EP2307697B1 - Fuel injector with two-piece armature - Google Patents

Fuel injector with two-piece armature Download PDF

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Publication number
EP2307697B1
EP2307697B1 EP09769057A EP09769057A EP2307697B1 EP 2307697 B1 EP2307697 B1 EP 2307697B1 EP 09769057 A EP09769057 A EP 09769057A EP 09769057 A EP09769057 A EP 09769057A EP 2307697 B1 EP2307697 B1 EP 2307697B1
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EP
European Patent Office
Prior art keywords
armature
fuel injector
valve
control chamber
anchor
Prior art date
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Active
Application number
EP09769057A
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German (de)
French (fr)
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EP2307697A1 (en
Inventor
Andreas Rettich
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Robert Bosch GmbH
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Robert Bosch GmbH
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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
    • F02M63/0024—Valves characterised by the valve actuating means electrical, e.g. using solenoid in combination with permanent magnet
    • 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
    • F02M2200/30—Fuel-injection apparatus having mechanical parts, the movement of which is damped
    • F02M2200/306—Fuel-injection apparatus having mechanical parts, the movement of which is damped using mechanical means
    • 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

Definitions

  • both pressure-controlled and stroke-controlled injection systems can be used.
  • fuel injection systems so-called accumulator injection systems are used in the pump-nozzle units, pump-line-nozzle units.
  • high pressure fuel eg, fuel at over 1000 bar
  • common rail injectors make it possible in an advantageous manner to adapt the injection pressure to the load and the speed of the internal combustion engine.
  • the following invention relates in particular to common rail fuel injectors, but is basically also applicable to other types of fuel injectors.
  • an actuator is generally used for opening the fuel injector, that is to say for starting the injection process, and for subsequently closing the fuel injector.
  • an actuator is generally used for opening the fuel injector, that is to say for starting the injection process, and for subsequently closing the fuel injector.
  • magnetic actuators or piezoactuators can be used here, the invention described below starting from the use of magnetic actuators.
  • Hydraulic valves with magnetic actuators in particular a pressure balance of the hydraulic valves is sought.
  • the very small solenoid valve strokes which may for example be about 50% smaller than, for example, the strokes of fuel injectors with comparable ball valves, increase the stability of fuel injectors with pressure balanced hydraulic solenoid valves significantly.
  • a problem with such fuel injectors is the bouncing of the solenoid valve anchor when closing the valve. Due to this bounce, the minimum time interval between switching operations is typically limited to 200 to 250 ⁇ s. This is due in particular to the fact that small changes in the bounce behavior over the runtime can lead to a significant injection quantity drift if the armature closing bounce is not completed when a follow-up injection, for example the second injection, is triggered. In many cases, however, spray intervals, ie distances between individual switching operations of the hydraulic valve, of about 100 microseconds are required.
  • a fuel injector for injecting fuel into the combustion chamber of an internal combustion engine, which at least largely avoids the disadvantages of known fuel injectors described above.
  • the fuel injector can be used in particular for use in accumulator injection systems, in particular in self-igniting internal combustion engines, although other uses are also conceivable.
  • the advantages of pressure balanced hydraulic valves can be maintained.
  • a basic idea of the present invention is that armature closing bouncing can be prevented by decoupling the anchor bolt and the anchor plate. As a result, the advantages of a pressure balanced valve can be further optimized, and in particular very small temporal spray clearances can be realized.
  • the invention can be combined with respect to the production, including assembly with fuel injectors with one-piece anchor, so that for example the fuel injector according to the invention with multi-part anchor can be offered as an option on customer request.
  • the manufacture of the armature is significantly simplified compared to conventional armature.
  • it can be separated by the decoupling of anchor bolt and anchor plate Optimize materials.
  • Different materials can be used for the anchor bolt and the anchor plate.
  • the anchor plate with respect to the magnetic properties and the geometry can be optimally designed, as well as the separately formed anchor bolt can be optimized, for example, optimal closure properties and the lowest possible wear.
  • no consideration must be given to wear on the valve seat with regard to the selection of materials and the geometric design of the anchor plate.
  • both material and geometry can be reduced for minimal wear and optimum sealing properties.
  • eliminates the need for using a spring plate since, for example, setting rings for an elevation can be used as a measure group.
  • the assembly of the proposed fuel injector can be carried out using an armature designed as an assembly.
  • this assembly can comprise an anchor plate, an anchor sleeve, an adjusting ring, in particular a sickle disc.
  • This assembly can be preassembled outside the actual assembly of the fuel injector, for example, and delivered as a ready-preassembled assembly to the assembly of the actual fuel injector.
  • the fuel injector comprises an injection valve member movably mounted in an injector body of the fuel injector for closing or releasing at least one injection opening.
  • the injection valve member may be designed in one or more members.
  • the proposed fuel injector comprises at least one hydraulic valve, which is set up to control a stroke of the injection valve via at least one control chamber.
  • the hydraulic valve can be designed as a pressure-balanced valve, that is, as a valve to which even in the closed state, no high pressure of the fuel, so for example, no rail pressure acts. This can take place, for example, in that the hydraulic valve does not provide a hydraulic surface acting on the fuel in an opening or closing direction of the hydraulic valve, for example, no surface or surface component oriented perpendicularly to the opening of a drainage bore to be closed.
  • the hydraulic valve has at least one magnetic actuator with at least one magnetic coil and at least one magnet armature.
  • the magnet armature in turn comprises at least one armature plate interacting with the magnet actuator and at least one movably mounted relative to the armature plate and controlling a pressure in the control chamber Anchor bolt on.
  • This anchor bolt is preferably designed to release or close at least one outlet throttle of the control chamber, in accordance with the control of the magnetic actuator.
  • An anchor bolt is thus to be understood as a fundamentally arbitrarily shaped closing element, which can be designed, for example, as an elongate closing element with an arbitrary cross-section, for example in the form of a solid bolt. Also, a hollow cross-section may be present, which is explained in more detail below using the example of a preferred sleeve shape.
  • the anchor bolt is mounted within the anchor plate or the anchor plate surrounding, so that the anchor bolt and the anchor plate are displaceable relative to each other in the closing direction.
  • the anchor bolt is mounted relative to the anchor plate such that a movement of the anchor plate in an opening direction against the closing direction, at least from a certain minimum stroke, entrains the anchor bolt, so that the hydraulic valve opens. This can be done for example via appropriate shoulders and / or other entrainment devices on the anchor bolt and / or on the anchor plate.
  • the anchor bolt according to the invention should be sleeve-shaped and thus comprise an anchor sleeve or designed as an anchor sleeve.
  • the anchor sleeve in the axial direction is slidably mounted on the anchor plate, in particular within the anchor plate.
  • the sleeve shape of the anchor bolt in the form of an anchor sleeve is advantageous for the design of a pressure balanced hydraulic valve, according to the above definition, since an anchor sleeve can be used to provide as possible no hydraulic surface against the closing direction of the fuel. All hydraulic forces on the anchor sleeve can then act in the radial direction without affecting a position of the anchor sleeve in the axial direction or exert a hydraulic force on this anchor sleeve.
  • the anchor bolt can be acted upon in particular by means of a valve spring element, for example a helical valve spring, with a force acting in a closing direction of the hydraulic valve first force.
  • the armature plate in turn can be acted upon in particular by means of at least one armature spring element, for example a helical armature spring, with a second force acting counter to the closing direction. In this case, this second force is preferably lower than the first force.
  • an anchor sleeve it is possible to receive a pressure pin for the hydraulic sealing of the interior of the anchor sleeve within the anchor sleeve, on the control chamber side facing the cavity within the anchor sleeve.
  • the interior the anchor sleeve can in particular be designed cylindrical, in particular as a circular cylinder and / or as a polygonal cylinder.
  • the outer diameter of the pressure pin can be adapted to the inner diameter or the inner dimensions of this inner space, so that the pressure pin is mounted, for example, sliding and sealing within the interior of the anchor sleeve.
  • the pressure pin, the anchor sleeve and a valve piece with an outlet throttle of the control chamber can then limit a valve space, wherein hydraulic forces act only on the pressure pin by the high pressure of the fuel within this valve space, but not on the anchor sleeve. In this way, a pressure balance can also be generated.
  • the fuel injector comprises a valve piece, within which at least one outlet throttle of the control chamber is accommodated.
  • an outlet throttle can generally be understood to mean an opening to the control chamber which, when the hydraulic valve is open, limits or controls the outflow of the fuel from the control chamber to a low-pressure drain.
  • valve piece has a, at least in the closed state of the hydraulic valve, projecting into the anchor sleeve approach, in particular a cylindrical approach.
  • This approach can be adapted at least in sections from its cross-section to the inner dimensions of the interior of the anchor sleeve, so at least in sections, for example, in turn, have a circular cross section, a polygonal cross section or the like.
  • the approach of the valve piece can also serve as a guide for the anchor sleeve, preferably a sealing guide is selected.
  • An orifice of the outlet throttle of the control chamber can be accommodated in particular in the approach.
  • This mouth can be arranged, for example, at a remote from the control chamber end of the approach.
  • the at least one orifice may also be received in a peripheral constriction of the neck.
  • the approach may initially comprise a first guide section, then the said constriction with the at least one mouth, and then a further guide section.
  • the at least one guide section can be adapted from its outer diameter preferably to the inner diameter of the interior of the anchor sleeve, so for example, in turn, have said circular and / or polygonal cross-section.
  • a changeable shim in particular a sickle disc
  • Such a shim which can be stored, for example, in different thicknesses, can be used to allow adjustment of the overstroke of the hydraulic valve. Under an overstroke is here after switching off the Magnetaktors, a distance referred to which, after the anchor bolt has reached its seat and thus its closed position, the anchor plate still further moves due to their own inertia.
  • a corresponding overstroke can be provided, in particular an adjustable overstroke.
  • This overstroke stop can also be set up as an exchangeable overstroke stop, for example once again in the form of a replaceable disc or a ring.
  • This overstroke stop can basically be provided between any part of the fuel injector, in particular the injector body, and the anchor plate.
  • the armature plate on its side facing away from the magnetic actuator side a guide extension, for example a cylindrical sleeve-shaped guide extension, wherein the fuel injector has a guide for receiving this guide extension.
  • the at least one overstroke stop can be arranged between this guide and the guide extension.
  • this guide which, for example, part of a valve piece, in which the above-described outlet throttle of the control chamber is added, may be, and the guide extension.
  • the at least one overstroke stop can be arranged.
  • it can be accommodated in the form of a replaceable disk between the guide and the guide extension.
  • FIG. 1 a first embodiment of a fuel injector 110 according to the invention is shown in a sectional view with a cutting direction parallel to a Injektorachse 112 in a partial view.
