EP2450556A2 - Agencement de raccordement pour une conduite de carburant tubulaire - Google Patents

Agencement de raccordement pour une conduite de carburant tubulaire Download PDF

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Publication number
EP2450556A2
EP2450556A2 EP20110008856 EP11008856A EP2450556A2 EP 2450556 A2 EP2450556 A2 EP 2450556A2 EP 20110008856 EP20110008856 EP 20110008856 EP 11008856 A EP11008856 A EP 11008856A EP 2450556 A2 EP2450556 A2 EP 2450556A2
Authority
EP
European Patent Office
Prior art keywords
sealing
fuel line
wall
channel
pressure
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.)
Granted
Application number
EP20110008856
Other languages
German (de)
English (en)
Other versions
EP2450556B1 (fr
EP2450556A3 (fr
Inventor
Hans-Jürgen Guido
Jürgen Ernst
Herrmann Wild
Original Assignee
Maschinenfabrik Guido 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 Maschinenfabrik Guido GmbH filed Critical Maschinenfabrik Guido GmbH
Publication of EP2450556A2 publication Critical patent/EP2450556A2/fr
Publication of EP2450556A3 publication Critical patent/EP2450556A3/fr
Application granted granted Critical
Publication of EP2450556B1 publication Critical patent/EP2450556B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • F02M55/00—Fuel-injection apparatus characterised by their fuel conduits or their venting means; Arrangements of conduits between fuel tank and pump F02M37/00
    • F02M55/002—Arrangement of leakage or drain conduits in or from 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
    • F02M55/00—Fuel-injection apparatus characterised by their fuel conduits or their venting means; Arrangements of conduits between fuel tank and pump F02M37/00
    • F02M55/004—Joints; Sealings
    • F02M55/005—Joints; Sealings for high pressure conduits, e.g. connected to pump outlet or to injector inlet
    • 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
    • F02M55/00—Fuel-injection apparatus characterised by their fuel conduits or their venting means; Arrangements of conduits between fuel tank and pump F02M37/00
    • F02M55/02—Conduits between injection pumps and injectors, e.g. conduits between pump and common-rail or conduits between common-rail and 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
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/16—Sealing of fuel injection apparatus not otherwise provided for
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/9029—With coupling

