EP1482168B1 - Serre-flan pour injecteur de carburant - Google Patents

Serre-flan pour injecteur de carburant Download PDF

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Publication number
EP1482168B1
EP1482168B1 EP04020734A EP04020734A EP1482168B1 EP 1482168 B1 EP1482168 B1 EP 1482168B1 EP 04020734 A EP04020734 A EP 04020734A EP 04020734 A EP04020734 A EP 04020734A EP 1482168 B1 EP1482168 B1 EP 1482168B1
Authority
EP
European Patent Office
Prior art keywords
fuel injection
injection valve
receiving bore
sealing
recess
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
EP04020734A
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German (de)
English (en)
Other versions
EP1482168A1 (fr
Inventor
Heinz-Martin Krause
Stefan Lauter
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP1482168A1 publication Critical patent/EP1482168A1/fr
Application granted granted Critical
Publication of EP1482168B1 publication Critical patent/EP1482168B1/fr
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
    • F02M61/14—Arrangements of injectors with respect to engines; Mounting of injectors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/85—Mounting of fuel injection apparatus
    • F02M2200/858—Mounting of fuel injection apparatus sealing arrangements between injector and engine

Definitions

  • the invention relates to a hold-down according to the preamble of claim 1.
  • the sealing means is formed by a radially encircling groove, which is formed on a nozzle body of a fuel injection valve inserted into a receiving bore, and a sealing ring inserted into the groove.
  • the sealing ring is biased in the radial direction, wherein it is supported on the one hand in the groove of the nozzle body and on the other hand on the wall of the receiving bore.
  • a disadvantage of the DE 197 35 665 A1 known sealing means is that the bias of the sealing element depends on the geometry and in particular on the diameter of the receiving bore. Therefore, the known sealant can not be used universally, but is specially adapted for each receiving bore. In addition, the bias of the sealing element can not be adjusted so that due to aging or due to production-technical fluctuations, the bias is set differently, whereby the seal may be insufficient. In addition, the seal is exposed directly to the hot exhaust gases, whereby an accelerated aging of the sealing ring occurs. In addition, in the known sealing means, in particular because of the almost circular cross-section of the sealing element, penetration of the sealing means occurs.
  • Another disadvantage is that due to the radial bias of the sealing element, a frictional force occurs, which counteracts an axial displacement of the sealant. As a result, both the installation and removal and the adjustment of the fuel injection valve considerably more difficult. Due to contamination, which are deposited on the sealing element, and aging of the sealing element, it may even be the case that the expansion of the fuel injection valve is no longer possible or that the expansion element of the fuel injection valve, the sealing element is destroyed.
  • a sealant which is designed as a heat protection sleeve.
  • the heat protection sleeve is inserted into a stepped receiving bore of a cylinder head of an internal combustion engine, and surrounds a discharge-side nozzle body of a fuel injection valve inserted into the receiving bore circumferentially.
  • the tubular heat protection sleeve is bent at the discharge end to achieve a double layer of the sleeve.
  • the double position of the sleeve is biased to seal a formed between the nozzle body and the receiving bore annular gap radially against the wall of the receiving bore.
  • the nozzle body of the fuel injection valve has a conical portion which is inserted into the sleeve and clamped in the region of the bent sleeve in the sleeve.
  • the fuel injector is also applied to an inclined stage to fix the position of the fuel injection valve in the receiving bore.
  • a disadvantage of the DE 197 43 103 A1 known fuel injection valve is that the heat protection sleeve is biased in the region of the double layer of the sleeve between the nozzle body and the receiving bore. This results in the problems already discussed above when installing or removing the fuel injector.
  • Another disadvantage is that the position of the fuel injection valve is fixed in the receiving bore. Due to production-related fluctuations, the axis of the introduced into the receiving bore fuel injection valve is generally not exactly coincide with the axis of a connecting piece of a high-pressure fuel line. For connecting the fuel injection valve to the fuel high-pressure line, therefore, an additional intermediate piece is required.
