EP2376765A1 - Decoupling element for a fuel injection device - Google Patents

Decoupling element for a fuel injection device

Info

Publication number
EP2376765A1
EP2376765A1 EP09771734A EP09771734A EP2376765A1 EP 2376765 A1 EP2376765 A1 EP 2376765A1 EP 09771734 A EP09771734 A EP 09771734A EP 09771734 A EP09771734 A EP 09771734A EP 2376765 A1 EP2376765 A1 EP 2376765A1
Authority
EP
European Patent Office
Prior art keywords
decoupling element
fuel injection
injection valve
decoupling
receiving bore
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
EP09771734A
Other languages
German (de)
French (fr)
Other versions
EP2376765B1 (en
Inventor
Michael Fischer
Andrej Elsinger
Frank-Holger Schoefer
Corren Heimgaertner
Michael Kleindl
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 EP2376765A1 publication Critical patent/EP2376765A1/en
Application granted granted Critical
Publication of EP2376765B1 publication Critical patent/EP2376765B1/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

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
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • 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

Definitions

  • the invention relates to a decoupling element for a fuel injection device according to the preamble of the main claim.
  • FIG 1 an example of a known from the prior art fuel injection device is 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.
  • manufacturing and assembly tolerances are compensated and ensured a lateral force-free storage even with slight misalignment of the fuel injector.
  • the fuel injector is particularly suitable for use in fuel injection systems of mixture-compression spark-ignition internal combustion engines.
  • 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.
  • intermediate elements for fuel injectors u.a. also known from DE 100 27 662 A1, DE 100 38 763 A1 and EP 1 223 337 A1. These intermediate elements are characterized by the fact that they are all constructed in several parts or multi-layered and z.T. Should take over sealing and damping functions.
  • the known from DE 100 27 662 Al intermediate element comprises a base and carrier body, in which a sealing means is used, which is penetrated by a nozzle body of the fuel injection valve.
  • a multilayer compensating element is known, which is composed 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.
  • a likewise multi-layer intermediate element is also known from EP 1 223 337 A1, wherein this intermediate element is composed of several washers, which consist of a damping material.
  • the damping material made of metal, rubber or PTFE is chosen and designed so that a noise attenuation of the vibrations generated by the operation of the fuel injection valve and noise is made possible.
  • the intermediate element must, however, include four to six layers to achieve a desired damping effect.
  • Disc-shaped damping elements for a fuel injector in particular an injector for injecting diesel fuel in a common-rail system, are also already known from DE 10 2005 057 313 A1.
  • the damping discs should be introduced between the injection valve and the wall of the receiving bore in the cylinder head so that even at high contact forces damping of structure-borne noise is made possible, so that the noise emissions be reduced.
  • the annular damping element abuts with an annular surface on the support surface of the cylinder head and with a circumferential bead on the conical support surface of the injector.
  • this overall arrangement has the disadvantage that the contact points of the damping element on the cylinder head and the injector seen in the radial direction are quite close to each other and the
  • Damping element is made quite stiff due to its installation situation. This has the consequence that in this arrangement still clearly audible noise emissions.
  • 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 design improved noise reduction by decoupling or isolation is achieved.
  • the spring stiffness of the decoupling element is selected to be so low and the decoupling element is placed between the valve housing of the fuel injection valve and the wall of the receiving bore, that the Entkoppelresonanz f R is in the frequency range below 2.5 kHz. In this way, arise during installation of the
  • Decoupling element in a fuel injection device with injectors for a direct fuel injection, in particular with piezoactuator-driven injectors several positive and advantageous aspects.
  • the low rigidity of the decoupling element enables effective decoupling of the fuel injection valve from the cylinder head and thereby significantly reduces in noise-critical operation the introduced into the cylinder head structure-borne sound power and thus the radiated from the cylinder head noise.
  • the measures listed in the dependent claims advantageous refinements and improvements of the claim 1 fuel injection device are possible.
  • the receiving bore for the fuel injection valve is formed in a cylinder head and the receiving bore has a shoulder which is perpendicular to the extension of the receiving bore and on which the decoupling element partially rests with its radially outer bearing region and the fuel injection valve again with a vertical extending to the valve longitudinal axis outer contour of the valve housing rests against the radially inner bearing region of the decoupling element.
  • the decoupling element is annular disk-shaped and overall cup-shaped or dish-shaped.
  • the cross section of the decoupling element has an S-shaped contour with two radii to the support areas. The installation can be done both orientations of the decoupling element, so cup-shaped with the bottom down or inversely cup-shaped with the bottom up.
  • the decoupling element is designed in a particularly advantageous manner with a non-linear progressive spring characteristic or with a non-linear degressive spring characteristic.
  • Show it 1 shows a partially illustrated fuel injection device in a known embodiment with a disc-shaped intermediate element
  • Figure 2 is a mechanical equivalent circuit diagram of the support of
  • Fuel injection valve in the cylinder head in direct fuel injection which is a common spring mass
  • FIG. 3 shows the transmission behavior of a spring mass shown in FIG.
  • Damper system with a gain at low frequencies in the range of the resonant frequency f R and an isolation range above the decoupling frequency f E ,
  • FIG. 4 shows a partially illustrated fuel injection device with a decoupling element according to the invention
  • FIG. 5 shows a cross section through a first embodiment of a decoupling element according to the invention according to FIG. 4
  • FIG. 6 shows a cross section through a second embodiment of a decoupling element according to the invention in a two-part solution
  • Figure 7 shows a third embodiment of an inventive
  • FIG. 8 shows a cross-section through the decoupling element according to the invention along the line VIII-VIII in FIG. 7, FIG.
  • Figure 9 shows a fourth embodiment of an inventive
  • FIG. 10 shows a cross section through the decoupling element according to the invention along the line X-X in FIG. 9, FIG.
  • FIG. 11 shows a partially illustrated fuel injection device with a fifth inventive decoupling element
  • Figure 12 is a partially illustrated fuel injection device with a sixth decoupling element according to the invention
  • Figure 13 is a non-linear, progressive spring characteristic for a decoupling element according to the invention, which can be used in an alternating pressure system
  • Figure 14 is a non-linear, degressive spring characteristic for a decoupling element according to the invention, which can be used in a constant pressure system.
  • 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 of the fuel injection valve 1, which is designed in the form of a direct-injection injector for injecting fuel directly into a combustion chamber 25 of the internal combustion engine, in a receiving bore 20 of a
  • Cylinder head 9 installed.
  • a flat intermediate element 24 is inserted, which is designed in the form of a washer.
  • Fuel injection valve 1 towards inside has a curved contact surface, manufacturing and assembly tolerances are compensated and ensured a lateral force-free storage even with slight misalignment of the fuel injection valve 1.
  • the fuel injection valve 1 has at its inlet-side end 3 a plug connection to a fuel rail (fuel rail) 4, which by a sealing ring 5 between a connecting piece 6 of the fuel distribution line 4, the is shown in section, and an inlet nozzle 7 of the fuel injection valve 1 is sealed.
  • the fuel injection valve 1 is inserted into a receiving opening 12 of the connection piece 6 of the fuel distribution line 4.
  • the connecting piece 6 is, for example, in one piece from the actual fuel distributor line 4 and has upstream of the receiving opening 12 a smaller diameter flow opening 15 through 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 a 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 Bacetti- and Dämpfungsscalenfiten in a simple manner improved noise reduction, especially in noise-critical idling operation but also in constant pressure systems at system pressure, through a targeted design and geometry of the intermediate element 24.
  • the relevant noise source 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 are emitted from this as airborne sound.
  • a minimization of the introduced into the cylinder head 9 forces should be sought. In addition to reducing the forces caused by the injection, this can be achieved by influencing the transmission behavior between the fuel injection valve 1 and the cylinder head 9.
  • the bearing of the fuel injection valve 1 can 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 assumed to be infinite compared to the mass m of the fuel injection valve 1 in the first approximation.
  • the transmission behavior of such a system is characterized by a gain at low frequencies in the range of the resonant frequency f R (decoupling resonance) and an isolation range above the decoupling frequency f E (see FIG. 3).
  • Isolation as much of the audible frequency spectrum includes. This can be achieved via a lower rigidity c of the intermediate element 24.
  • the aim of the invention is the design of an intermediate element 24 under the priority use of elastic isolation (decoupling) for noise reduction.
  • the invention comprises on the one hand the definition and design of a suitable spring characteristic taking into account the typical requirements and boundary conditions in the direct fuel injection and on the other the design of an intermediate element 24 which is able to map the characteristic of the spring characteristic defined in this way and easier on a choice geometric parameter to the specific boundary conditions of the Injection system can be adjusted.
