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EP2923067B1 - Ensemble destiné à un système d'injection de carburant, pourvu d'une soupape d'injection de carburant et d'un élément de désaccouplement - Google Patents

Ensemble destiné à un système d'injection de carburant, pourvu d'une soupape d'injection de carburant et d'un élément de désaccouplement Download PDF

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Publication number
EP2923067B1
EP2923067B1 EP13770870.7A EP13770870A EP2923067B1 EP 2923067 B1 EP2923067 B1 EP 2923067B1 EP 13770870 A EP13770870 A EP 13770870A EP 2923067 B1 EP2923067 B1 EP 2923067B1
Authority
EP
European Patent Office
Prior art keywords
cylinder
fuel injection
injection valve
decoupling element
main body
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.)
Active
Application number
EP13770870.7A
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German (de)
English (en)
Other versions
EP2923067A1 (fr
Inventor
Michael Knorpp
Martin Maier
Martin Scheffel
Michael Mayer
Pablo Antonio NAPAL JIMENEZ
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
Priority to EP17171749.9A priority Critical patent/EP3244057B1/fr
Publication of EP2923067A1 publication Critical patent/EP2923067A1/fr
Application granted granted Critical
Publication of EP2923067B1 publication Critical patent/EP2923067B1/fr
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/04—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series
    • F02M61/10—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
    • F02M61/14—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
    • F02M2200/09—Fuel-injection apparatus having means for reducing noise
    • 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
    • F02M2200/26—Fuel-injection apparatus with elastically deformable elements other than coil springs
    • 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
    • F02M2200/80—Fuel injection apparatus manufacture, repair or assembly
    • F02M2200/8023—Fuel injection apparatus manufacture, repair or assembly the assembly involving use of quick-acting mechanisms, e.g. clips