  • a hold-down according to the preamble of claim 1 is known.
  • the hold-down retains a fuel injection valve against a relatively high combustion pressure prevailing in the combustion chamber of the internal combustion engine.
  • the hold-down engages at two circumferentially opposite locations on a collar of the fuel injection valve, wherein the collar rests with its underside on the top of the cylinder head, so that the fuel injection valve is held.
  • Known hold-down device has the disadvantage that it acts only in the axial direction on the fuel injection valve. With a mechanical load of the fuel injection valve, the fuel injection valve can therefore be twisted, tilted or moved radially. As a result, the fuel injection valve can be released at the connection point and the high-pressure fuel line can be moved. In addition, an undesirable stress on the sealant can occur. In a trained as a sealing ring sealant, which bears against both the fuel injection valve and on the wall of the receiving bore, are in a rotation of the fuel injection valve in the Sealing ring extensively constructed shear stresses, whereby the sealing properties of the sealing ring are deteriorated.
  • From the DE 197 35 665 A1 is also designed as a clamping claw hold-down device, similar to that of JP-OS 08-312503 A known hold-down, known.
  • the cylinder head has a recess in which the collar of the fuel injection valve is arranged, whereby the collar of the fuel injection valve, which acts on the Niederhaltevorrichung, is sunk into the cylinder head. This hold-down also results in the already discussed disadvantages.
  • This hold-down device has a lever arm, which can be connected to the cylinder head of the internal combustion engine by means of a fastening element, in particular by means of a screw.
  • the hold-down device has a fastening part ring connected to the lever arm, which partially surrounds the fuel injection valve, wherein the fastening part ring has a recess into which a housing part, in particular an electrical connector plug of the fuel injection valve inserts, in order to prevent a twisting of the fuel injection valve.
  • the hold-down device according to the invention with the features of claim 1 has over the above-described prior Technology has the advantage that the position of the fuel injection valve and in particular the rotational position of the fuel injection valve is fixed.
  • the hold-down circumferentially acts at least approximately evenly distributed on the fuel injection valve, so that tilting of the fuel injection valve is prevented.
  • the fastening part ring has a circumferential inner collar, which cooperates with a circumferential shoulder of the fuel injection valve in order to prevent tilting of the fuel injection valve.
  • the force of the holddown is circumferentially at least almost uniformly transmitted to the fuel injection valve.
  • the housing part is arranged on the side facing away from the fastening element side of the fuel injection valve.
  • the fastening part ring can surround the fuel injection valve from two sides in an advantageous manner, with good force transmission from the fastening element to the fuel injection valve.
  • the mounting part ring has an inner surface on which the fuel injection valve at least substantially flat against, to prevent displacement of the fuel injection valve in a radial direction. Due to the flat concerns of the fuel injection valve on the inner surface of the Mounting part ring also prevents tilting of the fuel injection valve.
  • the base body is designed so that the sealing element is close to the valve tip. As a result, a reduction of the dead volume or the HC pockets can be achieved.
  • the base body serves as a heat sink to dissipate the heat from the fuel injection valve, in particular in the region of the nozzle body.
  • the main body is mounted with contact with the cylinder head to further improve the cooling of the valve body.
  • the hold-down is at least partially disposed in the receiving bore, and the inner surface of the hold-down is substantially in an area within the receiving bore on the fuel injection valve.
  • the hold-down can be at least partially sunk in the receiving bore of the cylinder head, so that the fuel injection valve can be made more compact. It also makes assembly easier and the hold-down better protected.
  • Fig. 1 shows a fuel injection valve 1, which is inserted with a sealing means 2 according to a first embodiment in a receiving bore 3 of a cylinder head 4.
