EP2167808B1 - Injecteur haute pression pour moteurs à combustion interne à appui de tige de commande à charge de flambage croissante par l'intermédiaire de carburant haute pression - Google Patents

Injecteur haute pression pour moteurs à combustion interne à appui de tige de commande à charge de flambage croissante par l'intermédiaire de carburant haute pression Download PDF

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Publication number
EP2167808B1
EP2167808B1 EP08758770A EP08758770A EP2167808B1 EP 2167808 B1 EP2167808 B1 EP 2167808B1 EP 08758770 A EP08758770 A EP 08758770A EP 08758770 A EP08758770 A EP 08758770A EP 2167808 B1 EP2167808 B1 EP 2167808B1
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EP
European Patent Office
Prior art keywords
pressure
control rod
coupling piece
injector according
pressure injector
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.)
Not-in-force
Application number
EP08758770A
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German (de)
English (en)
Other versions
EP2167808A1 (fr
Inventor
Alexander C. Kaiser
Hans-Joachim Koch
Wilhelm Malitsky
Horst Ressel
Wolfgang Scheibe
Bernd Wagner
Norbert Walter
Gert Wollnik
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.)
LOrange GmbH
Original Assignee
LOrange GmbH
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Filing date
Publication date
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Publication of EP2167808A1 publication Critical patent/EP2167808A1/fr
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Publication of EP2167808B1 publication Critical patent/EP2167808B1/fr
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M47/00—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
    • F02M47/02—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure of accumulator-injector type, i.e. having fuel pressure of accumulator tending to open, and fuel pressure in other chamber tending to close, injection valves and having means for periodically releasing that closing pressure
    • F02M47/027—Electrically actuated valves draining the chamber to release the closing pressure
    • 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
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0014—Valves characterised by the valve actuating means
    • F02M63/0015—Valves characterised by the valve actuating means electrical, e.g. using solenoid
    • 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
    • F02M2200/40—Fuel-injection apparatus with fuel accumulators, e.g. a fuel injector having an integrated fuel accumulator
    • 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
    • F02M2200/70—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger
    • 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
    • F02M2200/70—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger
    • F02M2200/701—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger mechanical
    • 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
    • F02M2200/70—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger
    • F02M2200/703—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic

Definitions

  • the invention relates to a high-pressure injection injector for internal combustion engines according to the preamble of claim 1.
  • Injection injectors of the aforementioned type are known from EP 1 208 297 B1 known. Axially opposite to the injection-side end containing the injector overflowed injection ports containing end of the elongated injection injector is provided with an actuator, and lying in the longitudinal central region therebetween with a control valve which has a connection to the high pressure side and the low pressure side and on when connected to the high pressure side a back pressure chamber lying on the back of the nozzle control chamber and the nozzle needle is loaded in the direction of its closed position. If the control chamber connected to the low pressure side, the nozzle needle is raised due to the pressurization of lying in the region of its injection-side end pressure shoulder in its open position.
  • control rod In the connection between the control valve and the actuator is an elongated control rod whose length corresponds to a multiple of its thickness and which in turn is guided in a running between the actuator and the control valve socket, which forms an inserted into the valve housing assembly together with the control rod.
  • the variety of the required fits, the machining tolerances and other factors also montage and Temperature-induced tensions are - despite the long and thin, in consideration of the pressure forces to be transmitted as slim as possible control rod and their consequent adaptability - adversely noticeable, in particular, the introduction of the restoring forces on the actuator is critical. Therefore, the control rod is provided in the transition to the actuator with a separate and separately guided headboard.
  • control rod from the head part and the rod part at transverse to the direction of support surfaces on the headboard and rod part angle and Desachs mecanicsmay can be largely compensated.
  • the inclusion of the control rod in a separate mounting sleeve also requires space, which is in a certain contradiction to the requirement given for internal combustion engines as slim as possible and space-saving injection injectors.
  • the DE 101 47 830 A1 shows a fuel injector with between actuator and control valve extending, elongated and guided in a mounting sleeve control rod.
  • the mounting sleeve intersperses, sealingly in each case at the end face, a cavity located in the area between actuator and control valve, which forms a fuel pressure accumulator integrated in the fuel injector and which lies in the fuel inlet from the fuel supply lying laterally to the housing to the injection openings controlled via the nozzle needle.
  • the integration of a pressure accumulator in the injector is also from the EP 0 333 096 A2 known.
  • the pressure accumulator is disposed between the nozzle opening on the injection ports and the control valve with downstream actuator and passing through a connecting the control valve with the nozzle needle control rod which is guided on the part of the control valve via a closure plate floating in an intermediate piece of the housing, in the back to Control rod of the control room is provided.
  • the relatively massive and the high-pressure accumulator guide-free passing through control rod is loaded via an enclosing and supported against the cover plate spring in the direction of the closed position of the nozzle needle.
  • an injection injector which has a pin-like slim housing part below the fuel supply to the injector, in which the nozzle needle with a shaft portion, whose length is a multiple of its diameter, in a central bore through which the fuel supply to the injection openings takes place the nozzle needle leaking on the Injection openings is guided in the nozzle body and back ends over its shaft portion against a control piston, which forms a boundary of the control chamber.
  • nozzle needle can be divided into a plurality of operatively connected, so connected to each other elements and the control valve is controlled via an opposite to the nozzle needle almost immediately adjoining actuator, so that actuator and control valve and the supply ports of the injector are combined in a head part that builds short compared to the pen-like nozzle needle side portion of the injector. Due to the elongated, tapered relative to the head part construction of the nozzle needle-side part of the injector, the unguided course of the shaft of the nozzle needle in the central bore of the housing and extending over the central bore fuel supply to the injection openings results in a low-production and low-leakage design with the installation in internal combustion engines favorable, slim shape. However, this is less suitable for use as a high-pressure injector, in which high, the system pressure far exceeding pressure peaks.
  • a similar structure of an injection injector also shows the EP 0 450 532 A1 ,
  • the coupling device comprises a liquid-filled, housing-enclosed coupling space with opposite, housing-guided actuators, between which extends a liquid column. About this liquid column as a pressure column, the actuators are supported against each other under pressure. Occurring leaks are compensated for tensile load of the actuators by a valve-controlled connection of the coupling chamber to the low pressure side.
  • an injection injector known in which the injector in the end opposite each other the injection nozzle is provided with nozzle needle extending in the direction of the injector axis and the return-side supply connection.
  • the control valve is located with the valve axis extending transversely to the injector axis and the actuating rod extending in the direction of the valve axis of the actuator designed as a magnetic actuator.