Definitions

  • the invention relates to a connection arrangement for a tubular fuel line referred to in the preamble of claim 1 Art.
  • This pressure transmission arrangement consists of two parts surrounding the fuel line coaxially, namely a pressure ring immediately adjacent to a pressure receiving surface of the pressure nipple and a pressure tube bridging the distance between the pressure ring and the union screw element in the assembled state.
  • the known Matterschraubelement an elongated shaft which protrudes in the fully screwed and tightened state from the input port of the channel to the outside and there carries an external thread on which a nut sits, by turning on a the input port of the channel on the Outside of the cylinder head surrounding, flat contact surface in the axial direction to or can be moved away from it. Between the contact surface and the flat side of the nut facing it, an annular sealing disc is arranged on the shaft of the union screw element, which is pressed against the contact surface when the nut is tightened when the screw element is completely screwed in.
  • the inner diameter of the sealing washer must be significantly larger than the outer diameter of the shaft of the union screw, so that the sealing washer when tightening the nut on the external thread of the shaft to the contact surface of the cylinder head can move, a further annular sealing element is required, which between the nut and the external thread of the shaft is arranged.
  • This known sealing arrangement has a number of disadvantages. It requires a pre-assembly of Studentsschraubelements on which first the nut screwed together with the intermediate annular sealing element and then the sealing washer must be postponed before the assembly thus formed can be positioned on the fuel line. If the fuel line is then introduced into the channel of the cylinder head until the pressure nipple is seated on the counter-sealing surface of the nozzle holder and the coupling screw element is tightened, the nut seated on the shaft of the coupling screw element must additionally be tightened in order to achieve a tight closure of the inlet opening of the channel. In this case, provided between the nut and the external thread of the shaft sealing element complicates both the initial unscrewing of the nut on the shaft as well as their final tightening.
  • the invention has the object, a connection arrangement of the type mentioned in such a way that with less and simpler parts and significantly simplified installation a sufficient requirements all sealing the fuel pipe receiving channel in the cylinder head can be achieved.
  • the entire sealing arrangement according to the invention is no longer located outside the channel but in its interior, its individual elements can be designed and matched to one another so that the compression of the sealing elements required for good, even high pressures is sufficient can be achieved by tightening the fürsch screw.
  • the use and operation of another element to be tightened, as it is the mother of the known arrangement, are not required.
  • a further advantage of positioning the sealing arrangement according to the invention is that the parts of the connection arrangement located outside the cylinder head in the assembled state have a very simple surface structure with a minimum of projections and recesses, so that the risk of permanent dirt accumulation in this area is reduced and Any necessary cleaning can be carried out easily and efficiently.
  • the entire sealing is carried out by means of a single, approximately hollow cylindrical sealing sleeve coaxially surrounding the tube of the fuel line and either between the union screw and the pressure tube is arranged so that it produced when screwing the former into the internal thread of the channel Transferring force to the pressure tube, which then passes on the pressure ring on the pressure nipple so that it is pressed with its pressure surface against the counter-pressure surface of the nozzle holder.
  • the hollow cylindrical, the tube of the fuel pipe coaxially surrounding the sealing sleeve between the inwardly directed nozzle holder towards the axial end of the pressure tube and the pressure nipple of the fuel line can be arranged by the Antikrohr when screwing the Matterschraubelements directly on the outwardly directed axial force exerted force and passes on the pressure nipple of the fuel line directly or via an interposed pressure ring.
  • Another possibility is to provide two such sealing sleeves, one of which is positioned between the union screw and the pressure tube and the other between the pressure tube and the pressure nipple. This is particularly important if the channel in the cylinder head, through which the pressure tube extends, is cut by a transverse bore bridged in the assembled state by the pressure tube, which connects the hollow spaces of the cylinder head filled with engine oil.
  • the two sealing sleeves then prevent this engine oil can pass through the above-mentioned clearances between the outer surface of the fuel line and the pressure transmission assembly on the one hand and the pressure transmission assembly and the inner wall of the channel on the other hand to the outside or to the nozzle holder.
  • At least one or each of the sealing sleeves in the transition region between its one axial end face and its outer peripheral wall has a first fold and in the transition region between its other axial end face and its inner peripheral wall on a second fold.
  • a sealing ring made of an elastomeric material is used, which protrudes initially over the respective front end in the axial direction, and whose radial thickness is dimensioned so that it does not so long on assembly on the inner wall of the channel or on the outer wall of the tubular fuel line comes to rest, as long as no axially directed force is exerted on him.
  • the union screw element is screwed and tightened so far into the channel, that the sealing sleeve is pressed by the inwardly facing end of the projecting into the channel tube section against the nozzle holder remote from the front end of the pressure tube, the sealing rings seated in the two folds are compressed in the axial direction and thereby simultaneously expand in the radial direction so far from that they come to both the sealing sleeve and on the inner wall of the channel or the outer wall of the tubular fuel pipe to a tight contact, thereby sealing the two spaces mentioned above tight.
