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
  • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
• • 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
  • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
  • F02M63/004—Sliding valves, e.g. spool valves, i.e. whereby the closing member has a sliding movement along a seat for opening and closing
• • 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
  • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
  • F02M63/0043—Two-way valves
• • 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
  • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
  • F02M63/0045—Three-way valves
• • 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
  • F02M2200/31—Fuel-injection apparatus having hydraulic pressure fluctuations damping elements
  • F02M2200/315—Fuel-injection apparatus having hydraulic pressure fluctuations damping elements for damping fuel pressure fluctuations
• • 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
  • F02M2547/00—Special features for fuel-injection valves actuated by fluid pressure
  • F02M2547/003—Valve inserts containing control chamber and valve piston
• • 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
  • F02M61/20—Closing valves mechanically, e.g. arrangements of springs or weights or permanent magnets; Damping of valve lift
  • F02M61/205—Means specially adapted for varying the spring tension or assisting the spring force to close the injection-valve, e.g. with damping of valve lift
• • 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

Definitions

• the invention is characterized by an injection injector according to claim 1, which is designed in terms of a cost and structurally relatively simple structure and despite this embodiment has only relatively small pressure oscillation amplitudes and also higher switching speeds with the possibility of multiple injections opened as well as working with higher injection pressures.
• a pressure accumulator is integrated in the injection injector via which the nozzle needle is controlled to the injection openings, via a built-in pressure accumulator Ménbegrenzungsventil whose locking piston preferably additionally serves as a guide element for the optionally hollow control rod from the Control chamber of the control valve starting out by the pressure accumulator extending against the nozzle needle is supported.
• the piston of the flow control valve is thus used for various functions and also offers the possibility for injection rate progression molding.
• this can be realized, for example, simply by the diameter of the blocking piston being larger than the diameter of a frontal piston attachment which engages in a section of the control chamber-side pressure storage part and releases corresponding overflow cross sections as a function of the engagement depth.
• no structurally complex measures are required for establishing the permissible fuel quantity passing through the blocking piston; rather, this can be achieved by a targeted determination of the leaks, so the games between locking piston and receiving bore and the possible game between control rod and locking piston.
• bores, in particular throttle bores can also be assigned to the blocking piston via which the passage takes place.
• the flow control valve can take over the function of a blocking safety valve, which - outside of the operating mode of the internal combustion engine - prevents an inflow of fuel to the cylinder of the internal combustion engine connected to the injector even if the associated injection openings are not completely closed via the nozzle needle.
• a blocking safety valve which - outside of the operating mode of the internal combustion engine - prevents an inflow of fuel to the cylinder of the internal combustion engine connected to the injector even if the associated injection openings are not completely closed via the nozzle needle.
• the control valve is designed in a manner that allows higher switching speeds, using hydrostatic as well as hydrodynamic effects, through which also a damping the control piston movement in the approach results in a respective stop surface as part of a sealing boundary.
• the advantages of Piezostell- members as actuators can be fully exploit, since according to the high switching speed when applying the control piston by the actuator, a correspondingly fast return movement for the control piston can be achieved, but within the scope of the invention Magnetic actuators can be used as actuators.
• FIG. 1 shows an injection injector, for illustrative purposes divided on an upper part (Fig. 1) and a lower part (Fig. 2)
• Fig. 3 shows a detail III of Fig. 4 in an enlarged
• Fig. 4 is a partial enlargement IV in Fig. 1, in particular to illustrate the structural design of the mushroom piston with respect to the support of actuating movements by overflow effects, and
• FIG. 5 to improve the overview of the structure of a Injektinjektors an overall view of the same, in a comparison with the embodiment of FIG. 1 and 2 slightly modified design.
• Figs. 1 and 2 show, in addition to each other, an injection injector 1 according to the invention in its entirety.
• Combustion chamber side - based on an internal combustion engine, not shown, in the cylinder head of the injection injector 1 is installed injecting the combustion chamber - runs from the injection injector 1 in a nozzle body 2, followed by a conical transition part 4 and an intermediate plate 5, via a clamping nut 3 against an injector 6 are clamped.
• a pressure accumulator 7 is provided, which is closed at the opposite end to the nozzle body 2 via a closing piece 8, followed by a control valve 9 and this downstream an actuator 10.
