EP0783626B1 - Kraftstoffeinspritzventilanordnung für brennkraftmaschinen - Google Patents

Kraftstoffeinspritzventilanordnung für brennkraftmaschinen Download PDF

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Publication number
EP0783626B1
EP0783626B1 EP96901242A EP96901242A EP0783626B1 EP 0783626 B1 EP0783626 B1 EP 0783626B1 EP 96901242 A EP96901242 A EP 96901242A EP 96901242 A EP96901242 A EP 96901242A EP 0783626 B1 EP0783626 B1 EP 0783626B1
Authority
EP
European Patent Office
Prior art keywords
valve
fuel injection
conical
injection valve
internal combustion
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
EP96901242A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0783626A1 (de
Inventor
Friedrich Boecking
Stefan Haug
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 EP0783626A1 publication Critical patent/EP0783626A1/de
Application granted granted Critical
Publication of EP0783626B1 publication Critical patent/EP0783626B1/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
    • 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
    • F02M61/10—Other injectors with elongated valve bodies, i.e. of needle-valve type
    • 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
    • F02M61/14—Arrangements of injectors with respect to engines; Mounting of injectors
    • 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

Definitions

  • the invention relates to a fuel injection valve arrangement for Internal combustion engines according to the preamble of claim 1 out.
  • a fuel injection valve arrangement for Internal combustion engines according to the preamble of claim 1 out.
  • the invention relates to a fuel injection valve arrangement for Internal combustion engines according to the preamble of claim 1 out.
  • common fuel injection valves kind of runs the fuel inlet channel in the valve body at an angle to the central axis next to that extending coaxially to the central axis Guide hole for the valve member (nozzle needle) and cuts the undercut Pressure chamber on the side. Due to the oblique course of the Inlet channel has the wall of the valve body between the inlet channel and the guide hole near the mouth of the inlet channel only a small thickness in the pressure chamber.
  • the wall of the valve body surrounding the pressure chamber due to the width required to distribute the fuel has the least thickness and strength. At injection pressures up to 400 bar occur with known fuel injection valves no significant damage.
  • a fuel injection valve is also known in which the annular shoulder of the clamping nut which axially braces the valve body against the holding body is conical at its end remote from the holding body.
  • this known fuel injection valve also has the disadvantage that the clamping of the entire fuel injection valve in the housing of the internal combustion engine can lead to an expansion of the clamping nut as a result of the axial load, so that the pressure force applied by the clamping nut in the direction of the pressure chamber makes no significant contribution to Can stabilize the valve body wall.
  • the fuel injection valve for internal combustion engines according to the invention with the characterizing features of claim 1 has the advantage that breakage of the valve body can be reliably avoided even at very high pressures (about 1800 bar) in the pressure chamber.
  • This is advantageously achieved by the combination of the two conical force introduction surfaces (2 bevels) between the clamping nut and valve body and the internal combustion engine housing and clamping nut, by means of which both the clamping force of the clamping nut when clamping the valve body against the holding body and the clamping force when clamping the whole Injection valve are introduced into the housing of the internal combustion engine on the valve body in such a way that they jointly counteract the pressure force of the pressure chamber under high fuel pressure, in particular in the region of the taper at the inlet of the inlet channel.
  • the conical design of the contact surface on the clamping nut and the counterstop surface in the internal combustion engine housing means that a large part of the clamping force applied to the fuel injection valve is converted into a radial component, which is transmitted directly to the conical ring shoulder of the valve body in the area of the spindle and so on counteracts a possible deformation of the valve body in the critical area due to the very high dynamic pressure loads.
  • the resulting force component from the pressure chamber is effectively absorbed by the applied clamping forces, so that the risk of breakage of the valve body can be minimized, which considerably increases the durability of the entire fuel injection valve at high operating pressures.
  • the conical design of the contact surface between the clamping nut and the internal combustion engine housing counteracts expansion of the clamping nut as a result of the clamping forces.
  • the conical surfaces are designed as uniform conical surfaces which have the same angle of inclination.