  • the fuel injection valve 1 has a nozzle body 5, which is connected to a central part 6 of the fuel injection valve 1.
  • the nozzle body 5 has a fuel nozzle for injecting fuel into a combustion chamber 7 of the internal combustion engine, wherein the fuel via an injection opening 8 of the cylinder head 4 in the combustion chamber. 7 arrives.
  • the sealing means 2 surrounds the nozzle body 5 circumferentially, wherein the outer diameter of the sealant 2 at least substantially coincides with the outer diameter of the central part 6, and the inner diameter of the sealant 2 at least substantially coincides with the outer diameter of the nozzle body 5.
  • the receiving bore 3 has a first portion 9 of smaller diameter and a second portion 10 of larger diameter.
  • the first portion 9 and the second portion 10 are connected to each other by means of a step 11 of the receiving bore 3.
  • the outer diameter of the central part 6 of the fuel injection valve 1 and the outer diameter of the sealant 2 correspond in this embodiment, at least substantially the diameter of the second portion 10 of the receiving bore 3.
  • the axis of the fuel injection valve 1 is in this embodiment with the axis 12 of the receiving bore 3 match.
  • a stepped, annular gap 13 is formed between the fuel injection valve 1 and the receiving bore 3, which comprises an annular gap 14 between the middle part 6 of the fuel injection valve 1 and the sealant 2 and the second portion 10 of the receiving bore 3 is formed.
  • the sealing means 2 comprises a base body 15, which has a recess 16, and a sealing element 17, which is inserted into a recess 18 of the base body 15.
  • the recess 16 of the base body 15 is designed in this embodiment as a central, axial bore through the base body 15, wherein the nozzle body. 5 extends through the recess 16.
  • the recess 18 is connected to the recess 16, so that there is a stepped bore 19.
  • the sealant 2 is supported by a sealing plate 20 on the stage 11 of the receiving bore 3. In addition, the sealant 2 is supported on the central part 6.
  • the fuel injection valve 1 is held by a hold-down device 21 in the receiving bore 3.
  • the hold-down device 21 has a holding-down device 22 and a fastening element embodied as a screw 23.
  • the screw 23 penetrates a lever arm 24 of the blank holder 22 and is screwed into a threaded bore 25 of the cylinder head 4. In this embodiment, the screw 23 is completely screwed into the threaded bore 25, so that the lever arm 24 rests flat on the top 26 of the cylinder head 4.
  • the hold-down 22 has a fastening part ring 27, which is connected to the lever arm 24 and partially surrounds the fuel injection valve 1.
  • the fastening part ring 27 of the hold-down 22 has a recess 28 (Fig. 4), in which a housing part 29 of the fuel injection valve 1 is inserted to prevent rotation of the fuel injection valve. Because the abutment of the housing part 29 on surfaces 31, 32 (FIG. 4) blocks a rotation of the fuel injection valve 1 about the axis of the fuel injection valve 1, which in this embodiment coincides with the axis 12 of the receiving bore 3, the rotational position of the fuel injection valve 1 is given at the same time.
  • the housing part 29 comprises an electrical connector 33rd
  • the fuel injection valve 1 has a shoulder 37 on which a circumferential inner collar 38 of the fastening part ring 27 of the hold-down 22 engages.
  • the biasing force generated by the tightening force of the screw 23 is circumferential uniformly transmitted to the shoulder 37 of the fuel injection valve 1, so that a uniform application of the fuel injection valve 1 is achieved in order to prevent tilting of the fuel injection valve 1.
  • the recess 28 (FIG. 4) is arranged on the side of the fastening part ring 27 facing away from the lever arm 24 of the hold-down 22.
  • the fuel injection valve 1 therefore has in the receiving bore 3 of the cylinder head 4 a rotational angle position with respect to the axis of the fuel injection valve 1, wherein the angular position of the housing part 29 is offset by 180 ° with respect to the angular position of the screw 23 and the lever arm 24.
  • the fuel injection valve 1 has a fuel inlet connection 39, via which fuel is passed from a high-pressure fuel line into the fuel injection valve 1 to the nozzle body 5.
  • the fuel inlet port 39 is connected to a housing part 40, on which the shoulder 37 is formed.
  • the housing part 40 has an outer surface 41.
