EP1066466B1 - Unite cylindre-piston haute pression - Google Patents

Unite cylindre-piston haute pression Download PDF

Info

Publication number
EP1066466B1
EP1066466B1 EP99915701A EP99915701A EP1066466B1 EP 1066466 B1 EP1066466 B1 EP 1066466B1 EP 99915701 A EP99915701 A EP 99915701A EP 99915701 A EP99915701 A EP 99915701A EP 1066466 B1 EP1066466 B1 EP 1066466B1
Authority
EP
European Patent Office
Prior art keywords
grooves
piston
unit according
pressure unit
guide surface
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
EP99915701A
Other languages
German (de)
English (en)
Other versions
EP1066466A1 (fr
Inventor
Bernd Danckert
Rainer Von Bischopinck
Wolfgang Scheibe
Bernd Wagner
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.)
LOrange GmbH
Rolls Royce Solutions GmbH
Original Assignee
MTU Friedrichshafen GmbH
LOrange 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
Priority claimed from DE1998113454 external-priority patent/DE19813454B4/de
Priority claimed from DE1998120264 external-priority patent/DE19820264A1/de
Application filed by MTU Friedrichshafen GmbH, LOrange GmbH filed Critical MTU Friedrichshafen GmbH
Publication of EP1066466A1 publication Critical patent/EP1066466A1/fr
Application granted granted Critical
Publication of EP1066466B1 publication Critical patent/EP1066466B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

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
    • F02M47/00—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
    • F02M47/02—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure of accumulator-injector type, i.e. having fuel pressure of accumulator tending to open, and fuel pressure in other chamber tending to close, injection valves and having means for periodically releasing that closing pressure
    • F02M47/027—Electrically actuated valves draining the chamber to release the closing pressure
    • 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
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
    • 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
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
    • F02M59/442—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston means preventing fuel leakage around pump plunger, e.g. fluid barriers
    • 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
    • F02M61/12—Other injectors with elongated valve bodies, i.e. of needle-valve type characterised by the provision of guiding or centring means for valve bodies
    • 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