Definitions

  • the invention relates to a decoupling element, which serves for decoupling a fuel injection valve from a cylinder head, and an arrangement with a fuel injection valve and such a decoupling element.
  • the invention relates to the field of fuel injection systems of internal combustion engines, wherein high pressure fuel is injected through fuel injectors into associated combustion chambers of the internal combustion engine.
  • the compensating element serves to support a fuel injection valve in a cylinder head of an internal combustion engine.
  • the compensation element is annular and arranged between a valve housing of the fuel injection valve and a wall of a receiving bore of the cylinder head.
  • the compensation element has legs, which are supported on the fuel injection valve and the cylinder head.
  • a first leg bears against a shoulder of the cylinder head.
  • a second leg abuts against a shoulder of the valve housing.
  • the compensating element undercuts and openings can be provided.
  • the compensating element may have segments that are punched out of the compensating element and bent radially inward. In this way, the compensation element ensures both a compensation of manufacturing tolerances of the individual components as well as tolerances, which are due to the heating of the fuel injection valve during operation, and thus prevents tilting and misalignments.
  • a decoupling element for a fuel injection device is known.
  • the decoupling element realizes a low-noise construction.
  • the spring stiffness of the decoupling element is chosen so low and the decoupling element is placed such that the Entkoppelresonanz in the frequency range below 2.5 kHz.
  • a possible misalignment of a fuel injection valve is absorbed by a local weakening of an inner bearing region of the decoupling element. This local weakening of the radially inner bearing area is achieved by radially extending slots, which extend from the inner diameter of the decoupling element, for example, to the inner radius.
  • such slots or other stiffness reducing apertures may be provided here in a number from three to twenty. That from the DE 10 2008 054 591 A1 known decoupling element has the disadvantage that it is constructed according to a plate spring and is loaded in the mounted state to train. Thus, over the life of the problem arises to ensure sufficient component strength and at the same time the desired noise reduction.
  • the decoupling element according to the invention with the features of claim 1 has the advantage that an improved vibration damping over the life is guaranteed. Specifically, there is the advantage that sufficient noise attenuation is ensured even after a long service life and premature component failure is avoided.
  • the proposed decoupling element the noise transmission of the fuel injection valve to the cylinder head can be reduced in a simple manner, with the least possible space and with low additional costs. In this case, a predetermined target rigidity, for example of less than 50 kN / mm can be maintained.
  • the associated operational stability which is required especially at high system pressures, such as in a gasoline direct injection, can be ensured.
  • a vibration isolation, decoupling and decoupling of structure-borne noise can be ensured.
  • the problem of the circumferential stresses can be limited by a special segmentation, which means breaking the rotational symmetry.
  • the decoupling stiffness then results from the sum of the stiffnesses of the individual segments distributed over the circumference. This corresponds to a parallel connection of bending springs.
  • the segments acting as individual bending elements are held together only by a comparatively small, circumferential, closed ring of the cylinder-side support region of the basic body.
  • the mechanical circumferential stresses concentrate on the cylinder-side contact area of the main body, which contributes nothing to the spring behavior and can thus be designed with respect to the required peripheral forces.
  • a further advantage is that in the shape of the segments (bending elements), the function of the required for lateral force compensation tolerance compensation element can be integrated in a simple manner.
  • the fuel injection valve on the decoupling element as a ball joint tilt and thereby acting lateral forces and tolerance offsets between a center line of a mounting hole on the cylinder head and a center line of a rail cup can be compensated.
  • the embodiment according to the invention in which only the cylinder-side support region of the base body is configured at least partially in the form of a closed ring, has significant advantages.
  • This embodiment is to be understood in such a way that the main body is in any case segmented outside the cylinder-side support area into the segments distributed over the circumference.
  • this also includes the possibility that the segments distributed over the circumference also partially extend into the cylinder-side support region of the main body.
  • the cylinder-side support region of the base body is only partially configured in the form of a closed ring. Only if the cylinder-side support region of the main body is designed entirely in the form of a closed ring, then the distributed over the circumference segments of the body do not extend into the cylinder-side support area.
  • the base body is subjected to pressure during the support of the fuel injection valve between the valve-side support region and the cylinder-side support region.
  • the segments distributed over the circumference can advantageously act as bending segments. In this case, comparatively large bending movements are possible with respect to a given maximum stress of the material. This allows, inter alia, an advantageous tolerance compensation with respect to the positioning of the fuel injection valve.
  • the closed ring of the cylinder-side support region has bulges between the segments distributed over the circumference, which extend radially outward.