  • the fuel injector 110 comprises an injector body 114, which in FIG. 1 is shown only slightly.
  • an injection valve member 116 is slidably mounted in the axial direction, of which in the sectional illustration according to FIG FIG. 1 only one valve piston 118 is shown.
  • the injection valve member 116 may be formed one or more members and serves to open or close at least one injection port, which in FIG. 1 not shown.
  • valve piston 118 At its upper end, the valve piston 118 is mounted in a sleeve extension 120 of a valve piece 122, so that a control chamber 124 is formed between the upper side of the valve piston 118 and the valve piece 122.
  • This control chamber can be acted upon by an inlet throttle 126 with high-pressure fuel, so that the pressure in the control chamber 124 controls a position of the valve piston 118 and thus a position of the injection valve member 116.
  • the valve piece 122 furthermore has an at least partially cylindrically configured valve body 128, which is supported on the injector body 114 downwards, that is to say in a closing direction of the injection valve member 116.
  • a conical sealing shoulder 130 and, subsequent to the sealing shoulder 130, a cylindrical projection 132 of the valve body 128 are first received on this valve body 128.
  • a discharge throttle 134 of the control chamber 124 is arranged in the valve piece 122.
  • This outlet throttle 134 starting from the control chamber 124, initially comprises an axial bore 136, followed by two throttle bores 138 running obliquely to the injector axis 112 in this exemplary embodiment.
  • These throttle bores 138 each open into openings 140 which are provided in a peripheral constriction 142 of the attachment 132 , Above the constriction 142, the projection 132 is widened again and has a guide section 144.
  • the outlet throttle 134 can the control chamber 124 with a (in FIG. 1 not shown) connect low-pressure drain, so that a pressure in the control chamber 124 and thus a position of the injection valve member 116 can be controlled by opening or closing the drain throttle 134.
  • a hydraulic valve 146 is provided in the fuel injector 110, which is designed as a solenoid valve.
  • the hydraulic valve 146 includes a magnetic actuator 148 having a solenoid 150 and a magnetic core 152 which are arranged axially symmetrically.
  • Magnetic actuator 154 further comprises a magnetic armature 154.
  • Magnetic armature 154 is acted upon by a force in the closing direction by means of a valve spring 158 mounted in a central cavity 156 of magnetic core 152.
  • the armature 154 is acted upon by an armature spring 160, which is supported on the valve body 128 with a force opposite to the closing direction.
  • the armature 154 is designed in two parts in the illustrated embodiment and includes an anchor plate 162 and an anchor bolt 164th
  • the armature plate 162 At its end facing the magnetic core 152, the armature plate 162 has an armature plate 166 in the form of an axially symmetrical annular disk. In the closing direction, a cylinder sleeve-shaped guide extension 168 adjoins this anchor plate 166.
  • the armature plate 162 cooperates with the magnetic coil 150 and can accordingly be made of a material optimized for magnetic actuation.
  • the anchor bolt 164 is slidably mounted in this embodiment.
  • This anchor bolt 164 has an anchor sleeve 170 in the illustrated embodiment.
  • This anchor sleeve 170 comprises a cylindrical inner space 172, in which the guide portion 144 of the projection 132 is slidably and sealingly mounted.
  • the anchor sleeve 170 has a sealing edge 174, which in the in FIG. 1 illustrated closed state of the hydraulic valve 146 is seated on the sealing shoulder 130 of the valve member 122 and forms a sealing seat.
  • the outlet throttle 134 is closed, so that in the control chamber 124 high pressure is applied and the injection valve member 116 in its in FIG. 1 Not shown valve seat is pressed and closes the at least one injection port.
  • hydraulic valve 146 configured as a pressure-balanced valve, as can act on the hydraulic valve 146, in particular the anchor bolt 164, in the axial direction no hydraulic forces.
  • the pressure, which is out the control chamber 124 transmits via the outlet throttle 134 in the constriction 142 can act only in the radial direction on the inner walls of the anchor sleeve 170.
  • the magnetic core 152 facing end of the anchor bolt 164 has a shim 176 which is inserted into a circumferential groove of the anchor sleeve 170.
  • This shim 176 is configured in the illustrated embodiment, for example, as a sickle plate 178, such as from a top view of the armature 154 in FIG. 2 evident.
  • the residual air gap disk 184 is not shown in this figure.
  • the anchor sleeve 170 has at its lower end, as in FIG. 1 can be seen, a shoulder 180, which limits the movement of the armature plate 162 down and which thus acts as an overstroke stop 182.
  • the armature sleeve 170 can first be inserted from below into the guide extension 168, whereupon the sickle disk 178 can be pushed into the groove in the armature sleeve 170 at the upper end.
  • the valve spring 158 is supported in the illustrated embodiment on the sickle plate 178, but may alternatively be supported on other parts of the anchor bolt 164, for example, the anchor sleeve 170.
  • the armature spring 160 is supported at its upper end on the armature plate 166.
  • the sliding support of the anchor sleeve 170 in the anchor plate 162 allows for relative movement between the anchor plate 162 and the anchor bolt 164, which is bounded upwardly by the sickle disc 178 and down through the shoulder 180.
  • a residual air gap disk 184 may be provided in the form of one or more annular disks, which may set a gap between the magnetic core 152 and the magnet armature 154.
  • the residual air gap between the magnetic core 152 and the magnet armature 154 may also be designed as an air gap.
  • a stop for the anchor bolt 164 or the anchor sleeve 170 of the anchor bolt 164 also take place in a different form than by the use of a disc.
  • the solenoid actuator 148 is turned off or the magnetic force is reduced, so that, driven by the valve spring 158, the anchor bolt 164 is pressed back into its seat and again in the control chamber 124 can build up a high pressure.
  • the injection valve member 116 then closes again.
  • the residual air gap disc 184 may preferably be clamped under the sickle disc 178 so that the residual air disc 184 may be held in a defined position by the sickle disc 178.
  • the anchor plate 162 is held between the injections by means of the armature spring 160 in a defined position or brought into such a defined position.
  • the spring force of the armature spring 160 should be chosen as small as possible, preferably at a maximum of 3 to 4 Newtons.
  • the armature plate 162 will continue to move downwardly due to its inertia , This way is also referred to as overstroke and is in FIG. 1 denoted by a.
  • Other sizes x (thickness of the sickle plate 178), z (axial length of the anchor plate 162) and y (distance between the upper edge of the sickle plate 178 and the underside of the anchor plate 162) are also in FIG. 1 Are defined.
  • the overstroke a is limited by the overstroke stop 182, which in this case is formed by the shoulder 180 at the top of a collar 186 of the anchor sleeve 170.
  • the excess stroke a should preferably not be greater than 10 microns. If, in individual cases, the tolerances of the individual parts of the dimensions relevant to the overstroke are greater than the overtravel tolerance requires, it is possible to set the overstroke a via an adjusting ring (measuring groups). In this case, the dimensions marked y and z in FIG. 1 are measured and then a corresponding dial 176 (dimension x in FIG. 1 ) to be selected.
  • FIG. 3 a second embodiment of a fuel injector 110 according to the invention is shown.
  • the fuel injector 110 comprises an injector body 114, in which an injection valve member 116 is mounted with a valve piston 118.
  • a control chamber 124 is formed in a valve piece 122, which can be acted upon by an inlet throttle 126 with high pressure.
  • the control chamber 124 is again pressure relieved, the Outflow throttle 134 in the in FIG. 3 illustrated embodiment, in contrast to the embodiment according to FIG. 1 , only an axial bore 136 includes.
  • This axial bore 136 opens into the interior of a cylindrical sleeve-shaped guide 188 of the valve piece 122 and can be closed or released by the hydraulic valve 146.
  • the hydraulic valve 146 is basically similar to that in FIG FIG. 1 shown hydraulic valve 146 shown. It is in the illustration according to FIG. 3 the magnetic actuator 148 is shown only partially, with only part of the magnetic core 152 being depicted.
  • the magnetic coil 150 which, for example, analogous to FIG. 1 can be designed, is in FIG. 1 Not shown.
  • the magnetic actuator 148 in the embodiment of FIG. 3 a magnet armature 154 with an anchor plate 162 and an anchor bolt 164.
  • the anchor plate 162 is again configured with an anchor plate 166 and a guide extension 168.
  • the guide extension 168 has at its lower end a constriction 190, which is cylindrical and corresponds to the inner diameter of the guide 188 from its outer diameter forth. The guide extension 168 is thus guided in the guide 188 of the valve piece 122.
  • the anchor sleeve 170 is in turn designed tubular and has at its lower end a seat edge 192, for example, a biting edge, a flat seat or a conical seat, which in the in FIG. 3 shown closed state on a sealing seat 194 in the interior of the guide 188 of the valve seat 122 is seated and a mouth 140 of the outlet throttle 134 seals.
  • a cylindrical pressure pin 196 added inside the tubular anchor sleeve 170 is in the in FIG. 1 illustrated embodiment.
  • This cylindrical pressure pin is supported at its upper end on the magnetic core 152 or another part of the magnetic actuator 148. From its outer diameter, the pressure pin 196 corresponds to the inner diameter of the tubular anchor sleeve 170, so that the anchor sleeve 170 is slidably mounted on this pressure pin 196, the pressure pin 196, however, ensures a pressure-tight seal of the control chamber 124. Due to the hydraulic pressure in the control chamber 124, which transmits through the outlet throttle 134 on the pressure pin 196, this pressure pin 196 is pressed up against the magnetic core 152.
  • this covenant can turn be configured as a dial 176 or a sickle disc 178 and, for example, in turn, be positively connected to the anchor sleeve 170.
  • the collar can also be configured in other ways, for example as part of the anchor sleeve 170 itself. Under the sickle plate 178, in turn, a residual air gap disc 184 can be arranged.
  • the hydraulic valve 146 used is a pressure compensated valve because no hydraulic forces are acting on the armature 154 in the axial direction.
  • the magnetic actuator 148 is energized, the armature plate 162 is attracted by the magnetic coil 150 and moved upward. Due to the collar in the form of the sickle plate 178 on the anchor bolt 164 and the anchor bolt 164 is pulled by the anchor plate 162 with up. The entrapment of the residual air gap disc 184 again serves to hold it in a defined position.
  • the anchor plate 162 is guided in the described upward movement by the guide 188 on the guide extension 168.
  • the anchor plate 162 is positioned in a defined position.
  • the spring force of the armature spring 160 should be as small as possible, for example, again at a maximum of 3 to 4 Newtons.
  • the solenoid actuator 148 can be switched off or switched to a lower current.
  • the valve spring 158 pushes the anchor bolt 164 back into its seat. Once the anchor bolt has reached the seat, the mouth 140 is closed, and the control chamber 124 is again acted upon by the inlet throttle 126 with high pressure, so that the injection valve member 116 back down moves and closes the at least one injection port.
  • This overstroke a is limited by an overstroke stop 182.
  • This overstroke stop 182 is formed by the upper edge of the guide 188 in the illustrated embodiment.
  • a replaceable overstroke stop 182 may be provided in the form of an adjusting ring 200, as shown in FIG FIG. 3 is indicated.
  • This adjusting ring 200 may in particular be configured as a replaceable adjusting ring, so that the overstroke stop 182 may be configured as a replaceable overstroke stop 182.
  • the overstroke stop 182 is conceivable, for example in that the shoulder 180 is not formed on the guide extension 168 of the anchor plate 162, but for example on the guide 188.
  • Other types of overstroke stop or combinations of such overstroke stops are conceivable.
  • the excess lift a should preferably again be no greater than 10 microns.
  • the minimum overtravel a is limited by the maximum wear or the resulting anchor stroke drift in the valve seat.
  • the wear or the Ankerhubdrift is less than 4 microns, so that the lower limit of the excess stroke a can be about 5 microns.
  • the tolerances of the individual parts of the dimensions relevant to the overstroke a should in each case be greater than necessary in each case, so it is again possible to adjust the overstroke a via an additional adjusting ring, such as, for example, the adjusting ring 182, 200. In this case, before the assembly would have to turn into the FIG. 3 Measured with y and z dimensions are measured so that the adjustment ring 200 can be selected with the dimension x accordingly.