  • the adjusting rod passes through the winding region of the magnetic actuator in a guide and is connected opposite to the control valve with the armature plate of the magnetic actuator.
  • the invention has for its object to form a high-pressure injector of the type mentioned in that results in an increased buckling stability of its control rod and that the injector with a simple structure both in terms of manufacturing and assembly tolerances as well as by clamping forces, pressurization and temperature fluctuations caused dimensional changes is insensitive.
  • the load on the injector is reduced by pressure peaks which extend far beyond the already high system pressures, resulting in lower deformations of the injector housing and a structurally easier construction of the injector, in particular of the injector housing becomes.
  • the invention thus also provides a method for increasing the buckling stiffness of thin rods by enclosing them with fluids under high pressure, in particular liquids.
  • the throttling connection between the gap and the receiving space, and thus to the high pressure side, can be in the context of
  • the height of the pressure building up between the work files in the gap space can also be influenced via the respective throttle cross section, be it as a bore cross section or as a leakage gap, as well as over the length of the respective throttle section.
  • the one or more engaging in the coupling rod parts are expediently resiliently supported on their gap-increasing position against each other or against the coupling piece, so that structurally a predetermined support length is adjustable by simple means and deviations thereof can be compensated by the self-adjusting length of the liquid column.
  • the coupling piece may also be formed by the upper and / or lower valve stem guide, the lower valve stem guide is suitably adjacent to an intermediate plate which is provided in the transition from the injector to the nozzle body that's on injection ports leaking nozzle needle receives and is clamped via a screw, in particular via a union nut, together with the intermediate intermediate plate against the injector.
  • the lower valve rod guide limits the receiving space, is supported radially to the receiving space and takes a floating seat body of the control valve, the seating surface is sealingly acted upon by the control rod.
  • a control chamber When lifted from the seat control rod a control chamber is connected to the low pressure side of the seat body.
  • This control chamber is located at the back to the nozzle needle and is delimited against the intermediate plate via a control sleeve which is axially resiliently clamped between the intermediate plate and the nozzle needle, so that the nozzle needle is loaded in the direction of its closed position to the injection openings.
  • the control chamber has a throttled connection to the high-pressure side, so that the nozzle needle is loaded via the pressure built up in the control chamber in the direction of its closed position and is adjustable pressure-dependent in its open position when switched by opening the control valve connection of the control chamber to the low pressure side.
  • the solution according to the invention expediently provides a structure in which a quantity-limiting valve is integrated in the receiving space.
  • this flow control valve is adjacent to the lower valve stem guide, so provided in the inlet region on the nozzle needle and thus lies between the valve housing associated high-pressure side port and the nozzle portion of the injector.
  • This results in a particularly simple construction when the flow control valve has a piston element lying in the inlet path to the nozzle part, the throttling overflow cross sections and which is spring-loaded in the direction of a constructive starting position against the flow direction.
  • the longitudinally displaceably guided in the receiving chamber piston member is preferably against a housing shoulder, with support of the spring opposite to the piston member on the lower valve stem guide.
  • the piston element During each injection process, the piston element is displaced in the direction of its blocking position, and, if the injection quantity was not too large, then returned to its original position. Only at large injection quantities, but otherwise properly operating injection injector, speaks the flow control valve and it is the piston member moved into a locked position, which prevents a further fuel supply to the nozzle needle enclosing the nozzle chamber.
  • a quantity limiting valve of the embodiment shown thus does not respond if the amount of fuel flowing over it, based on the throttling overflow cross section of the quantity limiting valve, is too small to displace its piston element.
  • an injection injector 1 for internal combustion engines is supplied via the supplied under high pressure fuel (arrow 2) of the injection nozzle 3, which has a nozzle body 4 in which in a central bore 5, a nozzle needle 6 is guided axially displaceably over the fuel flow to the injection ports 7 is controlled.
  • To the nozzle body 4 includes axially, this overlapping, an intermediate plate 8, which lies in the transition to the housing 9 of the injection injector 1 and 9 between nozzle body and housing 9 via a screw, here a union nut 10 is clamped, the nozzle body 4 in a Shoulder 11 engages under and which is screwed against the expiring against the intermediate plate 8, lower part of the housing 9.
  • an actuator 12 which is only indicated in outline and, based on the embodiment, is designed as a magnetic plate having an anchor plate 13.