  • the spring characteristics will be referred to with reference to FIGS. 13 and 14.
  • Decoupling element 240 is called, in addition to the small space by a restriction of the permissible maximum movement of the fuel injection valve 1 during engine operation difficult.
  • Combustion engines inherently generate alternating forces over a wide frequency range at the interface to the installation environment of these injection valves. These alternating forces stimulate the environment to vibrate, which in turn can be emitted as a sound and perceived. To avoid this often perceived as disturbing noises are today
  • Damping elements for vibration damping energy dissipation
  • damping elements are also often composed of different materials and individual parts.
  • Damping elements of the known type aim at a reduction of the force input by broadband energy dissipation, e.g. by micro-slip or material damping in the interior of the damping element.
  • broadband energy dissipation e.g. by micro-slip or material damping in the interior of the damping element.
  • the adhesion between the fuel injection valve and the environment can be reduced only limited. Damping mechanisms are proportional to the displacement or speed over the damping element, for the formation of which a force must be present, which is thus introduced into the structure via the damping element.
  • a decoupling element 240 By contrast, with the aid of a decoupling element 240 according to the invention, the force flow from the fuel injection valve 1 can largely be prevented over a large frequency range above the decoupling resonance f R.
  • the decoupling resonance In this case, f R can be shifted into a frequency range in which the resonant amplification is largely masked by other engine noise components (FIG. 3).
  • the decoupling element 240 is characterized in that it serves to reduce the flow of force between the fuel injection valve 1 and its installation environment with the aim of reducing unwanted noise excitation in the surrounding structure.
  • the respective advantageous characteristics of the spring characteristic are included in the geometry design and material selection of the decoupling element 240, i. progressive behavior in constant pressure systems and degressive behavior in alternating pressure systems.
  • the decoupling element 240 in its training and installation situation thus primarily aims at the effect of the vibration decoupling and not the
  • the decoupling element 240 is designed with regard to its rigidity properties and not with respect to the damping behavior, as is the case with known damping disks. Damping, for example in the form of plastic or elastomer layers, but can be used in addition to control the Entkoppelresonanz f R.
  • FIG. 4 shows a partially illustrated fuel injection device with a decoupling element 240 according to the invention
  • FIG. 5 shows a cross section through a first embodiment of the decoupling element 240 according to FIG.
  • the decoupling element 240 is carried out in an advantageous manner as a metallic perforated disc, which extends in this respect annular.
  • a metallic material also lends itself to the extent that it can be processed with cost-effective production methods (for example, turning, deep-drawing) in order to be able to produce the desired geometries of the decoupling element 240 dimensionally stable.
  • the spring stiffness of the decoupling element 240 is low (20-40 kN / mm) in relation to the mass of the fuel injection valve 1, which is approximately 250 g. In this way, disturbing noises occurring in the gasoline direct injection of this type, which are typically in a frequency range of 2.5-14 kHz, can be intentionally decoupled in a broadband manner.
  • the Entkoppelresonanz f R is in the frequency range below 2.5 kHz, where it is masked by combustion and engine noise and not disturbing perceived.
  • the low spring stiffness of the decoupling element 240 is achieved by a plurality of targeted measures.
  • the decoupling element 240 has, when installed, two support regions 30, 31, a radially outer support region 30 and a radially inner support region 31. With the outer support region 30, the decoupling element 240 lies annularly on the e.g. perpendicular to the valve longitudinal axis extending shoulder 23 of the receiving bore 20 in the cylinder head 9. With the inner bearing region 31, the decoupling element 240 engages below the fuel injection valve 1 annularly in a region in which the valve housing 22, e.g. also has an outer contour perpendicular to the valve longitudinal axis, so that the fuel injection valve 1 rests against the inner edge region of the decoupling element 240.
  • the arrangement of the two support areas 30, 31 of the decoupling element 240 is selected so that the maximum possible lever arm is formed.
  • these bearing areas 30, 31 are placed in the widest possible edge areas on the outer diameter and on the inner diameter of the decoupling element 240.
  • the cross-section of the decoupling element 240 has an S-shaped contour with two large radii Rl, R2 to the outer and inner bearing area 30, 31, the common leg merges tangentially into each other. Overall, the decoupling element 240 thus has a cup-shaped or dish-shaped form. With this configuration, the space in the receiving bore 20 of the cylinder head 9 typically only small space is also used optimally in favor of the longest possible lever arm.
  • the two radii Rl, R2 of this contour are chosen in their size and their relationship to each other so that the most favorable Stress distribution in the material is created and the specified stiffness characteristic is optimally fulfilled. In the present case, these are, for example, an upper radius Rl of 2 mm and a lower radius R2 of 2.5 mm.
  • the decoupling element 240 With the cup-shaped design of the decoupling element 240, it is possible to use sufficient material thicknesses for the strength of the decoupling element 240, and this with a low overall Federsteif technik the decoupling element 240.
  • a metallic material can be a material thickness in the order of 0 , 5 mm.
  • the thickness of the material can also be varied on a decoupling element 240 in favor of an optimized stiffness characteristic over its radial extent.
  • FIG. 6 shows a cross section through a second embodiment of a decoupling element 240 according to the invention in a two-part solution.
  • this decoupling element 240 in turn has a cup-shaped shape.
  • This embodiment takes into account assembly requirements in which it can lead to an increased misalignment of the fuel injection valve 1.
  • the decoupling element 240 is therefore divided into two nested sub-elements 34, 35. While the radially outer and thus upper part of the element 34 has the radially outer bearing portion 30 and with the radius Rl bent outwardly, the radially inner and thus lower part element 35 is provided with the radially inner support portion 31 and with the radius R2 inwardly inflected.
  • the inner sub-element 35 is inserted into the outer sub-element 34. Together, the sub-elements 34, 35 of the decoupling element 240 allow a slight shift to compensate for a misalignment, but follow in their overall behavior the desired design target.
  • FIG. 8 shows a cross-section through the decoupling element 240 according to the invention along the line VIII-VIII in FIG. 7.
  • This variant of the decoupling element 240 is characterized in that the radially inner support region 31 is changed compared with the previously described solutions.
  • a plurality of spaced-apart support points 31a, 31b, 31c are provided, which are arranged distributed at a number of three support points 31a, 31b, 31c, for example at a distance of 120 °.
  • Such an embodiment also takes into account the possibility of a misalignment of the fuel injection valve 1 by the on the
  • Decoupling element 240 formed spherical support points 31a, 31b, 31c, within which the fuel injection valve 1 can align.
  • FIG. 10 shows a cross-section through the decoupling element 240 according to the invention along the line X-X in FIG. 9.
  • This further variant of embodiment catches a possible misalignment of the fuel injector 1 by a local weakening of the inner support region 31.
  • This local weakening of the radially inner bearing region 31 is e.g. achieved by radially extending slots 37 emanating from the inner diameter of the decoupling element 240 and e.g. extend to the inner radius R2.
  • these slots 37 or other stiffness reducing apertures may be provided in the number of three to twenty.
  • FIGS. 11 and 12 two further fuel injection devices are partially shown, which are provided with a fifth and a sixth decoupling element 240 according to the invention.
  • the decoupling element 240 shown in FIG. 11 differs, in particular, from the decoupling element 240 shown in FIGS. 4 and 5 by its inverse bulge upward.
  • the decoupling element 240 is in turn cup-shaped, but installed in an inverted position, i. the radially outer bearing area 30 on the shoulder 23 of the cylinder head 9 is lower than the radially inner bearing area 31 on the valve housing 22 of the fuel injection valve 1.
  • the exemplary embodiment of FIG. 12 indicates that the decoupling element 240 can also be designed in the form of a flat disk.
  • the decoupling element 240 can also be designed in the form of a flat disk.
  • the material thickness can also vary over the radial extent of the decoupling element 240 here.
  • FIGS. 13 and 14 are intended to further clarify how an advantageous decoupling of fuel injection valves 1 in fuel systems can be achieved by a targeted nonlinearity of the decoupling rigidity of the decoupling element 240.
  • the fuel pressure is kept constant high (constant pressure system), in other systems, the system pressure varies depending on load or speed (alternating pressure systems) - typically takes place in the latter at idle, a lowering of the fuel pressure.
  • the fuel pressure acts as a static hydraulic force on the fuel injection valve and claims the decoupling element 240 with a constant preload and thus displacement. In the linear case, this is proportional to the force. With regard to tightness and wear of the injector connections to the fuel system and cylinder head, there are maximum limits for the permissible travel. Therefore, according to the invention, a non-linear relationship between force and spring travel for the decoupling element 240 is selected here.
  • the spring travel during pressure build-up (eg at each engine start) is limited by a high spring stiffness; in operation, however, low stiffness is again effective for a wide decoupling range.
  • This characteristic is achieved by a degressive spring characteristic.

