3839038A1 (de) * 1988-11-18 1990-05-23 Bosch Gmbh Robert Kraftstoff-einspritzduese fuer brennkraftmaschinen
DE3839637A1 (de) * 1988-11-24 1990-06-07 Bosch Gmbh Robert Kraftstoff-einspritzduese fuer brennkraftmaschinen
DE3842335A1 (de) * 1988-12-16 1990-06-21 Bosch Gmbh Robert Kraftstoff-einspritzduese fuer brennkraftmaschinen
DE3913062A1 (de) * 1989-04-21 1990-10-25 Daimler Benz Ag Kraftstoffeinspritzvorrichtung fuer eine luftverdichtende brennkraftmaschine, insbesondere solche als direkteinspritzer
DE4027493A1 (de) * 1989-09-19 1991-03-28 Avl Verbrennungskraft Messtech Einspritzduese fuer eine brennkraftmaschine
DE4005774A1 (de) * 1990-02-23 1991-08-29 Bosch Gmbh Robert Kraftstoff-einspritzduese fuer brennkraftmaschinen
FR2684416B1 (fr) * 1990-01-17 1994-06-03 Daimler Benz Ag Soupape d'injection de carburant pour des moteurs a combustion interne a injection directe et a compression d'air.
DE4001103C2 (de) * 1990-01-17 1994-04-28 Daimler Benz Ag Kraftstoffeinspritzventil für luftverdichtende direkteinspritzende Brennkraftmaschinen
GB9012288D0 (en) * 1990-06-01 1990-07-18 Lucas Ind Plc Fuel injection pump
DE4101235C1 (fr) * 1991-01-17 1992-06-04 Robert Bosch Gmbh, 7000 Stuttgart, De
US5211340A (en) * 1991-08-27 1993-05-18 Zexel Corporation Fuel injector
US5205492A (en) * 1991-12-16 1993-04-27 Gregory Khinchuk Fuel injection valve
AT408253B (de) * 1992-03-02 2001-10-25 Avl Verbrennungskraft Messtech Einspritzdüse für eine brennkraftmaschine
EP0824190B1 (fr) * 1992-12-23 2002-03-06 Ganser-Hydromag Ag Soupape d'injection de combustible
DE4340874C2 (de) * 1993-12-01 1996-10-24 Bosch Gmbh Robert Kraftstoff-Einspritzdüse für Brennkraftmaschinen
GB9416785D0 (en) * 1994-08-19 1994-10-12 Lucas Ind Plc Fuel injection nozzle
DE4434892A1 (de) * 1994-09-29 1996-04-11 Siemens Ag Einspritzventil
DE4440182C2 (de) * 1994-11-10 2003-09-18 Bosch Gmbh Robert Kraftstoffeinspritzventil für Brennkraftmaschinen
DE19608608A1 (de) * 1996-03-06 1997-09-11 Bosch Gmbh Robert Kraftstoffeinspritzventil für Brennkraftmaschinen
DE19638339B4 (de) * 1996-09-19 2008-10-02 Robert Bosch Gmbh Kraftstoffeinspritzventil für Brennkraftmaschinen
US5871155A (en) * 1997-06-10 1999-02-16 Caterpillar Inc. Hydraulically-actuated fuel injector with variable rate return spring
DE19907348A1 (de) * 1999-02-20 2000-08-24 Bosch Gmbh Robert Kraftstoffeinspritzventil
DE10126954A1 (de) * 2001-06-01 2002-12-12 Bosch Gmbh Robert Injektor zum Einspritzen von unter hohem Druck stehendem Kraftstoff
US7942214B2 (en) * 2006-11-16 2011-05-17 Schlumberger Technology Corporation Steerable drilling system
ATE551521T1 (de) * 2008-04-18 2012-04-15 Magneti Marelli Spa Kraftstoffeinspritzdüse mit direkter verschlussbetätigung für verbrennungsmotoren
DE102016213008A1 (de) 2016-07-15 2018-01-18 Bosch Limited Tellerfeder für einen Kraftstoffinjektor
CN107664081A (zh) * 2016-07-29 2018-02-06 博世有限公司 用于燃料喷射器的碟形弹簧
US10753493B2 (en) * 2018-03-29 2020-08-25 Hamilton Sunstrand Corporation Valve with segmented spring guide assembly

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH350835A (de) * 1956-11-16 1960-12-15 Friedmann & Maier Ag Einspritzdüse für Einspritzbrennkraftmaschinen
DE1284687B (de) * 1967-10-18 1968-12-05 Bosch Gmbh Robert Kraftstoffeinspritzventil fuer Vor- und Haupteinspritzung
DE2711350A1 (de) * 1977-03-16 1978-09-21 Bosch Gmbh Robert Kraftstoffeinspritzduese fuer brennkraftmaschinen
DE2711393A1 (de) * 1977-03-16 1978-09-21 Bosch Gmbh Robert Kraftstoffeinspritzduese
JPS56173757U (fr) * 1980-05-27 1981-12-22
DE3105686A1 (de) * 1981-02-17 1982-09-02 Robert Bosch Gmbh, 7000 Stuttgart "kraftstoffeinspritzduese"
GB2128252A (en) * 1982-10-14 1984-04-26 Lucas Ind Plc Fuel injection nozzle
US4566635A (en) * 1983-08-10 1986-01-28 Robert Bosch Gmbh Fuel injection nozzle for internal combustion engines
US4684067A (en) * 1986-03-21 1987-08-04 General Motors Corporation Two-stage, hydraulic-assisted fuel injection nozzle

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO8703339A1 *

Also Published As

Publication number Publication date
JPS63502767A (ja) 1988-10-13
US4768719A (en) 1988-09-06
DE3610658A1 (de) 1987-05-27
DE3668949D1 (de) 1990-03-15
JP2545523B2 (ja) 1996-10-23
EP0282480B1 (fr) 1990-02-07
WO1987003339A1 (fr) 1987-06-04

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