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
  • F02M2200/09—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
  • F02M2200/85—Mounting of fuel injection apparatus
  • F02M2200/858—Mounting of fuel injection apparatus sealing arrangements between injector and engine

Definitions

• the invention is based on a decoupling element for a
• Fuel injection device according to the preamble of the main claim.
• Fuel injection device shown in which a flat intermediate element is provided on a built-in a receiving bore of a cylinder head of an internal combustion engine fuel injection valve.
• such intermediate elements are stored as support elements in the form of a washer on a shoulder of the receiving bore of the cylinder head.
• Fuel injection valve ensured.
• the fuel injector is particularly suitable for use in fuel injection systems of
• Fuel injection device is already known from DE 101 08 466 AI.
• the intermediate element is a sub-ring having a circular cross-section which is frusto-conical in a region in which both the fuel injection valve and the wall of the receiving bore in the cylinder head are frustoconical run, arranged and serves as a compensation element for storage and support of the fuel injection valve.
• the known from DE 100 27 662 AI intermediate element comprises a basic and
• Carrier body in which a sealant is inserted which is penetrated by a nozzle body of the fuel injection valve.
• a multilayer compensating element which consists of two rigid rings and a sandwiched therebetween elastic intermediate ring
• This compensating element allows both a tilting of the fuel injection valve to the axis of the receiving bore over a relatively large angular range as well as a radial displacement of the fuel injection valve from the central axis of the receiving bore.
• the damping material is composed of a damping material.
• Damping material made of metal, rubber or PTFE is chosen and designed so that a noise attenuation by the operation of the
• the intermediate element must, however, include four to six layers to achieve a desired damping effect.
• US 6,009,856 A also proposes to surround the fuel injector with a sleeve and to fill the resulting gap with an elastic, noise-damping mass. This type of noise reduction is very complex, easy to install and expensive.
• the decoupling element according to the invention for a fuel injection device with the characterizing features of claim 1 has the advantage that in a very simple construction improved noise attenuation is achieved.
• the decoupling element has a non-linear, progressive spring characteristic, resulting in several positive and advantageous aspects when installing the decoupling element in a fuel injection device with injectors for direct fuel injection.
• the low stiffness of the decoupling element at idle point allows effective decoupling of the fuel injection valve from the cylinder head and thereby reduced in the
• the high rigidity at nominal system pressure provides for a low total fuel injector movement during vehicle operation, thereby ensuring the durability of the seal rings
• the spring ring are designed to be progressively targeted.
• Decoupling is characterized by a low height, making it similar to a plate spring can be used even in a small space.
• Decoupling element also has a high fatigue strength even at high temperatures.
• the non-linear spring characteristic can be adapted by the geometry of the spring ring specifically to the respective application.
• the stiffness can also be changed by changing the cone angle of the conical disk, whereby the
• Fuel injection device possible.
• Fuel injector rests in the cylinder head.
• Figure 1 is a partially illustrated fuel injection device in a
• Figure 2 is a mechanical equivalent circuit diagram of the support of
• Direct fuel injection which represents a common spring mass damper system
• FIG. 3 shows the transmission behavior of a spring-mass-damper system shown in FIG. 2 with a gain at low frequencies in the region of the resonant frequency f R and an isolation range above the decoupling frequency f E ,
• Figure 4 is a non-linear, progressive spring characteristic for realization
• FIG. 5 shows a cross section through an inventive decoupling element in a mounting situation on a fuel injection valve in the region of the disk-shaped intermediate element shown in FIG. 1 and
• FIG Figures 6 to 9 are cross-sections through alternative embodiments of spring washers. Description of the embodiments