  • the anchor plate 13 is axially above a designed as a screw plate 14 end plate, which is bolted to the housing 9 and over which a influencepfropfen 15 for a axially extending through the housing 9 receiving space 16 is clamped sealingly against the housing 9.
  • the receiving space 16 which passes through the housing 9 centrally, runs down on the intermediate plate 8, adjacent to the in the receiving space 16, a control valve 17 is provided, via which the pressurization of a control chamber 18 is controlled, the axially between the rear end of the nozzle needle 6 and the intermediate plate 8 is located and which is bounded by a control sleeve 19 which is axially displaceably guided on the rear, here thus upper end portion of the nozzle needle 4.
  • the rear, upper end portion of the nozzle needle 6 is then designed as a shaft portion 21 to the pressure shoulder 20 of the nozzle needle 6, and the control sleeve 19 is supported via a compression spring 22 in the direction of their engagement with the intermediate plate 8.
  • the nozzle needle 6 is loaded in the direction of its closed position, in which the fuel flow to the injection openings 7 is blocked by the nozzle needle 6 and the nozzle is closed.
  • the intermediate plate 8 and thus also adjacent to this control valve 17, based on the axial extent of the injection injector 1, near its lower end, and thus results in between the control valve 17 and the actuator serving the actuator 12 has a substantially the length of Housing 9 corresponding, and thus large distance, which is bridged to actuate the control valve 17 via a control valve 17 and actuator 12 extending control rod 23.
  • the control rod 23 is, as can be seen from the illustrations, formed as a knitting needle-like thin rod whose length corresponds to a multiple of its thickness. Based on the embodiment, the diameter of the control rod 23 is on the order of one millimeter, with a length of 150 mm. This size ratio reflects that the control rod 23 relative to their length in the frame
  • the invention is preferably chosen to be extremely thin, although the example given range within the scope of the invention can vary within wide limits.
  • Fig. 1 forms the receiving space 16 at least over part of its length, in particular in its upper longitudinal region a pressure accumulator 24, which communicates with the high pressure side - arrow 2 - but is not in the flow path between the high pressure port 27 and the control valve 17 to the nozzle needle 6 ,
  • the flow path between the high pressure supply (arrow 2) and the control valve 17 and the nozzle needle 6 leads in the lower region of the housing 9 via the lower part 25 of the total over the length of the housing 9 extending receiving space 16, wherein in the embodiment in the transition region between the lower Part 25 of the receiving space 16 and its upper part formed by the accumulator 24 part of the high-pressure side port 27 is located, and in the Ausmündungs Scheme on the receiving space 16, a coupling piece 26th
  • the coupling piece 26 is in Fig. 1 and 2 designed as lying in the receiving space 16 sleeve, which is guided over the housing 9 or also freely lying to the housing 9 and which has a central through hole 28.
  • this through hole 28 the opposite end portions of an upper control rod member 29 and a lower control rod member 30 of the control rod 23 and define within the through hole 28 of the coupling piece 26 with their end faces from a gap 31 from the receiving space 16, or in other ways to the high pressure side , having a restricted connection.
  • this connection is due to the leaking guiding the ends of the control rod parts 29, 30 in the through hole 28 formed, but may also be formed by a separate, not shown throttle bore.
  • the coupling piece 26 is fixed to the housing 9 and it is the control rod parts 29, 30 supported in opposite directions by springs 32, 33, so that on the resilient displacement of the control rod parts 29, 30, the control rod parts 29, 30 in an axial distance position to each other, which, due to the connection to the receiving space 16 or otherwise to the high pressure side, ensures the construction of a pressure column.
  • the control rod 23 as a whole is an axially multi-part element which is formed by the rod parts 29, 30 and the pressure column constructed in the region of the gap space 31.
  • an automatic adjustment of the adjusting length of the control rod 23 is achieved at the distance between the control valve 17 and the actuator 12 resulting from tolerances, assembly-related and / or by stresses, in particular thermal stresses.
  • the embodiment according to Fig. 1 and 2 further shows the arrangement of a flow control valve 34 integrated in the injection injector 1 in the lower part 25 of the receiving space 16.
  • the flow control valve 34 has a basically known construction with a locking piston 35 which is guided longitudinally displaceable in the receiving space 16 and on a flow-releasing upper stop position is supported by a spring 36 which is supported axially to the housing 9, to the intermediate plate 8 or, as shown, to a lower control rod guide 37.
  • the control rod guide 37 is in turn supported against the intermediate plate 8 and guided radially in the receiving space 16.
  • the locking piston 35 is supported in the flow-releasing position of the flow limiting valve 34 via the spring 36 against a housing shoulder 38 and has throttled overflow in the flow direction on the nozzle part 3.
  • the support position is according to the embodiment Fig. 1 and 2 determined by oppositely directed, peg-like projections 39, 40 on the locking piston 35 and on the lower control rod guide 37, wherein the pin-like projections 39 and 40 are central to the continuous control rod 23 centrally and axially directed against each other.