Definitions

  • the invention relates to a high-pressure piston-cylinder unit, in particular one Injection pump or an injection valve for an internal combustion engine, in particular for high number of lifting cycles, as provided in the preamble of claim 1.
  • a high-pressure piston-cylinder unit which has a large number of Lift cycles is exposed, as is particularly the case with an injection pump or a Injector for an internal combustion engine is generally a piston available, which is guided in a cylinder bore, and which a high Pressure difference is exposed.
  • the piston guided in the cylinder bore serves either the delivery of the fuel to be injected into the combustion chamber of the internal combustion engine, as in the case of an injection pump, or in the case of an injection valve, below Exposure to the fuel to be injected under high pressure Open the injector, typically by having the piston coupled or Nozzle needle formed in one piece from the valve seat of a needle valve takes off and thus an injection cross section for injecting the fuel into the Releases the combustion chamber of the internal combustion engine.
  • An injection valve for an internal combustion engine is known from DE 38 24 467 C2, at which the valve needle in two parts by a hollow needle and one in an inner bore the hollow needle guided valve needle is formed.
  • the hollow needle points in the area of Point a number of circumferential grooves, which in Longitudinal direction of the valve needle by a distance of about the order of magnitude Diameter of the valve needle are spaced and have a width and depth that correspond to about one tenth of the valve needle diameter.
  • EP 0 565 742 A1 describes methods for the fine machining of workpiece surfaces, in particular of walls of the bores in the cylinder of an internal combustion engine known in which the surface by blasting, in particular by means of a Lasers arranged according to a predetermined pattern are generated, which as Lubricant reservoir should serve.
  • EP 0 419 999 B1 describes a method for processing by friction highly stressed surfaces in internal combustion engines, especially the cylinder surfaces known from piston engines, in which the surface is honed and additionally one Laser beam treatment is subjected, the laser treatment for the evaporation of outstanding roughness peaks or scaling is used to make it smoother To reach surface.
  • WO 89/10479 describes a high-pressure piston-cylinder unit, in particular for one High pressure pump shown as an injection pump of a diesel engine.
  • the boundary gap between the piston surface area and expanded cylinder area is done in that one or more spaced circumferential grooves in the lateral surface of the Piston and / or in the cylinder surface. If the piston during the Operating in an eccentric position, it will be on the enlarged side Limit gap building pressure through the circumferential grooves on the entire circumference of the Limit gap distributed, whereby eccentric forces are avoided.
  • In one Exemplary embodiments are three in the region of the lateral surface of the printing edge spaced circumferential grooves or less. The grooves are obviously far apart. The disadvantage is that wear and tear and seizure are not prevented, since in the predominantly sliding surface areas of the piston no lubricating film is built up.
  • a high pressure fuel injection device is described in DE 41 39 907 A1, at which is a labyrinth seal in the form of ring grooves in the outer surface of a piston or is arranged in the inner wall surface of the cylinder bore associated with the piston.
  • a gap flow of this seal is to be reduced, it being disadvantageous that due to the seal, the access of fuel to the guide surfaces is reduced.
  • the object of the invention is to provide a high-pressure piston-cylinder unit, in particular for to specify an injection pump or an injection valve for an internal combustion engine, at which has a lower risk of wear on a guided in a cylinder bore Piston exists by deaxing.
  • the invention is intended to provide a method for producing such High pressure unit can be specified.
  • the invention provides a high-pressure piston-cylinder unit, in particular a Injection pump or an injection valve for an internal combustion engine, in particular for created a high number of lifting cycles, in which a guided in a cylinder bore Piston on one side a high pressure and thus a high pressure difference is exposed, according to the invention at least in a part of the guide surface of the Piston or the cylinder bore at a short distance from each other fine grooves are formed.
  • the grooves formed in the guide surface have a Width b from 5 to 100 ⁇ m. The distance between the grooves is 0.05 up to 1 mm.
  • An advantage of the guide surface of the piston designed according to the invention is that that there is a hydraulic pressure equalization on the circumference of the guide through the grooves and so that the one-sided contact of the piston in the cylinder bore is prevented or at least the contact forces are reduced.