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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)

Abstract

The invention relates to a fuel injector (110) for injecting fuel into the combustion chamber of an internal combustion engine, especially for use in accumulator injection systems. The fuel injector (110) comprises at least one injection valve member (116) for closing or releasing at least one injection opening, said injection valve member being movably supported in an injector body (114) of the fuel injector (110). The fuel injector (110) also comprises at least one hydraulic valve (146), wherein the hydraulic valve (146) is provided to control a stroke of the injection valve member (116) via at least one control chamber (124). The hydraulic valve (146) comprises a magnetic actuator (148) having at least one magnetic coil (150) and at least one armature (154). The armature (154) comprises at least one armature plate (162), which interacts with the magnetic actuator (148), and at least one armature bolt (164), which is supported so as to be movable relative to the armature plate (162) and which controls a pressure in the control chamber (124).

Description

Stand der TechnikState of the art

Zur Versorgung von Brennräumen von Verbrennungskraftmaschinen, insbesondere selbstzündender Verbrennungskraftmaschinen, mit Kraftstoff können sowohl druckgesteuerte als auch hubgesteuerte Einspritzsysteme eingesetzt werden. Als Kraftstoffeinspritzsysteme kommen in die Pumpe-Düse-Einheiten, Pumpe-Leitung-Düse-Einheiten auch so genannte Speichereinspritzsysteme zum Einsatz. Bei Speichereinspritzsystemen (Common-Rail-Systemen) wird ein unter einem Hochdruck stehender Kraftstoff (beispielsweise Kraftstoff bei über 1000 bar) durch einen Hochdruckspeicher an einen Kraftstoffinjektor bereitgestellt. Common-Rail-Injektoren ermöglichen es in vorteilhafter Weise, den Einspritzdruck an die Last und die Drehzahl der Verbrennungskraftmaschine anzupassen. Die folgende Erfindung bezieht sich insbesondere auf Common-Rail-Kraftstoffinjektoren, ist jedoch grundsätzlich auch für andere Arten von Kraftstoffinjektoren einsetzbar.For supplying combustion chambers of internal combustion engines, in particular self-igniting internal combustion engines, with fuel, both pressure-controlled and stroke-controlled injection systems can be used. As fuel injection systems, so-called accumulator injection systems are used in the pump-nozzle units, pump-line-nozzle units. In common rail systems, high pressure fuel (eg, fuel at over 1000 bar) is provided by a high pressure accumulator to a fuel injector. Common rail injectors make it possible in an advantageous manner to adapt the injection pressure to the load and the speed of the internal combustion engine. The following invention relates in particular to common rail fuel injectors, but is basically also applicable to other types of fuel injectors.