• FIG. 1 is as an embodiment of a valve in the form of an injection valve 1 for fuel injection systems of mixture compaction spark-ignited
• the fuel injection valve 1 is part of the fuel injection device. With a downstream end, the fuel injection valve 1, which is in the form of a direct-injection injector for injecting fuel directly into a combustion chamber 25 of the
• Internal combustion engine is designed in a receiving bore 20 of a
• Cylinder head 9 installed.
• Receiving bore 20 is a flat intermediate element 24 is inserted, which as
• Supporting element is designed in the form of a washer.
• Fuel injection valve 1 ensured.
• the fuel injection valve 1 has at its upstream end 3 a
• the fuel injection valve 1 is inserted into a receiving opening 12 of the connection piece 6 of the fuel distribution line 4.
• Connecting piece 6 goes in this case e.g. one piece from the actual
• Fuel distribution line 4 and has upstream of the receiving opening 12 a smaller diameter flow opening 15, via which the flow of the fuel injection valve 1 takes place.
• the fuel injection valve 1 has an electrical connection plug 8 for the electrical contacting for actuating the fuel injection valve 1.
• a holding-down device 10 is provided between the fuel injection valve 1 and the connecting piece 6.
• the hold-down 10 is designed as a bow-shaped component, e.g. as punching and bending part.
• the hold-down device 10 has a part-ring-shaped base element 11, from which a hold-down bar 13 extends, which abuts against a downstream end face 14 of the connecting piece 6 on the fuel distributor line 4 in the installed state.
• the object of the invention is to achieve over the known Bacettiariaen in a simple manner improved noise attenuation, especially in noise-critical idling operation, by a targeted design and geometry of the intermediate element 24.
• the relevant source of noise of the fuel injection valve 1 in the direct high-pressure injection are introduced during the valve operation in the cylinder head 9 forces (structure-borne sound), which lead to a structural excitation of the cylinder head 9 and from this as
• Airborne sound are radiated.
• a minimization of the introduced into the cylinder head 9 forces should be sought.
• this can be done by influencing the transfer behavior between the
• Fuel injection valve 1 and the cylinder head 9 can be achieved.
• the bearing of the fuel injector 1 may be mapped on the passive intermediate member 24 in the receiving bore 20 of the cylinder head 9 as a conventional spring-mass-damper system, as shown in Figure 2.
• the mass M of the cylinder head 9 can be compared to the mass m of the fuel injection valve 1 in the first approximation as infinitely large be accepted.
• the transmission behavior of such a system is characterized by a gain at low frequencies in the range of
• Resonance frequency f R and an isolation region above the decoupling frequency f E (see Figure 3).
• the aim of the invention is the design of an intermediate element 24 under the priority use of elastic isolation (decoupling) for
• the invention comprises on the one hand the definition and design of a suitable spring characteristic, taking into account the typical requirements and
• an intermediate element 24 which is able to map the characteristic of the spring characteristic defined in this way and can be adapted to the specific boundary conditions of the injection system via a choice of simple geometric parameters.
• the decoupling of the fuel injection valve 1 from the cylinder head 9 by means of a low spring stiffness c of the decoupling system according to the invention, which is formed from a spring ring 30 and a conical disk 31, is made difficult in addition to the small space by restricting the maximum permissible movement of the fuel injection valve 1 during engine operation.
• a low spring stiffness c of the decoupling system according to the invention which is formed from a spring ring 30 and a conical disk 31
• Fuel injector 1 must orientate and for an effective decoupling is too big. As nominal operating pressures are likely to increase further in the future, this problem will continue to increase.
• Fuel injection valve 1 between idle and system pressure.
• the decoupling system according to the invention of a spring ring 30 and a conical disk 31 is constructed, in particular the spring ring 30 generates a significantly progressive spring characteristic due to its special geometric design.
• the spring ring 30 differs significantly from conventional disc springs, which basically initially have only a linear or degressive characteristic curve.