• the pressure accumulator 7 is centrally penetrated by a control rod 11, which may also be formed hollow with advantage, which runs out in a bore of the end piece 8 runs on a control chamber 12, which is then connected to the final piece 8 is covered by a plate 13 to which the hous ⁇ se 14 of the control valve 9 follows, which in turn is covered by a cover plate 15 which is penetrated by the actuating plunger 16 of the actuator 10, which may be formed as a piezo or Mag ⁇ netsteller can, and preferably, as shown ⁇ , is designed as a piezoelectric actuator.
• the pressure accumulator 7 is connected via the channels 19 and 20 with the control chamber 12, and according to the thus given pressurization of the control chamber 12, the control rod 11 in Direction loaded on the nozzle body 2. If the control piston 17 is displaced by energizing the actuator 10 against the force of the spring 18 and against hydraulic forces in its lower Abdichtlage, the connection of the control chamber 10 is shut off to the accumulator 7 and the control chamber 12 is via the channel 20 and further channels 21, 22 (see Fig. 4) connected to the low pressure side, wherein the connection to the low pressure side is symbolized by the arrow 23.
• the pressure accumulator 7 communicates with a high-pressure source, for example a storage tube (common rail), via a channel 24 which opens onto the accumulator 7.
• a high-pressure source for example a storage tube (common rail)
• the pressure accumulator 7 is subdivided in the solution according to the invention into a control valve-side pressure accumulator part 25 and a nozzle-side pressure accumulator part 26, wherein the high-pressure side connecting passage 24 on the control valve side Pressure accumulator part 25 opens and the two pressure storage parts 25, 26 gegeneinan ⁇ are delimited via a flow limiting valve 28.
• the quantity limiting valve 28 is designed for the fuel throughput during operation of the internal combustion engine with maximum injection quantity and controls the connection between the pressure accumulator parts 25 and 26 when a threshold value lying above the aforementioned flow rate is exceeded.
• a support spring 30 is supported against the injector 6-position support plate 5 and enclosed in the illustrated embodiment by a stop sleeve 31 in its adjacent to the support plate 5 area, wherein the stop sleeve 31 is limited in against the force of the support spring 30 displaced locking piston 29 whose displacement and when plant the locking piston 29 is interrupted on the stop sleeve 31, the passage connection from the pressure accumulator 7 in the direction of the nozzle body 2.
• a further spring 32 is supported, which operates in the opposite direction to the support spring 30 and the control rod 11 is applied, which in turn is supported against the shaft 33 of a nozzle needle 34 which is guided in a nozzle needle bore 35 of the nozzle body 2 and in their illustrated closed position to the nozzle body 2 in the end region of the nozzle needle bore 35 lying injection openings 36 abgrest.
• the nozzle needle 34 is loaded in its closed position in addition to the application of the spring 32 by the hydraulic overweight of the control rod 11 and in the region of its shaft 33 by a stop sleeve 37, through which a positionally secure connection of the nozzle needle 34 to the control rod 11 is made by the control rod 11 protrudes into the stop sleeve 37 and held suitably in this is, wherein the fit is selected such that on the one hand a sealing connection between stop sleeve 37 and STEEL ⁇ 11 and the nozzle needle shaft 33 is reached, on the other hand - for assembly - the control rod 11 from the shaft 33 of the nozzle needle 34 can be separated.
• the stroke of the nozzle needle 34 is limited in the opening direction, wherein the stop sleeve 37 is supported in its wegbegrenzenden stop position on the transition part 4.
• the nozzle-side pressure storage part 26 is in open connection with the nozzle needle bore 35, as can be seen in FIG. 2, the nozzle needle 34 having a flow-enabling, in particular polygonal, for example triangular cross-section, in its guide region to the nozzle needle bore 35 , so that in this guide area, a free supply of fuel to the seating area of the nozzle needle 34 is given, the pressure-dependent in the Wegbe5-0e on the stop sleeve 37 opening position is adjustable when the control rod 11 is not pressurized by the control chamber 12 and the control chamber 12 by energizing the actuator 10 and adjustment of the control piston 17 against the force of the spring 18 via the channels 20, 21 and 22 is connected to the low pressure side.
• control rod 11 in the area of their expiring on the control chamber 12 end in the housing 14 sealingly and centering fixed end piece 8 and opposite by their position-fixed connection via the stop sleeve 37 at the Nozzle needle 34, so that the only a few millimeters thick control rod 11, which may optionally also be hollow, both in terms of vibrations and deformations is critical.
• the vibration behavior of the injection injector 1 with respect to pressure oscillations is improved by the internal pressure accumulator 7 integrated in the injection injector 1, wherein the accumulator 7 according to the invention advantageously also allows the integration of the flow control valve 28, through which the pressure accumulator 7 into its two pressure accumulator parts 25, 26 is divided and preferably forms a sliding guide for the control rod 11 with its locking piston 29.