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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)

Abstract

The decoupling element according to the invention for a fuel injection device is particularly characterized in that a low-noise design is realized. The fuel injection device comprises at least one fuel injection valve (1) and a receiving bore (20) in a cylinder head (9) for the fuel injection valve (1) and the decoupling element (240) between a valve housing (22) of the fuel injection valve (1) and a wall of the receiving bore (20). The spring stiffness of the decoupling element (240) is so low and the decoupling element (240) is placed between the valve housing (22) of the fuel injection valve (1) and the wall of the receiving bore (20) in such a way that the decoupling resonance fR lies in the frequency range below 2.5 kHz. The fuel injection device is particularly suitable for directly injecting fuel into a combustion chamber of a mixture-compressing spark-ignited internal combustion engine.

Description

Beschreibung description
Titeltitle
Entkopplungselement für eine BrennstoffeinspritzvorrichtungDecoupling element for a fuel injection device
Stand der TechnikState of the art
Die Erfindung geht aus von einem Entkopplungselement für eine Brennstoffeinspritzvorrichtung nach der Gattung des Hauptanspruchs.The invention relates to a decoupling element for a fuel injection device according to the preamble of the main claim.
In der Figur 1 ist beispielhaft eine aus dem Stand der Technik bekannte Brennstoff einspritzvorrichtung gezeigt, bei der an einem in einer Aufnahmebohrung eines Zylinderkopfes einer Brennkraftmaschine eingebauten Brennstoffeinspritzventil ein flaches Zwischenelement vorgesehen ist. In bekannter Weise werden solche Zwischenelemente als Abstützelemente in Form einer Unterlegscheibe auf einer Schulter der Aufnahmebohrung des Zylinderkopfes abgelegt. Mit Hilfe solcher Zwischenelemente werden Fertigungs- und Montagetoleranzen ausgeglichen und eine querkraftfreie Lagerung auch bei leichter Schiefstellung des Brennstoffeinspritzventils sichergestellt. Die Brennstoffeinspritzvorrichtung eignet sich besonders für den Einsatz in Brennstoffeinspritzanlagen von gemischverdichtenden fremdgezündeten Brennkraftmaschinen.In the figure 1 an example of a known from the prior art fuel injection device is 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. In known manner, 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. With the help of such intermediate elements manufacturing and assembly tolerances are compensated and ensured a lateral force-free storage even with slight misalignment of the fuel injector. The fuel injector is particularly suitable for use in fuel injection systems of mixture-compression spark-ignition internal combustion engines.
Eine andere Art eines einfachen Zwischenelements für eine Brennstoffeinspritzvorrichtung ist bereits aus der DE 101 08 466 Al bekannt. Bei dem Zwischenelement handelt es ich um einen Unterlegring mit einem kreisförmigen Querschnitt, der in einem Bereich, in dem sowohl das Brennstoffeinspritzventil als auch die Wandung der Aufnahmebohrung im Zylinderkopf kegelstumpfförmig verlaufen, angeordnet ist und als Ausgleichselement zur Lagerung und Stützung des Brennstoffeinspritzventils dient.Another type of simple intermediate element for a fuel injection device is already known from DE 101 08 466 A1. 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.
Kompliziertere und in der Herstellung deutlich aufwändigere Zwischenelemente für Brennstoffeinspritzvorrichtungen sind u.a. auch aus den DE 100 27 662 Al, DE 100 38 763 Al und EP 1 223 337 Al bekannt. Diese Zwischenelemente zeichnen sich dadurch aus, dass sie allesamt mehrteilig bzw. mehrlagig aufgebaut sind und z.T. Dicht- und Dämpfungsfunktionen übernehmen sollen. Das aus der DE 100 27 662 Al bekannte Zwischenelement umfasst einen Grund- und Trägerkörper, in dem ein Dichtmittel eingesetzt ist, das von einem Düsenkörper des Brennstoffeinspritzventils durchgriffen wird. Aus der DE 100 38 763 Al ist ein mehrlagiges Ausgleichselement bekannt, das sich aus zwei starren Ringen und einem sandwichartig dazwischen angeordneten elastischen Zwischenring zusammensetzt. Dieses Ausgleichselement ermöglicht sowohl ein Verkippen des Brennstoffeinspritzventils zur Achse der Aufnahmebohrung über einen relativ großen Winkelbereich als auch ein radiales Verschieben des Brennstoffeinspritzventils aus der Mittelachse der Aufnahmebohrung.More complicated and in the production significantly more expensive intermediate elements for fuel injectors u.a. also known from DE 100 27 662 A1, DE 100 38 763 A1 and EP 1 223 337 A1. These intermediate elements are characterized by the fact that they are all constructed in several parts or multi-layered and z.T. Should take over sealing and damping functions. The known from DE 100 27 662 Al intermediate element comprises a base and carrier body, in which a sealing means is used, which is penetrated by a nozzle body of the fuel injection valve. From DE 100 38 763 Al a multilayer compensating element is known, which is composed 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.
Ein ebenfalls mehrlagiges Zwischenelement ist auch aus der EP 1 223 337 Al bekannt, wobei dieses Zwischenelement aus mehreren Unterlegscheiben zusammengesetzt ist, die aus einem Dämpfungsmaterial bestehen. Das Dämpfungsmaterial aus Metall, Gummi oder PTFE ist dabei so gewählt und ausgelegt, dass eine Geräuschdämpfung der durch den Betrieb des Brennstoffeinspritzventils erzeugten Vibrationen und Geräusche ermöglicht wird. Das Zwischenelement muss dazu jedoch vier bis sechs Lagen umfassen, um einen gewünschten Dämpfungseffekt zu erzielen.A likewise multi-layer intermediate element is also known from EP 1 223 337 A1, wherein this intermediate element is composed of several washers, which consist of a damping material. The damping material made of metal, rubber or PTFE is chosen and designed so that a noise attenuation of the vibrations generated by the operation of the fuel injection valve and noise is made possible. The intermediate element must, however, include four to six layers to achieve a desired damping effect.
Dämpfungselemente in Scheibenform für einen Kraftstoffinjektor, insbesondere einen Injektor zur Einspritzung von Dieselkraftstoff in einem Common-Rail-System sind auch bereits aus der DE 10 2005 057 313 Al bekannt. Die Dämpfungsscheiben sollen zwischen dem Einspritzventil und der Wandung der Aufnahmebohrung im Zylinderkopf derart eingebracht sein, dass auch bei hohen Anpresskräften eine Dämpfung von Körperschall ermöglicht ist, so dass die Geräuschemissionen reduziert werden. Das ringförmige Dämpfungselement liegt mit einer Ringfläche an der Stützfläche des Zylinderkopfes an und mit einer umlaufenden Wulst an der konischen Stützfläche des Injektors an. Diese Gesamtanordnung hat jedoch den Nachteil, dass die Auflagepunkte des Dämpfungselements am Zylinderkopf und am Injektor in radialer Richtung gesehen recht nahe beieinander liegen und dasDisc-shaped damping elements for a fuel injector, in particular an injector for injecting diesel fuel in a common-rail system, are also already known from DE 10 2005 057 313 A1. The damping discs should be introduced between the injection valve and the wall of the receiving bore in the cylinder head so that even at high contact forces damping of structure-borne noise is made possible, so that the noise emissions be reduced. The annular damping element abuts with an annular surface on the support surface of the cylinder head and with a circumferential bead on the conical support surface of the injector. However, this overall arrangement has the disadvantage that the contact points of the damping element on the cylinder head and the injector seen in the radial direction are quite close to each other and the
Dämpfungselement aufgrund seiner Einbausituation recht steif ausgeführt ist. Dies hat zur Folge, dass bei dieser Anordnung immer noch deutlich hörbare Geräuschemissionen vorliegen.Damping element is made quite stiff due to its installation situation. This has the consequence that in this arrangement still clearly audible noise emissions.
Zur Reduzierung von Geräuschemissionen schlägt die US 6,009,856 A zudem vor, das Brennstoffeinspritzventil mit einer Hülse zu umgeben und den entstehenden Zwischenraum mit einer elastischen, geräuschdämpfenden Masse auszufüllen. Diese Art der Geräuschdämpfung ist allerdings sehr aufwändig, montageunfreundlich und kostspielig.To reduce noise emissions, 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.
Vorteile der ErfindungAdvantages of the invention
Das erfindungsgemäße Entkopplungselement für eine Brennstoffeinspritzvorrichtung mit den kennzeichnenden Merkmalen des Anspruchs 1 hat den Vorteil, dass in sehr einfacher Bauweise eine verbesserte Geräuschminderung durch Entkopplung bzw. Isolation erreicht wird. Erfindungsgemäß ist die Federsteifigkeit des Entkopplungselements derart niedrig gewählt und ist das Entkopplungselement so zwischen dem Ventilgehäuse des Brennstoffeinspritzventils und der Wandung der Aufnahmebohrung platziert, dass die Entkoppelresonanz fR im Frequenzbereich unter 2,5 kHz liegt. Auf diese Weise ergeben sich beim Einbau desThe 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 design improved noise reduction by decoupling or isolation is achieved. According to the invention, the spring stiffness of the decoupling element is selected to be so low and the decoupling element is placed between the valve housing of the fuel injection valve and the wall of the receiving bore, that the Entkoppelresonanz f R is in the frequency range below 2.5 kHz. In this way, arise during installation of the
Entkopplungselements in einer Brennstoff einspritzvorrichtung mit Injektoren für eine Kraftstoffdirekteinspritzung, insbesondere mit piezoaktorbetriebenen Injektoren mehrere positive und vorteilhafte Aspekte. Die niedrige Steifigkeit des Entkopplungselements ermöglicht eine effektive Entkopplung des Brennstoffeinspritzventils vom Zylinderkopf und verringert dadurch im geräuschkritischen Betrieb deutlich die in den Zylinderkopf eingeleitete Körperschallleistung und damit das vom Zylinderkopf abgestrahlte Geräusch. Durch die in den Unteransprüchen aufgeführten Maßnahmen sind vorteilhafte Weiterbildungen und Verbesserungen der im Anspruch 1 angegebenen Brennstoffeinspritzvorrichtung möglich.Decoupling element in a fuel injection device with injectors for a direct fuel injection, in particular with piezoactuator-driven injectors several positive and advantageous aspects. The low rigidity of the decoupling element enables effective decoupling of the fuel injection valve from the cylinder head and thereby significantly reduces in noise-critical operation the introduced into the cylinder head structure-borne sound power and thus the radiated from the cylinder head noise. The measures listed in the dependent claims advantageous refinements and improvements of the claim 1 fuel injection device are possible.