• a progressive course is achieved only when they are almost completely loaded on "block".
• FIG. 5 shows a cross section through a decoupling system according to the invention in a mounting situation on a fuel injection valve 1 in the region of the disk-shaped intermediate element 24 shown in FIG
• the progressiveness of the spring ring 30 can be easily designed by adjusting a few geometric parameters.
• the contour of the spring ring 30 is characterized in that starting from an outer plane, vertical lateral surface is followed by a rounded, convex convex inner contour.
• the spring ring 30 has a semicircular cross-section, in which the rounded boundary is directed inwards.
• the cross-section of the spring ring 30 may also be formed in the direction of a triangle rather, in which case sections should be provided with radii, or be formed circular.
• Decoupling system with a conical valve housing surface 21 Decoupling system with a conical valve housing surface 21.
• the design of the spring ring 30 is chosen so that it is ideal only for a 3-point contact of the spring ring 30 on the valve body 22 of the
• Fuel injection valve 1 comes.
• the three contact points can be located at a circumferential distance of approximately 135 ° -90 ° -135 °, but also distributed equally.
• a solid-state joint is integrated, which allows a tolerance compensation to avoid a geometric overdetermination.
• the decoupling system is supplemented by the spring ring 30 through the
• the conical disk 31 has a hexagonal cross-section, wherein the hexagonal cross section is not honeycombed uniformly, but is elongated, so seen in cross section two longer and four shorter boundary sides of the conical disk 31 are present, but in total circulate completely.
• the spring ring 30 is supported with its at least partially rounded, convex convex inner contour on the side facing away from the valve housing surface 21 on one of the two longer boundary sides of the
• Conical disk 31 from while the conical disk 31 rests with one of the four shorter boundary sides of the receiving bore 20.
• the receiving bore 20 of the cylinder head 9 has in this case a shoulder 23 which is perpendicular to the total extent of the receiving bore 20.
• the conical disk 31 is, as shown in Figure 5, used with its conical taper upwards, is also conceivable installation of a conical disk 31 with a conical taper downwards.
• the conical disk 31 may also have, for example, a triangular or pentagonal shape in cross section.
• spring rings 30 shown.
• the spring ring 30 in its cross section for example, triangular with additional upper and lower flats (Figure 6), triangular with an outer convex curved
• Decoupling system is realized by a shortening of the lever arm by reducing the free arc length with increasing load of the decoupling system.
• a smaller lever arm causes a higher stiffness of the
• the Hebelarmverkürzung is achieved by the nestling of the spring ring 30 on the respective two contact partners, so the valve housing 22 with its valve housing surface 21 and the conical disk 31.
• the nonlinear spring characteristic can be adapted by the geometry of the spring ring 30 specifically to the respective application. If necessary, the rigidity can also be changed by changing the cone angle of the conical disk 31, with which the contact surface to the spring ring 30 can be changed.

Landscapes

• 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)

Applications Claiming Priority (2)

Publications (1)

Family

ID=47222049

Family Applications (1)

Country Status (9)

Families Citing this family (5)

Citations (2)

Family Cites Families (15)

• 2011
  • 2011-12-20 DE DE102011089274A patent/DE102011089274A1/de not_active Withdrawn
• 2012
  • 2012-11-09 JP JP2014547790A patent/JP2015500948A/ja active Pending
  • 2012-11-09 BR BR112014006407A patent/BR112014006407A2/pt not_active Application Discontinuation
  • 2012-11-09 EP EP12790836.6A patent/EP2795097A1/de not_active Ceased
  • 2012-11-09 IN IN4430CHN2014 patent/IN2014CN04430A/en unknown
  • 2012-11-09 US US14/367,698 patent/US9938947B2/en active Active
  • 2012-11-09 WO PCT/EP2012/072317 patent/WO2013091998A1/de active Application Filing
  • 2012-11-09 KR KR1020147016800A patent/KR20140103964A/ko active IP Right Grant
  • 2012-11-09 CN CN201280063543.7A patent/CN104024625B/zh active Active
• 2016
  • 2016-08-08 JP JP2016155250A patent/JP2017015092A/ja active Pending

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