  • the base body has recesses which are provided between the segments of the base body and that the recesses of the base body partially extend into the cylinder-side support region of the base body, so that the cylinder-side support region of the base body only partially in the form of a closed ring is designed.
  • the distributed over the circumference segments of the body thus also extend slightly into the support area. This further facilitates bending of the segments.
  • the occurring component voltages in the circumferential direction can be concentrated in an advantageous manner to the closed ring.
  • the bulges provided between the circumferentially distributed segments, which in turn are distributed around the circumference, ensure a sufficiently large material cross-section in the region of the segments in order to absorb the forces acting in the circumferential direction.
  • the bulges do not influence the bending behavior of the segments.
  • the bulges on the cylinder head can be increased by the bulges.
  • the bulges allow for improved design with other advantages. It is also advantageous that the bulges of the closed ring, which partially bridge in the cylinder-side bearing region of the body extending recesses.
  • the bulges also extend somewhat into the areas of the cylinder-side support region, which adjoin the recesses in the circumferential direction in each case on both sides.
  • an advantageous introduction of force is achieved in the areas adjacent to the recesses and thus an advantageous adhesion over the circumference.
  • the closed ring of the cylinder-side support region is designed as an at least essentially flat cylinder-side support region for the cylinder head. This results in an advantageous support surface and a reliable positioning on the cylinder head. It is also advantageous that at least on a segment of the valve-side support region, a securing element is configured, which cooperates in the assembled state with the housing of the fuel injection valve. In particular, a plurality of securing elements may be provided, which are each biased in the radial direction against the housing of the fuel injection valve to form a captive. As a result, an advantageous assembly of the arrangement of the fuel injection valve and the decoupling element attached thereto is possible.
  • the closed ring of the cylinder-side bearing region is at least indirectly connected to a snap ring, which cooperates in the assembled state with the housing of the fuel injection valve.
  • This also represents a possibility for securing the decoupling element to the fuel injection valve, for example during pre-assembly.
  • the arrangement of the fuel injection valve and the decoupling element can be mounted in a simple manner on the cylinder head.
  • Fig. 1 shows an arrangement 1 with a fuel injection valve 2 and a decoupling element 3 and a cylinder head 4 in a partial, schematic and spatial representation.
  • the arrangement 1 is used for a fuel injection system of internal combustion engines.
  • the arrangement 1 is particularly suitable for fuel injection systems for the direct injection of fuel into combustion chambers of the internal combustion engine.
  • the internal combustion engine may be configured as a mixture-compression, spark-ignited internal combustion engine, whereby gasoline or other fuels suitable for such internal combustion engines as well as suitable mixtures of such fuels can be injected.
  • the decoupling element 3 is particularly suitable for such applications.
  • the fuel injection valve 2 can be configured as a high-pressure electromagnetic injection valve 2, which is used in direct injection gasoline engines. Without a decoupler there is the problem that the fuel injector 2 makes a conspicuous and disturbing contribution to the overall noise of the engine.
  • a recordable as a valve trough noise can be caused for example by the rapid opening and closing of the fuel injection valve 2, when a valve needle is moved with high dynamics in the respective end stops. The impact of the valve needle on the end stops leads to short-term, very high contact forces, which can be transmitted via a housing 5 of the fuel injection valve 2 in large parts on the cylinder head 4 as structure-borne noise and vibrations. This then leads to the cylinder head 4 to a strong noise, but by the decoupling element 3, which is located between the cylinder head 4 and the fuel injection valve 2, is significantly reduced.
  • the decoupling element 3 also has the requirement that it exhibits the required decoupling rigidity and required strength with respect to a given small installation space, in particular at high system pressures over the service life. This is achieved by the embodiment of the inventive decoupling element 3 described below with reference to the exemplary embodiments.
  • the decoupling element 3 has a main body 6 with a cylinder-side support region 7 and a valve-side support region 8.
  • the cylinder-side support region 7 serves for supporting on an upper side 9 of the cylinder head 4.
  • the valve-side support region 8 serves to support the fuel injection valve 2.
  • the decoupling element 3 surrounds the housing 5 of the fuel injection valve 2 circumferentially.
  • the top 9 of the cylinder head 4 is configured in this embodiment as a flat top 9.
  • the base body 6 of the decoupling element 3 is subjected to pressure during the support of the fuel injection valve 2 between the valve-side support region 8 and the cylinder-side support region 7.
  • the base body 6 in this case distributed over the handling segments 15, 16, 17, 18, which are bent elastically during the application. Due to the segmentation of the valve-side support region 8, an optimal elasticity over the service life is ensured with respect to the predetermined material thickness. Circumferentially acting stresses are considerably reduced by the segmentation in the valve-side support region 8.
