EP0611885B1 - Brennstoffeinspritzventil für eine Hubkolbenbrennkraftmaschine - Google Patents

Brennstoffeinspritzventil für eine Hubkolbenbrennkraftmaschine Download PDF

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Publication number
EP0611885B1
EP0611885B1 EP93810093A EP93810093A EP0611885B1 EP 0611885 B1 EP0611885 B1 EP 0611885B1 EP 93810093 A EP93810093 A EP 93810093A EP 93810093 A EP93810093 A EP 93810093A EP 0611885 B1 EP0611885 B1 EP 0611885B1
Authority
EP
European Patent Office
Prior art keywords
valve
combustion chamber
cap
seat
fuel
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
EP93810093A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0611885A1 (de
Inventor
Ulrich Staiger
Klaus Heim
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.)
Winterthur Gas and Diesel AG
Original Assignee
Winterthur Gas and Diesel AG
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 Winterthur Gas and Diesel AG filed Critical Winterthur Gas and Diesel AG
Priority to EP93810093A priority Critical patent/EP0611885B1/de
Priority to DK93810093.0T priority patent/DK0611885T3/da
Priority to DE59306670T priority patent/DE59306670D1/de
Priority to KR1019940002524A priority patent/KR100323937B1/ko
Priority to JP6018707A priority patent/JPH06317235A/ja
Priority to CN94101587A priority patent/CN1050877C/zh
Priority to FI940718A priority patent/FI106739B/fi
Publication of EP0611885A1 publication Critical patent/EP0611885A1/de
Application granted granted Critical
Publication of EP0611885B1 publication Critical patent/EP0611885B1/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
    • 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
    • F02M61/08—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 the valves opening in direction of fuel flow

