EP0696339B1 - Injecteur de carburant pour moteurs a combustion interne - Google Patents

Injecteur de carburant pour moteurs a combustion interne Download PDF

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Publication number
EP0696339B1
EP0696339B1 EP95900657A EP95900657A EP0696339B1 EP 0696339 B1 EP0696339 B1 EP 0696339B1 EP 95900657 A EP95900657 A EP 95900657A EP 95900657 A EP95900657 A EP 95900657A EP 0696339 B1 EP0696339 B1 EP 0696339B1
Authority
EP
European Patent Office
Prior art keywords
pressure
valve needle
pressure element
fuel injection
shoulder
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
EP95900657A
Other languages
German (de)
English (en)
Other versions
EP0696339A1 (fr
Inventor
Wilhelm Christ
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 EP0696339A1 publication Critical patent/EP0696339A1/fr
Application granted granted Critical
Publication of EP0696339B1 publication Critical patent/EP0696339B1/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
    • 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
    • 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

Definitions

  • the invention is based on a fuel injector according to the genus of claim 1.
  • injection nozzle of this type known from EP 0 568 845 A1 that flows from the guide play of the valve needle in the Leakage oil escaping through the breakthrough of the nozzle body Washer in the spring chamber in the nozzle holder that over a connecting piece with a leakage oil return line connected is. It happens in the area of the washer thereby the axial guide play between the Pressure intermediate link and the axial play between the Push pin of the first closing spring and the latter surrounding pressure ring of the second closing spring.
  • the invention is therefore based on the object further develop known fuel injection nozzles in such a way that an undamped return movement of the Valve needle for quick valve closing of the fuel injector is guaranteed.
  • the fuel injector with the distinctive Features of the invention has the advantage that a quick Closing the valve needle after the injection phase is guaranteed so that the emission behavior of the Internal combustion engine meets a high standard.
  • the proposed solution is inexpensive and reliable.
  • Figure 1 shows a fuel injector opening in two pressure stages in longitudinal section
  • Figures 2 and 3 a detail in Area of the pressure booster of the fuel injector according to Figure 1 in the positions "forward stroke” and “Total stroke”
  • Figure 4 is a pressure intermediate member in plan view
  • Figures 5 and 6 and Figures 7 and 8 alternative forms of training the pressure link in Cross section and top view.
  • the fuel injection nozzle has a nozzle holder 10 that with a union nut 13 via an intermediate washer 14 a nozzle body 15 is clamped.
  • the nozzle body 15 has a spray opening 18 and one of these upstream Valve seat 17 with which one is displaceable in the nozzle body 15 mounted valve needle 16 cooperates.
  • the pilot hole for the valve needle 16, as usual, is closed at one point a pressure chamber 19 expanded, in the area of which the valve needle 16 has a pressure shoulder 21 and the one Channel 22 with a nozzle 23 on the nozzle holder 10 for Connecting a fuel delivery line is connected.
  • the two are Closing springs 11, 12 radially in one another in a stepped Chamber 25 arranged in the nozzle holder 10; however, they can as known per se, also arranged axially one behind the other be.
  • the inner, first closing spring 11 is supported on the one hand via a disk 26 at the base 27 of the chamber 25 and on the other hand on a pressure pin 28, which with a Pin 29 the first closing spring 11 and with its jacket the second closing spring 12 leads.
  • the outer, second Closing spring 12 is supported on the one hand via a disk 31 on a shoulder 32 of the chamber 25 and on the other hand a pressure ring 33 surrounding the pressure pin 28 on one from the intermediate plate 14 formed shoulder 34.
  • the pressure bolt 28 presses with its end face 36, which has just been formed, continuously onto a pressure intermediate member 40, which in turn is supported on an end pin 37 of the valve needle 16.
  • This intermediate pressure member 40 is essentially in the form of a disk with two plane-parallel end faces 41, 42. It is guided with its circumference in an extension 46 of an opening 45 in the intermediate disk 14 near the chamber 25 of the nozzle holder 10 so as to be axially displaceable with play.
  • the diameter of the extension 46 and that of the pressure intermediate member 40 are larger than the inner diameter of the pressure ring 33, so that the edge region of the pressure intermediate member 40 is in axial alignment with the inner ring region of the pressure ring 33.
  • the thickness of the intermediate member 40 is dimensioned such that its upper end face 41 in the closed position of the valve needle 16 lies by the dimension h v under the shoulder 34 of the intermediate disk 14 or the end face 35 of the pressure ring 33 supported on the latter (FIG. 1).
  • the forward stroke h v of the valve needle 16 can be easily adjusted by selecting an intermediate member 40 with the appropriate thickness.
  • the pressure intermediate member 40 comes into contact with the pressure ring 33 after passing through the preliminary stroke distance, after which both closing springs 11 and 12 engage the valve needle 16 Act as a pressure stage ( Figure 2).
  • the total stroke h g of the valve needle 16 is, as is known, limited by the annular shoulder 38 of the valve needle 16 formed at the transition to the end pin 37 and the lower end face of the intermediate disk 14 (FIG. 3).
  • the channels 50 in the intermediate pressure member 40 are at Embodiment according to Figures 1 to 4 thereby formed that on the circumference of a cylindrical disc three edge sections 51 are evenly distributed, so that the circumference consists of three radially recessed Areas with rectilinear boundary surface 52 and from three Guide sections with an arcuate boundary surface 53 put together.
  • edge portions 51 not covered areas of the game gap 54 between the Pressure ring 33 and the pressure pin 28 is a permanent Connection between the low pressure side of the valve needle 16 and the pressure-relieved chamber 25.
  • FIGS. 7 and 8 are in Circumference of the cylindrical pressure intermediate member 40 diametrically two incisions 55 arranged, the game gap 54th partially between the pressure pin 28 and the pressure ring 33 cover.
  • the Channels 50 can also, as shown in FIGS. 7 and 8, through openings in the form of bores 58 in the cylindrical Pressure intermediate member 40 be formed, the Longitudinal axis essentially with the clearance 54 is aligned.
  • channels 50 in the pressure intermediate member 40 can such can also be arranged in the pressure ring 33.
  • Other Shapes of channels in the pressure ring 33 are possible.
  • bridging channels can also be in the shoulder 34 of the intermediate plate 14 may be arranged through which the guide play of the pressure intermediate member 40 is flowing Leakage oil in the gap between the inner wall of the chamber 25 and the outer circumference of the pressure ring 33 can flow off. It is also possible to use both such bridging channels in the intermediate pressure member 40 and in the pressure ring 33 and also in the shoulder 34 of the intermediate member 14 to arrange.