  • the cylinder-side support region 7 of the base body 6 is at least partially in the form of a closed ring 20 configured. In this case, only the cylinder-side support region 7 of the main body 6 is configured at least partially in the form of the closed ring 20.
  • the cylinder-side support region 7 of the base body 6 is configured only partially in the form of a closed ring 20.
  • recesses 21, 22, 23 are provided between the segments 15 to 18, which also extend somewhat into the cylinder-side support region 7. This leaves, for example, at the recess 22 a web 25 of the closed ring 20, in which the cylinder-side support portion 7 viewed in the circumferential direction a reduced radial extent of a flat support surface 26 (FIG. Fig. 5 ) having.
  • the closed ring 20 of the cylinder-side support region 7 is designed in this embodiment as a flat cylinder-side support region 7 with a flat contact surface 26 for the cylinder head 4.
  • a reliable positioning of the cylinder head 4 is possible.
  • the recesses 21, 22, 23 extending in the cylinder-side support region 7 are preferably maximally pronounced, so that the remaining ring strength at the web 25 is reduced to a possible minimum.
  • Fig. 2 shows the in Fig. 1 illustrated arrangement 1 and the cylinder head 4.
  • an outer edge 27 of the closed ring 20 is bent away from the top 9 of the cylinder head 4 viewed upward.
  • this allows a stability of the closed ring 20, in particular at the web 25, to be improved, especially in tight spaces.
  • Fig. 3 shows the in Fig. 1 illustrated arrangement 1 and the cylinder head 4.
  • the bulge 28 extends radially outward.
  • the support surface 26 of the cylinder-side support region 7 is increased by the bulge 28 in this embodiment.
  • the bulge 28 bridges the recess 22 which partially extends into the cylinder-side support region 7. This increases the cross-sectional area, which is significant for the absorption of the circumferential tensile forces, in particular in the region of the web 25.
  • the bulge 28 also extends into regions (zones) 29, 30 of the cylinder-side support region 7, which adjoin the recess 22 in the circumferential direction.
  • the zones 29, 30 thus enable an advantageous frictional connection in the closed ring 20.
  • Fig. 4 shows the decoupling element 3 of in Fig. 1 illustrated arrangement 1 in a partial, schematic and spatial representation to illustrate the operation.
  • the illustrated section may be, for example, a quarter of a possible embodiment.
  • the upwardly bent segments 16, 17 are designed in the form of curved tabs which provide the fuel injection valve 2 at the drawn for illustrative line 31 a support or support. About this line (support line) 31, the load is transmitted to the decoupling element 3 due to the low pressure and the pressure forces at the fuel injection valve.
  • the segments 16 to 18 bend through the load.
  • the total stiffness of the decoupling then results from the sum of the individual bending stiffnesses. This corresponds to a parallel connection of individual bending springs.
  • Fig. 5 shows an arrangement 1 with a fuel injection valve and a decoupling element 3 and a cylinder head 4 in a partial, schematic sectional view.
  • a segment 18 of the base body 6 is shown in section for illustration.
  • the valve-side support portion 8 is configured, wherein the housing 5 rests, for example, on the line 31 of the segments 18, as also with reference to FIG Fig. 4 is described accordingly.
  • a fuse element 32 is configured on the segment 18.
  • further securing elements configured correspondingly to the securing element 32 are preferably configured on further segments, not shown.
  • the fuse element 32 acts in the illustrated assembled state with the housing 5 together.
  • the securing element 32 can be expanded during application to the housing 5 in the radial direction to the outside.
  • a clawing into the housing 5, in particular a magnet pot of the housing 5 can be achieved by a special shaping of the securing element 32. As a result, a captive is formed.
  • Fig. 6 shows the in Fig. 5 illustrated arrangement 1 and the cylinder head 4.
  • the segment 18 is designed as an inwardly open segment 18.
  • die Segment 18 ist der Segment 18 ein Foundationig failed soft point.
  • This embodiment has the additional advantage that an end stop can be realized in order to limit the maximum deformation of the segment 18.
  • a spacer element 33 which faces the cylinder-side support region of the main body 6, is configured on the segment 18 of the valve-side support region 8.
  • the spacer 33 strikes against the cylinder-side support region 7 after a certain movement path.
  • the spacer element 33 then cooperates with the cylinder-side support area to limit the possible range of motion.
  • a snap ring 34 is provided, which cooperates with the housing 5.
  • the closed ring 20 of the cylinder-side support region 7 is at least indirectly connected to the snap ring 34, so that the decoupling element 3 is reliably fixed to the housing 2. This facilitates, in particular, an assembly of the fuel injection valve 2 in the cylinder head 4, since the decoupling element 3 can already be preassembled on the fuel injection valve 2.
  • a decoupling element 3, which is open to the outside can thus be used, for example, with reference to FIG Fig. 1 to 4 is described as well as an inwardly open decoupling element 3, as it is based on the Fig. 6 and the Fig. 7 is described, realized.
  • Fig. 7 shows the in Fig. 5 illustrated arrangement 1 and the cylinder head 4.
  • the housing 5 rests with its undercut cone 35 on the line 31 of the valve-side support region 8.
  • the design of the decoupling element 3 simplifies.
  • an arrangement 1 can be realized, which is used for a fuel injection system of internal combustion engines.
  • the fuel injection valve 2 can be supported in the assembled state via the decoupling element 3 on the cylinder head 4 of the internal combustion engine.

