EP0246220B1 - Buse d'injection pour moteurs à combustion interne en particulier pour moteurs diesel - Google Patents

Buse d'injection pour moteurs à combustion interne en particulier pour moteurs diesel Download PDF

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Publication number
EP0246220B1
EP0246220B1 EP19870890095 EP87890095A EP0246220B1 EP 0246220 B1 EP0246220 B1 EP 0246220B1 EP 19870890095 EP19870890095 EP 19870890095 EP 87890095 A EP87890095 A EP 87890095A EP 0246220 B1 EP0246220 B1 EP 0246220B1
Authority
EP
European Patent Office
Prior art keywords
valve
valve stem
projections
injection nozzle
stem
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
Application number
EP19870890095
Other languages
German (de)
English (en)
Other versions
EP0246220A1 (fr
Inventor
Hans Dipl.-Ing.Dr. List
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.)
AVL List GmbH
Original Assignee
AVL Gesellschaft fuer Verbrennungskraftmaschinen und Messtechnik mbH
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 AVL Gesellschaft fuer Verbrennungskraftmaschinen und Messtechnik mbH filed Critical AVL Gesellschaft fuer Verbrennungskraftmaschinen und Messtechnik mbH
Publication of EP0246220A1 publication Critical patent/EP0246220A1/fr
Application granted granted Critical
Publication of EP0246220B1 publication Critical patent/EP0246220B1/fr
Expired 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
    • F02M61/04—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
    • 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
    • F02M61/165—Filtering elements specially adapted in fuel inlets to injector
    • 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 relates to an injection nozzle for internal combustion engines, in particular diesel engines, with a poppet valve which consists of a valve disk and valve stem and which opens due to the fuel pressure in the flow direction with a very small stroke, the stroke of the poppet valve being limited by a stop which is in the vicinity of the valve disk is provided and is formed by projections which are provided on the inside of the valve housing and on the outside of the valve stem, the mutually facing contact surfaces of these projections projecting from one another by the desired maximum stroke when the valve is closed.
  • Such an injection nozzle is used for uniform distribution of the fuel along the circumference of an at least approximately rotationally shaped combustion chamber, the injection nozzle being arranged approximately in the axis of the combustion chamber.
  • the fuel emerges from the injection nozzle in the form of a cone jacket with a very small wall thickness; it offers the relatively little moving combustion air in the combustion chamber a very large target. As it moves against the circumference of the combustion chamber at high speed during injection, there is a strong friction between the fuel and the air, which splits the fuel into tiny droplets. The air is accelerated by the impulse of the fuel moving at high speed in the direction of the circumference of the combustion chamber in accordance with the impact laws, which creates flows in the combustion chamber which are directed from the injection nozzle to the circumference and then lead from the circumference against the injection nozzle.
  • the angle of the fuel jacket in the combustion chamber and this itself must be coordinated so that an equal mixture of fuel and air occurs.
  • the opening angle of the injected fuel cone jacket is at least 90 ° , preferably 120 to 160 ° .
  • the stroke of the valve plate is accordingly very small, approximately in the order of magnitude of one or several hundredths of a millimeter.
  • An injection nozzle of the type mentioned is known from DE-C 933 003.
  • a conical valve body is provided, but with an acute cone angle, which cooperates with a correspondingly conical valve seat in one valve seat plate.
  • the valve body opens due to the fuel pressure in the direction of flow and overcomes the force of a coil spring.
  • the valve seat plate is fixed in the valve housing, which is designed as a screw-in nipple, by a pressure bush, on which a pressure piece screwed into the valve housing and having an inlet bore acts.
  • the valve body has a shaft protruding into the cavity of the pressure sleeve, with which it engages the helical tension spring.
  • the helical tension spring is suspended at the top from an abutment which is supported on a shoulder provided at the upper end of the pressure bush.
  • the stem of the valve body is passed through a disc clamped between the pressure sleeve and the valve seat plate, which has a radial slot for mounting the stem.
  • the fuel can pass through to the valve seat through this slot and through axial bores in the disk.
  • the said disk serves to limit the stroke of the valve body, the stem of which strikes a shoulder on the disk.
  • This injector is particularly complicated in construction due to the separate stroke limiting disk and cumbersome in assembly and maintenance.
  • the injector must be completely disassembled to access the valve.
  • an injection nozzle was known from DE-OS 3 139 948, in which, however, the stop limiting the stroke of the valve plate is at a very considerable distance from the valve plate.
  • the valve plate has a larger diameter than the valve stem, which has an annular groove immediately above the valve plate, in which transverse bores end, which establish a connection to a central blind hole through which the fuel can be supplied.
  • the stop is formed by a sleeve held in the upper region of the valve stem, which is acted upon by a spring and is supported via intermediate elements on an O-ring held on the valve stem.
  • This injector also has the disadvantage that the valve is only accessible when the injector is practically completely disassembled, which results in a correspondingly high level of maintenance.
  • the relatively large distance between the stop and the valve seat results in an undesirable considerable thermal influence on the largest opening gap of the valve.
  • the object of the invention is to propose an injection nozzle of the type mentioned at the outset which avoids the disadvantages of the known designs and which, while ensuring the largest opening gap, is distinguished by a simple structure, simple assembly and a high degree of ease of maintenance.
  • this is achieved in that two radial projections on the valve housing are integral with this and form recesses in the valve housing, and two projections on the valve stem each diametrically opposite extend over less than 90 degrees and the axial coverage of these projections after insertion of the valve stem in the valve housing is reached through the recesses by turning the valve stem.
  • the stop can be easily manufactured with the necessary accuracy. Different thermal expansions from the valve stem and valve housing can only have a minor effect on the maximum valve lift. The result is a simple design and simple installation and maintenance options.
  • plate springs which are arranged coaxially to the valve stem and which are supported on the valve housing on the one hand and on nuts screwed onto the valve stem on the other hand can be provided on the end of the valve stem opposite the valve stem.
  • the disc springs can also be used to secure the valve stem against rotation by, according to a further feature of the invention, by providing the valve stem with a flattened portion on the one hand and a corresponding recess in the disc spring resting on the valve housing and, on the other hand, a pin for securing this disc spring against the valve housing is provided.
  • a filter for the fuel can be provided between the access of the fuel to the valve and the exit from the valve be formed in the valve housing, which is smaller than the maximum valve lift.
  • the injection nozzle according to the invention shown in FIGS. 1 to 3 consists of the valve housing 1, in which the valve stem 2 is axially slidably supported with play. At its lower end, the valve stem 2 has a valve disk 3 with a conical seat surface 4, the cone angle of which is denoted by 5 and is approximately 140 ° in the present example.
  • the injection nozzle is designed so that it opens in the direction of flow due to the pressure of the fuel supplied.
  • two identical plate springs 6 and 7 engage, which should generally be very stiff.
  • the upper part 8 of the valve stem 2 is provided with a thread, preferably a fine thread, and two nuts 9.
  • the maximum stroke of the valve is very small, about one to several hundredths of a millimeter. It is illustrated schematically in the drawing by dimension 10.
  • the stop which limits the maximum stroke 10, is formed by the outward projections 11 on the shaft 2 on the one hand and the inward projections 12 in the valve housing 1 on the other hand.
  • the valve stem 2 can be inserted into the valve housing 1 through corresponding recesses 13, which must be slightly larger than the projections 11, so that the projections 11 come to rest on the side of the projections 12 facing away from the valve disk 3.
  • the valve stem 2 is now rotated by 90 ° , so that the projections 11 on the valve stem 2 and the projections 12 in the valve housing 1 overlap in the axial direction and in this way result in the stroke limitation.
  • the plate spring 7 is used, which has an opening 14 for the flattened 15 upper part of the valve stem 2 and is also prevented by the pin 16 from rotating relative to the valve housing 1.
  • the pressure pipe coming from the injection pump (not shown) is connected in the bore 17, from there the fuel is supplied via the bore 18 to the annular groove 19 which is arranged in the valve stem 2.
  • the fuel is supplied to the annular groove 21 via the valve disk 3.
  • the number of grooves 20 to be carried out axially is to be selected so that the distribution on the circumference becomes sufficiently uniform.
  • the leak fuel is supplied to the leak fuel drain 24 via the bore 23.
  • FIG. 4 shows an embodiment according to the invention in which the upper contour of the inlet into the valve gap is rounded in contrast to the embodiment according to FIG. 1. In this way, the location of the highest fuel speed is moved in the vicinity of the exit of the jet, as a result of which a larger part of the pressure energy is converted into kinetic energy of the jet.
  • FIG. 5 differs from that of FIG. 1 in that the axially extending grooves between the annular grooves 19 and 25 are not continuous, but that axial grooves 26 and 27 are provided, which alternate from the upper annular groove 19 and the lower annular groove 25 go out and each end in front of the other annular groove.
  • the fuel is forced to take the path via the clearance between the valve stem 2 and the valve housing 21.
  • This game is dimensioned smaller than the maximum valve stroke 10, so that dirt particles are retained which could clog the valve gap.