  • a significant advantage of the arrangements described is that during assembly no frictional forces between the sealing rings and the inner wall of the channel or the outer wall of the tubular fuel line must be overcome, because these parts come into contact only during the final tightening of the Matterschraubelements. As a result, the assembly of such a trained connection arrangement is greatly facilitated
  • a further sealing arrangement which comprises at least one ring disk package, which consists of a rigid material of at least two circular annular disks concentrically surrounding the fuel line, one of which has an inner diameter slightly larger than the outer diameter the fuel line is, and carries on its outer circumference a sealing ring made of an elastomeric material, which initially protrudes in the axial direction over the two end faces of the annular disc and the radial thickness is dimensioned so that it initially not on assembly on the inner wall of the channel during assembly comes.
  • the second annular disc whose outer diameter is slightly smaller than the inner diameter of the channel and surrounding the fuel line in its central opening carries a sealing ring made of an elastomeric material, which initially protrudes in the axial direction over the two end faces of the annular disc and its radial Thickness is such that it initially does not come to the outer wall of the fuel line during assembly to plant.
  • ring disk packages can be used which comprise more than two such annular disks, in which case an annular disk of the former type then alternately follows in the axial direction of an annular disk of the second type.
  • the two or more sealing rings are compressed in the axial direction and so enlarged at the same time in the radial direction so that the required sealing of the free spaces between the outer wall of the fuel line and the pressure tube on the one hand and the pressure tube and the inner wall of the channel on the other hand when final tightening the Mattersch screw is achieved.
  • annular disc pact which is arranged either between the union screw and the pressure tube or between the pressure tube and the sealing nipple, as above for the inventive Sealing sleeves has been described.
  • two sets of annular disks one of which is positioned in the axial direction outside and the other in the axial direction inside the pressure tube. The latter is, but not limited to, particularly favorable again in those cases in which the channel formed in the cylinder head is cut by an oil-carrying bore.
  • a sealing sleeve coaxially surrounding the fuel line has only one or more peripheral grooves in its outer cylindrical surface, in each of which a sealing ring made of an elastomeric material is inserted.
  • the sealing of the free space between the fuel line and the pressure tube here assumes a hollow cylindrical sealing body made of an elastomeric material which is inserted into the inwardly facing end portion of the inner bore of the Matterschraubelements having an enlarged inner diameter to provide space for the hollow cylindrical sealing body. This surrounds the fuel line coaxial and at the time of assembly to her initially not to the plant, so that no significant frictional forces must be overcome during assembly.
  • the sealing body initially projects beyond the end face of the coupling screw element facing the sealing sleeve and is compressed in the axial direction when it is tightened by the end face of the sealing sleeve facing it.
  • its wall thickness increases in the radial direction, so that it comes to the fuel line as well as on the inner wall of the extended end portion of the inner bore of the union screw good sealing to the plant.
  • all sealing effects are automatically achieved when tightening the Matterschraubettis without additional work or assembly steps are required.
  • sealing sleeves and annular disc packs can be combined with one another, in particular if one of them is positioned axially in front of and axially behind the pressure tube.
  • two or more identical or different sealing devices can be either only axially forward or axially be used behind the pressure tube.
  • hermetic sealing of the fuel pipe receiving channel is carried out against the outside world. But it may be desirable to make the arrangement so that in the channel from the nozzle holder forth incoming fluid, such as fuel can be removed, as in the U.S. Patent 3,845,748 is shown.
  • connection arrangement in order to realize such an arrangement, in a further variant of the connection arrangement according to the invention, the above-mentioned sealing sleeve and annular disks are omitted, so that during assembly the inwardly directed front end of the Matterschraubelements acts directly on the nozzle holder remote from the front end of the pressure tube.
  • an initially slightly projecting, hollow cylindrical sealing body made of an elastomeric material is used, which during assembly on the end face facing the Antikrohrs comes to rest and is compressed when tightening the Matterschraubelements in the manner described above in the longitudinal direction, so that its wall thickness increases in the radial direction and it closes the free space between the outer surface of the fuel line and the inner wall of the pressure tube against the Au ⁇ enseite the cylinder head.
  • the sealing of the free space between the outer surface of the pressure tube and the inner wall of the fuel line receiving channel is effected by a sealing ring inserted in a groove in the outer surface of the shank of the cap screw of elastomeric material, in the assembled state in the axial direction on the input to the opening facing side of the internal thread of the channel is arranged. Between this sealing ring and the internal thread, which does not form a tight seal, an annular free space is formed, from which a fluid penetrating from the nozzle holder into the channel can be sucked off.