  • On the outer surface 41 of the housing part 40 of the fuel injection valve 1 is an inner surface 42 of the mounting part of the ring 27 of the blank holder 22 at.
  • the inner surface 42 is at least substantially flat against the outer surface 41, so that a displacement of the fuel injection valve 1 is prevented in a radial direction and the axial position of the fuel injection valve 1 is fixed.
  • the mounting part ring 27 is at least partially in a recess 43 which is part of the receiving bore 3, arranged so that the mounting part ring 27 is partially recessed in the cylinder head 4.
  • Fig. 2 shows the detail designated in Fig. 1 II. Already described elements are provided with matching reference numerals, whereby a repetitive description is unnecessary.
  • the fuel injection valve 1 has a step 50, which connects the central part 6 with the nozzle body 5.
  • the main body 15 of the sealant 2 abuts against a front-side first bearing surface 51 on the central part 6 of the fuel injection valve 1, wherein it has a recess 52 which receives the step 50.
  • the main body 15 has a recess 16, which is formed as an axial bore through which the nozzle body 5 extends.
  • the base body 15 has a recess 18 which is connected to the recess 16, whereby the stepped bore 19 of the base body 15 is formed.
  • the height of the recess 18 in the axial direction is approximately equal to half the height of the base body 15 in the axial direction in the exemplary embodiment.
  • the width of the recess 18 in the radial direction is approximately equal to half the width of the cross section of the base body 15 in the radial direction in the exemplary embodiment.
  • the recess 18 therefore has a rectangular cross-section.
  • the sealing element 17 In the recess 18 of the base body 15, the sealing element 17 is introduced, wherein the sealing element 17 bears against an axial surface 53 of the base body 15 and between the sealing element 17 and a radial surface 59 of the base body 15, an annular gap 54 is formed.
  • the inner diameter of the sealing element 17 is smaller than the outer diameter of the nozzle body 5 in the relaxed state, so that the sealing element 17 is subjected to a bias voltage.
  • the bias of the sealing element 17 acts on a sealing surface 55 on the nozzle body 5, whereby a gap 56 which is formed between the base body 15 and the nozzle body 5 is sealed.
  • the sealing element 17 can be particularly easily introduced into the recess 18 of the base body 15, since no friction between the base body 15 and the sealing element 17 occurs during insertion.
  • the base body 15 is supported via the sealing plate 20 on the stage 11 of the receiving bore 3 of the cylinder head 4.
  • the main body 15 is acted upon by the hold-down device 21 (FIG. 1) with an axial biasing force, so that the annular gap 14 is sealed by the sealing plate 20.
  • the sealing plate 20 is preferably made of a soft metal, in particular copper, so that the sealing element 17 is protected from direct contact with the combustion gases. The protection takes place both against the chemical and the thermal effect of the combustion gases on the sealing element 17.
  • the sealing plate 20 is located both on the nozzle body 5 and on a circumferential wall 73 of the receiving bore 3. As a result, the position of the nozzle body 5 is predetermined in the region of the sealing plate 20.
  • the outer and / or the inner diameter of the sealing plate 20 may also be selected so that between the nozzle body 5 and the sealing plate 20 and the sealing plate 20 and the circumferential wall 73 of the receiving bore 3, a gap is formed, whereby a displacement of the fuel injection valve. 1 in the radial direction is made possible.
  • the sealing element 17 may advantageously consist of polytetrafluoroethylene (PTFE).
  • PTFE polytetrafluoroethylene
  • Polytetrafluoroethylene has the advantage that it is temperature resistant and has an extremely high chemical resistance. Therefore, in a sealing member 17 made of polytetrafluoroethylene or a similar material, the sealing plate 20 also omitted.
  • PTFE polytetrafluoroethylene
  • a reversible increase in volume so that the sealing element 17 can be applied with some play on the nozzle body 5 of the fuel injector 1, wherein the sealing element 17 is heated in operation and due to the increase in volume, a seal on the sealing surface 55 takes place.
  • through the gap 54 between the base body 15 and the sealing element 17 is a compensation chamber created to prevent damage to the nozzle body 5 at a volume increase.
  • the sealing element 17 may also be made of a different material, which is correspondingly temperature and chemical resistant.