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. Buse d'injection pour moteurs à combustion interne, en particulier pour moteurs Diesel, comportant une soupape à disque constituée par une tête de soupape (3) et une tige de soupape (2), et s'ouvrant avec une très faible course, sous l'effet de la pression du carburant, dans la direction du courant, la course (10) de la soupape à disque étant limitée par une butée, qui est prévue à proximité de la tête de soupape (3), et qui est formée par des saillies (11, 12), qui sont prévues sur la cage de soupape (1) vers l'intérieur et sur la tige de soupape (2) vers l'extérieur, les surfaces de contact situées en regard l'une de l'autre, de ces saillies (11, 12) étant distantes l'une de l'autre, lorsque la soupape est fermée, de la course (10) maximale désirée, buse d'injection caractérisée en ce que deux saillies radiales (12), prévues sur la cage de soupape (1), sont d'une seule pièce avec celle-ci et forment des évidements (13) dans la cage de soupape (1), et également deux saillies (11) prévues sur la tige de soupape (2) s'étendent, en étant diamétralement opposées, sur moins de 90 degrés, et le recouvrement axial de ces saillies (11, 12) après insertion de la tige de soupape (2) dans la cage de soupape (1) par les évidements (13), est obtenu en faisant tourner la tige de soupape (2).
2. Buse d'injection selon la revendication 1, caractérisée en ce que, à l'extrémité de la tige de soupape (2), située à l'opposé de la tête de soupape (3), sont prévus des ressorts à disques (6, 7), disposés coaxialement par rapport à la tige de soupape (2) et qui s'appuient d'une part sur la cage de soupape (1) et d'autre part sur des écrous (9) vissés sur la tige de soupape (2).
3. Buse d'injection selon la revendication 2, caractérisée en ce qu'un dispositif de sûreté, empêchant une rotation de la tige de soupape (2), est formé par la coopération d'un aplatissement (15) de la tige de soupape (2) et d'un évidement (14), lui correspondant, du ressort à disques (7), qui s'applique contre la cage de soupape (1), d'une part, et par une cheville (16) pour empêcher une rotation de ce ressort à disques (7) par rapport à la cage de soupape (1), d'autre part.
EP19870890095 1986-05-13 1987-05-12 Buse d'injection pour moteurs à combustion interne en particulier pour moteurs diesel Expired EP0246220B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
AT1277/86 1986-05-13
AT127786A AT395638B (de) 1986-05-13 1986-05-13 Einspritzduese fuer brennkraftmaschinen, insbesondere dieselmotoren