Besonders vorteilhaft ist es, das Entkopplungselement so auszubilden, dass die beiden Auflagebereiche des Entkopplungselements im radial äußeren und radial inneren Randbereich derart weitestmöglich voneinander beabstandet gewählt sind, dass ein maximal möglicher Hebelarm entsteht.It is particularly advantageous to design the decoupling element in such a way that the two bearing areas of the decoupling element in the radially outer and radially inner edge area are selected as far apart as possible so that a maximum possible lever arm is created.
Dazu ist es von Vorteil, dass die Aufnahmebohrung für das Brennstoffeinspritzventil in einem Zylinderkopf ausgebildet ist und die Aufnahmebohrung eine Schulter besitzt, die senkrecht zur Erstreckung der Aufnahmebohrung verläuft und auf der das Entkopplungselement mit seinem radial äußeren Auflagebereich teilweise aufliegt und das Brennstoffeinspritzventil wiederum mit einer senkrecht zur Ventillängsachse verlaufenden Außenkontur des Ventilgehäuses an dem radial inneren Auflagebereich des Entkopplungselements anliegt.For this purpose, it is advantageous that the receiving bore for the fuel injection valve is formed in a cylinder head and the receiving bore has a shoulder which is perpendicular to the extension of the receiving bore and on which the decoupling element partially rests with its radially outer bearing region and the fuel injection valve again with a vertical extending to the valve longitudinal axis outer contour of the valve housing rests against the radially inner bearing region of the decoupling element.
In vorteilhafter Weise ist das Entkopplungselement ringscheibenförmig und insgesamt napf- bzw. tellerförmig ausgebildet. Der Querschnitt des Entkopplungselements hat dabei eine S-förmige Kontur mit zwei Radien zu den Auflagebereichen hin. Der Einbau kann beiden Ausrichtungen des Entkopplungselements erfolgen, also napfförmig mit dem Boden nach unten oder invers napfförmig mit dem Boden nach oben.In an advantageous manner, the decoupling element is annular disk-shaped and overall cup-shaped or dish-shaped. The cross section of the decoupling element has an S-shaped contour with two radii to the support areas. The installation can be done both orientations of the decoupling element, so cup-shaped with the bottom down or inversely cup-shaped with the bottom up.
Je nach Einsatz in einem Wechseldrucksystem oder in einem Konstantdrucksystem ist das Entkopplungselement in besonders vorteilhafter Weise mit einer nicht-linearen progressiven Federkennlinie oder mit einer nicht-linearen degressiven Federkennlinie ausgelegt.Depending on the use in an alternating pressure system or in a constant pressure system, the decoupling element is designed in a particularly advantageous manner with a non-linear progressive spring characteristic or with a non-linear degressive spring characteristic.
Zeichnungdrawing
Ausführungsbeispiele der Erfindung sind in der Zeichnung vereinfacht dargestellt und in der nachfolgenden Beschreibung näher erläutert. Es zeigen Figur 1 eine teilweise dargestellte Brennstoffeinspritzvorrichtung in einer bekannten Ausführung mit einem scheibenförmigen Zwischenelement,Embodiments of the invention are shown in simplified form in the drawing and explained in more detail in the following description. Show it 1 shows a partially illustrated fuel injection device in a known embodiment with a disc-shaped intermediate element,
Figur 2 ein mechanisches Ersatzschaltbild der Abstützung desFigure 2 is a mechanical equivalent circuit diagram of the support of
Brennstoffeinspritzventils im Zylinderkopf bei der Kraftstoffdirekteinspritzung, das ein gewöhnliches Feder- Masse-Fuel injection valve in the cylinder head in direct fuel injection, which is a common spring mass
Dämpfer-System wiedergibt,Damper system reproduces,
Figur 3 das Übertragungsverhalten eines in Figur 2 gezeigten Feder- Masse-FIG. 3 shows the transmission behavior of a spring mass shown in FIG.
Dämpfer-Systems mit einer Verstärkung bei niedrigen Frequenzen im Bereich der Resonanzfrequenz fR und einem Isolationsbereich oberhalb der Entkoppelfrequenz fE,Damper system with a gain at low frequencies in the range of the resonant frequency f R and an isolation range above the decoupling frequency f E ,
Figur 4 eine teilweise dargestellte Brennstoffeinspritzvorrichtung mit einem erfindungsgemäßen Entkopplungselement,FIG. 4 shows a partially illustrated fuel injection device with a decoupling element according to the invention;
Figur 5 einen Querschnitt durch eine erste Ausführung eines erfindungsgemäßen Entkopplungselements gemäß Figur 4, Figur 6 einen Querschnitt durch eine zweite Ausführung eines erfindungsgemäßen Entkopplungselements in einer zweiteiligen Lösung,5 shows a cross section through a first embodiment of a decoupling element according to the invention according to FIG. 4, FIG. 6 shows a cross section through a second embodiment of a decoupling element according to the invention in a two-part solution,
Figur 7 eine dritte Ausführung eines erfindungsgemäßenFigure 7 shows a third embodiment of an inventive
Entkopplungselements in einer Draufsicht, Figur 8 einen Querschnitt durch das erfindungsgemäße Entkopplungselement entlang der Linie VIII-VIII in Figur 7,8 shows a cross-section through the decoupling element according to the invention along the line VIII-VIII in FIG. 7, FIG.
Figur 9 eine vierte Ausführung eines erfindungsgemäßenFigure 9 shows a fourth embodiment of an inventive
Entkopplungselements in einer Draufsicht,Decoupling element in a plan view,
Figur 10 einen Querschnitt durch das erfindungsgemäße Entkopplungselement entlang der Linie X-X in Figur 9,10 shows a cross section through the decoupling element according to the invention along the line X-X in FIG. 9, FIG.
Figur 11 eine teilweise dargestellte Brennstoffeinspritzvorrichtung mit einem fünften erfindungsgemäßen Entkopplungselement,11 shows a partially illustrated fuel injection device with a fifth inventive decoupling element, FIG.
Figur 12 eine teilweise dargestellte Brennstoff einspritzvorrichtung mit einem sechsten erfindungsgemäßen Entkopplungselement, Figur 13 eine nicht-lineare, progressive Federkennlinie für ein erfindungsgemäßes Entkopplungselement, das in einem Wechseldrucksystem zum Einsatz kommen kann und Figur 14 eine nicht-lineare, degressive Federkennlinie für ein erfindungsgemäßes Entkopplungselement, das in einem Konstantdrucksystem zum Einsatz kommen kann.Figure 12 is a partially illustrated fuel injection device with a sixth decoupling element according to the invention, Figure 13 is a non-linear, progressive spring characteristic for a decoupling element according to the invention, which can be used in an alternating pressure system and Figure 14 is a non-linear, degressive spring characteristic for a decoupling element according to the invention, which can be used in a constant pressure system.
Beschreibung der AusführungsbeispieleDescription of the embodiments
Zum Verständnis der Erfindung wird im Folgenden anhand der Figur 1 eine bekannte Ausführungsform einer Brennstoffeinspritzvorrichtung näher beschrieben. In der Figur 1 ist als ein Ausführungsbeispiel ein Ventil in der Form eines Einspritzventils 1 für Brennstoffeinspritzanlagen von gemischverdichtenden fremdgezündetenTo understand the invention, a known embodiment of a fuel injection device will be described in more detail below with reference to FIG. In the figure 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
Brennkraftmaschinen in einer Seitenansicht dargestellt. Das Brennstoffeinspritzventil 1 ist Teil der Brennstoffeinspritzvorrichtung. Mit einem stromabwärtigen Ende ist das Brennstoffeinspritzventil 1, das in Form eines direkt einspritzenden Einspritzventils zum direkten Einspritzen von Brennstoff in einen Brennraum 25 der Brennkraftmaschine ausgeführt ist, in eine Aufnahmebohrung 20 einesInternal combustion engine shown in a side view. The fuel injection valve 1 is part of the fuel injection device. With a downstream end of the fuel injection valve 1, which is designed in the form of a direct-injection injector for injecting fuel directly into a combustion chamber 25 of the internal combustion engine, in a receiving bore 20 of a
Zylinderkopfes 9 eingebaut. Ein Dichtring 2, insbesondere aus Teflon ®, sorgt für eine optimale Abdichtung des Brennstoffeinspritzventils 1 gegenüber der Wandung der Aufnahmebohrung 20 des Zylinderkopfes 9.Cylinder head 9 installed. A sealing ring 2, in particular of Teflon®, ensures optimum sealing of the fuel injection valve 1 with respect to the wall of the receiving bore 20 of the cylinder head 9.
Zwischen einem Absatz 21 eines Ventilgehäuses 22 (nicht gezeigt) oder einer unteren Stirnseite 21 eines Abstützelements 19 (Figur 1) und einer z.B. rechtwinklig zur Längserstreckung der Aufnahmebohrung 20 verlaufenden Schulter 23 der Aufnahmebohrung 20 ist ein flaches Zwischenelement 24 eingelegt, das in Form einer Unterlegscheibe ausgeführt ist. Mit Hilfe eines solchen Zwischenelements 24 bzw. zusammen mit einem steifen Abstützelement 19, das z.B. zumBetween a shoulder 21 of a valve housing 22 (not shown) or a lower end face 21 of a support element 19 (Figure 1) and a e.g. perpendicular to the longitudinal extent of the receiving bore 20 extending shoulder 23 of the receiving bore 20, a flat intermediate element 24 is inserted, which is designed in the form of a washer. With the aid of such an intermediate element 24 or together with a rigid support element 19, which e.g. to the
Brennstoffeinspritzventil 1 hin nach innen eine gewölbte Berührungsfläche besitzt, werden Fertigungs- und Montagetoleranzen ausgeglichen und eine querkraftfreie Lagerung auch bei leichter Schiefstellung des Brennstoffeinspritzventils 1 sichergestellt.Fuel injection valve 1 towards inside has a curved contact surface, manufacturing and assembly tolerances are compensated and ensured a lateral force-free storage even with slight misalignment of the fuel injection valve 1.
Das Brennstoffeinspritzventil 1 weist an seinem zulaufseitigen Ende 3 eine Steckverbindung zu einer Brennstoffverteilerleitung (Fuel Rail) 4 auf, die durch einen Dichtring 5 zwischen einem Anschlussstutzen 6 der Brennstoffverteilerleitung 4, der im Schnitt dargestellt ist, und einem Zulaufstutzen 7 des Brennstoffeinspritzventils 1 abgedichtet ist. Das Brennstoffeinspritzventil 1 ist in eine Aufnahmeöffnung 12 des Anschlussstutzens 6 der Brennstoffverteilerleitung 4 eingeschoben. Der Anschlussstutzen 6 geht dabei z.B. einteilig aus der eigentlichen Brennstoffverteilerleitung 4 hervor und besitzt stromaufwärts der Aufnahmeöffnung 12 eine durchmesserkleinere Strömungsöffnung 15, über die die Anströmung des Brennstoffeinspritzventils 1 erfolgt. Das Brennstoffeinspritzventil 1 verfügt über einen elektrischen Anschlussstecker 8 für die elektrische Kontaktierung zur Betätigung des Brennstoffeinspritzventils 1.The fuel injection valve 1 has at its inlet-side end 3 a plug connection to a fuel rail (fuel rail) 4, which by a sealing ring 5 between a connecting piece 6 of the fuel distribution line 4, the is shown in section, and an inlet nozzle 7 of the fuel injection valve 1 is sealed. The fuel injection valve 1 is inserted into a receiving opening 12 of the connection piece 6 of the fuel distribution line 4. The connecting piece 6 is, for example, in one piece from the actual fuel distributor line 4 and has upstream of the receiving opening 12 a smaller diameter flow opening 15 through 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.