  • Another advantage is that the Leakage flow after central alignment of the piston in the longitudinal direction of the Guide surface of the piston is reduced and thus the hydraulic efficiency of the Unity is improved.
  • a reduction in the leakage flow is also coming only because the grooves running transverse to the direction of the leakage flow act like a labyrinth seal.
  • Another advantage is that this is in the grooves fluid present wets the contact surfaces, whereby a lubrication effect is achieved.
  • the width b of the grooves is preferably between 10 and 40 ⁇ m.
  • the depth t of the grooves is advantageously between 3 to 50 microns, preferably between 10 to 30 microns.
  • the distance a between the grooves is preferably between 0.1 and 0.3 mm.
  • the width b corresponds to a groove in the essentially their depth t.
  • the ratio of the depth t of the groove to Nominal diameter D of the guide surface is between 1/200 and 1/1000.
  • the grooves in the circumferential direction are Guide surface designed to run.
  • the grooves can also be provided in the longitudinal direction Guide surface varying distance a be formed.
  • the grooves in Longitudinal direction of the guide surface are formed.
  • the grooves under are formed at an angle to the longitudinal direction of the guide surface.
  • the grooves can be arranged in the longitudinal direction of the Guide surface have varying slope.
  • the grooves are formed by a helix.
  • the helix can have a gradient varying in the longitudinal direction of the guide surface to have.
  • the grooves' at different angles to the longitudinal direction of the guide surface crosswise are progressive.
  • the grooves in one the high pressure side of the piston adjoining area of the guide surface are trained.
  • the grooves can extend over the entire area of the guide surface be trained.
  • the invention is of particular value in the case of a high-pressure piston-cylinder unit which Part of a fuel injector of a common rail injection system, in which the Piston is used to actuate the injector of the fuel injector, and wherein the Pressure difference permanently applied to the piston.
  • a permanent from The component subjected to fuel pressure can undergo constant deaxing, i.e. from the beginning the movement of the piston in the cylinder bore occur, which is why Invention here achieved a significant reduction in wear with particular advantage can be.
  • the piston is advantageously made of one piece of material on the nozzle needle of the injection valve, wherein the piston has a shoulder that is permanent is acted upon by the fuel pressure of the common rail injection system.
  • the grooves on which the fuel pressure is advantageous are advantageous acted shoulder adjoining, serving as a guide surface jacket surface of the Pistons trained.
  • the inventive method for manufacturing a high pressure unit of the invention it provides that the grooves are produced by machining, for example fine turning become.
  • An alternative method which is particularly advantageous, provides for the grooves to generate by beam processing.
  • Such beam processing is advantageously carried out in particular by laser engraving.
  • An advantageous development of the method according to the invention provides that after the grooves have been created, lapping or fine grinding the Guide surface is made. One can also create the grooves Fine machining of the guide surface must be upstream.
  • Figure 1 shows a view, partially in cross section, of the injector Fuel injector for a common rail fuel injection system.
  • the one with the Injection nozzle designated 1 has a needle housing 2, in which a cylinder bore 3 is provided.
  • a piston 5 is located in this cylinder bore 3 performed, which is integrally formed with a nozzle needle 4.
  • the nozzle needle 4 has a needle tip 8 which interacts with a valve seat 9.
  • an injection cross section 11 in the form of injection openings educated.
  • the fuel channel 7 leads to a High-pressure accumulator of the common rail system, in which fuel is to be injected is held under high pressure.
  • the Fuel injector via an actuating element, not shown in FIG. 1 electromechanical or hydraulic, as is well known, by which the piston 5 is released in the sense of an upward movement, so that in the Annulus 12 acting on the shoulder 6 of the piston 5 fuel pressure raising the Nozzle needle 4 and thus the needle tip 8 from the valve seat 9 and thus a release of the injection cross section 11.
  • the nozzle needle 4 is provided in one piece with the piston 5 shown enlarged.
  • the piston 5 has a nominal diameter D, which at the illustrated embodiment is 6.8 millimeters. From shoulder 6 and so from the fuel under high pressure in the annulus 12 acted side of the piston 5 ago over a length 1, the grooves 10 in Formed circumferentially on the lateral surface of the piston 5. In which In the illustrated embodiment, this length is 1, over which the grooves 10 approximately 22 mm are provided.
  • Figure 3 is a greatly enlarged cross section through the surface of the jacket of the Piston 5 shown, which shows two grooves 10.