Bei üblichen Common-Rail-Injektoren wird in der Regel ein Aktor zum Öffnen des Kraftstoffinjektors, das heißt zum Starten des Einspritzvorgangs, und zum anschließenden Schließen des Kraftstoffinjektors eingesetzt. Beispielsweise lassen sich hier Magnetaktoren oder Piezoaktoren einsetzen, wobei die im folgenden beschriebene Erfindung von der Verwendung von Magnetaktoren ausgeht.In conventional common rail injectors, an actuator is generally used for opening the fuel injector, that is to say for starting the injection process, and for subsequently closing the fuel injector. For example, magnetic actuators or piezoactuators can be used here, the invention described below starting from the use of magnetic actuators.

Bei derartigen Kraftstoffinjektoren wie z.B. EP 0 851 114 , mit hydraulischen Ventilen mit Magnetaktoren wird insbesondere eine Druckausgeglichenheit der hydraulischen Ventile angestrebt. Dies bedeutet, dass die Schließkraft der hydraulischen Ventile, also die Kraft, mittels derer die hydraulischen Ventile einen Druck in einem Steuerraum des Kraftstoffinjektors abdichten, vom System- bzw. Raildruck unabhängig ist. Dies wird dadurch erreicht, dass die abdichtende Wirkung der hydraulischen Ventile nicht gegen den anstehenden Druck aufgebracht werden muss. Bei kleineren Hüben lassen sich damit insbesondere große Ventilquerschnitte darstellen.In such fuel injectors such as EP 0 851 114 , Hydraulic valves with magnetic actuators in particular a pressure balance of the hydraulic valves is sought. This means that the closing force of the hydraulic valves, ie the force by means of which the hydraulic valves seal a pressure in a control chamber of the fuel injector, is independent of the system or rail pressure. This is achieved in that the sealing effect of the hydraulic valves does not have to be applied against the applied pressure. For smaller strokes can thus be used in particular large valve cross sections.

Mit derartig druckausgeglichenen Magnetventilen lassen sich deutliche Verbesserungen bezüglich der Mehrfacheinspritzung erreichen. Insbesondere die sehr kleinen Magnetventilhübe, welche beispielsweise um ca. 50 % kleiner sein können als beispielsweise die Hübe von Kraftstoffinjektoren mit vergleichbaren Kugelventilen, erhöhen die Stabilität von Kraftstoffinjektoren mit druckausgeglichenen hydraulischen Magnetventilen deutlich.With such pressure balanced solenoid valves, significant improvements in multiple injection can be achieved. In particular, the very small solenoid valve strokes, which may for example be about 50% smaller than, for example, the strokes of fuel injectors with comparable ball valves, increase the stability of fuel injectors with pressure balanced hydraulic solenoid valves significantly.

Eine Problematik bei derartigen Kraftstoffinjektoren stellt jedoch das Prellen des Magnetventilankers beim Schließen des Ventils dar. Aufgrund dieses Prellens wird der zeitliche Mindestabstand zwischen Schaltvorgängen typischerweise auf 200 bis 250 µs begrenzt. Dies ist insbesondere dadurch bedingt, dass über der Laufzeit bereits geringe Änderungen im Prellverhalten zu einer deutlichen Einspritzmengendrift führen können, wenn das Ankerschließprellen bei einer Ansteuerung einer Folgeeinspritzung, beispielsweise der zweiten Einspritzung, nicht abgeschlossen ist. In vielen Fällen werden jedoch Spritzabstände, das heißt Abstände zwischen einzelnen Schaltvorgängen des hydraulischen Ventils, von ca. 100 µs gefordert.A problem with such fuel injectors, however, is the bouncing of the solenoid valve anchor when closing the valve. Due to this bounce, the minimum time interval between switching operations is typically limited to 200 to 250 μs. This is due in particular to the fact that small changes in the bounce behavior over the runtime can lead to a significant injection quantity drift if the armature closing bounce is not completed when a follow-up injection, for example the second injection, is triggered. In many cases, however, spray intervals, ie distances between individual switching operations of the hydraulic valve, of about 100 microseconds are required.

Offenbarung der ErfindungDisclosure of the invention

Es wird daher ein Kraftstoffinjektor zum Einspritzen von Kraftstoff in den Brennraum einer Brennkraftmaschine vorgeschlagen, welcher die oben beschriebenen Nachteile bekannter Kraftstoffinjektoren zumindest weitgehend vermeidet. Der Kraftstoffinjektor ist insbesondere für den Einsatz in Speichereinspritzsystemen, insbesondere in selbstzündenden Brennkraftmaschinen, einsetzbar, wobei jedoch auch andere Einsatzzwecke denkbar sind. Insbesondere lassen sich mittels des vorgeschlagenen Kraftstoffinjektors die beschriebenen Ankerschließprellungen erheblich reduzieren, was zu Spritzabständen von weniger als 200 µs führen kann. Gleichzeitig können die Vorteile druckausgeglichener hydraulischer Ventile beibehalten werden.It is therefore proposed a fuel injector for injecting fuel into the combustion chamber of an internal combustion engine, which at least largely avoids the disadvantages of known fuel injectors described above. The fuel injector can be used in particular for use in accumulator injection systems, in particular in self-igniting internal combustion engines, although other uses are also conceivable. In particular, can be significantly reduced by means of the proposed fuel injector described Ankerschließprellungen, which can lead to spray intervals of less than 200 microseconds. At the same time, the advantages of pressure balanced hydraulic valves can be maintained.

Ein Grundgedanke der vorliegenden Erfindung besteht darin, dass ein Ankerschließprellen durch eine Entkopplung von Ankerbolzen und Ankerplatte verhindert werden kann. Dadurch können die Vorteile eines druckausgeglichenen Ventils weiter optimiert werden, und insbesondere können sehr kleine zeitliche Spritzabstände realisiert werden. Die Erfindung kann bezüglich der Fertigung einschließlich einer Montage mit Kraftstoffinjektoren mit einteiligem Anker kombiniert werden, so dass beispielsweise der erfindungsgemäße Kraftstoffmjektor mit mehrteiligem Anker als Option auf Kundenwunsch angeboten werden kann.A basic idea of the present invention is that armature closing bouncing can be prevented by decoupling the anchor bolt and the anchor plate. As a result, the advantages of a pressure balanced valve can be further optimized, and in particular very small temporal spray clearances can be realized. The invention can be combined with respect to the production, including assembly with fuel injectors with one-piece anchor, so that for example the fuel injector according to the invention with multi-part anchor can be offered as an option on customer request.

Die Fertigung des Ankers ist im Vergleich zu herkömmlichen Magnetankern deutlich vereinfacht. Zudem lassen sich durch die Entkopplung von Ankerbolzen und Ankerplatte getrennt Werkstoffoptimierungen vornehmen. Für den Ankerbolzen und die Ankerplatte können unterschiedliche Materialien eingesetzt werden. So kann beispielsweise die Ankerplatte bezüglich der magnetischen Eigenschaften und der Geometrie optimal ausgestaltet werden, ebenso wie der getrennt davon ausgebildete Ankerbolzen beispielsweise auf optimale Schließeigenschaften und möglichst geringen Verschleiß optimiert werden kann. So muss insbesondere keine Rücksicht auf einen Verschleiß am Ventilsitz genommen werden hinsichtlich der Materialauswahl und der geometrischen Ausgestaltung der Ankerplatte. Für den Ankerbolzen hingegen lassen sich sowohl Werkstoff als auch Geometrie für einen minimalen Verschleiß und optimale Dichteigenschaften verringern. Weiterhin entfällt die Notwendigkeit der Verwendung eines Federtellers, da stattdessen beispielsweise Einstellringe für eine Überhöhung als Maßgruppe verwendet werden können.The manufacture of the armature is significantly simplified compared to conventional armature. In addition, it can be separated by the decoupling of anchor bolt and anchor plate Optimize materials. Different materials can be used for the anchor bolt and the anchor plate. Thus, for example, the anchor plate with respect to the magnetic properties and the geometry can be optimally designed, as well as the separately formed anchor bolt can be optimized, for example, optimal closure properties and the lowest possible wear. In particular, no consideration must be given to wear on the valve seat with regard to the selection of materials and the geometric design of the anchor plate. For the anchor bolt, however, both material and geometry can be reduced for minimal wear and optimum sealing properties. Furthermore, eliminates the need for using a spring plate, since, for example, setting rings for an elevation can be used as a measure group.