  • a particularly favorable transmission of force to the valve body is achieved at an angle of inclination of the conical surfaces (chamfer) of approximately 10 ° to 60 °, preferably 30 °, a vertical line standing on the conical conical surfaces then pointing in the direction of the taper at the transition of the guide bore into the pressure chamber .
  • FIG. 1 shows the installation position of the fuel injection valve into the housing of the internal combustion engine
  • FIG. 2 a longitudinal section through the combustion chamber side part of the Fuel injection valve
  • Figure 3 shows a detail from the fuel injection valve of Figure 2 in an enlarged Scale.
  • FIG. 1 shows a cylindrical fuel injection valve 1 which is inserted into a receiving bore 3 in a housing 5 of the internal combustion engine to be supplied.
  • the receiving bore 3 is designed as a stepped bore, the conical cross-sectional transition of which forms a counter abutment surface 7.
  • the fuel injection valve 1 is axially clamped by means of a clamping device 11 with a conical contact surface 9 likewise formed by a cross-sectional reduction.
  • the clamping device 11 has a tensioning plate 15 which acts on a face 13 of the fuel injection valve 1 facing away from the housing and which can be screwed to the housing 5 by means of a plurality of clamping screws 17 distributed over its circumference, and thus the fuel injection valve 1 axially against the counter stop 7 in the housing 5 Internal combustion engine clamped.
  • the fuel injector 1 shown in section in FIG. 2 in its combustion chamber area has a valve body 19 which is attached to a valve holding body 25 with a sleeve-shaped clamping nut 23 with the interposition of an intermediate disk 21.
  • a stepped piston-shaped valve member 27 (valve needle) is displaceable in an axial bore 29 of the valve body 19, the valve member 27 having a conical valve sealing surface 31 on its combustion chamber end, with which it has an inwardly directed valve seat 33 in a combustion chamber side dome 35 of the valve body 19 cooperates, downstream of which a plurality of injection openings 37 are arranged.
  • the valve body 19 is designed as a rotating body, with an upper thick section 39 and a lower slender section 41, the combustion chamber end of which is closed by the cap 35.
  • the part of the bore 29 arranged in the upper section 39 is designed as a guide section 43 for a guide part 45 of the valve member 27 which is larger in cross section.
  • annular gap 49 In the upper section 39 of the valve body 19 there is between the guide section 43 of the bore 29 and the valve section 19, near the lower section 41
  • annular gap 49 In the annular gap 49 there is an undercut pressure chamber 51 which is enlarged in diameter, the outer boundary 53 of which is preferably of arcuate design and merges into the annular gap 49.
  • an inlet channel 59 which can be connected to a high-pressure injection line (not shown), runs through the valve holding body 25, the intermediate disk 21 and the upper thick section 39 of the valve body 19 starting from its upper end face next to the guide section 43 of the bore 29 to the pressure chamber 51.
  • the inlet channel 59 cuts the pressure chamber 51 laterally from above to form a gusset, the inlet channel 59 running obliquely to the guide section 43 in order to keep the diameter of the pressure chamber 51 as small as possible and the cross section at the mouth as large as possible.
  • the clamping nut 23 designed as a union nut, which is screwed over the upper section 39 of the valve body 19 with an internal thread 61 to an external thread 63 on the valve holding body 25, has an inner annular shoulder 65 on which the valve body 19 with an annular shoulder 67 at the transition of the the upper section 39 is supported in the slender section 41.
  • the ring shoulder 65 and the ring shoulder 67 are conical, preferably frustoconical, with the same angle of inclination ⁇ (FIG. 3) to a radial plane 69 intersecting the axis of the valve member 27 at right angles.
  • the contact surface 9 of the fuel injection valve 1 formed on the end face of the clamping nut 23 on the combustion chamber side and the counterstop surface 7 in the housing 5 of the internal combustion engine shown in FIG. 1, which forms part of the receiving bore 3, are conical, preferably frustoconical.
  • the angle of inclination ⁇ of these conical surfaces, shown enlarged in FIG. 3, to a radial plane 69 intersecting the axis of the valve member 27 at right angles should preferably be the same as the angle of inclination ⁇ on the ring shoulder 65 and the ring shoulder 67.
  • angles ⁇ and ⁇ should be such that a vertical on the conical surfaces 65, 67, 7, 9 in the direction of the transition of the guide section 43 of the bore 29 into the pressure chamber 51 or the inlet opening of the inlet channel 59 into the Pressure chamber 51 (gusset) has for this purpose the angles of inclination ⁇ and ⁇ have a size of 10 ° to 60 °, preferably 30 ° to the radial plane 69.