  • the cross section of the grooves 10 has the illustrated embodiment has a substantially triangular shape.
  • the width b a groove is, for example, 5 to 100 microns, preferably between 10 to 40 microns. at the illustrated embodiment, the groove width b is 30 microns.
  • the groove depth t can be 3 to 50 microns, preferably between 10 to 30 microns. In the illustrated Embodiment is the depth t 15 microns.
  • the distance a between two grooves can between 0.05 to 1 mm, preferably between 0.1 to 0.5 mm, preferably between 0.1 to 0.3 mm. In the illustrated embodiment, the distance is a 0.2 mm.
  • the ratio of the depth t of the groove 10 to the nominal diameter D of the guide surface or of the piston 5 is advantageously between 1/200 and 1/1000. at the illustrated embodiment, the said ratio is around 1/450, which turns out to be has proven particularly advantageous.
  • the cross section of the grooves 10 can also have other shapes instead of a triangular shape assume, for example, a semicircular shape.
  • FIG. 4 again shows a representation corresponding to FIG. 2 and examples a) to d) of the Structuring the outer surface of the piston 5.
  • the grooves 10 are in the circumferential direction of the piston 5 formed, as shown in the side view above and also in Figure 2.
  • the grooves 10 can also with a in the longitudinal direction Guide surface varying distance a be formed.
  • the grooves 10 are in the longitudinal direction Guide surface designed to run.
  • the grooves 10 are closed at an angle Longitudinal direction of the guide surface.
  • the grooves 10 all have the same pitch.
  • the grooves 10 can also vary with a lengthways direction of the guide surface Slope should be provided.
  • the Grooves 10 may be formed by a helix.
  • a section of the guide surface with Grooves formed as a screw thread 22 are shown in FIG.
  • the Guide surface is a cylindrical piston surface, which of the threads of the Screw thread 22 is divided.
  • the pitch of the screw thread 22 is s specified.
  • the screw thread or the screw line can be catchy or also be multi-course.
  • the helix can be one in the longitudinal direction of the Guide surface constant slope or alternatively one in the longitudinal direction of the Guide surface have a varying slope.
  • the formation of the grooves as a helix is particularly advantageous in terms of manufacturing technology.
  • the grooves 10 can be at different angles to the longitudinal direction the guide surface may be designed to run crosswise, the angles opposite, but the same amount or different amount can. While in the illustrated embodiment the slope of the grooves 10 in In the longitudinal direction of the guide surface is the same, the grooves 10 can alternatively also with be designed in the longitudinal direction of the guide surface varying slope.
  • the structuring patterns according to FIGS. 4a) to 4d) are basic patterns, different ones However, patterns are also possible. Furthermore, several patterns according to the under Combined with reference to Figures 4a) to 4d) described type.
  • the distance a is the grooves 10 chosen in the longitudinal direction of the guide surface so that it is essentially the Operating stroke of the piston 5 in the cylinder bore 3 corresponds.
  • This has the beneficial Effect that the remaining guide surface on the jacket of the piston 5 between the grooves 10 is constantly moving on the wetted surfaces of the guide and thus Running dry the guide is made largely impossible.
  • a catchy Thread corresponds to the distance a between the grooves 10 then the thread pitch.
  • the grooves 10 can also be in the Cylinder bore 3 can be formed as a guide surface.
  • an injection valve for a common rail fuel injector is the one held by the pre-memory Fuel pressure via the fuel channel 7 and the annulus 12 permanently on the Shoulder 6 of the piston 5, so that the piston 5 permanently one-sided Pressure difference is exposed.
  • This has the advantage of that caused by the grooves 10 hydraulic pressure compensation and the reduction of leakage flow especially for Wear.
  • the invention leads to a corresponding advantage.
  • the grooves 10 in the guide surface of the piston that is to say in the lateral surface of the piston 5 or in the surface of the cylinder bore 3 by machining, for example by turning, fine turning, grinding or milling. alternative for this purpose, the grooves can pass through, in particular on the lateral surface of the piston 5 Beam processing are generated, in particular the method of laser engraving is advantageous.
  • the grooves 10 are produced after the finishing (grinding) of the Guide surface. After the creation of the grooves 10, a lapping or Fine grinding the guide surface made to the final surface of the Manufacture guide surface. Finishing the guide surface before creating it the grooves can also be omitted if there is adequate dimensional accuracy through suitable Manufacturing measures can be guaranteed.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Superconductors And Manufacturing Methods Therefor (AREA)
  • Pens And Brushes (AREA)
  • Glass Compositions (AREA)

