EP0553310B1 - Brennstoffeinspritzventil - Google Patents

Brennstoffeinspritzventil Download PDF

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Publication number
EP0553310B1
EP0553310B1 EP92911364A EP92911364A EP0553310B1 EP 0553310 B1 EP0553310 B1 EP 0553310B1 EP 92911364 A EP92911364 A EP 92911364A EP 92911364 A EP92911364 A EP 92911364A EP 0553310 B1 EP0553310 B1 EP 0553310B1
Authority
EP
European Patent Office
Prior art keywords
valve
fuel
seat
valve seat
perforated
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
EP92911364A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0553310A1 (de
Inventor
Peter Romann
Ferdinand Reiter
Martin Maier
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 EP0553310A1 publication Critical patent/EP0553310A1/de
Application granted granted Critical
Publication of EP0553310B1 publication Critical patent/EP0553310B1/de
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
    • F02M61/18—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for
    • 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
    • F02M61/18—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for
    • F02M61/1853—Orifice plates

Definitions

  • the invention is based on a fuel injection valve according to the preamble of claim 1.
  • a fuel injection valve is already known (US Pat. No. 4,971,254) in which the perforated disk is held on the valve seat body by means of a support disk. The perforated disk and the support disk are fixed by a flanged edge of the seat support engaging the support disk, a sealing ring being required between the seat support, valve seat body and perforated disk, which is intended to prevent fuel from escaping accidentally over the circumference of the perforated disk and support disk.
  • the sealing effect of the sealing ring will deteriorate, in particular also because of the constant temperature changes, and fuel will inadvertently emerge from the fuel injection valve.
  • the fuel injector according to the invention with the characterizing features of claim 1 has the advantage that a thin perforated disc can be used, which leads to an optimal fuel preparation with the finest fuel droplets without deterioration of the spray pattern of the sprayed fuel jet and still ensures the tightness of the fuel injector.
  • the support disk in a pot shape and to tightly connect its circumferential retaining edge to the seat support in its axial position after the adjustment of the valve seat body, so that this makes it possible to adjust the valve lift and thus the amount of fuel injected.
  • the holding edge of the support disk is bent outwards towards its free end and, with this free end, bears against the wall of a longitudinal opening of the seat support under radial tension, so that the valve seat body is in its axial direction during the adjustment process Position is held until the desired setting is reached and the retaining edge of the support plate is welded to the wall of the longitudinal opening of the seat support for final fixing.
  • the through-opening of the support disk encompasses as close as possible to the region of the perforated disk which is provided with the at least one spray opening and is curved in a dome shape downstream, in order to avoid undesirable deflection of the perforated disk due to the prevailing fuel pressure.
  • the fuel injector for fuel injection systems of mixture-compression-ignition Internal combustion engines partially shown.
  • the fuel injector has a tubular seat support 1, in which a longitudinal opening 3 is formed concentrically with a valve longitudinal axis 2.
  • a longitudinal opening 3 is formed concentrically with a valve longitudinal axis 2.
  • tubular valve needle 5 is arranged which is connected at its downstream end 6 with an example spherical valve closing body 7.
  • the fuel injector is actuated in a known manner, for example electromagnetically.
  • An indicated electromagnetic circuit with a magnet coil 10, an armature 11 and a core 12 is used for the axial movement of the valve needle 5 and thus for opening or closing the fuel injection valve.
  • the armature 11 is connected to the end of the valve needle 5 facing away from the valve closing body 7 and on the core 12 aligned.
  • a guide opening 16 of a valve seat body 18 serves to guide the valve closing body 7 during the axial movement.
  • the circumference of the valve seat body 18 has a slightly smaller diameter than the diameter of the longitudinal opening 3 of the seat carrier 1.
  • a metal perforated disk 22 is arranged concentrically on the valve seat body 18 and is firmly connected to it.
  • the perforated disc 22 has a thickness of 0.1 mm, for example.
  • the metal support disk 26 has a cup-shaped cross-sectional shape and has a thickness of 0.2 mm, for example.
  • a circumferential holding edge 28 adjoins a bottom part 27 of the support disk 26 which bears against the end face 25 of the perforated body 22 and extends in the axial direction away from the valve seat body 18 and is conically bent outwards up to one end 29.
  • the holding edge 28 has at its end 29 a slightly larger diameter than the diameter of the longitudinal opening 3 of the seat carrier 1.
  • the connection of the valve seat body 18, perforated disk 22 and support disk 26 is carried out, for example, by a circumferential and dense, e.g. B. first weld seam 24 formed by a laser. For this reason, good weldability should also be ensured in the material selection for the perforated disk 22 and the support disk 26.
  • valve seat body 18 with the perforated disk 22 and the support disk 26 attached to it is inserted into the longitudinal opening 3. Due to the somewhat smaller diameter of the circumference of the valve seat body 18 compared to the longitudinal opening 3 of the seat support 1, there is only radial pressure between the longitudinal opening 3 and the slightly conical outwardly bent retaining edge 28 of the support disk 26, the retaining edge 28 having a radial spring action exerts on the wall of the longitudinal opening 3. As a result, chip formation is avoided when the valve seat body 18 with the perforated disk 22 and the support disk 26 is inserted into the longitudinal opening 3 of the seat support 1.