Publications (2)

Publication Number Publication Date
EP0246220A1 EP0246220A1 (fr) 1987-11-19
EP0246220B1 true EP0246220B1 (fr) 1989-09-27

Family

ID=3510402

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19870890095 Expired EP0246220B1 (fr) 1986-05-13 1987-05-12 Buse d'injection pour moteurs à combustion interne en particulier pour moteurs diesel

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EP (1) EP0246220B1 (fr)
AT (1) AT395638B (fr)
DE (1) DE3760630D1 (fr)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4034203C2 (de) * 1990-10-27 1995-02-09 Rinsum Cornelis Van Dipl Ing Kraftstoff-Einspritzdüse für Brennkraftmaschinen
DE4322313A1 (de) * 1993-07-05 1995-01-12 Kanis Paul Gerhard Dipl Ing Schwingstößeldüse
DE19719295A1 (de) * 1997-05-07 1998-11-12 Bosch Gmbh Robert Kraftstoffeinspritzventil für Brennkraftmaschinen
DE102006053556A1 (de) * 2006-11-14 2008-05-15 Purem Abgassysteme Gmbh & Co. Kg Vorrichtung zum Dosieren von Reduktionsmittel und Injektor in einer Vorrichtung zum Dosieren von Reduktionsmittel

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE475116C (de) * 1925-01-21 1929-04-19 Deckel Friedrich Verfahren und Vorrichtung zum Einspritzen von Brennstoff in Verbrennungskraftmaschinen
GB400539A (en) * 1932-05-21 1933-10-26 Bosch Robert Improvements in or relating to fuel injection nozzles for internal combustion engines
US1985289A (en) * 1932-07-18 1934-12-25 Aerol Engine Corp Injector for internal combustion engines
US2263197A (en) * 1939-03-08 1941-11-18 Eisemann Magneto Corp Fuel injection nozzle
GB539856A (en) * 1940-02-19 1941-09-26 Ex Cell O Corp Improvements in or relating to fuel-injection nozzles for internal-combustion engines
DE933003C (de) * 1954-03-19 1955-09-15 Rudolf Dipl-Ing Schenk Einspritzventil fuer Brennkraftmaschinen
DE1086487B (de) * 1955-03-22 1960-08-04 Borg Warner Kraftstoffeinspritzduese
FR1169811A (fr) * 1956-04-16 1959-01-06 Mowag Motorwagenfabrik Ag Gicleur
DE3139948A1 (de) * 1981-10-08 1983-04-28 Robert Bosch Gmbh, 7000 Stuttgart Kraftstoff-einspritzduese fuer brennkraftmaschinen
DE3410476A1 (de) * 1983-08-13 1985-02-21 Robert Bosch Gmbh, 7000 Stuttgart Kraftstoff-einspritzduese fuer brennkraftmaschinen

Also Published As

Publication number Publication date
AT395638B (de) 1993-02-25
DE3760630D1 (en) 1989-11-02
EP0246220A1 (fr) 1987-11-19
ATA127786A (de) 1992-06-15

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