Die Montage des vorgeschlagenen Kraftstoffinjektors kann unter Verwendung eines als Baugruppe ausgestalteten Ankers erfolgen. So kann diese Baugruppe beispielsweise, wie unten näher ausgeführt wird, eine Ankerplatte, eine Ankerhülse, einen Einstellring, insbesondere eine Sichelscheibe, umfassen. Diese Baugruppe kann außerhalb der eigentlichen Montage des Kraftstoffinjektors beispielsweise vormontiert werden und als fertig vormontierte Baugruppe an die Montage des eigentlichen Kraftstoffinjektors geliefert werden.The assembly of the proposed fuel injector can be carried out using an armature designed as an assembly. For example, as explained in more detail below, this assembly can comprise an anchor plate, an anchor sleeve, an adjusting ring, in particular a sickle disc. This assembly can be preassembled outside the actual assembly of the fuel injector, for example, and delivered as a ready-preassembled assembly to the assembly of the actual fuel injector.

Zur Umsetzung des oben beschriebenen Erfindungsgedankens umfasst der Kraftstoffinjektor einen in einem Injektorkörper des Kraftstoffinjektors bewegbar gelagertes Einspritzventilglied zum Verschließen oder Freigeben mindestens einer Einspritzöffnung. Das Einspritzventilglied kann eingliedrig oder mehrgliedrig ausgestaltet sein.In order to implement the inventive idea described above, the fuel injector comprises an injection valve member movably mounted in an injector body of the fuel injector for closing or releasing at least one injection opening. The injection valve member may be designed in one or more members.

Weiterhin umfasst der vorgeschlagene Kraftstoffinjektor mindestens ein hydraulisches Ventil, welches eingerichtet ist, um über mindestens einen Steuerraum einen Hub des Einspritzventils zu steuern. Dabei kann, wie oben beschrieben, das hydraulische Ventil als druckausgeglichenes Ventil ausgestaltet sein, das heißt als Ventil, auf welches auch im geschlossenen Zustand kein Hochdruck des Kraftstoffs, also beispielsweise kein Raildruck, wirkt. Dies kann beispielsweise dadurch erfolgen, dass das hydraulische Ventil keine in einer Öffnungs- oder Schließrichtung des hydraulischen Ventils wirkende hydraulische Fläche an den Kraftstoff bereitstellt, beispielsweise keine senkrecht zur zu verschließenden Öffnung einer Ablaufbohrung ausgerichtete Fläche oder Flächenkomponente.Furthermore, the proposed fuel injector comprises at least one hydraulic valve, which is set up to control a stroke of the injection valve via at least one control chamber. In this case, as described above, the hydraulic valve can be designed as a pressure-balanced valve, that is, as a valve to which even in the closed state, no high pressure of the fuel, so for example, no rail pressure acts. This can take place, for example, in that the hydraulic valve does not provide a hydraulic surface acting on the fuel in an opening or closing direction of the hydraulic valve, for example, no surface or surface component oriented perpendicularly to the opening of a drainage bore to be closed.

Das hydraulische Ventil weist mindestens einen Magnetaktor mit mindestens einer Magnetspule und mindestens einem Magnetanker auf. Der Magnetanker seinerseits umfasst mindestens eine mit dem Magnetaktor zusammenwirkende Ankerplatte und mindestens einen relativ zu der Ankerplatte beweglich gelagerten und einen Druck in dem Steuerraum steuernden Ankerbolzen auf. Dieser Ankerbolzen ist vorzugsweise eingerichtet, um, entsprechend der Steuerung des Magnetaktors, mindestens eine Ablaufdrossel des Steuerraums freizugeben oder zu verschließen. Unter einem Ankerbolzen ist somit ein grundsätzlich beliebig geformtes Schließelement zu verstehen, welches beispielsweise als langgestrecktes Schließelement mit einem beliebigen Querschnitt ausgestaltet sein kann, beispielsweise in Form eines soliden Bolzens. Auch ein hohler Querschnitt kann vorliegen, was unten am Beispiel einer bevorzugten Hülsenform näher ausgeführt wird.The hydraulic valve has at least one magnetic actuator with at least one magnetic coil and at least one magnet armature. The magnet armature in turn comprises at least one armature plate interacting with the magnet actuator and at least one movably mounted relative to the armature plate and controlling a pressure in the control chamber Anchor bolt on. This anchor bolt is preferably designed to release or close at least one outlet throttle of the control chamber, in accordance with the control of the magnetic actuator. An anchor bolt is thus to be understood as a fundamentally arbitrarily shaped closing element, which can be designed, for example, as an elongate closing element with an arbitrary cross-section, for example in the form of a solid bolt. Also, a hollow cross-section may be present, which is explained in more detail below using the example of a preferred sleeve shape.

Der Ankerbolzen ist innerhalb der Ankerplatte oder die Ankerplatte umgebend gelagert, so dass der Ankerbolzen und die Ankerplatte relativ zueinander in Schließrichtung verschiebbar sind. Dabei ist der Ankerbolzen derart relativ zur Ankerplatte gelagert, dass eine Bewegung der Ankerplatte in einer Öffnungsrichtung entgegen der Schließrichtung, zumindest ab einem gewissen Mindesthub, den Ankerbolzen mitnimmt, so dass das hydraulische Ventil öffnet. Dies kann beispielsweise über entsprechende Schultern und/oder andere Mitnahmevorrichtungen am Ankerbolzen und/oder an der Ankerplatte erfolgen.The anchor bolt is mounted within the anchor plate or the anchor plate surrounding, so that the anchor bolt and the anchor plate are displaceable relative to each other in the closing direction. In this case, the anchor bolt is mounted relative to the anchor plate such that a movement of the anchor plate in an opening direction against the closing direction, at least from a certain minimum stroke, entrains the anchor bolt, so that the hydraulic valve opens. This can be done for example via appropriate shoulders and / or other entrainment devices on the anchor bolt and / or on the anchor plate.

Der Ankerbolzen sollte erfindungsgemäss hülsenförmig ausgestaltet sein und somit eine Ankerhülse umfassen oder als Ankerhülse ausgestaltet sein. Dabei ist die Ankerhülse in der axialen Richtung gleitend an der Ankerplatte, insbesondere innerhalb der Ankerplatte, gelagert. Die Hülsenform des Ankerbolzens in Form einer Ankerhülse ist von Vorteil für die Ausgestaltung eines druckausgeglichenen hydraulichen Ventils, gemäß der obigen Definition, da eine Ankerhülse genutzt werden kann, um möglichst keine hydraulische Fläche entgegen der Schließrichtung an den Kraftstoff bereitzustellen. Sämtliche hydraulischen Kräfte auf die Ankerhülse können dann in radialer Richtung wirken, ohne eine Stellung der Ankerhülse in axialer Richtung zu beeinflussen bzw. eine hydraulische Kraft auf diese Ankerhülse auszuüben.The anchor bolt according to the invention should be sleeve-shaped and thus comprise an anchor sleeve or designed as an anchor sleeve. In this case, the anchor sleeve in the axial direction is slidably mounted on the anchor plate, in particular within the anchor plate. The sleeve shape of the anchor bolt in the form of an anchor sleeve is advantageous for the design of a pressure balanced hydraulic valve, according to the above definition, since an anchor sleeve can be used to provide as possible no hydraulic surface against the closing direction of the fuel. All hydraulic forces on the anchor sleeve can then act in the radial direction without affecting a position of the anchor sleeve in the axial direction or exert a hydraulic force on this anchor sleeve.

Der Ankerbolzen kann insbesondere mittels eines Ventilfederelements, beispielsweise einer spiralförmigen Ventilfeder, mit einer in einer Schließrichtung des hydraulischen Ventils wirkenden ersten Kraft beaufschlagt werden. Die Ankerplatte ihrerseits kann insbesondere mittels mindestens eines Ankerfederelements, beispielsweise einer spiralförmigen Ankerfeder, mit einer zweiten, entgegen der Schließrichtung wirkenden Kraft beaufschlagt werden. Dabei ist diese zweite Kraft vorzugsweise geringer als die erste Kraft.The anchor bolt can be acted upon in particular by means of a valve spring element, for example a helical valve spring, with a force acting in a closing direction of the hydraulic valve first force. The armature plate in turn can be acted upon in particular by means of at least one armature spring element, for example a helical armature spring, with a second force acting counter to the closing direction. In this case, this second force is preferably lower than the first force.