  • valve seat body 18 In addition, in the manufacture of the valve seat body 18 it is not necessary to maintain a narrow dimensional tolerance on its circumference, since the valve seat body 18 has a slight play in the radial opening in the longitudinal opening 3 of the seat carrier 1, so that the manufacturing costs compared to a valve seat body pressed into the longitudinal opening 3 be significantly reduced.
  • the insertion depth of the valve seat body 18 into the longitudinal opening 3 of the seat support 1 determines the presetting of the stroke of the valve needle 5 guided radially through the guide opening 16, since the one end position of the valve needle 5 when the magnet coil 10 is not energized due to the valve closing body 7 resting against a downstream of the guide opening 16 formed valve seat surface 32 of the valve seat body 18 is fixed.
  • the other end position of the valve needle 5 is determined when the solenoid 10 is excited, for example by the armature 11 resting on the core 12. The path between these two end positions represents the stroke of the valve needle 5.
  • the holding edge 28 of the support disk 26 is connected to the wall of the longitudinal opening 3, for example by a circumferential and tight second weld seam 30.
  • the second weld 30 is just like the first weld 24 z. B. generated by a laser, so that there is a safe and reliable, easy to produce weld, in which the heating of the parts to be welded together is low.
  • valve seat body 18 and perforated disk 22 or support disk 26 and of support disk 26 and seat support 1 is required so that the medium used, for example a fuel, does not pass between the longitudinal opening 3 of the seat support 1 and the circumference of the valve seat body 18 or between the Longitudinal opening 3 of the seat support 1 and the holding edge 28 of the support plate 26 can flow directly into an intake line of the internal combustion engine.
  • medium used for example a fuel
  • the spherical valve closing body 7 interacts with the valve seat surface 32 of the valve seat body 18, which tapers conically in the flow direction, for example, and which is formed in the axial direction between the guide opening 16 and the end face 19 of the valve seat body 18, and has a plurality of flats 33, preferably five, which form a flow of the medium from the valve interior 35 delimited in the radial direction by the longitudinal opening 3 of the seat carrier 1 to the valve seat surface 32, from where the medium, in the opened state of the valve, reaches spray openings 37 of the perforated disk 22 via a short intermediate opening 36 formed downstream in the valve seat body 18.
  • the diameter of the guide opening 16 is designed such that the spherical valve closing body 7 projects into the guide opening 16 with a small radial distance.
  • the support disk 26 is used for the exact adjustment of the stroke of the valve needle 5 in the axial direction in the area between the second weld seam 30 and of the first weld seam 24 is stretched in this way by means of a tool 39 and, if necessary, is plastically deformed until the measured actual medium quantity matches the specified medium target quantity.
  • the exact setting of the stroke and the static flow quantity of a medium which is emitted during the stationary opening state of the injection valve is carried out in a simple manner on the fully assembled fuel injection valve.
  • a protective cap 45 is arranged on the circumference of the seat support 1 at its downstream end and is connected to the circumference of the seat support 1 by means of a latching connection 46.
  • the protective cap 45 rests with a first radial section 47 on an end face 48 of the seat support 1.
  • the first radial section 47 of the protective cap 45 is first adjoined by an axially extending parallel section 49 and a second radial section 50 pointing radially outward.
  • a sealing ring 51 is arranged in an annular groove 53, the side surfaces of which are formed by an end face 54 of the second radial section 50 of the protective cap 45 facing the magnetic coil 10 and by a radially outwardly facing contact surface 55 of the seat support 1 and the groove base 57 thereof by the circumference of the seat support 1 .
  • the sealing ring 51 serves to seal between the circumference of the fuel injection valve and a valve receptacle, not shown, for example the intake line of the internal combustion engine.
  • the intermediate opening 36 downstream of the valve seat surface 32 of the valve seat body 18 encompasses a central region 60 of the perforated disk 22, in which the at least one spray opening 37 is, but for example four spray openings 37 are formed.
  • a through-opening 61 is provided in the support disk 26 approximately concentrically to the valve longitudinal axis 2, which likewise encompasses the area 60 of the perforated disk 22 on the opposite side. The fuel sprayed through the spray openings 37 is thus sprayed through the through opening 61 of the support disk 26.
  • the area 60 of the perforated disk 22 which is encompassed by the through-opening 61 of the support disk 26 can be curved in the direction of flow such that it has the shape of a spherical cap.
  • the first weld 24 has a sufficiently large radial distance from the area 60 of the perforated disk 22 in order to avoid the formation of deformations in the area 60.
  • the axial distance between the area 60 of the perforated disk 22 and the lower end of the valve closing body 7 is kept as small as possible in order to form the smallest possible dead volume.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)
EP92911364A 1991-07-17 1992-06-10 Brennstoffeinspritzventil Expired - Lifetime EP0553310B1 (de)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE4123692A DE4123692C2 (de) 1991-07-17 1991-07-17 Brennstoffeinspritzventil
DE4123692 1991-07-17
PCT/DE1992/000477 WO1993002285A1 (de) 1991-07-17 1992-06-10 Brennstoffeinspritzventil