• the blocking piston 29 is designed such that in the period between successive injections, an amount of fuel can pass from the control valve-side pressure storage part 25 to the nozzle-side pressure storage part 26, which essentially corresponds to the respective regular injection quantity corresponds and is below a predetermined threshold. Shown is the formation of the locking piston 29 on its side remote from the support spring 30 side with an end-side piston extension 38 in a diameter of the locking piston 29 in diameter reduced region 39 of the pressure accumulator 7 protrudes.
• the front-side piston extension 38 offers the possibility of injection rate development by the fact that in the overlap region of the piston extension 38 to the area 39 of the pressure accumulator 7 by tighter fit, by graduated circumferential contours or the like StudentsströmJ from pressure accumulator 25 to the pressure accumulator 26 with displacement of the locking piston 29 against the force of Support spring 30 are varied path-dependent.
• the leakage connection between the locking piston 29 and the control rod 11 largely To interrupt, it may be expedient to provide the locking piston 29 instead of, or in addition to the piston shoulder 38 with a fle ⁇ xible, in particular pressure-dependent neck-collar 64 can be provided.
• the control piston 17, as shown in FIGS. 3 and 4 designed as a mushroom piston, that is with a conically widening headboard 40, the protrudes beyond the diameter 41 of the shaft 42.
• the conical head part 40 corresponds on the part of the housing 14 has a conical receptacle 43, and the head part 40 has on the one hand in the direction of the actuator 10 is determined by a sealing edge sealing diameter 44 against the covering cover plate 15 and on the other hand determined by a further sealing edge sealing diameter 45th against the housing 14 in the region of the conical receptacle 43.
• the sealing diameters 44 and 45 are each larger than the diameter 41 of the shank 42, so that in the direction of the respective sealing abutment pressure-dependent results in a supporting force.
• the respective inflow-side edge 46 and 48 adjoins the respective mating surface 50, 51 tapering to the sealing diameter 44 and 45, respectively Position of the control piston 17 from a tapered fürströmspalt, and depending on the gap height arise - based on the pressure in the stationary medium - pressure deviations, corresponding to the flow rate in the direction of a negative pressure.
• annular flanks 48, 49 on both sides of the lower, sealing diameter 44 narrow and inclined to the counter surface 51 on the receiving cone 43 only flat, and it is a broader outer edge 46 sought to counter surface 50.
• the solution according to the invention thus leads to a relatively simple injection injector, in which only small pressure oscillations result, in particular due to the integration of an accumulator into the injector, and in which only pressure peaks occur that are slightly above the system pressure, wherein, in addition, low pressure oscillation ranges are achieved , This allows high system pressures.
• Advantageous angular sizes in the sense of influencing the adjusting movements of the control piston 17 according to the invention are for the cone angle 52 of the receiving cone 43, for example, 90 °, at a cone angle 53 of lying in the inlet on the lower, sealing diameter 45 edge 48 of about 120 ° and a cone angle 54 of in the course of the lower sealing diameter 55 lying edge 49 of about 80 °, with other angular sizes with a comparable ratio of the angle to each other are within the scope of the invention.
• Fig. 5 shows an overall view of an injection injector 60, which largely corresponds in its overall construction to the injection injector 1 according to FIGS. 1 and 2, which is why the relevant reference numerals have been adopted and reference is made to the description of FIGS. 1 and 2.
• the injection injector 60 is provided with an actuator 10 designed as a magnetic actuator.
• the pressure storage part 26, which is delimited against the pressure storage part 25 via the quantity limiting valve 28, is widely located. Hend within a subsequent to the intermediate plate 5, lying in the transition to the housing 6 insert piece 61 which is sleeve-shaped and which is clamped on the clamping nut 3 together with the nozzle body 2, the transition part 4 and the intermediate plate 5.
• the actuator piston 29 of the flow control valve 28 supporting support spring 30 is enclosed by the sleeve-shaped insert 61 and is supported against the intermediate plate 5 via a sleeve-shaped base piece, which is designated 62 and, as well as the support spring 30, the control rod 11 surrounds.
• the stop limit for the locking piston 29 via the insert 61 which has an engaging in the displacement of the locking piston 29 annular collar 63.
• the annular collar 63 is located on the housing 6 facing the end of the insert piece 61, and the flow control valve 28 is located with its locking piston 29 near the insert 61 facing the end of the housing 6.

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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)
• Nitrogen Condensed Heterocyclic Rings (AREA)
• Pharmaceuticals Containing Other Organic And Inorganic Compounds (AREA)

Applications Claiming Priority (2)

Publications (2)

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• 2005
  • 2005-11-23 DE DE102005056133A patent/DE102005056133A1/de not_active Withdrawn
• 2006
  • 2006-11-20 AT AT06818660T patent/ATE435369T1/de active
  • 2006-11-20 DE DE502006004149T patent/DE502006004149D1/de active Active
  • 2006-11-20 EP EP06818660A patent/EP1952012B1/fr not_active Not-in-force
  • 2006-11-20 WO PCT/EP2006/011093 patent/WO2007059906A1/fr active Application Filing

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