Definitions

  • the invention relates to a fuel injection valve for a reciprocating piston internal combustion engine according to the preamble of claim 1.
  • DE-A-15 26 717 describes an injection nozzle for internal combustion engines.
  • the nozzle contains a needle housing, a valve needle with a valve cone 11 at the end on the combustion chamber side, a nozzle body with a cap and nozzle holes which are arranged in the cap, and a valve seat sleeve which is inserted in the nozzle body.
  • the cap is provided below the valve cone and serves to guide the valve needle within the cap of the nozzle body.
  • An annular channel is provided on the inside of the cap.
  • the end of the valve needle forms a flat cone to displace the fuel remaining under the needle through the annular gap of the cylindrical guide.
  • the nozzle has the disadvantages that after the valve needle is closed on the combustion chamber side of the valve seat there is a volume of fuel which is blown out by the gas flow into the combustion chamber and leads to coking and that the needle stroke is very low to reduce the stress on the valve seat and needle and reduce stop.
  • the invention solves the problem of improving a fuel injector for a reciprocating engine.
  • Another advantage of the injection valve according to the invention is that the stroke of the striker can now be made larger.
  • the injection valve has a housing 1, which consists of an upper part 2 and a lower part 3, which are held together by a union nut 4.
  • the housing 1 rests with a flange 5 on a cylinder head 6, which limits the combustion chamber 7 in the cylinder, not shown, of the reciprocating internal combustion engine of the diesel type.
  • the housing 1 penetrates the Zylin6 and projects into the combustion chamber 7 with a section 3 ′ of the lower part 3 with a diameter.
  • the housing 1 For the supply of fuel (arrow A) to the injection valve, the housing 1 has a channel 10 which initially extends radially into the flange 5 and is then guided essentially in the longitudinal direction of the housing through the upper part 2 and into the lower part 3 , where it opens into a room 11 which is located near the center of the housing.
  • a striker 20 In the center of the housing 1 there is an axially displaceable rod 12 of a striker 20 which carries a mushroom-like valve cone 20 'at its lower end in FIG. 1 and which is held at the upper end in a spring plate 13 which is located on its underside on a Compression spring 14 supports.
  • the upper part 2 To guide the axially displaceable rod 12, the upper part 2 has a bore 9 of constant diameter in its lower half and the lower part throughout.
  • the bore 9 is enlarged in diameter and forms a guide for the spring plate 13 which is axially displaceable with the rod 12.
  • the space 15 formed by the enlarged bore, which also receives the compression spring 14, is directed upwards a screw 16 closed.
  • the diameter of the rod 12 is reduced above the space 11, so that between the thinner rod section 12 'thus formed and the bore 9 there is an annular channel 17 which extends to the lowest end of the section 3'.
  • the end face of section 3 ' is designed as a conical seat surface 18 (FIG. 2) which widens towards the combustion chamber 7.
  • the seat surface 18 interacts with a correspondingly conical sealing surface 19 which is formed on the top of the mushroom-like valve cone 20 '.
  • a threaded cap 8 is screwed onto the housing section 3 'and spans the valve cone 20' with its lower section located in the combustion chamber 7.
  • nozzle channels 21 are provided in the cap 8 which extend transversely to the longitudinal axis of the valve and are used to form fuel jets.
  • the channels 21 have a circular cross section.
  • a raised stop surface 8 ' is formed on the inside thereof, against which the striker 20 rests in its fully open position.
  • the threaded cap 8 forms on its inside below the seat surface 18 a cylindrical surface 8 ′′, which serves as a guide surface for the striker 20, which is also cylindrical below the sealing surface 19.
  • the upper limit of the nozzle channel 21 is offset relative to the seat surface 18 by the distance X from the combustion chamber 7, as a result of which the injection valve receives a preliminary stroke without opening.
  • the valve is normally in the closed position, ie the closing piece 20 lies with its sealing surface 19 close to the seat surface 18, which is accomplished by the compression spring 14.
  • the channel 10 and the annular space 17 are filled with fuel which has a pressure of less than 100 bar.
  • the injection of fuel into the combustion chamber 7 is dependent on the delivery pressure of the injection pump, not shown, connected to the channel 10. At the moment when the opening force generated by the fuel pressure and acting on the valve cone 20 ′ outweighs the closing force of the compression spring 14, the closing piece is displaced downward, so that the fuel can flow from the annular space 17 to the channels 21.
  • the nozzle channels 31 have an essentially rectangular cross section and the seat surface 18 is displaced relative to the upper boundary of the channels 31 towards the combustion chamber 7.
  • the injection process begins immediately when the valve cone 20 'is lifted off the seat 18.
  • the striker 40 there is again a mushroom-like valve cone 40' with a sealing surface 42 which interacts with the seat surface 18 at the lower end of the section 3 '.
  • the valve cone 40 ' is surrounded by a threaded cap 48 which, in terms of the stop surface and the cylindrical guide surface for the striker, is of the same design as the threaded cap 8.
  • the difference is that the highly rectangular channels 41 are larger than in the threaded cap 8 according to FIG. 3 and that a slide plate 45 protrudes into the channels 41, which are attached to the closing piece 40 below the sealing surface 42.
  • each channel 41 measured in the circumferential direction, the threaded cap 48 is provided with a slot of the same width at the top.
  • a leg 43 of a ring 44 which encloses the section 3 ', rests on the upper edge of the threaded cap 48 and can be rotated with the threaded cap.
  • the lower end face 43 'of each leg 43 in FIGS. 4 and 5 thus delimits the beam-forming cross section of the associated channel 41 on its upper side.
  • the mode of operation of the injection valve according to FIGS. 4 and 5 is in principle the same as that described for FIGS. 1 and 2, i.e. if the delivery pressure of the injection pump exceeds the force of the closing spring, the closing piece 40 moves in the direction of the combustion chamber 7, as a result of which fuel can flow from the annular space 17 to the nozzle channels 41.
  • the flow cross section of the jet-forming part of the nozzle channels 41 is determined by the axial distance between the surfaces 43 'and 45'.
  • the number of nozzle channels depends on the application of the injection valve. If the injection valve is used in a four-stroke diesel engine, it is usually located in the center of the combustion chamber and the nozzle channels are distributed evenly over the circumference of the injection valve. If the injection valve is arranged in a two-stroke diesel engine with an outlet valve arranged in the center of the combustion chamber, a plurality of injection valves are usually arranged distributed outside the center. One or more nozzle channels per injection valve can be arranged in such a way that the fuel jets emerging from them are distributed in the combustion chamber as cheaply as possible for combustion.
  • a clamp connection for the cap 8 or 48 can also be used instead of a threaded connection.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)
EP93810093A 1993-02-17 1993-02-17 Brennstoffeinspritzventil für eine Hubkolbenbrennkraftmaschine Expired - Lifetime EP0611885B1 (de)

Priority Applications (7)

