EP0809756A1 - Soupape d'injection de carburant pour moteurs a combustion interne - Google Patents

Soupape d'injection de carburant pour moteurs a combustion interne

Info

Publication number
EP0809756A1
EP0809756A1 EP96934344A EP96934344A EP0809756A1 EP 0809756 A1 EP0809756 A1 EP 0809756A1 EP 96934344 A EP96934344 A EP 96934344A EP 96934344 A EP96934344 A EP 96934344A EP 0809756 A1 EP0809756 A1 EP 0809756A1
Authority
EP
European Patent Office
Prior art keywords
valve
spring
fuel injection
internal combustion
injection valve
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
EP96934344A
Other languages
German (de)
English (en)
Other versions
EP0809756B1 (fr
Inventor
Karl Hofmann
Peter Kuegel
Ibrahim Oezyesilova
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 EP0809756A1 publication Critical patent/EP0809756A1/fr
Application granted granted Critical
Publication of EP0809756B1 publication Critical patent/EP0809756B1/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
    • 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
    • F02M61/168—Assembling; Disassembling; Manufacturing; Adjusting
    • 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

Definitions

  • the invention is based on a fuel injection valve for internal combustion engines according to the preamble of claim 1.
  • a valve member is guided axially displaceably in a valve body.
  • the valve member has one at one end on the combustion chamber side
  • Valve sealing surface with which it interacts for the purpose of controlling an injection cross section with a fixed valve seat on the valve body.
  • the valve member is acted upon at its other end remote from the combustion chamber by a valve spring, which the valve member abuts on
  • This valve spring is inserted into a spring chamber within the housing of the injection valve here in a holding body and is supported with its end facing away from the valve member on a stationary stop surface.
  • the valve spring is as
  • Coil spring formed the turns of a spring wire have a circular cross section.
  • the spring force of the valve spring determines the opening pressure at the injection valve, which is built up by the high fuel pressure acting on the valve member in the opening direction.
  • the performance or the spring force of the valve spring is therefore of great importance, this spring force being essentially dependent on the wire cross-sectional area at the windings. If the spring force is to be increased, it is customary with conventional round wire to increase the wire thickness, since its maximum area results from the given external and
  • the known fuel injection valve has the disadvantage that an increase in the wire thickness or an axial extension of the valve spring for one
  • valve spring which is designed as a helical spring, from stronger Spring wire is made with an enlarged basic cross-section on the windings and then ground on the outer diameter to such an extent that the valve spring can be inserted straight into the cylindrical spring chamber and only has as much play with the inner wall as with
  • the initially circular basic cross section of the spring windings then has bevels at its ends pointing radially outward to the spring axis, which are aligned parallel to the spring axis and to the wall of the spring chamber.
  • the tolerance on the outside diameter of the valve spring towards unprocessed springs can be reduced to a minimum.
  • the valve spring designed according to the invention has the advantage over alternative wire cross-sections such as rectangular, elliptical or other shaped wires that there is no additional outlay in wire production and the valve spring is therefore easier and cheaper to produce than these solutions.
  • the subsequent grinding of the outside diameter of the valve spring also enables a more precise outside diameter on the spring and thus a better use of space in the specified spring chamber.
  • possible material defects on the outside diameter of the valve spring are also removed in this way.
  • the use of this optimized spring is not limited to the use described in a fuel injection valve, but can be carried out wherever the spring force of a return spring should be increased despite a limited installation space, for example in injection pumps or gas exchange valves of internal combustion engines and the like.
  • Fuel injection valve for internal combustion engines is shown in the drawing and is explained in more detail in the following description.
  • Fuel injection valve and Figure 2 is an enlarged sectional view of the valve spring from Figure 1.
  • a piston-shaped valve member 1 is axially displaceably guided in a bore 3 in a valve body 5, which has a conical end at one end near the combustion chamber of the internal combustion engine
  • valve sealing surface 7, with which it interacts with a conical valve seat 9 on the inwardly projecting closed end of the bore 3.
  • the valve body 5 is with its end remote from the combustion chamber by means of a clamping nut 11 axially clamped against a valve holding body 13, an intermediate disk 15 with a central opening being clamped between the end faces of the valve body 5 and the valve holding body 13.
  • the valve body 5 is with its end remote from the combustion chamber by means of a clamping nut 11 axially clamped against a valve holding body 13, an intermediate disk 15 with a central opening being clamped between the end faces of the valve body 5 and the valve holding body 13.
  • Valve member 1 via a pressure piece 17 projecting through the intermediate disk 15 is acted upon by a valve spring 19 designed as a helical spring in the direction of the valve seat 9, which is inserted into a cylindrical spring chamber 21 in the valve holding body 13 and which on the other hand is fixed on a stationary wall formed by the upper axial wall of the spring chamber 21 Stop 23 supports.
  • a valve spring 19 designed as a helical spring in the direction of the valve seat 9, which is inserted into a cylindrical spring chamber 21 in the valve holding body 13 and which on the other hand is fixed on a stationary wall formed by the upper axial wall of the spring chamber 21 Stop 23 supports.
  • Injection opening 25 is provided in the wall of the valve body 5, which opens out from the bore 3 into the combustion chamber of the internal combustion engine to be supplied.
  • the high-pressure fuel supply to the sealing seat takes place in a known manner via an annular channel 27 formed between the shaft of the valve member 1 and the wall of the bore 3, which extends in the region of a ring shoulder 31 of the valve member 1 into a pressure chamber 29, one of which is not shown Injection pump discharging pressure line 33 opens.
  • valve spring 19 has, as shown in FIG cylindrical spring chamber 21 are aligned.
  • the valve spring 19 is first made from a round spring wire with such a large cross section y that the theoretical outer diameter of the unprocessed valve spring 19 is larger than the inner diameter of the spring chamber 21.
  • as much material is removed from the outer diameter of the valve spring, preferably ground that the valve spring 19 can be used with the necessary clearance in the spring chamber 21.
  • the remaining cross-sectional area z of the spring coils 41 is still significantly larger than the cross-sectional area of an unprocessed valve spring with an annular spring wire, the outside diameter of which is the same size, despite the cuts 43, so that the spring force of the valve spring 19 achieved can be increased considerably without additional installation space.
  • the ratio of y / z is preferably in a range from 1.05 to 1.3.