  • the biasing force of the fuel injection valve 1 can also be determined by the height of the main body 15 and / or by the thickness of the sealing plate 20.
  • the first contact surface 51 extends parallel to the second contact surface 57, there is a particularly favorable force transmission of the biasing force of the fuel injection valve 1 on the sealing plate 20.
  • the base body 15 is formed as a metal block to the biasing force without significant deformation on the sealing plate 20 transfer.
  • Fig. 3 shows the detail designated II in Fig. 1 in an alternative embodiment according to a second embodiment of a sealant 2. Already described element are provided with matching reference numerals, whereby a repetitive description is unnecessary.
  • the base body 15 has a sleeve 65 which is bent at its ends 66, 67, so that at the end 66 a radially outwardly projecting collar 68 and at the end 67 a radially outwardly projecting collar 69 is formed.
  • the collar 68 at the end 66 of the main body 15 has a first contact surface 51, which at the stage 50th is applied. The system takes place on an end face 58 of the stage 50 of the fuel injection valve 1.
  • the collar 69 of the base body 15 has a second contact surface 57, which is connected to the sealing element 17.
  • the sealing element 17 is also connected to an inner bearing surface 70 which is formed opposite to a lateral surface 71 of the nozzle body 5 on the base body 15. The sealing element 17 therefore forms both with the nozzle body 5, the sealing surface 55 and the step 11, a sealing surface 72. Therefore, the sealing plate 20 from the first embodiment of FIGS. 1 and 2 omitted.
  • the compound of the sealing element 17 with the base body 15 results from the fact that a vulcanization of the sealing element 17 takes place on the base body 15.
  • a vulcanization of the sealing element 17 takes place on the base body 15.
  • vinylidene fluoride-hexafluoropropylene copolymers are applied to the base body and then vulcanized, whereby the corresponding fluoroelastomer is produced.
  • the preparation of the sealing element 17 by the vulcanization of the resulting fluoroelastomer adheres to the metallic body 15.
  • the sealant 2 is therefore made in one piece, which simplifies the application to the nozzle body 5 and the assembly of the fuel injection valve 1.
  • the sealing of the sealant 2 takes place on the one hand in the radial direction against the nozzle body 5 and the other in the axial direction against the stage 11 of the receiving bore 3. Since no seal in the radial direction against the wall 73 of the receiving bore 3, acts during insertion the sealant 2 in the receiving bore 3 and no frictional force, which would be caused by contact of the sealant 2 with the wall 73, so that the installation and removal of the fuel injector 1 substantially simplified.
  • the sealing means 2 seals the receiving bore 3 reliably, so that a stepped, annular gap 13 may be formed, which is a radial displacement of the Fuel injection valve 1 allows, whereby an offset of the axis 12 of the receiving bore 3 and an axis of a connecting piece of a high-pressure fuel line can be compensated.
  • the base body 15 is advantageously designed as a spring plate, whereby it deforms elastically under an axial load.
  • Fig. 4 shows the hold-down 22 shown in Fig. 1 in a plan view.
  • the hold-down 22 has a lever arm 24 and a mounting part ring 27, which are interconnected.
  • the fastening part ring 27 is interrupted by a recess 28, whereby a first pitch circle section 74 and a second pitch circle section 75 are formed.
  • the first pitch circle section 74 has a surface 31 which faces a surface 32 formed on the second pitch circle section 75.
  • the fastening part ring 27 has a circumferential inner collar 38, which is also interrupted by the recess 28.
  • the two surfaces 31, 32 are arranged parallel to each other and the axis of symmetry 76 of the blank holder 22 is parallel to each of the surfaces 31, 32nd
  • the fastening part ring 27 is used for fastening the fuel injection valve 1 in the receiving bore 3, wherein the surfaces 31, 32 abut against a housing part 29 of the fuel injection valve 1 in order to prevent rotation of the fuel injection valve 1.
  • the circumferential inner collar 38 cooperates with the shoulder 37 of the fuel injection valve 1 in order to achieve a uniform transfer of a holding force of the hold-down 22 to the fuel injection valve 1.
  • the lever arm 24 of the hold-down 22 has a bore 77 to allow attachment of the hold-down 22 in the threaded bore 25 of the cylinder head 4 by means of the screw 23 ( Figure 1).