Claims (28)

  1. Unité cylindre-piston à haute pression, en particulier d'une pompe d'injection ou d'une soupape d'injection pour un moteur à combustion interne, en particulier pour des régimes élevés, avec un piston (5) guidé dans un alésage de cylindre (3) et couplé à un organe de commande, qui est soumis à une différence de pression élevée, dans laquelle des gorges (10) sont formées au moins dans une partie de la surface de guidage du piston (5), notamment dans la surface latérale du piston (5) ou de l'alésage de cylindre (3), caractérisée en ce que les gorges (10) présentent une largeur b comprise entre 5 et 100 µm et sont situées à une distance a comprise entre 0,05 et 1 mm l'une de l'autre.
  2. Unité à haute pression suivant la revendication 1, caractérisée en ce que les gorges (10) présentent une largeur b comprise entre 10 et 40 µm.
  3. Unité à haute pression suivant la revendication 1 ou 2, caractérisée en ce que les gorges (10) présentent une profondeur t comprise entre 3 et 50 µm, de préférence entre 10 et 30 µm.
  4. Unité à haute pression suivant une revendication 1, 2 ou 3, caractérisée en ce que les gorges (10) présentent une distance a comprise entre 0,1 et 0,5 mm, de préférence entre 0,1 et 0,3 mm.
  5. Unité à haute pression suivant l'une quelconque des revendications 1 à 4, caractérisée en ce que la largeur b d'une gorge (10) correspond sensiblement à sa profondeur t.
  6. Unité à haute pression suivant l'une quelconque des revendications 1 à 5, caractérisée en ce que le rapport de la profondeur t de la gorge (10) au diamètre nominal D de la surface de guidage est compris entre 1/200 et 1/1000.
  7. Unité à haute pression suivant l'une quelconque des revendications 1 à 6, caractérisée en ce que les gorges (10) sont orientées dans le sens périphérique de la surface de guidage.
  8. Unité à haute pression suivant la revendication 7, caractérisée en ce que les gorges (10) sont formées avec une distance a variable dans le sens longitudinal de la surface de guidage.
  9. Unité à haute pression suivant l'une quelconque des revendications 1 à 6, caractérisée en ce que les gorges (10) sont orientées dans le sens longitudinal de la surface de guidage.
  10. Unité à haute pression suivant l'une quelconque des revendications 1 à 6, caractérisée en ce que les gorges (10) sont orientées en oblique par rapport au sens longitudinal de la surface de guidage.
  11. Unité à haute pression suivant la revendication 10, caractérisée en ce que les gorges (10) présentent une pente variable dans le sens longitudinal de la surface de guidage.
  12. Unité à haute pression suivant l'une quelconque des revendications 1 à 6, caractérisée en ce que les gorges (10) sont formées par une ligne hélicoïdale tournant à gauche ou à droite.
  13. Unité à haute pression suivant la revendication 12, caractérisée en ce que la ligne hélicoïdale a plusieurs entrées.
  14. Unité à haute pression suivant la revendication 12 ou 13, caractérisée en ce que la ligne hélicoïdale a une pente variable dans le sens longitudinal de la surface de guidage.
  15. Unité à haute pression suivant l'une quelconque des revendications 1 à 6, caractérisée en ce que des gorges (10) sont orientées en se croisant sous différents angles par rapport au sens longitudinal de la surface de guidage.
  16. Unité à haute pression suivant la revendication 15, caractérisée en ce que les gorges (10) sont formées avec une pente variable dans le sens longitudinal de la surface de guidage.
  17. Unité à haute pression suivant l'une quelconque des revendications 7 à 16, caractérisée en ce que la distance a des gorges (10) dans le sens longitudinal de la surface de guidage correspond sensiblement à la course utile du piston (5) dans l'alésage de cylindre (3).
  18. Unité à haute pression suivant l'une quelconque des revendications 1 à 6, caractérisée en ce que les gorges (10) sont formées par une combinaison de plusieurs motifs suivant les revendications 7 à 16.
  19. Unité à haute pression suivant l'une quelconque des revendications 1 à 18, caractérisée en ce que les gorges (10) sont formées dans une région de la surface de guidage se raccordant au côté de haute pression du piston (5).
  20. Unité à haute pression suivant l'une quelconque des revendications 1 à 18, caractérisée en ce que les gorges (10) sont formées sur toute la région de la surface de guidage.
  21. Unité à haute pression suivant l'une quelconque des revendications 1 à 20, caractérisée en ce que l'unité cylindre-piston à haute pression est une partie d'un injecteur de carburant d'un système d'injection Common Rail, dans laquelle le piston (5) sert à actionner la soupape d'injection de l'injecteur de carburant, et dans laquelle la différence de pression est appliquée en permanence sur le piston (5).
  22. Unité à haute pression suivant la revendication 21, caractérisée en ce que le piston (5) est formé d'une seule matière sur le pointeau (4) de la soupape d'injection, dans laquelle le piston (5) présente un épaulement (6), qui est soumis en permanence à la pression de carburant du système d'injection Common Rail.
  23. Unité à haute pression suivant la revendication 22, caractérisée en ce que les gorges (10) sont formées sur la surface latérale du piston (5) servant de surface de guidage, se raccordant à l'épaulement (6) soumis à la pression de carburant.
  24. Procédé pour la fabrication d'une unité à haute pression suivant l'une quelconque des revendications 1 à 23, caractérisé en ce que les gorges (10) sont produites par un usinage avec enlèvement de matière, en particulier par tournage, tournage de précision, meulage ou fraisage.
  25. Procédé pour la fabrication d'une unité à haute pression suivant l'une quelconque des revendications 1 à 23, caractérisé en ce que les gorges (10) sont produites par usinage avec un faisceau, en particulier un faisceau laser ou un faisceau d'électrons.
  26. Procédé suivant la revendication 25, caractérisé en ce que les gorges (10) sont produites par gravure au laser.
  27. Procédé suivant une revendication 24, 25 ou 26, caractérisé en ce qu'après la production des gorges (10), on effectue un rodage ou un meulage de précision de la surface de guidage.
  28. Procédé suivant la revendication 27, caractérisé en ce que la production des gorges (10) est précédée par un usinage de précision de la surface de guidage.
EP99915701A 1998-03-26 1999-03-24 Unite cylindre-piston haute pression Expired - Lifetime EP1066466B1 (fr)