Um das Brennstoffeinspritzventil 1 und die Brennstoffverteilerleitung 4 weitgehend radialkraftfrei voneinander zu beabstanden und das Brennstoffeinspritzventil 1 sicher in der Aufnahmebohrung des Zylinderkopfes niederzuhalten, ist ein Niederhalter 10 zwischen dem Brennstoffeinspritzventil 1 und dem Anschlussstutzen 6 vorgesehen. Der Niederhalter 10 ist als bügeiförmiges Bauteil ausgeführt, z.B. als Stanz-Biege- Teil. Der Niederhalter 10 weist ein teilringförmiges Grundelement 11 auf, von dem aus abgebogen ein Niederhaltebügel 13 verläuft, der an einer stromabwärtigen Endfläche 14 des Anschlussstutzens 6 an der Brennstoffverteilerleitung 4 im eingebauten Zustand anliegt.In order to space the fuel injection valve 1 and the fuel distributor line 4 substantially free of radial force from one another and to hold down the fuel injection valve 1 securely in the receiving bore of the cylinder head, 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 a 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.
Aufgabe der Erfindung ist es, gegenüber den bekannten Zwischenelemente- und Dämpfungsscheibenlösungen auf einfache Art und Weise eine verbesserte Geräuschminderung, vor allen Dingen im geräuschkritischen Leerlaufbetrieb aber auch in Konstantdrucksystemen bei Systemdruck, durch eine gezielte Auslegung und Geometrie des Zwischenelements 24 zu erreichen. Die maßgebliche Geräuschquelle des Brennstoffeinspritzventils 1 bei der direkten Hochdruckeinspritzung sind die während des Ventilbetriebs in den Zylinderkopf 9 eingeleiteten Kräfte (Körperschall), die zu einer strukturellen Anregung des Zylinderkopfs 9 führen und von diesem als Luftschall abgestrahlt werden. Um eine Geräuschverbesserung zu erreichen, ist daher eine Minimierung der in den Zylinderkopf 9 eingeleiteten Kräfte anzustreben. Neben der Verringerung der durch die Einspritzung verursachten Kräfte kann dies durch eine Beeinflussung des Übertragungsverhaltens zwischen dem Brennstoffeinspritzventil 1 und dem Zylinderkopf 9 erreicht werden. Im mechanischen Sinne kann die Lagerung des Brennstoffeinspritzventils 1 auf dem passiven Zwischenelement 24 in der Aufnahmebohrung 20 des Zylinderkopfes 9 als ein gewöhnliches Feder- Masse- Dämpfer-System abgebildet werden, wie dies in Figur 2 dargestellt ist. Die Masse M des Zylinderkopfs 9 kann dabei gegenüber der Masse m des Brennstoffeinspritzventils 1 in erster Näherung als unendlich groß angenommen werden. Das Übertragungsverhalten eines solchen Systems zeichnet sich durch eine Verstärkung bei niedrigen Frequenzen im Bereich der Resonanzfrequenz fR (Entkoppelresonanz) und einen Isolationsbereich oberhalb der Entkoppelfrequenz fE aus (siehe Figur 3).The object of the invention is to achieve over the known Zwischenelemente- and Dämpfungsscheibenlösungen in a simple manner improved noise reduction, especially in noise-critical idling operation but also in constant pressure systems at system pressure, through a targeted design and geometry of the intermediate element 24. The relevant noise source 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 are emitted from this as airborne sound. In order to achieve a noise improvement, therefore, a minimization of the introduced into the cylinder head 9 forces should be sought. In addition to reducing the forces caused by the injection, this can be achieved by influencing the transmission behavior between the fuel injection valve 1 and the cylinder head 9. In the mechanical sense, the bearing of the fuel injection valve 1 can 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 assumed to be infinite compared to the mass m of the fuel injection valve 1 in the first approximation. The transmission behavior of such a system is characterized by a gain at low frequencies in the range of the resonant frequency f R (decoupling resonance) and an isolation range above the decoupling frequency f E (see FIG. 3).
Ausgehend von diesem sich aus dem Feder- Masse- Dämpfer-System ergebenden Übertragungsverhalten ergeben sich zur Geräuschminderung mehrere Möglichkeiten: 1. Verschiebung der Eigenfrequenz zu kleineren Frequenzen, so dass derStarting from this resulting from the spring-mass damper system transmission behavior results in several ways to reduce noise: 1. shift the natural frequency to lower frequencies, so that the
Isolationsbereich einen möglichst großen Teil des hörbaren Frequenzspektrums umfasst. Dies kann über eine niedrigere Steifigkeit c des Zwischenelementes 24 erreicht werden.Isolation as much of the audible frequency spectrum includes. This can be achieved via a lower rigidity c of the intermediate element 24.
2. Erhöhung der Dämpfungseigenschaften (z.B. Reibung) des Zwischenelementes 24, um eine Abschwächung der Verstärkung bei niedrigen Frequenzen zu erreichen.2. Increase the damping characteristics (e.g., friction) of the intermediate element 24 to achieve attenuation of the gain at low frequencies.
Mit höheren Dämpfungseigenschaften verringert sich jedoch ebenso die Isolationswirkung in den höheren Frequenzbereichen.With higher damping properties, however, also reduces the insulation effect in the higher frequency ranges.
3. Eine Kombination der beiden vorgenannten Möglichkeiten.3. A combination of the two aforementioned possibilities.
Ziel der Erfindung ist die Auslegung eines Zwischenelementes 24 unter der vorrangigen Verwendung der elastischen Isolation (Entkopplung) zur Geräuschminderung. Die Erfindung umfasst dabei zum einen die Definition und Auslegung einer geeigneten Federkennlinie unter Berücksichtigung der typischen Anforderungen und Randbedingungen bei der Kraftstoffdirekteinspritzung und zum anderen die Auslegung eines Zwischenelementes 24, welches in der Lage ist, die Charakteristik der so definierten Federkennlinie abzubilden und über eine Wahl einfacher geometrischer Parameter an die spezifischen Randbedingungen des Einspritzsystems angepasst werden kann. Zu den Federkennlinien wird anhand der Figuren 13 und 14 Bezug genommen.The aim of the invention is the design of an intermediate element 24 under the priority use of elastic isolation (decoupling) for noise reduction. The invention comprises on the one hand the definition and design of a suitable spring characteristic taking into account the typical requirements and boundary conditions in the direct fuel injection and on the other the design of an intermediate element 24 which is able to map the characteristic of the spring characteristic defined in this way and easier on a choice geometric parameter to the specific boundary conditions of the Injection system can be adjusted. The spring characteristics will be referred to with reference to FIGS. 13 and 14.
Die Entkopplung des Brennstoffeinspritzventils 1 vom Zylinderkopf 9 mit Hilfe einer geringen Federsteifigkeit c des Zwischenelements 24, das im Folgenden alsThe decoupling of the fuel injection valve 1 from the cylinder head 9 by means of a low spring stiffness c of the intermediate element 24, hereinafter referred to as
Entkopplungselement 240 bezeichnet wird, wird neben dem geringen Bauraum durch eine Einschränkung der zulässigen Maximalbewegung des Brennstoffeinspritzventils 1 während des Motorbetriebs erschwert.Decoupling element 240 is called, in addition to the small space by a restriction of the permissible maximum movement of the fuel injection valve 1 during engine operation difficult.
Im Betrieb von Brennstoffeinspritzventilen zur Kraftstoffeinspritzung inIn the operation of fuel injection valves for fuel injection in
Verbrennungsmotoren entstehen an der Schnittstelle zur Einbauumgebung dieser Einspritzventile prinzipbedingt Wechselkräfte über einen breiten Frequenzbereich. Diese Wechselkräfte regen die Umgebung zu Schwingungen an, die wiederum als Geräusch abgestrahlt und wahrgenommen werden können. Zur Vermeidung dieser oftmals als störend wahrgenommenen Geräusche werden heuteCombustion engines inherently generate alternating forces over a wide frequency range at the interface to the installation environment of these injection valves. These alternating forces stimulate the environment to vibrate, which in turn can be emitted as a sound and perceived. To avoid this often perceived as disturbing noises are today
Dämpfungselemente zur Schwingungsdämpfung (Energiedissipation) beschrieben (siehe Abschnitt „Stand der Technik") und auch eingesetzt. Diese Dämpfungselemente sind dabei darüber hinaus häufig aus verschiedenen Materialen und Einzelteilen zusammengesetzt.Damping elements for vibration damping (energy dissipation) described (see section "state of the art") and also used.These damping elements are also often composed of different materials and individual parts.
Dämpfungselemente der bekannten Art zielen jedoch auf eine Reduktion des Krafteintrags durch breitbandige Energiedissipation z.B. durch Mikroschlupf oder Materialdämpfung im Inneren des Dämpfungselementes. Der Kraftschluss zwischen dem Brennstoffeinspritzventil und der Umgebung kann dabei aber nur begrenzt reduziert werden. Dämpfungsmechanismen sind proportional der Verschiebung bzw. Geschwindigkeit über dem Dämpfungselement, für deren Entstehung eine Kraft vorhanden sein muss, die damit über das Dämpfungselement in die Struktur eingeleitet wird.Damping elements of the known type, however, aim at a reduction of the force input by broadband energy dissipation, e.g. by micro-slip or material damping in the interior of the damping element. However, the adhesion between the fuel injection valve and the environment can be reduced only limited. Damping mechanisms are proportional to the displacement or speed over the damping element, for the formation of which a force must be present, which is thus introduced into the structure via the damping element.
Mithilfe eines erfindungsgemäßen Entkopplungselementes 240 kann dagegen über einen großen Frequenzbereich oberhalb der Entkoppelresonanz fR der Kraftfluss vom Brennstoffeinspritzventil 1 weitgehend unterbunden werden. Die Entkoppelresonanz fR kann dabei in einen Frequenzbereich verschoben werden, in der die resonante Verstärkung durch andere Motorgeräuschanteile weitgehend maskiert wird (Figur 3).By contrast, with the aid of a decoupling element 240 according to the invention, the force flow from the fuel injection valve 1 can largely be prevented over a large frequency range above the decoupling resonance f R. The decoupling resonance In this case, f R can be shifted into a frequency range in which the resonant amplification is largely masked by other engine noise components (FIG. 3).