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)
EP96901242A 1995-03-10 1996-02-09 Kraftstoffeinspritzventilanordnung für brennkraftmaschinen Expired - Lifetime EP0783626B1 (de)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19508636A DE19508636A1 (de) 1995-03-10 1995-03-10 Kraftstoffeinspritzventil für Brennkraftmaschinen
DE19508636 1995-03-10
PCT/DE1996/000203 WO1996028656A1 (de) 1995-03-10 1996-02-09 Kraftstoffeinspritzventil für brennkraftmaschinen

Publications (2)

Publication Number Publication Date
EP0783626A1 EP0783626A1 (de) 1997-07-16
EP0783626B1 true EP0783626B1 (de) 2000-08-23

Family

ID=7756305

Family Applications (1)

Application Number Title Priority Date Filing Date
EP96901242A Expired - Lifetime EP0783626B1 (de) 1995-03-10 1996-02-09 Kraftstoffeinspritzventilanordnung für brennkraftmaschinen

Country Status (6)

Country Link
US (1) US5746181A (zh)
EP (1) EP0783626B1 (zh)
JP (1) JP3625840B2 (zh)
CN (1) CN1065589C (zh)
DE (2) DE19508636A1 (zh)
WO (1) WO1996028656A1 (zh)

Families Citing this family (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2311558A (en) * 1996-03-28 1997-10-01 Stanadyne Automotive Corp Fuel injection nozzle with compressive radial pre-loading
DE19808660A1 (de) * 1998-03-02 1999-10-07 Siemens Ag Kraftstoffeinspritzventil für Brennkraftmaschinen
DE19850387A1 (de) * 1998-11-02 2000-05-04 Bosch Gmbh Robert Kraftstoffeinspritzventil für Brennkraftmaschinen
GB9824735D0 (en) * 1998-11-12 1999-01-06 Lucas Ind Plc Injector and injector assembly
DE19902282A1 (de) * 1999-01-21 2000-08-17 Siemens Ag Injektor für eine Einspritzanlage einer Brennkraftmaschine
DE19947194A1 (de) 1999-10-01 2001-04-05 Bosch Gmbh Robert Kraftstoffeinspritzventil für Brennkraftmaschinen
DE10018663A1 (de) 2000-04-14 2001-10-25 Siemens Ag Einspritzventil mit optimierter Flächengeometrie zwischen einem Düsenkörper und einer Spannmutter
DE10044933A1 (de) * 2000-09-12 2002-03-21 Bosch Gmbh Robert Kraftstoffeinspritzventil für Brennkraftmaschinen
DE10115325A1 (de) * 2001-03-28 2002-10-17 Bosch Gmbh Robert Kraftstoff-Einspritzvorrichtung, insbesondere Injektor, für Brennkraftmaschinen
DE50208654D1 (de) 2001-06-13 2006-12-21 Bosch Gmbh Robert Kraftstoffeinspritzventil für brennkraftmaschinen
DE10202722A1 (de) * 2002-01-24 2003-11-27 Siemens Ag Düsenspannmutter für Einspritzventil sowie Verfahren zur Herstellung der Düsenspannmutter
DE10215980B4 (de) * 2002-04-11 2008-03-27 Siemens Ag Leckageanschluss für einen Kraftstoffinjektor
DE10346845B4 (de) 2003-10-09 2022-07-07 Robert Bosch Gmbh Kraftstoffeinspritzventil für Brennkraftmaschinen
ATE461363T1 (de) * 2006-07-27 2010-04-15 Magneti Marelli Spa Kraftstoffeinspritzventil für eine direkteinspritzende brennkraftmaschine
DE102012211009A1 (de) 2012-06-27 2014-01-02 Robert Bosch Gmbh Kraftstoffinjektor für eine Verbrennungskraftmaschine
DE102013226817A1 (de) * 2013-12-20 2015-06-25 Robert Bosch Gmbh Hydraulikaggregat
FI126534B (en) * 2014-12-17 2017-01-31 Waertsilae Finland Oy Reinforcing device and method for increasing the fatigue strength of a chamber chamber element

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1834058A (en) * 1928-11-16 1931-12-01 Westinghouse Electric & Mfg Co Injection nozzle
US3695235A (en) * 1970-08-26 1972-10-03 Mcculloch Corp Heat seal for fuel injection nozzles
JPH0660609B2 (ja) * 1986-03-07 1994-08-10 工業技術院長 ディーゼル機関の燃料噴射ノズルボディー
JPS62210158A (ja) * 1986-03-10 1987-09-16 Nippon Ee B S Kk ２系統型アンチスキツドブレ−キ液圧制御装置
JP2537983Y2 (ja) * 1990-12-21 1997-06-04 株式会社ゼクセル 燃料噴射ノズル
DE4329774A1 (de) * 1993-09-03 1995-03-09 Bosch Gmbh Robert Vorrichtung zur Befestigung und Sicherung eines Ventils
DE4332118A1 (de) * 1993-09-22 1995-03-23 Bosch Gmbh Robert Brennstoffeinspritzvorrichtung
US5394850A (en) * 1993-11-19 1995-03-07 Siemens Electric Limited Top-feed fuel injector mounting in an integrated air-fuel system
DE4413914A1 (de) * 1994-04-21 1995-10-26 Bosch Gmbh Robert Brennstoffeinspritzeinrichtung
US5499612A (en) * 1994-10-03 1996-03-19 Caterpillar Inc. Dual-function clamping assembly adapted for a hydraulically-actuated fuel injector
FR2727722A1 (fr) * 1994-12-01 1996-06-07 Magneti Marelli France Jupe de dispersion de carburant, pour injecteur d'un moteur a injection

Also Published As

Publication number Publication date
US5746181A (en) 1998-05-05
CN1065589C (zh) 2001-05-09
CN1146791A (zh) 1997-04-02
EP0783626A1 (de) 1997-07-16
DE59605793D1 (de) 2000-09-28
WO1996028656A1 (de) 1996-09-19
JP3625840B2 (ja) 2005-03-02
JPH10500466A (ja) 1998-01-13
DE19508636A1 (de) 1996-09-12

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