Landscapes

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

Claims (3)

  1. Injecteur de carburant pour la préinjection et l'injection principale dans des moteurs à combustion interne comprenant :
    un corps d'injecteur (15) dans lequel coulisse une aiguille d'injecteur (16) et ce corps est serré avec interposition d'une rondelle intermédiaire (14) dans un porte-injecteur (10) dans lequel est formée une chambre à ressort (25), déchargée en pression, reliée à une conduite de retour de carburant, pour recevoir deux ressorts obturateurs (11, 12) coaxiaux, parmi lesquels le premier ressort (11) agit en permanence sur l'aiguille (16) par un goujon de pression (28) central et le second ressort obturateur (12) pousse contre une bague de pression (33) entourant le goujon de pression (28) et reçu en position de fermeture de l'aiguille d'injecteur (16) sur un épaulement (34) formé au niveau de la rondelle intermédiaire (14) et
    sur lequel vient s'appuyer après avoir parcouru la course d'avance, un élément intermédiaire de pression (40), guidé à sa périphérie, coulissant axialement avec l'aiguille d'injecteur dans un passage (45) de la rondelle intermédiaire (14), cet élément délimitant une chambre basse pression de la chambre à ressort (25), cette chambre basse pression, formée par le passage le passage (45) dans la rondelle intermédiaire (14), étant ouvert vers le corps d'injecteur(15) et vers l'aiguille d'injecteur,
    caractérisé en ce que
    dans l'élément intermédiaire de pression (40) et/ou dans la bague de pression (33) et/ou dans l'épaulement (34) de la rondelle intermédiaire (14), il y a au moins un canal (50) interrompant la position axiale de la bague de pression (33) contre l'épaulement (34) de l'élément intermédiaire (14) et/ou de l'élément intermédiaire de pression (40), ce canal étant formé par une cavité continue axialement sur l'élément intermédiaire de pression (40).
  2. Injecteur de carburant selon la revendication 1,
    caractérisé en ce que
    le canal (50) correspond à un enlèvement radial (51, 55) à la périphérie de l'élément de pression.
  3. Injecteur de carburant selon la revendication 1,
    caractérisé en ce que
    le canal (50) est un passage traversant l'élément intermédiaire de pression (40).
EP95900657A 1993-12-01 1994-11-24 Injecteur de carburant pour moteurs a combustion interne Expired - Lifetime EP0696339B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE4340874 1993-12-01
DE4340874A DE4340874C2 (de) 1993-12-01 1993-12-01 Kraftstoff-Einspritzdüse für Brennkraftmaschinen
PCT/DE1994/001386 WO1995015435A1 (fr) 1993-12-01 1994-11-24 Injecteur de carburant pour moteurs a combustion interne