Wenn eine Ankerhülse verwendet wird, so ist es möglich, innerhalb der Ankerhülse, auf der dem Steuerraum zugewandten Seite des Hohlraums innerhalb der Ankerhülse, einen Druckstift zur hydraulischen Abdichtung des Innenraums der Ankerhülse aufzunehmen. Der Innenraum der Ankerhülse kann insbesondere zylinderförmig ausgestaltet sein, insbesondere als Kreiszylinder und/oder als polygonaler Zylinder. Der Außendurchmesser des Druckstifts kann auf den Innendurchmesser bzw. die Innenmaße dieses Innenraums angepasst sein, so dass der Druckstift beispielsweise gleitend und abdichtend innerhalb des Innenraums der Ankerhülse gelagert ist. Der Druckstift, die Ankerhülse und ein Ventilstück mit einer Ablaufdrossel des Steuerraums können dann einen Ventilraum begrenzen, wobei hydraulische Kräfte durch den Hochdruck des Kraftstoffs innerhalb dieses Ventilraums lediglich auf den Druckstift wirken, nicht jedoch auf die Ankerhülse. Auf diese Weise kann ebenfalls eine Druckausgeglichenheit erzeugt werden.If an anchor sleeve is used, it is possible to receive a pressure pin for the hydraulic sealing of the interior of the anchor sleeve within the anchor sleeve, on the control chamber side facing the cavity within the anchor sleeve. The interior the anchor sleeve can in particular be designed cylindrical, in particular as a circular cylinder and / or as a polygonal cylinder. The outer diameter of the pressure pin can be adapted to the inner diameter or the inner dimensions of this inner space, so that the pressure pin is mounted, for example, sliding and sealing within the interior of the anchor sleeve. The pressure pin, the anchor sleeve and a valve piece with an outlet throttle of the control chamber can then limit a valve space, wherein hydraulic forces act only on the pressure pin by the high pressure of the fuel within this valve space, but not on the anchor sleeve. In this way, a pressure balance can also be generated.

Ebenfalls bei Verwendung einer Ankerhülse ist es bevorzugt, wenn der Kraftstoffinjektor ein Ventilstück umfasst, innerhalb dessen mindestens eine Ablaufdrossel des Steuerraums aufgenommen ist. Unter einer Ablaufdrossel kann dabei allgemein eine Öffnung hin zum Steuerraum verstanden werden, welche, bei geöffnetem hydraulischem Ventil, den Abfluss des Kraftstoffs aus dem Steuerraum hin zu einem Niederdruckablauf begrenzt bzw. steuert.Also when using an anchor sleeve, it is preferred if the fuel injector comprises a valve piece, within which at least one outlet throttle of the control chamber is accommodated. In this context, an outlet throttle can generally be understood to mean an opening to the control chamber which, when the hydraulic valve is open, limits or controls the outflow of the fuel from the control chamber to a low-pressure drain.

Dabei ist es besonders bevorzugt, wenn das Ventilstück einen, zumindest im geschlossenen Zustand des hydraulischen Ventils, in die Ankerhülse hineinragenden Ansatz aufweist, insbesondere einen zylindrischen Ansatz. Dieser Ansatz kann von seinem Querschnitt her zumindest abschnittsweise auf die Innenabmessungen des Innenraums der Ankerhülse angepasst sein, kann also zumindest abschnittsweise beispielsweise wiederum einen kreisförmigen Querschnitt, einen polygonalen Querschnitt oder ähnliches aufweisen. Auf diese Weise kann der Ansatz des Ventilstücks gleichzeitig als Führung für die Ankerhülse dienen, wobei vorzugsweise eine abdichtende Führung gewählt wird.It is particularly preferred if the valve piece has a, at least in the closed state of the hydraulic valve, projecting into the anchor sleeve approach, in particular a cylindrical approach. This approach can be adapted at least in sections from its cross-section to the inner dimensions of the interior of the anchor sleeve, so at least in sections, for example, in turn, have a circular cross section, a polygonal cross section or the like. In this way, the approach of the valve piece can also serve as a guide for the anchor sleeve, preferably a sealing guide is selected.

Eine Mündung der Ablaufdrossel des Steuerraums kann insbesondere in dem Ansatz aufgenommen sein. Diese Mündung kann beispielsweise an einem vom Steuerraum abgewandten Ende des Ansatzes angeordnet sein. Alternativ oder zusätzlich kann die mindestens eine Mündung jedoch auch in einer umfangsseitigen Einschnürung des Ansatzes aufgenommen sein. So kann der Ansatz beispielsweise zunächst einen ersten Führungsabschnitt aufweisen, dann die genannte Einschnürung mit der mindestens einen Mündung, und anschließend einen weiteren Führungsabschnitt. Der mindestens eine Führungsabschnitt kann dabei von seinem Außendurchmesser vorzugsweise an den Innendurchmesser des Innenraums der Ankerhülse angepasst sein, also beispielsweise wiederum den genannten kreisförmigen und/oder polygonalen Querschnitt aufweisen.An orifice of the outlet throttle of the control chamber can be accommodated in particular in the approach. This mouth can be arranged, for example, at a remote from the control chamber end of the approach. Alternatively or additionally, however, the at least one orifice may also be received in a peripheral constriction of the neck. For example, the approach may initially comprise a first guide section, then the said constriction with the at least one mouth, and then a further guide section. The at least one guide section can be adapted from its outer diameter preferably to the inner diameter of the interior of the anchor sleeve, so for example, in turn, have said circular and / or polygonal cross-section.

Weitere bevorzugte Ausführungsformen der vorliegenden Erfindung betreffen die Ausgestaltung der Einstellmöglichkeiten der Hübe und Wege des hydraulischen Ventils. So ist es besonders bevorzugt, wenn der Ankerbolzen an einer dem Steuerraum abgewandten Seite zumindest teilweise von.einer auswechselbaren Einstellscheibe, insbesondere einer Sichelscheibe, umgeben ist. Eine derartige Einstellscheibe, welche beispielsweise in unterschiedlichen Dicken bevorratet werden kann, kann genutzt werden, um eine Einstellung des Überhubs des hydraulischen Ventils zu ermöglichen. Unter einem Überhub wird dabei nach Abschalten des Magnetaktors, eine Strecke bezeichnet, um welche sich, nachdem der Ankerbolzen seinen Sitz und damit seine Schließstellung erreicht hat, die Ankerplatte aufgrund ihrer eigenen Trägheit noch weiter bewegt.Further preferred embodiments of the present invention relate to the configuration of the adjustment possibilities of the strokes and paths of the hydraulic valve. That's the way it is particularly preferred when the anchor bolt is at least partially surrounded by a changeable shim, in particular a sickle disc, on a side facing away from the control space. Such a shim, which can be stored, for example, in different thicknesses, can be used to allow adjustment of the overstroke of the hydraulic valve. Under an overstroke is here after switching off the Magnetaktors, a distance referred to which, after the anchor bolt has reached its seat and thus its closed position, the anchor plate still further moves due to their own inertia.

Auch auf der gegenüberliegenden, dem Steuerraum zuweisenden Seite, kann ein entsprechender Überhubanschlag vorgesehen sein, insbesondere ein einstellbarer Überhubanschlag. Auch dieser Überhubanschlag kann wiederum als auswechselbarer Überhubanschlag eingerichtet sein, beispielsweise wiederum in Form einer austauschbaren Scheibe oder eines Rings. Dieser Überhubanschlag kann grundsätzlich zwischen einem beliebigen Teil des Kraftstoffinjektors, insbesondere des Injektorkörpers, und der Ankerplatte vorgesehen sein. Besonders bevorzugt ist es jedoch, wenn die Ankerplatte an ihrer von dem Magnetaktor abgewandten Seite einen Führungsfortsatz, beispielsweise einem zylinderhülsenförmigen Führungsfortsatz, aufweist, wobei der Kraftstoffinjektor eine Führung zur Aufnahme dieses Führungsfortsatzes aufweist. Zwischen dieser Führung, welche beispielsweise Bestandteil eines Ventilstücks, in dem die oben beschriebene Ablaufdrossel des Steuerraums aufgenommen ist, sein kann, und dem Führungsfortsatz kann der mindestens eine Überhubanschlag angeordnet sein. Beispielsweise kann dieser, wie oben beschrieben, in Form einer auswechselbaren Scheibe zwischen der Führung und dem Führungsfortsatz aufgenommen sein.Also on the opposite, the control room facing side, a corresponding overstroke can be provided, in particular an adjustable overstroke. This overstroke stop can also be set up as an exchangeable overstroke stop, for example once again in the form of a replaceable disc or a ring. This overstroke stop can basically be provided between any part of the fuel injector, in particular the injector body, and the anchor plate. However, it is particularly preferred if the armature plate on its side facing away from the magnetic actuator side a guide extension, for example a cylindrical sleeve-shaped guide extension, wherein the fuel injector has a guide for receiving this guide extension. Between this guide, which, for example, part of a valve piece, in which the above-described outlet throttle of the control chamber is added, may be, and the guide extension, the at least one overstroke stop can be arranged. For example, as described above, it can be accommodated in the form of a replaceable disk between the guide and the guide extension.