  • Fig. 1 is a schematic section through a portion of a cylinder head 1 is shown, which has a vertically extending first bore into which from above a partially reproduced injector or nozzle holder 2 is inserted, in the known manner, a nozzle for injecting fuel into the Combustion chamber of the cylinder in question is added.
  • Fuel line 5 Perpendicular to the first bore extends through the cylinder head, a further horizontal bore with an approximately circular cross-section, which forms an opening from an opening to the outside inlet opening 3 to the nozzle holder 2 channel 4, in the left of a tube formed by Fuel line 5 is inserted, which serves to supply the injection nozzle arranged in the nozzle holder 2 under high pressure fuel.
  • the fuel line 5 has at its end facing the nozzle holder 2, a duck nipple 6, for example, produced by upsetting, which with a sealing surface 8 formed on a nozzle holder 2, hollow conical mating surface 10 is applied, which surrounds the mouth of a further in the nozzle holder 2 fuel flow channel.
  • the pressure nipple 6 On its axially opposite side of the sealing surface 8, the pressure nipple 6 has a shoulder 11, which forms a pressure-receiving surface in that it protrudes radially beyond the outer surface of the fuel line 5, to which a contact force is transmitted by means of a pressure transmission arrangement coaxially surrounding the fuel line 5, which is produced by a screw-threaded element 15 formed by a pressure screw being screwed into an internal thread 16 of a section of the channel 4 directly adjoining the inlet opening 3, so that a pipe section 17 of the screw-connecting screw element 15 protruding into the channel 4 is first attached to it facing front end of the pressure transfer assembly comes to rest and then moves in the direction of the nozzle holder 2 back .
  • the pressure transmission assembly consists of a in the mounted state on the pressure receiving surface of the shoulder 11 supporting, substantially hollow cylindrical pressure ring 18, a subsequent thereto hollow cylindrical pressure tube 19, which bridges most of the length of the channel 4, and a hollow cylindrical sealing sleeve 20 against which abuts the inner end face of the pipe section 17 of the union screw 15.
  • the pressure nipple 6 is first upset on the pipe forming it, whereupon the individual parts of the pressure transmission arrangement are then pushed from the not yet deformed end to which then in general also a pressure or sealing nipple is upset.
  • each of these components must be slightly larger than the outer diameter of the fuel line 5, whereby between these components a continuous, hollow cylindrical space 21 is present, which is a very owns small clear width and because of that for the Fig.1 selected scale in this not directly visible but only indicated by the end point of the reference line.
  • the inner diameter of the channel 4 must be greater than the outer diameter of the pressure ring 18 and the pressure tube 19, so that the fuel line surrounded by these components can be inserted into the channel 4.
  • the resulting hollow cylindrical space 22 must be much larger than the space 21 to allow for mounting.
  • the two mentioned clearances 21, 22 must be sealed to the outside, to prevent both the leakage of leakage fuel and / or engine oil, which could penetrate into it from the engine, and on the other hand, the ingress of moisture from the outside space.
  • the actual sealing function is adopted by three sealing rings 24, 25 and 26, which consist of an elastic material resistant to engine oil and fuel and of which the former in a in the wall of the sealing sleeve 20 approximately in the middle of its axial length from the outside her incorporated, is arranged around the circumference extending groove, while the other two sit in grooves which are incorporated into the wall of the sealing sleeve 20 from the inside with approximately equal axial distances from the center of the axial length of the sealing sleeve 20.
  • two or more grooves with sealing elements arranged in them and only one or more than two grooves with sealing elements arranged therein may be provided in the inside of the wall of the sealing sleeve 20.
  • Fig. 2 is one of the fig1 , corresponding section through a cylinder head 1, which encloses a valve chamber 7, from which a motor oil leading, the channel 4 intersecting transverse bore 9 leads to another (not shown) cavity of the cylinder head 1.
  • the sealing arrangement according to the invention comprises two sealing sleeves 20, 20 'of the associated Fig. 1 described type, one of which is arranged between the inwardly facing end face of the union screw 15 and the outwardly directed axial end face of the pressure tube 19 and the other between the inner, pointing to the nozzle holder 1 front end of the pressure tube 19 and the pressure ring 18.
  • FIG. 3 is only a part of one of the Fig. 1 reproduced similar section through a further embodiment, in which the union screw 15 is not yet completely screwed into the internal thread 16 of the channel 4 and therefore not with its inner end face on the tubular fuel pipe 5 concentrically surrounding sealing sleeve 28 is applied, here in principle the same function has like the sealing sleeve 20 from in conjunction with Fig. 1 described embodiment.
  • sealing rings circumferential grooves in its inner or outer surface but two folds, one of which in the transition region between the outer peripheral surface and the pressure tube 19 facing end face of the sealing sleeve 28 and the other is formed in the transition region between the inner peripheral surface and the Matterschraubelement facing end face of the sealing sleeve 28.
  • a sealing ring 30 and 31 is inserted, whose axial length is dimensioned so that it is in the in Fig. 3 shown, not yet assembled state protrudes out of its associated fold out over the relevant end face of the sealing sleeve 28 in the axial direction.
  • sealing rings 30, 31 each have a radial thickness or wall thickness which is not greater than the radial depth of the respective fold, so that they in the in Fig. 3 shown rest neither on the inner wall of the channel 4 nor on the outer wall of the conduit 5, whereby the assembly is greatly facilitated, since no special frictional forces must be overcome.