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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 (6)

  1. Elément de désaccouplement (3), qui permet de désaccoupler une soupape d'injection de carburant (2) d'une culasse (4), avec un corps de base (6) qui, dans l'état monté, entoure un boîtier (5) de la soupape d'injection de carburant (2), dans lequel une zone d'appui côté cylindre (7), qui sert d'appui sur la culasse (4), et une zone de soutien côté soupape (8), qui sert de soutien de la soupape d'injection de carburant (2), sont formées sur le corps de base (6), dans lequel seule la zone d'appui côté cylindre (7) du corps de base (6) est configurée au moins en partie sous la forme d'un anneau fermé (20) et le corps de base (6) présente des segments (15 - 18) répartis sur une périphérie, qui sont reliés l'un à l'autre par l'anneau fermé (20) de la zone d'appui côté cylindre (7), caractérisé en ce que l'anneau fermé (20) de la zone d'appui côté cylindre (7) présente entre les segments (15 - 18) répartis sur la périphérie des renflements (28), qui s'étendent radialement vers l'extérieur.
  2. Elément de désaccouplement selon la revendication 1, caractérisé en ce que le corps de base (6) est soumis à une pression lors de l'appui de la soupape d'injection de carburant (2) entre la zone de soutien côté soupape (8) et la zone d'appui côté cylindre (7).
  3. Elément de désaccouplement selon la revendication 1, caractérisé en ce que le corps de base (6) présente des évidements (21 - 23), qui sont prévus entre les segments (15 - 18) du corps de base (6), et en ce que les évidements (21 - 23) du corps de base (6) s'étendent en partie dans la zone d'appui côté cylindre (7) du corps de base (6), de telle manière que la zone d'appui côté cylindre (7) du corps de base (6) ne soit que partiellement configurée sous la forme d'un anneau fermé (20).
  4. Elément de désaccouplement selon la revendication 3, caractérisé en ce que les renflements (28) de l'anneau fermé (20) enjambent les évidements (21 - 23) s'étendant en partie dans la zone d'appui côté cylindre (7) du corps de base (6).
  5. Elément de désaccouplement selon l'une quelconque des revendications 1 à 4, caractérisé en ce que l'anneau fermé (20) de la zone d'appui côté cylindre (7) est configuré au moins essentiellement sous forme de zone d'appui côté cylindre plane (7) pour la culasse (4).
  6. Elément de désaccouplement selon la revendication 1, caractérisé en ce qu'un élément d'écartement (33) est formé sur au moins un segment (18) de la zone de soutien côté soupape (8), qui coopère avec la zone d'appui côté cylindre (7) pour limiter une zone de mouvement lors d'une charge de la zone de soutien côté soupape (8) contre la zone d'appui côté cylindre (7).
EP13770870.7A 2012-11-20 2013-09-24 Ensemble destiné à un système d'injection de carburant, pourvu d'une soupape d'injection de carburant et d'un élément de désaccouplement Active EP2923067B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP17171749.9A EP3244057B1 (fr) 2012-11-20 2013-09-24 Dispositif pour un système d'injection de carburant comprenant un injecteur de carburant et un élément de découplage