Kurze Beschreibung der ZeichnungenBrief description of the drawings

Ausführungsbeispiele der Erfindung sind in den Zeichnungen dargestellt und in der nachfolgenden Beschreibung näher erläutert.Embodiments of the invention are illustrated in the drawings and explained in more detail in the following description.

Es zeigen:

Figur 1
eine Schnittdarstellung eines ersten Ausführungsbeispiels eines erfindungsgemäßen Kraftstoffinjektors;
Figur 2
eine Draufsicht auf eine Ankerplatte des Ausführungsbeispiels gemäß Figur 1; und
Figur 3
eine Schnittdarstellung eines Ausschnitts eines zweiten Ausführungsbeispiels eines erfindungsgemäßen Kraftstoffinjektors.
Show it:
FIG. 1
a sectional view of a first embodiment of a fuel injector according to the invention;
FIG. 2
a plan view of an anchor plate of the embodiment according to FIG. 1 ; and
FIG. 3
a sectional view of a section of a second embodiment of a fuel injector according to the invention.

In Figur 1 ist ein erstes Ausführungsbeispiel eines erfindungsgemäßen Kraftstoffinjektors 110 in Schnittdarstellung mit einer Schnittrichtung parallel zu einer Injektorachse 112 in einer Teildarstellung gezeigt. Der Kraftstoffinjektor 110 umfasst einen Injektorkörper 114, welcher in Figur 1 lediglich ansatzweise gezeigt ist. In dem Injektorkörper 114 ist in axialer Richtung ein Einspritzventilglied 116 gleitend gelagert, von welchem in der ausschnittsweisen Darstellung gemäß Figur 1 lediglich ein Ventilkolben 118 gezeigt ist. Das Einspritzventilglied 116 kann ein- oder mehrgliedrig ausgebildet sein und dient zum Öffnen oder Verschließen mindestens einer Einspritzöffnung, welche in Figur 1 nicht dargestellt ist.In FIG. 1 a first embodiment of a fuel injector 110 according to the invention is shown in a sectional view with a cutting direction parallel to a Injektorachse 112 in a partial view. The fuel injector 110 comprises an injector body 114, which in FIG. 1 is shown only slightly. In the injector body 114, an injection valve member 116 is slidably mounted in the axial direction, of which in the sectional illustration according to FIG FIG. 1 only one valve piston 118 is shown. The injection valve member 116 may be formed one or more members and serves to open or close at least one injection port, which in FIG. 1 not shown.

An seinem oberen Ende ist der Ventilkolben 118 in einem Hülsenansatz 120 eines Ventilstücks 122 gelagert, so dass sich zwischen der Oberseite des Ventilkolbens 118 und dem Ventilstück 122 ein Steuerraum 124 ausbildet. Dieser Steuerraum ist über eine Zulaufdrossel 126 mit unter Hochdruck stehendem Kraftstoff beaufschlagbar, so dass der Druck in dem Steuerraum 124 eine Stellung des Ventilkolbens 118 und damit eine Stellung des Einspritzventilgliedes 116 steuert.At its upper end, the valve piston 118 is mounted in a sleeve extension 120 of a valve piece 122, so that a control chamber 124 is formed between the upper side of the valve piston 118 and the valve piece 122. This control chamber can be acted upon by an inlet throttle 126 with high-pressure fuel, so that the pressure in the control chamber 124 controls a position of the valve piston 118 and thus a position of the injection valve member 116.

Das Ventilstück 122 weist weiterhin einen zumindest teilweise zylindrisch ausgestalteten Ventilstückkörper 128 auf, welcher sich auf dem Injektorkörper 114 nach unten, das heißt in einer Schließrichtung des Einspritzventilglieds 116, abstützt. Auf diesem Ventilstückkörper 128 ist zunächst eine konische Dichtschulter 130 und, anschließend an die Dichtschulter 130, ein zylindrischer Ansatz 132 des Ventilstückkörpers 128 aufgenommen.The valve piece 122 furthermore has an at least partially cylindrically configured valve body 128, which is supported on the injector body 114 downwards, that is to say in a closing direction of the injection valve member 116. A conical sealing shoulder 130 and, subsequent to the sealing shoulder 130, a cylindrical projection 132 of the valve body 128 are first received on this valve body 128.

In dem Ventilstück 122 ist eine Ablaufdrossel 134 des Steuerraums 124 angeordnet. Diese Ablaufdrossel 134 umfasst, ausgehend vom Steuerraum 124, zunächst eine axiale Bohrung 136, gefolgt von in diesem Ausführungsbeispiel zwei schräg zur Injektorachse 112 verlaufenden Drosselbohrungen 138. Diese Drosselbohrungen 138 münden jeweils in Mündungen 140, welche in einer umfangsseitigen Einschnürung 142 des Ansatzes 132 vorgesehen sind. Oberhalb der Einschnürung 142 ist der Ansatz 132 wieder aufgeweitet und weist einen Führungsabschnitt 144 auf.In the valve piece 122, a discharge throttle 134 of the control chamber 124 is arranged. This outlet throttle 134, starting from the control chamber 124, initially comprises an axial bore 136, followed by two throttle bores 138 running obliquely to the injector axis 112 in this exemplary embodiment. These throttle bores 138 each open into openings 140 which are provided in a peripheral constriction 142 of the attachment 132 , Above the constriction 142, the projection 132 is widened again and has a guide section 144.

Über die Ablaufdrossel 134 lässt sich der Steuerraum 124 mit einem (in Figur 1 nicht dargestellten) Niederdruckablauf verbinden, so dass über ein Öffnen bzw. Verschließen der Ablaufdrossel 134 ein Druck in dem Steuerraum 124 und damit eine Stellung des Einspritzventilglieds 116 gesteuert werden kann.About the outlet throttle 134 can the control chamber 124 with a (in FIG. 1 not shown) connect low-pressure drain, so that a pressure in the control chamber 124 and thus a position of the injection valve member 116 can be controlled by opening or closing the drain throttle 134.

Zum Öffnen bzw. Verschließen der Mündung 140 der Ablaufdrossel 134 ist in dem Kraftstoffinjektor 110 ein hydraulisches Ventil 146 vorgesehen, welches als Magnetventil ausgestaltet ist. Das hydraulische Ventil 146 umfasst ein Magnetaktor 148 mit einer Magnetspule 150 und einem Magnetkern 152, welche axialsymmetrisch angeordnet sind.To open or close the mouth 140 of the outlet throttle 134, a hydraulic valve 146 is provided in the fuel injector 110, which is designed as a solenoid valve. The hydraulic valve 146 includes a magnetic actuator 148 having a solenoid 150 and a magnetic core 152 which are arranged axially symmetrically.

Weiterhin umfasst der Magnetaktor 148 einen Magnetanker 154. Der Magnetanker 154 wird mittels einer in einem zentralen Hohlraum 156 des Magnetkerns 152 gelagerten Ventilfeder 158 mit einer Kraft in Schließrichtung beaufschlagt. In Gegenrichtung wird der Magnetanker 154 über eine Ankerfeder 160, welche sich am Ventilstückkörper 128 abstützt, mit einer Kraft entgegen der Schließrichtung beaufschlagt.Magnetic actuator 154 further comprises a magnetic armature 154. Magnetic armature 154 is acted upon by a force in the closing direction by means of a valve spring 158 mounted in a central cavity 156 of magnetic core 152. In the opposite direction, the armature 154 is acted upon by an armature spring 160, which is supported on the valve body 128 with a force opposite to the closing direction.