Erfindungsgemäß zeichnet sich das Entkopplungselement 240 dadurch aus, dass es zur Reduzierung des Kraftflusses zwischen dem Brennstoffeinspritzventil 1 und seiner Einbauumgebung mit dem Ziel der Reduktion unerwünschter Geräuschanregung in der umgebenden Struktur dient. Bei den im Folgenden beschriebenen Ausführungsformen der Entkopplungselemente 240 sind die jeweils vorteilhafte Ausprägung der Federcharakteristik bei der Geometriegestaltung und Materialwahl des Entkopplungselementes 240 einbezogen, d.h. progressives Verhalten bei Konstantdrucksystemen und degressives Verhalten bei Wechseldrucksystemen.According to the invention, the decoupling element 240 is characterized in that it serves to reduce the flow of force between the fuel injection valve 1 and its installation environment with the aim of reducing unwanted noise excitation in the surrounding structure. In the embodiments of the decoupling elements 240 described below, the respective advantageous characteristics of the spring characteristic are included in the geometry design and material selection of the decoupling element 240, i. progressive behavior in constant pressure systems and degressive behavior in alternating pressure systems.
Das Entkopplungselement 240 in seiner Ausbildung und Einbausituation zielt dabei also primär auf den Effekt der Schwingungsentkopplung und nicht den derThe decoupling element 240 in its training and installation situation thus primarily aims at the effect of the vibration decoupling and not the
Schwingungsdämpfung. Das Entkopplungselement 240 wird hinsichtlich seiner Steifigkeitseigenschaften ausgelegt und nicht wie bei bekannten Dämpfungsscheiben hinsichtlich des Dämpfungsverhaltens. Dämpfung, z.B. in Form von Kunststoff- oder Elastomerschichten, kann jedoch ergänzend zur Beherrschung der Entkoppelresonanz fR eingesetzt werden.Vibration damping. The decoupling element 240 is designed with regard to its rigidity properties and not with respect to the damping behavior, as is the case with known damping disks. Damping, for example in the form of plastic or elastomer layers, but can be used in addition to control the Entkoppelresonanz f R.
In der Figur 4 ist eine teilweise dargestellte Brennstoffeinspritzvorrichtung mit einem erfindungsgemäßen Entkopplungselement 240 gezeigt, während in Figur 5 ein Querschnitt durch eine erste Ausführung des Entkopplungselements 240 gemäß Figur 4 gezeigt ist. Bei dieser Ausführung der Brennstoffeinspritzvorrichtung handelt es sich um ein System für die Benzindirekteinspritzung mit Brennstoffeinspritzventilen 1, die mit Piezoaktoren betrieben und z.B. in einem Konstantdrucksystem eingesetzt werden. Das Entkopplungselement 240 ist in vorteilhafter Weise als metallische Lochscheibe ausgeführt, die insofern ringförmig verläuft. Ein metallischer Werkstoff bietet sich auch insofern an, dass dieser mit kostengünstigen Fertigungsverfahren (z.B. Drehen, Tiefziehen) bearbeitbar ist, um die gewünschten Geometrien des Entkopplungselementes 240 maßhaltig herstellen zu können. Die Federsteifigkeit des Entkopplungselementes 240 ist im Verhältnis zur Masse des Brennstoffeinspritzventils 1, die bei ca. 250g liegt, niedrig gewählt (20 - 40 kN/mm). Damit können bei der Benzindirekteinspritzung dieses Typs auftretende störende Geräusche, die typischerweise in einem Frequenzbereich von 2,5 - 14 kHz liegen, gezielt breitbandig entkoppelt werden. Die Entkoppelresonanz fR liegt dabei im Frequenzbereich unter 2,5 kHz, wo sie von Verbrennungs- und Motorgeräuschen maskiert und nicht störend wahrgenommen wird.FIG. 4 shows a partially illustrated fuel injection device with a decoupling element 240 according to the invention, while FIG. 5 shows a cross section through a first embodiment of the decoupling element 240 according to FIG. In this embodiment of the fuel injection device is a system for gasoline direct injection with fuel injection valves 1, which are operated with piezo actuators and used for example in a constant pressure system. The decoupling element 240 is carried out in an advantageous manner as a metallic perforated disc, which extends in this respect annular. A metallic material also lends itself to the extent that it can be processed with cost-effective production methods (for example, turning, deep-drawing) in order to be able to produce the desired geometries of the decoupling element 240 dimensionally stable. The spring stiffness of the decoupling element 240 is low (20-40 kN / mm) in relation to the mass of the fuel injection valve 1, which is approximately 250 g. In this way, disturbing noises occurring in the gasoline direct injection of this type, which are typically in a frequency range of 2.5-14 kHz, can be intentionally decoupled in a broadband manner. The Entkoppelresonanz f R is in the frequency range below 2.5 kHz, where it is masked by combustion and engine noise and not disturbing perceived.
Die geringe Federsteifigkeit des Entkopplungselementes 240 wird durch mehrere gezielte Maßnahmen erreicht. Das Entkopplungselement 240 besitzt im eingebauten Zustand zwei Auflagebereiche 30, 31, einen radial äußeren Auflagebereich 30 und einen radial inneren Auflagebereich 31. Mit dem äußeren Auflagebereich 30 liegt das Entkopplungselement 240 ringförmig auf der z.B. senkrecht zur Ventillängsachse verlaufenden Schulter 23 der Aufnahmebohrung 20 im Zylinderkopf 9 auf. Mit dem inneren Auflagebereich 31 untergreift das Entkopplungselement 240 das Brennstoffeinspritzventil 1 ringförmig in einem Bereich, in dem das Ventilgehäuse 22 z.B. auch eine zur Ventillängsachse senkrecht verlaufende Außenkontur besitzt, so dass das Brennstoffeinspritzventil 1 an dem inneren Randbereich des Entkopplungselements 240 anliegt. Die Anordnung der beiden Auflagebereiche 30, 31 des Entkopplungselements 240 ist so gewählt, dass der maximal mögliche Hebelarm entsteht. Im gezeigten Ausführungsbeispiel sind diese Auflagebereiche 30, 31 insofern in die jeweils weitestmöglichen Randbereiche am Außendurchmesser und am Innendurchmesser des Entkopplungselements 240 gelegt.The low spring stiffness of the decoupling element 240 is achieved by a plurality of targeted measures. The decoupling element 240 has, when installed, two support regions 30, 31, a radially outer support region 30 and a radially inner support region 31. With the outer support region 30, the decoupling element 240 lies annularly on the e.g. perpendicular to the valve longitudinal axis extending shoulder 23 of the receiving bore 20 in the cylinder head 9. With the inner bearing region 31, the decoupling element 240 engages below the fuel injection valve 1 annularly in a region in which the valve housing 22, e.g. also has an outer contour perpendicular to the valve longitudinal axis, so that the fuel injection valve 1 rests against the inner edge region of the decoupling element 240. The arrangement of the two support areas 30, 31 of the decoupling element 240 is selected so that the maximum possible lever arm is formed. In the exemplary embodiment shown, these bearing areas 30, 31 are placed in the widest possible edge areas on the outer diameter and on the inner diameter of the decoupling element 240.
Der Querschnitt des Entkopplungselements 240 hat eine S-förmige Kontur mit zwei großen Radien Rl, R2 zum äußeren und inneren Auflagebereich 30, 31 hin, deren gemeinsamer Schenkel tangential ineinander übergeht. Insgesamt weist das Entkopplungselement 240 damit eine napf- bzw. tellerförmige Gestalt auf. Mit dieser Ausgestaltung wird der in der Aufnahmebohrung 20 des Zylinderkopfes 9 typischerweise nur geringe Bauraum ebenfalls zugunsten eines möglichst langen Hebelarmes optimal genutzt. Die beiden Radien Rl, R2 dieser Kontur sind in ihrer Größe und ihrem Verhältnis zueinander so gewählt, dass eine möglichst günstige Spannungsverteilung im Material entsteht und die vorgegebene Steifigkeitscharakteristik optimal erfüllt wird. Im vorliegenden Fall sind dies z.B. ein oberer Radius Rl von 2 mm und ein unterer Radius R2 von 2,5 mm.The cross-section of the decoupling element 240 has an S-shaped contour with two large radii Rl, R2 to the outer and inner bearing area 30, 31, the common leg merges tangentially into each other. Overall, the decoupling element 240 thus has a cup-shaped or dish-shaped form. With this configuration, the space in the receiving bore 20 of the cylinder head 9 typically only small space is also used optimally in favor of the longest possible lever arm. The two radii Rl, R2 of this contour are chosen in their size and their relationship to each other so that the most favorable Stress distribution in the material is created and the specified stiffness characteristic is optimally fulfilled. In the present case, these are, for example, an upper radius Rl of 2 mm and a lower radius R2 of 2.5 mm.
Mit der napfförmigen Ausgestaltung des Entkopplungselements 240 ist es ermöglicht, für die Festigkeit des Entkopplungselements 240 ausreichende Materialstärken verwenden zu können, und dies bei einer zugleich geringen Gesamt- Federsteif igkeit des Entkopplungselements 240. Bei einem metallischen Werkstoff kann dabei eine Materialstärke in der Größenordnung von 0,5 mm geeignet sein. Die Dicke des Materials kann aber auch an einem Entkopplungselement 240 zugunsten einer optimierten Steifigkeitscharakteristik über seine radiale Erstreckung variiert werden.With the cup-shaped design of the decoupling element 240, it is possible to use sufficient material thicknesses for the strength of the decoupling element 240, and this with a low overall Federsteif igkeit the decoupling element 240. In a metallic material can be a material thickness in the order of 0 , 5 mm. However, the thickness of the material can also be varied on a decoupling element 240 in favor of an optimized stiffness characteristic over its radial extent.