  • the blocking position of the flow control valve 34 thus form on the one hand the overlapping projections 39, 40, the control rod 23 delimiting sealing surface, and it is on the other the locking piston 35 provided with its piston shaft in axial and radial coverage to along the lower control rod guide 37, for example, by longitudinal grooves formed overflow channels 41.
  • overflow channels 41 open in the embodiment of an annular channel 42 in the intermediate plate 8, which has a supply bore 43 and another Ring channel 44 with the lying in the shaft portion of the nozzle needle 5 pressure chamber 45 is in communication, in which the pressure shoulder 20 of the nozzle needle 6 is located.
  • the control valve 17 has a seat body 47 lying in an end-side recess 46 of the control rod guide 37 that is open to the intermediate plate 8, which abuts against a connecting channel 48, overlapping the intermediate plate 8 with a drainage bore 49.
  • the drain hole 49 is connected to the control chamber 18.
  • the drainage hole 49 runs opposite to the connection channel 48 in a seat surface for the control rod 23, and with the control rod 23 raised from the seat surface, the drainage hole 49 communicates via connection channels 50 in the intermediate plate 8 with a connection channel 51 to the low pressure side.
  • the drain hole 49 is itself designed as a throttle bore, or it is formed the inlet to the drain hole 49 throttled.
  • the control room 18 is via a throttled connection 52, as in Fig. 4 indicated, with the high pressure side, here the pressure chamber 45, in conjunction.
  • the nozzle needle 6 is loaded both via the compression spring 22 as well as the pending in the control chamber 18 pressure in the direction of its closed position. It can thus take place no injection process.
  • the control rod 23 is clamped between the seat body 47, on which it bears sealingly, and the actuator 12, in particular due to the built-up in the gap 31 pressure column through which the rod parts 29 and 30 supported against each other and against their respective contact positions on the actuator 12th and are applied to the seat body 47. If the actuator 12 is actuated to initiate an injection process, the armature plate 13 is lifted against spring force and the upper rod part 29 can move in the direction of the actuator 12.
  • the armature plate 13 spring-loaded in the direction of its support position to the control rod 23 drops and acts on the control rod 23 in the direction of its closed position to the drain hole 49, because of the throttling connection between the gap space 31 and the high-pressure side in the gap space in turn a supporting liquid column is constructed.
  • Fig. 1 makes it clear that the axially one behind the other arrangement of pressure accumulator 24, flow control valve 34 and optionally intervening coupling piece 26 is a very compact and structurally very well controllable arrangement, especially since the control rod 23 due to their slim design and their unclad free position within the receiving space 16, which at least partially serves as a pure pressure accumulator 24, has a minimal space requirement, so that it is also possible to realize large and effective accumulator chambers.
  • the coupling piece 26 arranged in the transition between pressure accumulator 24 and flow control valve 34, it is advantageous if the high-pressure side port 27 opens in the region of the coupling piece 26 on the receiving space 16 and this divides, with over the coupling piece 26 associated channel connections 57, 58 in Direction to the accumulator 24 and in the direction of the flow control valve 34th
  • Such a configuration favors, regardless of the operating conditions of injection or non-injection, the maintenance of a substantially same, high pressure levels in the pressure accumulator 24 and thus at large guide-free length of the control rod 23 and their training with a minimized cross section, characterized in that the computational buckling load of a thin, a Pressure accumulator 24 passing through the control rod 23 relative to the rod length between the memory axially penetrating sealing guides increases with increasing pressure, thus the control rod can be designed for a buckling load, which corresponds to the arithmetical buckling load plus an additional buckling load, which is a product of the pressure in the accumulator and the cross-sectional area of the control rod in the axial sealing guides to the receiving space 16 results.
  • the invention thus also provides a method, when using pressure-applied thin rods, such as control rods 23 of the type mentioned above, to minimize them in terms of their dimensions, characterized in that the product given from the enclosing to the rod in a pressure accumulator Pressure and the cross-sectional area of the rod in its exit surface to the pressure accumulator as an aggregate size for arithmetic buckling load is taken into account.
  • a method for increasing the buckling strength of thin rods is shown.
  • the invention can also be in an embodiment according to Fig. 3 realize, in which - a flow control valve is not provided here, but may also be provided according to the invention - the coupling piece is formed by one of the control rod guides, in particular, as shown by the lower control rod guide 45.
  • a flow control valve is not provided here, but may also be provided according to the invention - the coupling piece is formed by one of the control rod guides, in particular, as shown by the lower control rod guide 45.
  • FIG. 3 also, in addition to Fig. 1 , Another arrangement possibility for the anchor plate 13 supporting compression spring 59 as part of the actuator 12 illustrated.