Publications (2)

Publication Number Publication Date
EP0696339A1 EP0696339A1 (fr) 1996-02-14
EP0696339B1 true EP0696339B1 (fr) 1998-09-30

Family

ID=6503867

Family Applications (1)

Application Number Title Priority Date Filing Date
EP95900657A Expired - Lifetime EP0696339B1 (fr) 1993-12-01 1994-11-24 Injecteur de carburant pour moteurs a combustion interne

Country Status (8)

Country Link
US (1) US5632447A (fr)
EP (1) EP0696339B1 (fr)
JP (1) JPH08506641A (fr)
BR (1) BR9406076A (fr)
CZ (1) CZ285169B6 (fr)
DE (2) DE4340874C2 (fr)
RU (1) RU2121596C1 (fr)
WO (1) WO1995015435A1 (fr)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10017657A1 (de) * 2000-04-08 2001-10-11 Bosch Gmbh Robert Kraftstoffeinspritzventil für Brennkraftmaschinen
AT511075B1 (de) * 2011-05-26 2012-09-15 Avl List Gmbh Zweistoffbrennkraftmaschine
EP2857670B1 (fr) 2013-10-04 2018-12-12 Continental Automotive GmbH Injecteur à carburant
DE102014220877B3 (de) 2014-10-15 2015-12-03 Continental Automotive Gmbh Kraftstoffeinspritzventil

Family Cites Families (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE866574C (de) * 1944-07-02 1953-02-12 Bosch Gmbh Robert Lochduese fuer Brennkraftmaschinen mit Selbstzuendung
DE3106470A1 (de) * 1980-03-01 1982-02-18 Diesel Kiki Co. Ltd., Tokyo Kraftstoffeinspritzventil
DE3610658A1 (de) * 1985-11-21 1987-05-27 Bosch Gmbh Robert Kraftstoff-einspritzduese fuer brennkraftmaschinen
US4684067A (en) * 1986-03-21 1987-08-04 General Motors Corporation Two-stage, hydraulic-assisted fuel injection nozzle
JP2523759B2 (ja) * 1987-02-04 1996-08-14 フエスト − アルピネ オウトモチブ ゲゼルシャフト ミットベシュレンクテル ハフツンク 燃料噴射ノズル
GB8809268D0 (en) * 1988-04-20 1988-05-25 Lucas Ind Plc Fuel injection nozzle
DE3831695A1 (de) * 1988-09-17 1990-03-22 Hoechst Ag Elaiophylinderivate, verfahren zu ihrer herstellung ihre verwendung als arzneimittel und sie enthaltende arzneimittel
JPH081160B2 (ja) * 1988-09-19 1996-01-10 株式会社ゼクセル 燃料噴射弁
DE3928912A1 (de) * 1988-09-29 1990-04-05 Avl Verbrennungskraft Messtech Kraftstoffeinspritzduese fuer brennkraftmaschinen
GB9012288D0 (en) * 1990-06-01 1990-07-18 Lucas Ind Plc Fuel injection pump
GB9109066D0 (en) * 1991-04-26 1991-06-12 Lucas Ind Plc Fuel injection nozzle
DE9205975U1 (de) * 1992-05-02 1993-09-09 Robert Bosch Gmbh, 70469 Stuttgart Kraftstoffeinspritzdüse für Brennkraftmaschinen

Also Published As

Publication number Publication date
JPH08506641A (ja) 1996-07-16
DE4340874C2 (de) 1996-10-24
EP0696339A1 (fr) 1996-02-14
CZ285169B6 (cs) 1999-05-12
RU2121596C1 (ru) 1998-11-10
WO1995015435A1 (fr) 1995-06-08
CZ192995A3 (en) 1996-05-15
DE59407014D1 (de) 1998-11-05
DE4340874A1 (de) 1995-06-08
US5632447A (en) 1997-05-27
BR9406076A (pt) 1996-01-16

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