  • the two sealing rings 30, 31 are brought together in the axial direction, so that they expand so much in the radial direction that they between the sealing sleeve 28 on the one hand and the inner wall of the channel 4 and the outer wall of the fuel line 5 on the other hand, the desired tight closure of the free spaces 21 or 22 cause.
  • the sealing arrangement positioned between the union screw element 15 and the pressure tube 19 comprises an annular disc package consisting of three substantially non-deformable material, for example steel, annular discs 34, 35, 36, consisting of a fixed axial force due to the tightening screw element 15 being tightened. which are arranged one behind the other in the axial direction and surround the fuel line 5 concentrically.
  • the two axially outer annular discs 34, 36 have an inner diameter which is slightly larger than the outer diameter of the fuel line 5, so that they can be easily slid onto them during assembly.
  • each of these two annular discs 34, 36 On the outer circumference of each of these two annular discs 34, 36, a sealing ring 37, 39 is mounted, whose axial length is greater than that of the associated annular disc 34 and 36, so that it in the in Fig. 5 shown state in which the union screw 15 is not screwed far enough into the internal thread 16 of the channel 4, beyond the end faces in the axial direction also stands.
  • the outer diameter of each of these sealing rings 37, 39 is initially, ie slightly smaller than without axial compression the inner diameter of the channel 4, so that when introducing the provided with these sealing rings 37, 38 annular discs 34, 36 in the channel 4 no significant frictional forces must be overcome.
  • the third, between the other two arranged annular disc 35 has an outer diameter which is slightly smaller than the inner diameter of the channel 4 and carries a seal inserted into its central opening 38, which in the uncompressed state (see Fig. 5 ) protrudes in the axial direction over its end faces and has an inner diameter which is greater than the outer diameter of the fuel line 5.
  • the sealing arrangement can also comprise only two or more than three annular disks, wherein then always the annular disks 34 and 36 on the one hand and the annular disk 35 on the other hand corresponding annular disks are arranged alternately.
  • a sealing sleeve 40 concentrically surrounding the tubular fuel line 5 and forming part of the pressure transfer arrangement is provided in the region between the end of the pipe section 17 of the screw connection element 15 facing away from the nozzle holder 2 and the end of the pressure tube 19 facing away from the nozzle holder 2, but this sealing sleeve 40 only has one single, formed by a sealing ring 41 sealing element, which is arranged in the same manner as the outer sealing ring 24 of the associated Fig. 1 described example; Thus, it causes only a seal between the inner wall of the channel 4 and the outer wall of the pressure tube 19 existing free space 22nd
  • the sealing of the free space 21 between the outer wall of the fuel line 5 and the inner wall of the pressure tube 19 is effected here by a hollow cylindrical sealing body 43 made of an elastomeric, resistant to engine oil and / or fuel material in an extension of the pipe section 17 of the union screw element 15 passing hole is accommodated and the fuel line 5 coaxially encloses.
  • the axial length of this sealing body 43 is slightly larger than that of the extension of the bore of the pipe section 17, so that it out of this, as in Fig. 6 shown projects slightly in the axial direction as long as the union screw 15 is not completely screwed and tightened in the channel 4 during assembly of the assembly.
  • sealing sleeve 40 may wear more than a sealing ring on its outer side.
  • Fig. 9 is not the tubular fuel line 5 coaxially surrounding, provided between the pipe section 17 of the union screw 15 and the Anduckrohr 19 sealing sleeve.
  • the pressure tube 19 is formed correspondingly longer, so that when assembling a sealing body 45 which is formed and arranged as the sealing body 43 in the FIGS. 7 and 8 , when tightening the cap screw 15 instead of the axially outwardly directed end of a sealing sleeve of the corresponding end of the pressure tube 19 is compressed in the same manner as described above, whereby a tight closure of the space 21 between the outer wall of the fuel line 5 and Inner wall of the pressure tube 19 takes place with respect to the outer region of the cylinder head 1.
  • the union screw element 15 has a shank portion 50, to which the pipe section 17 to be screwed into the internal thread 16 of the channel 4 adjoins in the axial direction.
  • This shank portion 50 has a larger outer diameter than the pipe section 17, so that between these two sections and on Kochschraubelement 15 extending in the radial direction, circumferential shoulder 51 is present.
  • the axial lengths of the shank portion 50 of the union screw element 15 and of the sealing region 47 of the channel 4 adjoining the inlet opening 3 are coordinated with one another such that the shoulder 51 in the fully assembled state, in which the Sprintschraubelement 15 is tightened in the axial direction closer to the input port 3, as the shoulder 48, so that between these two shoulders 51, 48 remains a clearance 53, which on the no tight seal forming screw between the cap screw 15 and the internal thread 16 fluidly communicates with the clearance 22 between the inner wall of the channel 4 and the outer wall of the pressure tube 19, so that existing there engine oil or fuel can pass into the space 53.
  • a circumferentially extending groove is provided in the outer wall of the shank portion 50 of the Matterschraubelements 15, sitting in the sealing ring 54 which rests firmly in the assembled state on the inner wall of the sealing region 47 of the channel 4 and ensures a tight seal against the outside. From the free space 53 between the shoulders 48 and 51, a drainage channel can lead away, via which optionally a controlled removal and return of a fluid (engine oil or fuel) that has entered the free spaces 22 and 53 can take place.
  • a fluid engine oil or fuel