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
DE19813454 1998-03-26
DE1998113454 DE19813454B4 (de) 1998-03-26 1998-03-26 Hochdruck-Kolbenzylindereinheit für hohe Hubzyklen
DE1998120264 DE19820264A1 (de) 1998-05-07 1998-05-07 Hochdruck-Kolbenzylindereinheit
DE19820264 1998-05-07
PCT/EP1999/002010 WO1999049209A1 (fr) 1998-03-26 1999-03-24 Unite cylindre-piston haute pression

Publications (2)

Publication Number Publication Date
EP1066466A1 EP1066466A1 (fr) 2001-01-10
EP1066466B1 true EP1066466B1 (fr) 2002-10-16

Family

ID=26044996

Family Applications (1)

Application Number Title Priority Date Filing Date
EP99915701A Expired - Lifetime EP1066466B1 (fr) 1998-03-26 1999-03-24 Unite cylindre-piston haute pression

Country Status (5)

Country Link
US (1) US6477940B1 (fr)
EP (1) EP1066466B1 (fr)
AT (1) ATE226279T1 (fr)
DE (1) DE59903092D1 (fr)
WO (1) WO1999049209A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102011051904A1 (de) 2011-07-18 2012-06-21 L'orange Gmbh Vorrichtung mit in einer Führungsbahn längsverschieblicher Hubstange

Families Citing this family (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19843344A1 (de) * 1998-09-22 2000-03-23 Bosch Gmbh Robert Kraftstoffeinspritzventil für Brennkraftmaschinen
DE10024854C2 (de) * 2000-05-19 2002-11-28 Siemens Ag Ventilnadel und Ventilsteuerkolben von Injektoren
DE10046323B4 (de) * 2000-09-19 2004-02-12 Siemens Ag Hydraulisches Spielausgleichssystem
DE10232050A1 (de) * 2002-07-16 2004-02-05 Robert Bosch Gmbh Kraftstoffeinspritzventil für Brennkraftmaschinen
EP1469187B1 (fr) * 2003-04-16 2006-10-04 Siemens Aktiengesellschaft Ensemble de soupape a pointeau et procédé pour le réaliser
KR101307563B1 (ko) * 2003-07-16 2013-09-12 베르트질레 슈바이츠 악티엔게젤샤프트 실린더부 내의 고압 피스톤용 피스톤
JP4066959B2 (ja) * 2004-01-27 2008-03-26 株式会社デンソー 燃料噴射装置
DE102005011574A1 (de) * 2005-03-14 2006-09-21 Robert Bosch Gmbh Zwischenelement für ein Brennstoffeinspritzventil
US7487844B2 (en) * 2005-11-04 2009-02-10 Robert Bosch Gmbh Drill with solid state speed control
JP2008057458A (ja) * 2006-08-31 2008-03-13 Mitsubishi Heavy Ind Ltd 燃料噴射弁
DE102009000181A1 (de) * 2009-01-13 2010-07-15 Robert Bosch Gmbh Kraftstoff-Injektor
DE102011090148B4 (de) 2011-12-30 2017-06-01 Continental Automotive Gmbh Verfahren zur Herstellung einer Düsennadel für einen Injektor zur Einspritzung von Kraftstoff in Zylinderbrennräume einer Brennkraftmaschine und Injektor mit solch einer Düsennadel
JP6660548B2 (ja) * 2015-07-23 2020-03-11 住友ゴム工業株式会社 医療用注射器、注射器に適用されるガスケットおよびその製造方法
DE102016207171A1 (de) 2016-04-27 2017-11-02 Robert Bosch Gmbh Hochdruckpumpe mit vermindertem Verschleiß
EP3464874B1 (fr) 2016-05-25 2020-11-18 Wärtsilä Finland Oy Unité de soupape d'injection de carburant pour moteur à piston à combustion interne et procédé d'exploitation de ladite unité
IT201700054112A1 (it) * 2017-05-18 2018-11-18 Bosch Gmbh Robert Gruppo pompa per l'alimentazione di carburante ad un motore a combustione interna
KR102268258B1 (ko) * 2019-11-08 2021-06-23 엘지전자 주식회사 압축기 및 그 제조방법