  • FIG. 5 shows the holding-down device 22 shown in FIG. 4 from the direction indicated by V in FIG. 4 in the front view. Already described element are also provided here with matching reference numerals.
  • the mounting part ring 27 has the inner surface 42, which rests in the mounted state on the housing of the fuel injection valve 1, to further fix the axial position of the fuel injection valve 1.
  • the axial position of the fuel injection valve 1 can be fixed by the hold-down 22.
  • a sealing means 2 is used together with a holding-down device 22 according to the invention for fastening a fuel injection valve 1 in a receiving bore 3.
  • the sealant 2 and the hold-down 22 according to the invention can also be used independently of each other.
  • the sealant 2 and the hold-down 22 according to the invention are also suitable for other applications.
  • the sealing plate 20 (FIG. 1) can also be replaced by a differently configured sealing body.
  • FIG. 6 shows the detail designated VI in FIG. 2 in an alternative embodiment according to a third exemplary embodiment of a sealant 2. Elements already described are provided with identical reference symbols in this and the following exemplary embodiments, whereby a repetitive description is unnecessary.
  • the sealing element 17, which is arranged in a ring around the nozzle body 5, non-positively connected to the base body 15 by means of a nose-like projection 80 of the base body 15.
  • the sealing element 17 has a recess 81 into which the projection 80 of the base body 15 engages.
  • the sealing element 2 according to the third embodiment has the advantage that during the assembly of the sealing element 2, the position of the sealing element 17 of the sealant 2 is fixed. In addition, it is prevented that the sealing element 17, the z. B. as a result of heating with the nozzle body 5 or the sealing plate 20 and the stage 11, if the plate 20 is not provided, at least partially entered into a connection with a disassembly of the sealant 2, the z. B. is required due to maintenance, is separated from the body 15.
  • FIG. 7 shows the detail designated VI in FIG. 2 in an alternative embodiment according to a fourth exemplary embodiment.
  • the recess 18 of the main body 15 is formed to extend from a position interposed between the first abutment surface 51 and the second abutment surface 57 (FIG. 3) from a diameter provided through the recess 16 up to a diameter, which is preferably smaller than the outer diameter of the base body 15, monotonously widened, so that the recess 18 has a triangular cross-section.
  • an annular sealing element 17 is introduced, which has a triangular cross-section corresponding to the recess 18.
  • the sealing force with which the sealing element 17 is pressed against the nozzle body 5 in order to seal the gap 56 as a result of the axis 12 inclined relative to the radial surface 59 by applying the sealant 2 with an axial bias increase.
  • the Opening angle of the recess 18, which determines the inclination of the radial surface 59 relative to the axis 12, while the size of the sealing forces with which the gap 56 and the gap 14 are sealed can be adjusted.
  • the recess 18 also consist of a plurality of inclined sections which have at least partially different opening angles.
  • FIG. 8 shows the detail designated VI in FIG. 2 in an alternative embodiment according to a fifth exemplary embodiment of a sealant 2.
  • the recess 18 of the main body 15 according to the fifth embodiment has a first part 82 and a second part 83.
  • the second part 83 is similar to the recess 18 according to the fourth embodiment (see Fig. 7) is formed, wherein the second part 83 of the recess 18 in this case increases from a diameter which is greater than the diameter of the nozzle body 5.
  • Der first part 82 of the recess 18 narrows, starting from the axial surface 53 of the base body 15, which has a diameter which is greater than the diameter from which the second part 83 of the recess 18 increases, continuously up to this.
  • the sealing element 17 is shaped so that it fits into the recess 18, wherein due to the protrusion 80 formed on the base body 15 results in a frictional connection with the base body 15 of the sealant 2, which is similar to the compound according to the third embodiment (see Fig. 6).
  • sealant 2 described in the embodiments can be seen as exemplary embodiments, which are characterized by a simple structure. By combining and modifying these embodiments, sealing means adapted to various boundary conditions can be formed.