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)
EP11008856.4A 2010-11-06 2011-11-07 Agencement de raccordement pour une conduite de carburant tubulaire Active EP2450556B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE201010050296 DE102010050296B4 (de) 2010-11-06 2010-11-06 Anschlussanordnung für eine rohrförmige Kraftstoffleitung

Publications (3)

Publication Number Publication Date
EP2450556A2 true EP2450556A2 (fr) 2012-05-09
EP2450556A3 EP2450556A3 (fr) 2015-07-08
EP2450556B1 EP2450556B1 (fr) 2018-05-30

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP11008856.4A Active EP2450556B1 (fr) 2010-11-06 2011-11-07 Agencement de raccordement pour une conduite de carburant tubulaire

Country Status (3)

Country Link
US (1) US8695572B2 (fr)
EP (1) EP2450556B1 (fr)
DE (1) DE102010050296B4 (fr)

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Publication number Priority date Publication date Assignee Title
AT509177B1 (de) * 2009-11-23 2013-09-15 Bosch Gmbh Robert Druckrohrstutzen für common-rail-einspritzsystem
US8991360B2 (en) * 2012-06-27 2015-03-31 Caterpillar Inc. Coaxial quill assembly retainer and common rail fuel system using same
FR3028296B1 (fr) * 2014-11-07 2016-11-11 Delphi Int Operations Luxembourg Sarl Dispositif anti rotation d'une lance a carburant

Citations (1)

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Publication number Priority date Publication date Assignee Title
US3845748A (en) 1972-09-29 1974-11-05 Mack Trucks Fuel injection nozzle holder installation

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Publication number Priority date Publication date Assignee Title
US4485790A (en) * 1982-04-19 1984-12-04 Yanmar Diesel Engine Company Limited Holding construction of a fuel injection valve in an internal combustion engine
US5775303A (en) * 1995-06-30 1998-07-07 Cummins Engine Company, Inc. High Pressure Fuel Line Connection
DE19524520A1 (de) * 1995-07-05 1997-01-09 Bosch Gmbh Robert Kraftstoffeinspritzventil für Brennkraftmaschinen
IT1284691B1 (it) * 1996-07-23 1998-05-21 Iveco Fiat Motore endotermico a iniezione
AT407900B (de) * 1997-04-09 2001-07-25 Avl List Gmbh Brennkraftmaschine mit einlass- und auslassventilen
GB9816264D0 (en) * 1998-07-24 1998-09-23 Lucas Ind Plc Connector
US6431150B1 (en) * 2000-09-12 2002-08-13 Detroit Diesel Corporation Fuel system
DE10240518A1 (de) * 2002-09-03 2004-03-11 Deutz Ag Kraftstoffeinspritzsystem für eine Brennkraftmaschine
JP2008267449A (ja) * 2007-04-18 2008-11-06 Nok Corp バックアップリング
DE102007047518B4 (de) * 2007-10-04 2019-08-29 Man Truck & Bus Ag Druckrohrstutzen
US7543567B2 (en) * 2007-10-29 2009-06-09 Caterpillar Inc. Fuel system having a one-piece hollow tube connection
ATE527444T1 (de) * 2007-11-13 2011-10-15 Delphi Tech Holding Sarl Brennstofflanze
EP2354529B1 (fr) * 2010-01-21 2012-09-19 Delphi Technologies Holding S.à.r.l. Ensemble de tuyau de carburant et supports de fixation

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3845748A (en) 1972-09-29 1974-11-05 Mack Trucks Fuel injection nozzle holder installation

Also Published As

Publication number Publication date
US8695572B2 (en) 2014-04-15
EP2450556B1 (fr) 2018-05-30
EP2450556A3 (fr) 2015-07-08
US20120125462A1 (en) 2012-05-24
DE102010050296B4 (de) 2013-11-07
DE102010050296A1 (de) 2012-05-10

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