Application Number Priority Date Filing Date Title
EP93810093A EP0611885B1 (de) 1993-02-17 1993-02-17 Brennstoffeinspritzventil für eine Hubkolbenbrennkraftmaschine
DK93810093.0T DK0611885T3 (fi) 1993-02-17 1993-02-17
DE59306670T DE59306670D1 (de) 1993-02-17 1993-02-17 Brennstoffeinspritzventil für eine Hubkolbenbrennkraftmaschine
KR1019940002524A KR100323937B1 (ko) 1993-02-17 1994-02-14 왕복내연기관의연료분사밸브
JP6018707A JPH06317235A (ja) 1993-02-17 1994-02-15 レシプロ式内燃機関の燃料噴射ノズル
CN94101587A CN1050877C (zh) 1993-02-17 1994-02-16 一种往复式内燃机的燃油喷射阀
FI940718A FI106739B (fi) 1993-02-17 1994-02-16 Iskumäntäpolttomoottorikoneen polttoaineen ruiskutusventtiili

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP93810093A EP0611885B1 (de) 1993-02-17 1993-02-17 Brennstoffeinspritzventil für eine Hubkolbenbrennkraftmaschine

Publications (2)

Publication Number Publication Date
EP0611885A1 EP0611885A1 (de) 1994-08-24
EP0611885B1 true EP0611885B1 (de) 1997-06-04

Family

ID=8214916

Family Applications (1)

Application Number Title Priority Date Filing Date
EP93810093A Expired - Lifetime EP0611885B1 (de) 1993-02-17 1993-02-17 Brennstoffeinspritzventil für eine Hubkolbenbrennkraftmaschine

Country Status (7)

Country Link
EP (1) EP0611885B1 (fi)
JP (1) JPH06317235A (fi)
KR (1) KR100323937B1 (fi)
CN (1) CN1050877C (fi)
DE (1) DE59306670D1 (fi)
DK (1) DK0611885T3 (fi)
FI (1) FI106739B (fi)

Families Citing this family (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4440369A1 (de) * 1994-11-11 1996-05-15 Bosch Gmbh Robert Kraftstoffeinspritzventil für Brennkraftmaschinen
DE19929473B4 (de) * 1999-06-26 2005-12-08 Robert Bosch Gmbh Kraftstoffeinspritzventil
EP1854798A3 (en) 2000-09-19 2007-11-28 Bristol-Myers Squibb Company Fused heterocyclic succinimide compounds and analogs thereof, modulators of nuclear hormone receptor function
JP2002130087A (ja) 2000-10-23 2002-05-09 Toyota Motor Corp 筒内噴射式内燃機関用燃料噴射弁
US20040087548A1 (en) 2001-02-27 2004-05-06 Salvati Mark E. Fused cyclic succinimide compounds and analogs thereof, modulators of nuclear hormone receptor function
JP4127703B2 (ja) * 2005-09-07 2008-07-30 三菱電機株式会社 燃料噴射装置
EP2397683B1 (en) * 2010-06-18 2014-12-03 Caterpillar Motoren GmbH & Co. KG Injection Nozzle System
DE102016215637A1 (de) 2016-08-19 2018-02-22 Robert Bosch Gmbh Kraftstoffeinspritzdüse
EP3404235A1 (de) * 2017-05-19 2018-11-21 Winterthur Gas & Diesel AG Grossdieselmotor und verfahren zum betreiben eines grossdieselmotors
CN113623108B (zh) * 2021-09-04 2022-09-09 重庆红江机械有限责任公司 一种船用低速机喷油器针阀偶件

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2351965A (en) * 1939-03-01 1944-06-20 Ex Cell O Corp Nozzle
DE1526717A1 (de) * 1966-09-06 1970-02-26 Maschf Augsburg Nuernberg Ag Einspritzduese fuer Brennkraftmaschinen
GB8410749D0 (en) * 1984-04-26 1984-05-31 Lumber P M P Fuel injection nozzles
US4862857A (en) * 1988-02-12 1989-09-05 Outboard Marine Corporation Fuel injection system for multi cylinder two-stroke engine
DE4034203C2 (de) * 1990-10-27 1995-02-09 Rinsum Cornelis Van Dipl Ing Kraftstoff-Einspritzdüse für Brennkraftmaschinen

Also Published As

Publication number Publication date
FI940718A (fi) 1994-08-18
CN1050877C (zh) 2000-03-29
DK0611885T3 (fi) 1997-06-30
EP0611885A1 (de) 1994-08-24
KR100323937B1 (ko) 2002-06-20
KR940019986A (ko) 1994-09-15
DE59306670D1 (de) 1997-07-10
CN1092504A (zh) 1994-09-21
FI106739B (fi) 2001-03-30
FI940718A0 (fi) 1994-02-16
JPH06317235A (ja) 1994-11-15

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