Publications (2)

Publication Number Publication Date
EP0553310A1 EP0553310A1 (de) 1993-08-04
EP0553310B1 true EP0553310B1 (de) 1995-09-13

Family

ID=6436375

Family Applications (1)

Application Number Title Priority Date Filing Date
EP92911364A Expired - Lifetime EP0553310B1 (de) 1991-07-17 1992-06-10 Brennstoffeinspritzventil

Country Status (7)

Country Link
US (1) US5335864A (ja)
EP (1) EP0553310B1 (ja)
JP (1) JP3107825B2 (ja)
KR (1) KR100254305B1 (ja)
DE (2) DE4123692C2 (ja)
ES (1) ES2078745T3 (ja)
WO (1) WO1993002285A1 (ja)

Families Citing this family (28)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4141930B4 (de) * 1991-12-19 2007-02-08 Robert Bosch Gmbh Elektromagnetisch betätigbares Einspritzventil
US5484108A (en) * 1994-03-31 1996-01-16 Siemens Automotive L.P. Fuel injector having novel multiple orifice disk members
DE69518432T2 (de) * 1994-10-17 2001-03-15 Siemens Automotive Corp Lp Einspritzventil mit verringerter stromdispersion, insbesondere eines ausseraxialen eingespritzten stromes
DE4445358A1 (de) * 1994-12-20 1996-06-27 Bosch Gmbh Robert Ventil und Verfahren zur Herstellung eines Ventiles
DE4446241A1 (de) * 1994-12-23 1996-06-27 Bosch Gmbh Robert Brennstoffeinspritzventil
EP0781917A1 (en) * 1995-12-26 1997-07-02 General Motors Corporation Fuel injector valve seat retention
JP3750126B2 (ja) * 1996-03-26 2006-03-01 株式会社デンソー 燃料噴射弁
DE19625059A1 (de) * 1996-06-22 1998-01-02 Bosch Gmbh Robert Einspritzventil, insbesondere zum direkten Einspritzen von Kraftstoff in einen Brennraum eines Verbrennungsmotors
DE19724075A1 (de) * 1997-06-07 1998-12-10 Bosch Gmbh Robert Verfahren zur Herstellung einer Lochscheibe für ein Einspritzventil und Lochscheibe für ein Einspritzventil und Einspritzventil
DE19822896A1 (de) 1998-05-22 1999-11-25 Bosch Gmbh Robert Brennstoffeinspritzventil
DE19855568A1 (de) * 1998-12-02 2000-06-08 Bosch Gmbh Robert Brennstoffeinspritzventil
DE19856920A1 (de) 1998-12-10 2000-06-15 Bosch Gmbh Robert Brennstoffeinspritzventil
DE19935262A1 (de) * 1999-07-27 2001-02-01 Bosch Gmbh Robert Brennstoffeinspritzventil
DE10059007A1 (de) * 2000-11-28 2002-05-29 Bosch Gmbh Robert Brennstoffeinspritzventil
DE10118164B4 (de) * 2001-04-11 2007-02-08 Robert Bosch Gmbh Brennstoffeinspritzventil
EP1581737B1 (en) * 2003-01-09 2009-05-27 Continental Automotive Systems US, Inc. Spray pattern control with non-angled orifices formed on a dimpled fuel injection metering disc having a sac volume reducer