  • Fig. 4 illustrates that when dividing the control rod 23 in the region of the lower control rod guide 37, the upper control rod member 29 is many times longer than the lower control rod member 30, in position of the gap 31 between these rod parts.
  • the leakage between the gap 31 and the receiving space 16 and the height of the build-up in the gap 31 pressure by the definition of different guide lengths and leadership games between upper rod portion 29 and lower in the dipping into the control rod guide portion 37 of the upper control rod member 29 Determine control rod guide 37 as a coupling piece, taking into account the corresponding radial tolerances in the leadership of the control rod 23 in the lower control rod guide 37th
  • Fig. 4 in relation to the extent to which Fig. 1 and 2 corresponding to the lower part of the flow control valve supplemented representation of Fig. 3 , the high-pressure side connection 52 of the control chamber 18 via connection channels 60 with interposed throttle 61 to the pressure chamber 45.
  • the invention in particular in the embodiment according to FIG Fig. 4 advantageously allows a structure of the control rod 23 from different materials over their length.
  • the short lower control rod part 30 in the embodiment according to Fig. 4 altogether consist of a high-strength material which is particularly suitable with respect to the seal to the drainage bore 49.
  • Fig. 5 to 7 show highly schematized and isolated representation of a structure in which a control rod 70 passes through a coupling piece 71 in an axial bore 72 and in which the control rod 70 has two control rod parts 73 and 74, of which the control rod part 73, based on the above-described exemplary embodiments, a upper, actuator-side control rod portion forms and the control rod portion 74 a lower.
  • the control rod parts 73 and 74 are guided longitudinally displaceably in the axial bore 72 and delimit axially with their mutually adjacent end faces within the axial bore 72 a gap 75 radially enclosed by the coupling piece 71.
  • the coupling piece 71 is shown as lying within a receiving space 76, which is penetrated by the control rod 70, so that the control rod parts 73, 74, in the embodiments according to FIG FIGS. 5 and 6 starting from the gap 75 extending in the axial bore 72, expire on opposing areas of the receiving space 76, based on the representations according to FIGS. 5 and 6 each, as shown by the + sign, at high pressure level.
  • the control rod parts 73 and 74 define in the axial bore 72 opposite the coupling piece 71 respectively leakage gaps 77, 78, so that in the gap space 75, from the receiving space 76th supplied via the leakage gaps 77 and 78, the receiving space 76 corresponding pressure builds up, and in the gap 75 is given a pressure column over which, with a corresponding axial load, the control rod parts 73, 74 are supported against each other, so can transmit corresponding axial support forces.
  • the control rod parts 73, 74 are displaced from each other by enlarging the gap space 75, if no corresponding opposing forces are present, or if - for example due to a resilient support - due to the built-up in the gap 75 pressure actuating forces that are greater than these opposing forces.
  • either the pressure in the gap 75 must be limited accordingly, or the gap space limiting cross-sectional area of the respective control rod part are so dimensioned in that, based on a predetermined limit pressure, a predetermined limit force corresponding to the spring force is not exceeded.
  • Fig. 6 is the gap 75 via a throttling connection 79 in addition to a low-pressure space 80 is connected, the pressure level - as a low pressure level - below the given in the receiving space 76 high pressure level (indicated by +), and is characterized by -.
  • the throttling connection 79 is shown schematically as a bore 81 in the control rod portion 74, but can also be realized in other ways, for example, by a gap opening on the gap 75, the coupling piece 71 passing through and opening to the low-pressure chamber 80 bore.
  • connection to the low pressure space 80 is formed in conjunction with the analogous to the embodiment according to Fig. 5
  • Fig. 7 shows a variant in which the coupling piece 71 is axially delimiting a receiving space 76 in the transition to a low pressure space 80, in such a way that the control rod 70 terminates from the coupling piece 71 at one end to the high pressure receiving space 76 and the other end to the low pressure space 80 ,
  • the control rod parts 73 and 74 thus form a delimitation of the enclosed between their opposite end faces gap 75 on the one hand against high pressure, on the other hand against low pressure, so that on the leakage gaps 77 and 78 in the gap 75 a lying between the high pressure side and the low pressure side pending, mean Pressure setting.
  • a connection of the gap 75 to the low-pressure chamber 80 via a throttling bore connection 79 in the imaginary manner to the coupling piece 71 position-fixed control rod part 74 can be done.
  • the connection to the low-pressure chamber 80 can preferably also take place directly via a bore passing through the coupling piece 71.
  • the control rod it is also to divide the control rod several times, so that there are several separation points.
  • Under production and / or mounting points may be expedient, forms at the separation point, a correspondingly enclosing coupling piece, a the correct distance adjusting gap space in which forms the largest supporting force.
  • the rod parts are in abutment with each other, so there is no transmitting, the support length adjusting liquid column between the facing end faces of the rod parts available.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Fuel-Injection Apparatus (AREA)