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3398936A (en) * 1966-08-02 1968-08-27 Curtiss Wright Corp Fuel injection pintle
US3425635A (en) * 1967-02-15 1969-02-04 Int Harvester Co Fuel injection nozzle
US3722801A (en) * 1970-09-11 1973-03-27 Stanadyne Inc Fuel injector
WO1989010479A1 (fr) * 1988-04-22 1989-11-02 Hei-Tech B.V. Unite de cylindre et piston a haute pression
DE3824467A1 (de) 1988-07-19 1990-01-25 Man B & W Diesel Ag Einspritzventil
DE3932328A1 (de) 1989-09-28 1991-04-11 Opel Adam Ag Verfahren zur bearbeitung von durch reibung hochbeanspruchten flaechen in brennkraftmaschinen und vorrichtung zur durchfuehrung des verfahrens
DE4139907A1 (de) * 1991-12-04 1993-06-09 Robert Bosch Gmbh, 7000 Stuttgart, De Hochdruckkraftstoffeinspritzeinrichtung
DE59201549D1 (de) 1992-04-11 1995-04-06 Gehring Gmbh & Co Maschf Verfahren zur Feinbearbeitung von Werkstück-Oberflächen.
JP3159593B2 (ja) * 1994-02-28 2001-04-23 三菱電機株式会社 レーザ加工方法及びその装置
IT1276503B1 (it) * 1995-07-14 1997-10-31 Elasis Sistema Ricerca Fiat Perfezionamenti ad una valvola di dosaggio a comando elettromagnetico, per un iniettore di combustibile.

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102011051904A1 (de) 2011-07-18 2012-06-21 L'orange Gmbh Vorrichtung mit in einer Führungsbahn längsverschieblicher Hubstange

Also Published As

Publication number Publication date
US6477940B1 (en) 2002-11-12
EP1066466A1 (fr) 2001-01-10
DE59903092D1 (de) 2002-11-21
ATE226279T1 (de) 2002-11-15
WO1999049209A1 (fr) 1999-09-30

Similar Documents

Publication Publication Date Title
EP1066466B1 (fr) Unite cylindre-piston haute pression
EP1911986B1 (fr) Palier lisse hydrodynamique
EP2683955B9 (fr) Coquille de coussinet lisse
EP1546547B1 (fr) Soupape d'injection de carburant pour moteurs a combustion interne
WO2005052358A1 (fr) Soupape, notamment pour une pompe a haute pression d'un systeme d'injection de carburant pour moteur a combustion interne
DE2756878A1 (de) Kolben, insbesondere fuer brennkraftmaschinen, wie hochgeschwindigkeits-dieselmotoren sowie verfahren zu seiner herstellung
DE10151518A1 (de) Verriegelungsmechanismus I für eine Pleuelstange mit variablem Verdichtungsverhältnis
EP1527276B1 (fr) Soupape d'injection de carburant pour moteurs a combustion
EP2814636B1 (fr) Procédé permettant d'augmenter la résistance d'arbres, notamment de vilebrequins
DE102011055871A1 (de) Kraftstoffversorgungspumpe und Verfahren zur Herstellung eines Gehäuses für diese
DE10151507A1 (de) Hydraulikkreis zum Entriegeln von Verriegelungsmechanismen für Pleuelstangen mit variablem Verdichtungsverhältnis
DE19820264A1 (de) Hochdruck-Kolbenzylindereinheit
DE69921242T2 (de) Kraftstoffeinspritzventil
DE102005059031A1 (de) Radialkolben-Hochdruckpumpe einer Einspritzanlage zum Einspritzen eines flüssigen Brennstoffs
DE10346075B4 (de) Verfahren zur Herstellung eines Kraftstoffeinspritzventils und nach diesem Verfahren hergestelltes Kraftstoffeinspritzventil
WO1989010479A1 (fr) Unite de cylindre et piston a haute pression
DE102005061781A1 (de) Injektor eines Kraftstoff-Einspritzsystems
WO2008101749A1 (fr) Pompe à haute pression pour transporter du carburant avec un guidage amélioré du piston de pompe
DE10127389B4 (de) Hydrostatisches Fluidlager mit Zellen und Verfahren zu seiner Herstellung
DE10249818A1 (de) Oberfläche eines Körpers, auf dem ein anderer Körper in einer bevorzugten Gleitrichtung gegeneinander gleitend anordenbar ist
EP1518050B1 (fr) Injecteur pour un systeme d'injection
DE4108272C2 (de) Kolbenschieberventil
EP1642023B1 (fr) Raccordement pour espaces haute pression d'injecteurs de carburant
WO2019081238A1 (fr) Poussoir, en particulier poussoir à galets, pour une pompe et pompe comprenant un poussoir
DE19843912B4 (de) Kraftstoffeinspritzdüse