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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)
  • Cylinder Crankcases Of Internal Combustion Engines (AREA)

Claims (4)

  1. Serre-flan (22) pour injecteur de carburant (1) à installer dans un perçage de réception (3) de la culasse (4) d'un moteur à combustion interne, pour l'injection directe de carburant dans une chambre de combustion (7) du moteur à combustion interne, avec un bras de levier (24) pouvant être relié à la culasse (4) du moteur à combustion interne à l'aide d'un élément de fixation, notamment à l'aide d'une vis (23), le serre-flan (22) présentant un anneau partiel de fixation (27) relié au bras de levier (24), entourant partiellement l'injecteur de carburant (1), l'anneau partiel de fixation (27) présentant un évidement (28) dans lequel s'insère une partie de boîtier (29) de l'injecteur de carburant (1) pour empêcher une rotation de l'injecteur de carburant,
    caractérisé en ce que
    l'anneau partiel de fixation (27) présente un collet intérieur (38) coopérant avec un épaulement (37) de l'injecteur de carburant (1) pour empêcher un défaut d'alignement angulaire de l'injecteur de carburant (1).
  2. Serre-flan selon la revendication 1,
    caractérisé en ce que
    la partie de boîtier (29) est du côté de l'injecteur de carburant (1) opposé à l'élément de fixation (23).
  3. Serre-flan selon la revendication 1 ou 2,
    caractérisé en ce que
    l'anneau partiel de fixation (27) présente une surface intérieure (42), contre laquelle l'injecteur de carburant (1) s'applique au moins sensiblement en surface pour empêcher le déplacement de l'injecteur de carburant (1) dans une direction radiale.
  4. Serre-flan selon la revendication 3,
    caractérisé en ce que
    le serre-flan (22) se monte au moins partiellement dans le perçage de réception (3), et la surface intérieure (42) du serre-flan (22) s'applique contre l'injecteur de carburant (1) essentiellement à l'intérieur du perçage de réception (3).
EP04020734A 2000-06-03 2001-05-31 Serre-flan pour injecteur de carburant Expired - Lifetime EP1482168B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10027662A DE10027662A1 (de) 2000-06-03 2000-06-03 Dichtmittel und Niederhalter für ein Brennstoffeinspritzventil
DE10027662 2000-06-03
EP01951353A EP1290338B1 (fr) 2000-06-03 2001-05-31 Moteur a combustion interne

Related Parent Applications (1)

Application Number Title Priority Date Filing Date
EP01951353A Division EP1290338B1 (fr) 2000-06-03 2001-05-31 Moteur a combustion interne

Publications (2)

Publication Number Publication Date
EP1482168A1 EP1482168A1 (fr) 2004-12-01
EP1482168B1 true EP1482168B1 (fr) 2007-07-25

Family

ID=7644665

Family Applications (2)

Application Number Title Priority Date Filing Date
EP04020734A Expired - Lifetime EP1482168B1 (fr) 2000-06-03 2001-05-31 Serre-flan pour injecteur de carburant
EP01951353A Expired - Lifetime EP1290338B1 (fr) 2000-06-03 2001-05-31 Moteur a combustion interne

Family Applications After (1)

Application Number Title Priority Date Filing Date
EP01951353A Expired - Lifetime EP1290338B1 (fr) 2000-06-03 2001-05-31 Moteur a combustion interne

Country Status (8)

Country Link
US (2) US6811102B2 (fr)
EP (2) EP1482168B1 (fr)
JP (1) JP2003536019A (fr)
KR (1) KR100744961B1 (fr)
CN (1) CN1394256A (fr)
BR (1) BR0106711A (fr)
DE (3) DE10027662A1 (fr)
WO (1) WO2001094776A2 (fr)

Families Citing this family (76)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10108194A1 (de) 2001-02-21 2002-08-29 Bosch Gmbh Robert Dichtvorrichtung für ein Brennstoffeinspritzventil
DE10200044A1 (de) * 2002-01-03 2003-07-24 Bosch Gmbh Robert Brennstoffeinspritzventil
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US20020162538A1 (en) 2002-11-07
EP1290338B1 (fr) 2004-12-01
BR0106711A (pt) 2002-04-16
WO2001094776A3 (fr) 2002-08-01
DE50104696D1 (de) 2005-01-05
CN1394256A (zh) 2003-01-29
EP1290338A2 (fr) 2003-03-12
US7261246B2 (en) 2007-08-28
WO2001094776A2 (fr) 2001-12-13
JP2003536019A (ja) 2003-12-02
KR100744961B1 (ko) 2007-08-02
US6811102B2 (en) 2004-11-02
EP1482168A1 (fr) 2004-12-01
US20050016501A1 (en) 2005-01-27
DE10027662A1 (de) 2001-12-06
KR20020020803A (ko) 2002-03-15
DE50112774D1 (de) 2007-09-06

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