Claims (18)

  1. Injecteur haute pression (1) pour moteurs à combustion interne comprenant un actionneur (12) et une buse d'injection (3) pour du carburant acheminé à haute pression, qui sont disposés sur des côtés d'extrémité mutuellement opposés axialement du boîtier d'injecteur (9) allongé, et comprenant une soupape de commande (17) située dans la commande de la buse d'injection (3), disposée dans le passage du boîtier d'injecteur (9) à la buse d'injection (3), qui est commandée par l'actionneur (12) par le biais d'une tige de commande (23) en forme de barre allongée, mince comme une aiguille à tricoter, qui s'étend dans le passage de l'actionneur (12) à la soupape de commande (17) dans un espace de réception (16) traversant axialement le boîtier d'injecteur (9) et qui présente deux parties de tige de commande (29, 30) supportées l'une par rapport à l'autre du côté frontal,
    caractérisé en ce que
    l'espace de réception (16) est raccordé du côté haute pression, en ce que la tige de commande (23) est directement entourée par le carburant dans un espace de réception (16) formant un accumulateur haute pression, en ce que les côtés frontaux tournés l'un vers l'autre des parties de la tige de commande (29, 30) sont supportés fluidiquement l'un par rapport à l'autre et se situent à l'intérieur d'une pièce d'accouplement périphérique (26) et en ce que dans le cas d'une mobilité axiale d'au moins l'une des parties de la tige de commande (29, 30) par rapport à la pièce d'accouplement (26), les parties de la tige de commande (29, 30) délimitent axialement avec leurs côtés frontaux un espace d'interstice (31) qui est en liaison d'étranglement au moins avec le côté haute pression.
  2. Injecteur haute pression selon la revendication 1,
    caractérisé en ce que
    l'espace d'interstice (31) est en liaison d'étranglement avec le côté basse pression.
  3. Injecteur haute pression selon la revendication 1 ou 2,
    caractérisé en ce que
    les deux parties de tige de commande (29, 30) sont déplaçables axialement dans la pièce d'accouplement (26).
  4. Injecteur haute pression selon l'une quelconque des revendications 1 à 3,
    caractérisé en ce que
    la pièce d'accouplement (26) se situe dans l'espace de réception (16).
  5. Injecteur haute pression selon l'une quelconque des revendications 1 à 3,
    caractérisé en ce que
    la pièce d'accouplement (26) forme une limitation axiale de l'espace de réception (16).
  6. Injecteur haute pression selon l'une quelconque des revendications précédentes,
    caractérisé en ce
    qu'au moins l'une des liaisons d'étranglement de l'espace d'interstice (31) avec le côté haute pression ou le côté basse pression est formée par un interstice de fuite entre la tige de commande (23) et la pièce d'accouplement (26).
  7. Injecteur haute pression selon l'une quelconque des revendications 1 à 6,
    caractérisé en ce que
    parmi les liaisons d'étranglement de l'espace d'interstice (31) avec le côté haute pression ou avec le côté basse pression, au moins l'une est formée par un alésage d'étranglement.
  8. Injecteur haute pression selon la revendication 6 ou 7, caractérisé en ce que
    la liaison d'étranglement de l'espace d'interstice (31) avec le côté haute pression part de l'espace de réception (16).
  9. Injecteur haute pression selon l'une quelconque des revendications précédentes,
    caractérisé en ce que
    la pièce d'accouplement (26) est fixée en position axialement par rapport à l'espace de réception (16).
  10. Injecteur haute pression selon l'une quelconque des revendications 1 à 8,
    caractérisé en ce que
    la pièce d'accouplement (26) est déplaçable axialement par rapport à l'espace de réception (16).
  11. Injecteur haute pression selon l'une quelconque des revendications précédentes,
    caractérisé en ce que
    la pièce d'accouplement (16) forme un guide radial pour la tige de commande (23).
  12. Injecteur haute pression selon l'une quelconque des revendications 1 à 4,
    caractérisé en ce que
    l'espace de réception (16) est divisé axialement par la pièce d'accouplement (26) en une partie supérieure adjacente à l'actionneur (12) servant de partie accumulateur et en une partie inférieure, et forme, dans la région de la partie inférieure située entre la pièce d'accouplement (26) et la soupape de commande (17), un canal de carburant.
  13. Injecteur haute pression selon la revendication 12,
    caractérisé en ce que
    le raccord du côté haute pression à l'espace de réception (16) se situe dans la région de la pièce d'accouplement (26).
  14. Injecteur haute pression selon l'une quelconque des revendications précédentes,
    caractérisé en ce
    qu'une soupape de limitation de quantité (34) est disposée dans l'espace de réception (16).
  15. Injecteur haute pression selon l'une quelconque des revendications 12 à 14,
    caractérisé en ce que
    la soupape de limitation de quantité (34) est disposée dans la partie inférieure de l'espace de réception (16).
  16. Injecteur haute pression selon la revendication 14 ou 15,
    caractérisé en ce que
    la soupape de limitation de quantité (34) présente un piston de verrouillage (35) supporté par ressort, limitant une section transversale d'écoulement d'étranglement vers la buse d'injection (3).
  17. Injecteur haute pression selon l'une quelconque ou plusieurs des revendications précédentes, caractérisé en ce que
    la tige de commande (23) est supportée, avec stabilisation du flambage, dans l'espace de réception (16) raccordé du côté haute pression par le biais du carburant haute pression qui l'entoure.
  18. Injecteur haute pression selon la revendication 17,
    caractérisé en ce que
    la tige de commande (23) est supportée, avec augmentation de la charge de flambage, par le biais du carburant haute pression qui l'entoure du côté périphérique.
EP08758770A 2007-05-29 2008-05-27 Injecteur haute pression pour moteurs à combustion interne à appui de tige de commande à charge de flambage croissante par l'intermédiaire de carburant haute pression Not-in-force EP2167808B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102007025050A DE102007025050B3 (de) 2007-05-29 2007-05-29 Hochdruck-Einspritzinjektor für Brennkraftmaschinen mit einer knicklaststeigernden Steuerstangenabstützung über unter Hochdruck stehendem Kraftstoff
PCT/EP2008/004183 WO2008145330A1 (fr) 2007-05-29 2008-05-27 Injecteur haute pression pour moteurs à combustion interne à appui de tige de commande à charge de flambage croissante par l'intermédiaire de carburant haute pression