US6948665B2 (en) * 2003-06-30 2005-09-27 Siemens Vdo Automotive Corporation Fuel injector including an orifice disc, and a method of forming the orifice disc with an asymmetrical punch
US7163159B2 (en) * 2003-07-15 2007-01-16 Siemens Vdo Automotive Corporation Fuel injector including a compound angle orifice disc
US7744020B2 (en) * 2003-07-21 2010-06-29 Continental Automotive Systems Us, Inc. Fuel injector including an orifice disc, and a method of forming the orifice disc including punching and shaving
US7159436B2 (en) * 2004-04-28 2007-01-09 Siemens Vdo Automotive Corporation Asymmetrical punch
US7201329B2 (en) * 2004-04-30 2007-04-10 Siemens Vdo Automotive Corporation Fuel injector including a compound angle orifice disc for adjusting spray targeting
US7086615B2 (en) 2004-05-19 2006-08-08 Siemens Vdo Automotive Corporation Fuel injector including an orifice disc and a method of forming an oblique spiral fuel flow
US20060157595A1 (en) * 2005-01-14 2006-07-20 Peterson William A Jr Fuel injector for high fuel flow rate applications
US20060192036A1 (en) * 2005-02-25 2006-08-31 Joseph J M Fuel injector including a multifaceted dimple for an orifice disc with a reduced footprint of the multifaceted dimple
US20060200988A1 (en) 2005-03-11 2006-09-14 Siemens Vdo Automotive Corporation Sandwich orifice disc
DE602005007856D1 (de) * 2005-04-14 2008-08-14 Siemens Ag Ventilkörper und Flüssigkeitsinjektor mit Ventilkörper
JP5161853B2 (ja) * 2009-09-29 2013-03-13 三菱電機株式会社 燃料噴射弁
JP2018530698A (ja) * 2015-09-30 2018-10-18 ノストラム エナジー ピーティーイー．リミテッドＮｏｓｔｒｕｍ Ｅｎｅｒｇｙ Ｐｔｅ．Ｌｔｄ． 非対称的な放射状分布による衝突噴流微粒化装置の噴霧方向調整およびプルーム整形

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1589247A (en) * 1926-01-07 1926-06-15 Super Diesel Tractor Corp Reed-type spray nozzle
US4030668A (en) * 1976-06-17 1977-06-21 The Bendix Corporation Electromagnetically operated fuel injection valve
US4934653A (en) * 1987-12-23 1990-06-19 Siemens-Bendix Automotive Electronics L.P. Multi-stream thin edge orifice disks for valves
DE3841142C2 (de) * 1988-12-07 1994-09-29 Bosch Gmbh Robert Einspritzventil
US4971254A (en) * 1989-11-28 1990-11-20 Siemens-Bendix Automotive Electronics L.P. Thin orifice swirl injector nozzle

Also Published As

Publication number Publication date
KR930702610A (ko) 1993-09-09
DE4123692A1 (de) 1993-01-21
EP0553310A1 (de) 1993-08-04
KR100254305B1 (ko) 2000-06-01
US5335864A (en) 1994-08-09
DE4123692C2 (de) 1995-01-26
JPH06501087A (ja) 1994-01-27
DE59203684D1 (de) 1995-10-19
JP3107825B2 (ja) 2000-11-13
WO1993002285A1 (de) 1993-02-04
ES2078745T3 (es) 1995-12-16

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