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102012221134.9A DE102012221134A1 (de) 2012-11-20 2012-11-20 Anordnung für eine Brennstoffeinspritzanlage mit einem Brennstoffeinspritzventil und einem Entkoppelelement
PCT/EP2013/069817 WO2014079609A1 (fr) 2012-11-20 2013-09-24 Ensemble destiné à un système d'injection de carburant, pourvu d'une soupape d'injection de carburant et d'un élément de désaccouplement

Related Child Applications (2)

Application Number Title Priority Date Filing Date
EP17171749.9A Division EP3244057B1 (fr) 2012-11-20 2013-09-24 Dispositif pour un système d'injection de carburant comprenant un injecteur de carburant et un élément de découplage
EP17171749.9A Division-Into EP3244057B1 (fr) 2012-11-20 2013-09-24 Dispositif pour un système d'injection de carburant comprenant un injecteur de carburant et un élément de découplage

Publications (2)

Publication Number Publication Date
EP2923067A1 EP2923067A1 (fr) 2015-09-30
EP2923067B1 true EP2923067B1 (fr) 2018-01-17

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EP17171749.9A Active EP3244057B1 (fr) 2012-11-20 2013-09-24 Dispositif pour un système d'injection de carburant comprenant un injecteur de carburant et un élément de découplage
EP13770870.7A Active EP2923067B1 (fr) 2012-11-20 2013-09-24 Ensemble destiné à un système d'injection de carburant, pourvu d'une soupape d'injection de carburant et d'un élément de désaccouplement

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EP17171749.9A Active EP3244057B1 (fr) 2012-11-20 2013-09-24 Dispositif pour un système d'injection de carburant comprenant un injecteur de carburant et un élément de découplage

Country Status (8)

Country Link
US (1) US10072623B2 (fr)
EP (2) EP3244057B1 (fr)
JP (1) JP6039153B2 (fr)
KR (1) KR20150084863A (fr)
CN (1) CN104797808B (fr)
BR (1) BR112015011059A2 (fr)
DE (1) DE102012221134A1 (fr)
WO (1) WO2014079609A1 (fr)

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DE102008054591A1 (de) 2008-12-12 2010-06-17 Robert Bosch Gmbh Entkopplungselement für eine Brennstoffeinspritzvorrichtung
US7823565B2 (en) * 2009-01-14 2010-11-02 Ford Global Technologies Fuel injection system for internal combustion engine with injector isolator ring
DE112010002642B4 (de) * 2009-06-29 2022-12-22 Illinois Tool Works Inc. Brennstoffeinspritzdüseneinrichtung
US8069842B2 (en) * 2009-07-02 2011-12-06 Robert Bosch Gmbh Injector mounting assembly
WO2011121728A1 (fr) * 2010-03-30 2011-10-06 トヨタ自動車 株式会社 Isolateur de vibration pour injecteur de carburant et structure porteuse pour injecteur de carburant
EP2469069A1 (fr) 2010-12-27 2012-06-27 Continental Automotive GmbH Élément d'amortissement pour soupape d'injection

Also Published As

Publication number Publication date
EP3244057B1 (fr) 2019-12-18
EP2923067A1 (fr) 2015-09-30
US10072623B2 (en) 2018-09-11
JP6039153B2 (ja) 2016-12-07
CN104797808B (zh) 2018-02-23
US20160169176A1 (en) 2016-06-16
CN104797808A (zh) 2015-07-22
BR112015011059A2 (pt) 2017-07-11
DE102012221134A1 (de) 2014-05-22
JP2015535052A (ja) 2015-12-07
KR20150084863A (ko) 2015-07-22
WO2014079609A1 (fr) 2014-05-30
EP3244057A1 (fr) 2017-11-15

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