Publications (2)

Publication Number Publication Date
EP2167808A1 EP2167808A1 (fr) 2010-03-31
EP2167808B1 true EP2167808B1 (fr) 2011-08-31

Family

ID=39722638

Family Applications (1)

Application Number Title Priority Date Filing Date
EP08758770A Not-in-force EP2167808B1 (fr) 2007-05-29 2008-05-27 Injecteur haute pression pour moteurs à combustion interne à appui de tige de commande à charge de flambage croissante par l'intermédiaire de carburant haute pression

Country Status (4)

Country Link
EP (1) EP2167808B1 (fr)
AT (1) ATE522717T1 (fr)
DE (1) DE102007025050B3 (fr)
WO (1) WO2008145330A1 (fr)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102012204659A1 (de) * 2012-03-22 2013-09-26 Man Diesel & Turbo Se Injektor für eine Kraftstoffversorgungsanlage einer Brennkraftmaschine sowie Kraftstoffversorgungsanlage
AT512277B1 (de) * 2012-04-10 2013-07-15 Bosch Gmbh Robert Injektor eines modularen Common-Rail-Kraftstoffeinspritzsystems mit Durchflussbegrenzer
DE102012025051B4 (de) * 2012-12-20 2014-10-09 L'orange Gmbh Mengenbegrenzungsventilvorrichtung
GB201415539D0 (en) * 2014-09-03 2014-10-15 Delphi International Operations Luxembourg S.�.R.L. Fuel injector

Family Cites Families (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3297261A (en) * 1964-12-02 1967-01-10 Pneumo Dynamics Corp Fuel injection nozzle valve
FR2145081A5 (fr) * 1971-07-08 1973-02-16 Peugeot & Renault
ES2025054B3 (es) * 1985-12-02 1992-03-16 Marco Alfredo Ganser Aparato para inyeccion de fuel para motores de combustion interna.
US4899935A (en) * 1988-03-14 1990-02-13 Yamaha Hatsudoki Kabushiki Kaisha Valve support for accumulator type fuel injection nozzle
IT1240173B (it) * 1990-04-06 1993-11-27 Weber Srl Dispositivo di iniezione del carburante ad azionamento elettromagnetico per un motore a combustione interna
DE59506715D1 (de) * 1994-06-06 1999-10-07 Ganser Hydromag Brennstoffeinspritzventil für Verbrennungskraftmaschinen
JP3823391B2 (ja) * 1996-08-31 2006-09-20 いすゞ自動車株式会社 エンジンの燃料噴射装置
DE19650865A1 (de) * 1996-12-07 1998-06-10 Bosch Gmbh Robert Magnetventil
JPH11200977A (ja) * 1998-01-08 1999-07-27 Nippon Soken Inc 燃料噴射装置の制御二方弁
DE19938921B4 (de) * 1999-08-17 2004-02-19 L'orange Gmbh Einspritzventil für eine Verbrennungskraftmaschine
EP1118765A3 (fr) * 2000-01-19 2003-11-19 CRT Common Rail Technologies AG Injecteur de combustible pour moteur à combustion interne
DE10065220A1 (de) * 2000-12-27 2002-07-18 Bosch Gmbh Robert Kraftausgeglichenes Steuerventil am Steuerraum eines Kraftstoffinjektors
DE10147830B4 (de) * 2001-09-27 2008-05-08 L'orange Gmbh Kraftstoffinjektor
DE50302779D1 (de) * 2002-03-18 2006-05-18 Orange Gmbh Einspritzinjektor für Brennkraftmaschinen
DE102005056133A1 (de) * 2005-11-23 2007-05-24 L'orange Gmbh Einspritzinjektor

Also Published As

Publication number Publication date
EP2167808A1 (fr) 2010-03-31
DE102007025050B3 (de) 2008-10-16
ATE522717T1 (de) 2011-09-15
WO2008145330A1 (fr) 2008-12-04

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