In der Figur 6 ist ein Querschnitt durch eine zweite Ausführung eines erfindungsgemäßen Entkopplungselements 240 in einer zweiteiligen Lösung gezeigt. Auch dieses Entkopplungselement 240 weist wiederum eine napfförmige Gestalt auf. Diese Ausführungsvariante berücksichtigt Montageanforderungen, bei denen es zu einer verstärkten Schiefstellung des Brennstoffeinspritzventils 1 kommen kann. Das Entkopplungselement 240 wird deshalb in zwei ineinander liegende Teilelemente 34, 35 aufgeteilt. Während das radial äußere und damit obere Teilelement 34 den radial äußeren Auflagebereich 30 aufweist und mit dem Radius Rl nach außen gebogen verläuft, ist das radial innere und damit untere Teilelement 35 mit dem radial inneren Auflagebereich 31 versehen und mit dem Radius R2 nach innen eingebogen. Das innere Teilelement 35 ist in das äußere Teilelement 34 eingelegt. Gemeinsam lassen die Teilelemente 34, 35 des Entkopplungselements 240 eine leichte Verschiebung zur Kompensation einer Schiefstellung zu, folgen aber in ihrem Gesamtverhalten dem gewünschten Auslegungsziel.FIG. 6 shows a cross section through a second embodiment of a decoupling element 240 according to the invention in a two-part solution. Again, this decoupling element 240 in turn has a cup-shaped shape. This embodiment takes into account assembly requirements in which it can lead to an increased misalignment of the fuel injection valve 1. The decoupling element 240 is therefore divided into two nested sub-elements 34, 35. While the radially outer and thus upper part of the element 34 has the radially outer bearing portion 30 and with the radius Rl bent outwardly, the radially inner and thus lower part element 35 is provided with the radially inner support portion 31 and with the radius R2 inwardly inflected. The inner sub-element 35 is inserted into the outer sub-element 34. Together, the sub-elements 34, 35 of the decoupling element 240 allow a slight shift to compensate for a misalignment, but follow in their overall behavior the desired design target.
Eine dritte Ausführung eines erfindungsgemäßen Entkopplungselements 240 ist in einer Draufsicht in Figur 7 dargestellt. Figur 8 zeigt einen Querschnitt durch das erfindungsgemäße Entkopplungselement 240 entlang der Linie VIII-VIII in Figur 7. Diese Ausführungsvariante des Entkopplungselements 240 zeichnet sich dadurch aus, dass der radial innere Auflagebereich 31 gegenüber den vorher beschriebenen Lösungen verändert ist. Anstelle eines ringförmig umlaufenden Auflagebereichs 31 am Entkopplungselement 240 sind mehrere voneinander beabstandete Auflagestellen 31a, 31b, 31c vorgesehen, die bei einer Anzahl von drei Auflagestellen 31a, 31b, 31c z.B. in einem Abstand von 120° verteilt angeordnet sind. Auch eine solche Ausführungsvariante berücksichtigt die Möglichkeit einer Schiefstellung des Brennstoffeinspritzventils 1 durch die an demA third embodiment of a decoupling element 240 according to the invention is shown in a plan view in FIG. FIG. 8 shows a cross-section through the decoupling element 240 according to the invention along the line VIII-VIII in FIG. 7. This variant of the decoupling element 240 is characterized in that the radially inner support region 31 is changed compared with the previously described solutions. Instead of an annular peripheral bearing area 31st on the decoupling element 240 a plurality of spaced-apart support points 31a, 31b, 31c are provided, which are arranged distributed at a number of three support points 31a, 31b, 31c, for example at a distance of 120 °. Such an embodiment also takes into account the possibility of a misalignment of the fuel injection valve 1 by the on the
Entkopplungselement 240 ausgeformten kugelförmigen Auflagestellen 31a, 31b, 31c, innerhalb derer sich das Brennstoffeinspritzventil 1 ausrichten kann.Decoupling element 240 formed spherical support points 31a, 31b, 31c, within which the fuel injection valve 1 can align.
Eine vierte Ausführung eines erfindungsgemäßen Entkopplungselements 240 ist in einer Draufsicht in Figur 9 dargestellt. Figur 10 zeigt einen Querschnitt durch das erfindungsgemäße Entkopplungselement 240 entlang der Linie X-X in Figur 9. Diese weitere Ausführungsvariante fängt eine mögliche Schiefstellung des Brennstoffeinspritzventils 1 durch eine lokale Schwächung des inneren Auflagebereichs 31 auf. Diese lokale Schwächung des radial inneren Auflagebereichs 31 wird z.B. durch radial verlaufende Schlitze 37 erzielt, die vom Innendurchmesser des Entkopplungselements 240 ausgehen und z.B. bis zum inneren Radius R2 verlaufen. Typischerweise können diese Schlitze 37 oder auch andere die Steifigkeit reduzierende Öffnungen in einer Anzahl von drei bis zwanzig vorgesehen sein.A fourth embodiment of a decoupling element 240 according to the invention is shown in a plan view in FIG. FIG. 10 shows a cross-section through the decoupling element 240 according to the invention along the line X-X in FIG. 9. This further variant of embodiment catches a possible misalignment of the fuel injector 1 by a local weakening of the inner support region 31. This local weakening of the radially inner bearing region 31 is e.g. achieved by radially extending slots 37 emanating from the inner diameter of the decoupling element 240 and e.g. extend to the inner radius R2. Typically, these slots 37 or other stiffness reducing apertures may be provided in the number of three to twenty.
In den Figuren 11 und 12 sind zwei weitere Brennstoffeinspritzvorrichtungen teilweise dargestellt, die mit einem fünften bzw. sechsten erfindungsgemäßen Entkopplungselement 240 versehen sind. Das in der Figur 11 gezeigte Entkopplungselement 240 unterscheidet sich insbesondere von dem in den Figuren 4 und 5 gezeigten Entkopplungselement 240 durch seine inverse Auswölbung nach oben. Das Entkopplungselement 240 ist wiederum napf- bzw. tellerförmig ausgestaltet, jedoch in einer umgekehrten Lage eingebaut, d.h. der radial äußere Auflagebereich 30 an der Schulter 23 des Zylinderkopfes 9 liegt tiefer als der radial innere Auflagebereich 31 am Ventilgehäuse 22 des Brennstoffeinspritzventils 1.In FIGS. 11 and 12, two further fuel injection devices are partially shown, which are provided with a fifth and a sixth decoupling element 240 according to the invention. The decoupling element 240 shown in FIG. 11 differs, in particular, from the decoupling element 240 shown in FIGS. 4 and 5 by its inverse bulge upward. The decoupling element 240 is in turn cup-shaped, but installed in an inverted position, i. the radially outer bearing area 30 on the shoulder 23 of the cylinder head 9 is lower than the radially inner bearing area 31 on the valve housing 22 of the fuel injection valve 1.
Das Ausführungsbeispiel der Figur 12 zeigt an, dass das Entkopplungselement 240 auch in der Form einer ebenen Scheibe ausgeführt sein kann. Für beide in den Figuren 11 und 12 gezeigten Ausführungsvarianten von Entkopplungselementen 240 gelten jedoch die zuvor ausführlich beschriebenen Anforderungen an die Federsteifigkeit und den erforderlichen Abstand der Auflagebereiche 30, 31 voneinander. Entsprechend der gewünschten Steifigkeitscharakteristik kann auch hier die Materialstärke über die radiale Ausdehnung des Entkopplungselements 240 variieren.The exemplary embodiment of FIG. 12 indicates that the decoupling element 240 can also be designed in the form of a flat disk. For both embodiments of decoupling elements 240 shown in FIGS. 11 and 12 However, the requirements described in detail above to the spring stiffness and the required distance of the support areas 30, 31 from each other. In accordance with the desired stiffness characteristic, the material thickness can also vary over the radial extent of the decoupling element 240 here.
Anhand der Diagramme der Figuren 13 und 14 soll nochmals verdeutlicht werden, wie durch eine gezielte Nichtlinearität der Entkoppelsteifigkeit des Entkopplungselements 240 eine vorteilhafte Entkopplung von Brennstoffeinspritzventilen 1 in Kraftstoffsystemen erreicht werden kann. In einigen Systemen wird der Kraftstoff druck konstant hoch gehalten (Konstantdrucksystem), in anderen Systemen wird der Systemdruck last- oder drehzahlabhängig variiert (Wechseldrucksysteme) - typischerweise erfolgt bei letzteren bei Leerlauf eine Absenkung des Kraftstoffdrucks.The diagrams of FIGS. 13 and 14 are intended to further clarify how an advantageous decoupling of fuel injection valves 1 in fuel systems can be achieved by a targeted nonlinearity of the decoupling rigidity of the decoupling element 240. In some systems, the fuel pressure is kept constant high (constant pressure system), in other systems, the system pressure varies depending on load or speed (alternating pressure systems) - typically takes place in the latter at idle, a lowering of the fuel pressure.
Der Kraftstoff druck wirkt als statische hydraulische Kraft auf das Brennstoffeinspritzventil und beansprucht das Entkopplungselement 240 mit einer konstanten Vorlast und damit Verschiebung. Im linearen Fall ist diese der Kraft proportional. Im Hinblick auf Dichtheit und Verschleiß der Injektoranschlüsse an Kraftstoffsystem und Zylinderkopf gibt es maximale Grenzen für den zulässigen Federweg. Deshalb wird hier erfindungsgemäß ein nichtlinearer Zusammenhang zwischen Kraft und Federweg für das Entkopplungselement 240 gewählt.The fuel pressure acts as a static hydraulic force on the fuel injection valve and claims the decoupling element 240 with a constant preload and thus displacement. In the linear case, this is proportional to the force. With regard to tightness and wear of the injector connections to the fuel system and cylinder head, there are maximum limits for the permissible travel. Therefore, according to the invention, a non-linear relationship between force and spring travel for the decoupling element 240 is selected here.
Im Falle des Wechseldrucksystems (Figur 13) bewirkt eine progressive Federsteifigkeit eine geringe Steifigkeit bei niederem Systemdruck, d.h. Leerlauf oder niedriger Last, und damit nach dem Entkopplungsprinzip einen weiten Bereich der Geräuschentkopplung. Typischerweise sind Geräuschauffälligkeiten vor allem in diesen Betriebsbereichen zu finden. Bei höherer Last und damit höherem Druck versteift das Entkopplungselement 240 und begrenzt damit den Weg. Andere Motorgeräuschanteile verdecken in diesen Betriebsbereichen dann das schlechter entkoppelte injektorinduzierte Geräusch. Im Falle eines Konstantdrucksystems (Figur 14) liegt ein konstant hoher Druck am Entkopplungselement 240 an. Hier ist es vorteilhaft, dass der Federweg beim Druckaufbau (z.B. bei jedem Motorstart) begrenzt ist durch eine hohe Federsteifigkeit; im Betrieb ist jedoch wieder eine geringe Steifigkeit für einen breiten Entkopplungsbereich wirksam. Diese Charakteristik wird durch eine degressive Federkennlinie erreicht. In the case of the alternating pressure system (Figure 13) causes a progressive spring stiffness low stiffness at low system pressure, ie idle or low load, and thus the decoupling principle, a wide range of noise decoupling. Typically, noise is particularly noticeable in these areas of operation. At higher load and thus higher pressure stiffened the decoupling element 240 and thus limits the way. Other engine noise components then obscure the less decoupled injector-induced noise in these operating ranges. In the case of a constant pressure system (FIG. 14), a constant high pressure is applied to the decoupling element 240. Here it is advantageous that the spring travel during pressure build-up (eg at each engine start) is limited by a high spring stiffness; in operation, however, low stiffness is again effective for a wide decoupling range. This characteristic is achieved by a degressive spring characteristic.