Landscapes

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

Abstract

Cette soupape d'injection de carburant pour moteurs à combustion interne comprend un organe de soupape axialement mobile dans un corps de soupape et qui présente, à une extrémité, une surface d'étanchéité qui coopère avec un siège fixe de soupape afin d'agir sur la section transversale d'injection. Au moins un ressort de soupape (19) qui sollicite l'organe de soupape dans la direction du siège de soupape s'appuie sur une butée fixe. Afin d'augmenter la force du ressort de soupape (19) sans accroître son diamètre extérieur, les spires (41) du ressort de soupape (19) qui est un ressort hélicoïdal, ont une section transversale de base circulaire élargie (y) dont une zone dirigée radialement vers l'extérieur par rapport à l'axe (X) du ressort présente une partie polie (43) parallèle à l'axe (X) du ressort.
EP96934344A 1995-12-16 1996-08-08 Soupape d'injection de carburant pour moteurs a combustion interne Expired - Lifetime EP0809756B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19547102 1995-12-16
DE19547102A DE19547102A1 (de) 1995-12-16 1995-12-16 Kraftstoffeinspritzventil für Brennkraftmaschinen
PCT/DE1996/001480 WO1997022801A1 (fr) 1995-12-16 1996-08-08 Soupape d'injection de carburant pour moteurs a combustion interne

Publications (2)

Publication Number Publication Date
EP0809756A1 true EP0809756A1 (fr) 1997-12-03
EP0809756B1 EP0809756B1 (fr) 2001-12-12

Family

ID=7780367

Family Applications (1)

Application Number Title Priority Date Filing Date
EP96934344A Expired - Lifetime EP0809756B1 (fr) 1995-12-16 1996-08-08 Soupape d'injection de carburant pour moteurs a combustion interne

Country Status (5)

Country Link
US (1) US5934572A (fr)
EP (1) EP0809756B1 (fr)
JP (1) JP3737124B2 (fr)
DE (2) DE19547102A1 (fr)
WO (1) WO1997022801A1 (fr)

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19719295A1 (de) 1997-05-07 1998-11-12 Bosch Gmbh Robert Kraftstoffeinspritzventil für Brennkraftmaschinen
JP4016370B2 (ja) * 1999-03-29 2007-12-05 株式会社デンソー 電磁弁
DE10016425A1 (de) 2000-04-01 2001-10-04 Bosch Gmbh Robert Schraubendruckfeder zur Verwendung in einem Bauteil eines Kraftstoffeinspritzsystems
US6776401B2 (en) * 2000-04-01 2004-08-17 Robert Bosch Gmbh Helical compression spring for use in a component of a fuel injection system
US6784370B1 (en) 2003-07-21 2004-08-31 Ideal Industries, Inc. Twist-on wire connector
US20060107511A1 (en) * 2004-11-23 2006-05-25 Richard Pare Methods and apparatus for centering spring reactive forces
DE102007050819A1 (de) * 2007-10-24 2009-04-30 Robert Bosch Gmbh Elektromagnetisch betätigbares Ventil
DE102018001566A1 (de) * 2018-02-23 2019-09-26 Woodward L'orange Gmbh Dual-Fuel-Kraftstoffinjektor

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB286445A (en) * 1927-02-22 1928-03-08 Henry Beaumont Taylor Improvements in or relating to internal combustion engines
US2521670A (en) * 1945-12-05 1950-09-05 Fletcher Trust Company Clutch spring
US2586646A (en) * 1946-03-29 1952-02-19 Thompson Prod Inc Joint
US2622448A (en) * 1951-06-04 1952-12-23 United States Steel Corp Apparatus for automatically centering and aligning moving objects
DE1803732A1 (de) * 1965-10-25 1969-06-04 Cohausz Dipl Ing Werner Einspritzduese
FR1512436A (fr) * 1966-12-23 1968-02-09 Réservoir de pression
DE2020678A1 (de) * 1970-04-28 1971-11-25 Daimler Benz Ag Schrauben-Druckfeder
DE3727366A1 (de) * 1987-08-17 1989-03-02 Bosch Gmbh Robert Kraftstoff-einspritzduese fuer brennkraftmaschinen
GB9012288D0 (en) * 1990-06-01 1990-07-18 Lucas Ind Plc Fuel injection pump

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO9722801A1 *

Also Published As

Publication number Publication date
US5934572A (en) 1999-08-10
EP0809756B1 (fr) 2001-12-12
JPH11501102A (ja) 1999-01-26
WO1997022801A1 (fr) 1997-06-26
DE19547102A1 (de) 1997-06-19
DE59608445D1 (de) 2002-01-24
JP3737124B2 (ja) 2006-01-18

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