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20000907

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AT CH DE FR GB IT LI

17Q First examination report despatched

Effective date: 20010711

RAP1 Party data changed (applicant data changed or rights of an application transferred)

Owner name: L'ORANGE GMBH

Owner name: MTU FRIEDRICHSHAFEN GMBH

GRAG Despatch of communication of intention to grant

Free format text: ORIGINAL CODE: EPIDOS AGRA

GRAG Despatch of communication of intention to grant

Free format text: ORIGINAL CODE: EPIDOS AGRA

GRAH Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOS IGRA

GRAH Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOS IGRA

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AT CH DE FR GB IT LI

REF Corresponds to:

Ref document number: 226279

Country of ref document: AT

Date of ref document: 20021115

Kind code of ref document: T

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

REG Reference to a national code

Ref country code: CH

Ref legal event code: NV

Representative=s name: ISLER & PEDRAZZINI AG

Ref country code: CH

Ref legal event code: EP

REF Corresponds to:

Ref document number: 59903092

Country of ref document: DE

Date of ref document: 20021121

GBT Gb: translation of ep patent filed (gb section 77(6)(a)/1977)

Effective date: 20030128

ET Fr: translation filed
PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed

Effective date: 20030717

REG Reference to a national code

Ref country code: CH

Ref legal event code: PCAR

Free format text: ISLER & PEDRAZZINI AG;POSTFACH 1772;8027 ZUERICH (CH)

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 18

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 19

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 20

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 20180321

Year of fee payment: 20

Ref country code: CH

Payment date: 20180321

Year of fee payment: 20

Ref country code: DE

Payment date: 20180322

Year of fee payment: 20

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: AT

Payment date: 20180322

Year of fee payment: 20

Ref country code: FR

Payment date: 20180323

Year of fee payment: 20

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: IT

Payment date: 20180327

Year of fee payment: 20

REG Reference to a national code

Ref country code: DE

Ref legal event code: R082

Ref document number: 59903092

Country of ref document: DE

Representative=s name: FISH & RICHARDSON P.C., DE

Ref country code: DE

Ref legal event code: R081

Ref document number: 59903092

Country of ref document: DE

Owner name: WOODWARD L'ORANGE GMBH, DE

Free format text: FORMER OWNERS: MTU FRIEDRICHSHAFEN GMBH, 88045 FRIEDRICHSHAFEN, DE; L'ORANGE GMBH, 70435 STUTTGART, DE

REG Reference to a national code

Ref country code: DE

Ref legal event code: R082

Ref document number: 59903092

Country of ref document: DE

Representative=s name: FISH & RICHARDSON P.C., DE

Ref country code: DE

Ref legal event code: R081

Ref document number: 59903092

Country of ref document: DE

Owner name: WOODWARD L'ORANGE GMBH, DE

Free format text: FORMER OWNER: L'ORANGE GMBH, 70435 STUTTGART, DE

REG Reference to a national code

Ref country code: DE

Ref legal event code: R071

Ref document number: 59903092

Country of ref document: DE

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

REG Reference to a national code

Ref country code: GB

Ref legal event code: PE20

Expiry date: 20190323

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF EXPIRATION OF PROTECTION

Effective date: 20190323

REG Reference to a national code

Ref country code: AT

Ref legal event code: MK07

Ref document number: 226279

Country of ref document: AT

Kind code of ref document: T

Effective date: 20190324