Claims

Ansprüche claims
1. Entkopplungselement für eine Brennstoffeinspritzvorrichtung für Brennstoffeinspritzanlagen von Brennkraftmaschinen, insbesondere zum direkten Einspritzen von Brennstoff in einen Brennraum, wobei die Brennstoffeinspritzvorrichtung wenigstens ein Brennstoffeinspritzventil (1) und eine Aufnahmebohrung (20) für das Brennstoffeinspritzventil (1) umfasst, und das Entkopplungselement (240) zwischen einem Ventilgehäuse (22) des Brennstoffeinspritzventils (1) und einer Wandung der Aufnahmebohrung (20) eingebracht ist, dadurch gekennzeichnet, dass die Federsteifigkeit des Entkopplungselements (240) derart niedrig ist und das Entkopplungselement (240) so zwischen dem Ventilgehäuse (22) des Brennstoffeinspritzventils (1) und der Wandung der Aufnahmebohrung (20) platziert ist, dass die Entkoppelresonanz fR im Frequenzbereich unter 2,5 kHz liegt.1. decoupling element for a fuel injection device for fuel injection systems of internal combustion engines, in particular for direct injection of fuel into a combustion chamber, wherein the fuel injection device comprises at least one fuel injection valve (1) and a receiving bore (20) for the fuel injection valve (1), and the decoupling element (240) between a valve housing (22) of the fuel injection valve (1) and a wall of the receiving bore (20) is introduced, characterized in that the spring stiffness of the decoupling element (240) is so low and the decoupling element (240) between the valve housing (22) of the Fuel injection valve (1) and the wall of the receiving bore (20) is placed, that the Entkoppelresonanz f R is in the frequency range below 2.5 kHz.
2. Entkopplungselement nach Anspruch 1, dadurch gekennzeichnet, dass die Federsteifigkeit des Entkopplungselementes (240) im Bereich von 20 - 40 kN/mm liegt.2. decoupling element according to claim 1, characterized in that the spring stiffness of the decoupling element (240) in the range of 20 - 40 kN / mm.
3. Entkopplungselement nach Anspruch 1 oder 2, dadurch gekennzeichnet, dass das Entkopplungselement (240) einen radial äußeren Auflagebereich (30) und einen radial inneren Auflagebereich (31) besitzt, mit denen das Entkopplungselement (240) radial außen ringförmig auf eine Schulter (23) der Aufnahmebohrung (20) auflegbar ist und radial innen das Brennstoffeinspritzventil (1) Untergriffen ist.3. Decoupling element according to claim 1 or 2, characterized in that the decoupling element (240) has a radially outer bearing region (30) and a radially inner bearing region (31), with which the decoupling element (240) radially outwardly annular on a shoulder (23 ) of the receiving bore (20) can be placed and radially inside the fuel injection valve (1) is under-gripped.
4. Entkopplungselement nach Anspruch 3, dadurch gekennzeichnet, dass die beiden Auflagebereiche (30, 31) des Entkopplungselements (240) derart weit voneinander beabstandet gewählt sind, dass ein maximal möglicher Hebelarm entsteht.4. decoupling element according to claim 3, characterized the two bearing areas (30, 31) of the decoupling element (240) are selected so far apart from each other that a maximum possible lever arm is created.
5. Entkopplungselement nach Anspruch 3 oder 4, dadurch gekennzeichnet, dass der radial innere Auflagebereich (31) entweder ringförmig umläuft, durch radial verlaufende Schlitze (37) oder andere die Steifigkeit reduzierende Öffnungen unterbrochen ist oder durch mehrere voneinander beabstandete Auflagestellen (31a, 31b, 31c) gebildet ist.5. decoupling element according to claim 3 or 4, characterized in that the radially inner bearing region (31) either encircles annularly, by radially extending slots (37) or other stiffness-reducing openings is interrupted or by a plurality of spaced-apart support points (31a, 31b, 31c) is formed.
6. Entkopplungselement nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass das Entkopplungselement (240) ringscheibenförmig und insgesamt napf- bzw. tellerförmig ausgebildet ist.6. decoupling element according to one of the preceding claims, characterized in that the decoupling element (240) is annular disc-shaped and cup-shaped overall or dish-shaped.
7. Entkopplungselement nach Anspruch 6, dadurch gekennzeichnet, dass der Querschnitt des Entkopplungselements (240) eine S-förmige Kontur mit zwei Radien (Rl, R2) zu einem äußeren und einem inneren Auflagebereich (30, 31) hin hat.7. decoupling element according to claim 6, characterized in that the cross section of the decoupling element (240) has an S-shaped contour with two radii (Rl, R2) to an outer and an inner support region (30, 31) out.
8. Entkopplungselement nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass die Materialstärke des scheibenförmigen Entkopplungselements (240) entweder konstant ist oder zugunsten einer optimierten Steifigkeitscharakteristik über seine radiale Erstreckung variiert.8. decoupling element according to one of the preceding claims, characterized in that the material thickness of the disc-shaped decoupling element (240) is either constant or varies in favor of an optimized stiffness characteristic over its radial extent.
9. Entkopplungselement nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass das Entkopplungselement (240) bei einem Einsatz in einem Wechseldrucksystem mit einer nicht-linearen progressiven Federkennlinie ausgelegt ist. 9. decoupling element according to one of the preceding claims, characterized in that the decoupling element (240) is designed for use in an alternating pressure system with a non-linear progressive spring characteristic.
10. Entkopplungselement nach einem der Ansprüche 1 bis 8, dadurch gekennzeichnet, dass das Entkopplungselement (240) bei einem Einsatz in einem Konstantdrucksystem mit einer nicht-linearen degressiven Federkennlinie ausgelegt ist.10. decoupling element according to one of claims 1 to 8, characterized in that the decoupling element (240) is designed for use in a constant pressure system with a non-linear degressive spring characteristic.
11. Entkopplungselement nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass die Aufnahmebohrung (20) für das Brennstoffeinspritzventil (1) in einem Zylinderkopf (9) ausgebildet ist und die Aufnahmebohrung (20) eine Schulter (23) besitzt, die senkrecht zur Erstreckung der Aufnahmebohrung (20) verläuft und auf der das Entkopplungselement (240) mit seinem radial äußeren Auflagebereich (30) teilweise aufliegt und das Brennstoffeinspritzventil (1) wiederum mit einer senkrecht zur Ventillängsachse verlaufenden Außenkontur des Ventilgehäuses (22) an dem radial inneren Auflagebereich (31) des Entkopplungselements (240) anliegt. 11. decoupling element according to one of the preceding claims, characterized in that the receiving bore (20) for the fuel injection valve (1) in a cylinder head (9) is formed and the receiving bore (20) has a shoulder (23) perpendicular to the extent of Receiving bore (20) extends and on which the decoupling element (240) partially rests with its radially outer bearing region (30) and the fuel injection valve (1) in turn with a perpendicular to the valve longitudinal axis extending outer contour of the valve housing (22) on the radially inner bearing region (31) of the decoupling element (240) is applied.
EP09771734.2A 2008-12-12 2009-11-26 Decoupling element for a fuel injection device Active EP2376765B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102008054591A DE102008054591A1 (en) 2008-12-12 2008-12-12 Decoupling element for a fuel injection device
PCT/EP2009/065889 WO2010066586A1 (en) 2008-12-12 2009-11-26 Decoupling element for a fuel injection device

Publications (2)

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EP2376765A1 true EP2376765A1 (en) 2011-10-19
EP2376765B1 EP2376765B1 (en) 2015-08-05

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EP09771734.2A Active EP2376765B1 (en) 2008-12-12 2009-11-26 Decoupling element for a fuel injection device

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US (1) US9057349B2 (en)
EP (1) EP2376765B1 (en)
CN (1) CN102245890B (en)
DE (1) DE102008054591A1 (en)
WO (1) WO2010066586A1 (en)

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Also Published As

Publication number Publication date
EP2376765B1 (en) 2015-08-05
DE102008054591A1 (en) 2010-06-17
US9057349B2 (en) 2015-06-16
US20120031375A1 (en) 2012-02-09
CN102245890B (en) 2016-01-20
CN102245890A (en) 2011-11-16
WO2010066586A1 (en) 2010-06-17

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