Der Magnetanker 154 ist in dem dargestellten Ausführungsbeispiel zweiteilig ausgestaltet und umfasst eine Ankerplatte 162 und einen Ankerbolzen 164.The armature 154 is designed in two parts in the illustrated embodiment and includes an anchor plate 162 and an anchor bolt 164th

Die Ankerplatte 162 weist an ihrem dem Magnetkern 152 zuweisenden Ende einen Ankerteller 166 in Form einer axialsymmetrischen Kreisringscheibe auf. In Schließrichtung schließt sich an diesen Ankerteller 166 ein zylinderhülsenförmiger Führungsfortsatz 168 an. Die Ankerplatte 162 wirkt mit der Magnetspule 150 zusammen und kann dementsprechend aus einem für eine Magnetaktuation optimierten Material hergestellt werden.At its end facing the magnetic core 152, the armature plate 162 has an armature plate 166 in the form of an axially symmetrical annular disk. In the closing direction, a cylinder sleeve-shaped guide extension 168 adjoins this anchor plate 166. The armature plate 162 cooperates with the magnetic coil 150 and can accordingly be made of a material optimized for magnetic actuation.

Innerhalb des Führungsfortsatzes 168 ist in diesem Ausführungsbeispiel der Ankerbolzen 164 gleitend gelagert. Dieser Ankerbolzen 164 weist in dem dargestellten Ausführungsbeispiel eine Ankerhülse 170 auf. Diese Ankerhülse 170 umfasst einen zylindrischen Innenraum 172, in welchem der Führungsabschnitt 144 des Ansatzes 132 gleitend und abdichtend gelagert ist.Within the guide extension 168, the anchor bolt 164 is slidably mounted in this embodiment. This anchor bolt 164 has an anchor sleeve 170 in the illustrated embodiment. This anchor sleeve 170 comprises a cylindrical inner space 172, in which the guide portion 144 of the projection 132 is slidably and sealingly mounted.

An ihrem unteren Ende weist die Ankerhülse 170 eine Dichtkante 174 auf, welche in dem in Figur 1 dargestellten geschlossenen Zustand des hydraulischen Ventils 146 auf der Dichtschulter 130 des Ventilstücks 122 aufsitzt und einen Dichtsitz bildet. Auf diese Weise wird in dem in Figur 1 dargestellten geschlossenen Zustand durch die Ankerhülse 170 die Ablaufdrossel 134 verschlossen, so dass im Steuerraum 124 Hochdruck anliegt und das Einspritzventilglied 116 in seinen in Figur 1 nicht dargestellten Ventilsitz gepresst wird und die mindestens eine Einspritzöffnung verschließt.At its lower end, the anchor sleeve 170 has a sealing edge 174, which in the in FIG. 1 illustrated closed state of the hydraulic valve 146 is seated on the sealing shoulder 130 of the valve member 122 and forms a sealing seat. In this way, in the in FIG. 1 illustrated closed state by the anchor sleeve 170, the outlet throttle 134 is closed, so that in the control chamber 124 high pressure is applied and the injection valve member 116 in its in FIG. 1 Not shown valve seat is pressed and closes the at least one injection port.

Dabei ist das in Figur 1 gezeigte hydraulische Ventil 146 als druckausgeglichenes Ventil ausgestaltet, da auf das hydraulische Ventil 146, insbesondere den Ankerbolzen 164, in axialer Richtung keine hydraulischen Kräfte wirken können. Der Druck, welcher sich aus dem Steuerraum 124 über die Ablaufdrossel 134 in die Einschnürung 142 überträgt, kann lediglich in radialer Richtung auf die Innenwände der Ankerhülse 170 wirken.It is in FIG. 1 shown hydraulic valve 146 configured as a pressure-balanced valve, as can act on the hydraulic valve 146, in particular the anchor bolt 164, in the axial direction no hydraulic forces. The pressure, which is out the control chamber 124 transmits via the outlet throttle 134 in the constriction 142 can act only in the radial direction on the inner walls of the anchor sleeve 170.

An seinem oberen, dem Magnetkern 152 zuweisenden Ende weist der Ankerbolzen 164 eine Einstellscheibe 176 auf, welche in eine Umfangsnut der Ankerhülse 170 eingefügt ist. Diese Einstellscheibe 176 ist in dem dargestellten Ausführungsbeispiel beispielsweise als Sichelscheibe 178 ausgestaltet, wie beispielsweise aus einer Draufsicht auf den Magnetanker 154 in Figur 2 hervorgeht. Die Restluftspaltscheibe 184 ist in dieser Figur nicht dargestellt. Die Ankerhülse 170 weist an ihrem unteren Ende, wie in Figur 1 ersichtlich, eine Schulter 180 auf, welche die Bewegung der Ankerplatte 162 nach unten begrenzt und welche somit als Überhubanschlag 182 wirkt. Zur Montage des Magnetankers 154 kann die Ankerhülse 170 zunächst von unten in die den Führungsfortsatz 168 eingeschoben werden, woraufhin am oberen Ende die Sichelscheibe 178 in die Nut in der Ankerhülse 170 eingeschoben werden kann. Die Ventilfeder 158 ist dabei in dem dargestellten Ausführungsbeispiel auf der Sichelscheibe 178 abgestützt, kann jedoch alternativ auch auf anderen Teilen des Ankerbolzens 164, beispielsweise der Ankerhülse 170, abgestützt sein.At its upper, the magnetic core 152 facing end of the anchor bolt 164 has a shim 176 which is inserted into a circumferential groove of the anchor sleeve 170. This shim 176 is configured in the illustrated embodiment, for example, as a sickle plate 178, such as from a top view of the armature 154 in FIG. 2 evident. The residual air gap disk 184 is not shown in this figure. The anchor sleeve 170 has at its lower end, as in FIG. 1 can be seen, a shoulder 180, which limits the movement of the armature plate 162 down and which thus acts as an overstroke stop 182. For mounting the magnet armature 154, the armature sleeve 170 can first be inserted from below into the guide extension 168, whereupon the sickle disk 178 can be pushed into the groove in the armature sleeve 170 at the upper end. The valve spring 158 is supported in the illustrated embodiment on the sickle plate 178, but may alternatively be supported on other parts of the anchor bolt 164, for example, the anchor sleeve 170.

Die Ankerfeder 160 ist an ihrem oberen Ende auf dem Ankerteller 166 abgestützt. Auch eine andere Art der Abstützung ist jedoch möglich. Die gleitende Lagerung der Ankerhülse 170 in der Ankerplatte 162 ermöglicht eine Relativbewegung zwischen Ankerplatte 162 und dem Ankerbolzen 164, welche nach oben durch die Sichelscheibe 178 und nach unten durch die Schulter 180 begrenzt wird. Weiterhin kann auf der Oberseite des Ankertellers 166 noch eine Restluftspaltscheibe 184 in Form einer oder mehrerer Kreisringscheiben vorgesehen sein, welche einen Spalt zwischen dem Magnetkern 152 und dem Magnetanker 154 einstellen kann. Alternativ oder zusätzlich zu der Einstellung über die Restluftspaltscheibe 184 kann der Restluftspalt zwischen dem Magnetkern 152 und dem Magnetanker 154 auch als Luftspalt ausgestaltet sein. So kann beispielsweise ein Anschlag für den Ankerbolzen 164 bzw. die Ankerhülse 170 des Ankerbolzens 164 auch in anderer Form als durch die Verwendung einer Scheibe erfolgen.The armature spring 160 is supported at its upper end on the armature plate 166. However, another type of support is possible. The sliding support of the anchor sleeve 170 in the anchor plate 162 allows for relative movement between the anchor plate 162 and the anchor bolt 164, which is bounded upwardly by the sickle disc 178 and down through the shoulder 180. Furthermore, on the upper side of the anchor plate 166, a residual air gap disk 184 may be provided in the form of one or more annular disks, which may set a gap between the magnetic core 152 and the magnet armature 154. Alternatively or in addition to the adjustment via the residual air gap disk 184, the residual air gap between the magnetic core 152 and the magnet armature 154 may also be designed as an air gap. Thus, for example, a stop for the anchor bolt 164 or the anchor sleeve 170 of the anchor bolt 164 also take place in a different form than by the use of a disc.

Wird das hydraulische Ventil 146 betätigt, so liegt Magnetkraft an dem Magnetaktor 148 an. Die Ankerplatte 162 wird durch die Magnetspule 152 in Figur 1 nach oben angezogen. Die Sichelscheibe 178, welche formschlüssig mit dem Ankerbolzen 164 verbunden ist, wirkt als Mitnehmer und sorgt dafür, dass die Ankerhülse 170 von der Ankerplatte 162 mit nach oben gezogen wird. Auf diese Weise wird die Dichtkante 174 aus ihrem Sitz auf der Dichtschulter 130 gehoben, so dass Druck aus dem Steuerraum 124 über die Ablaufdrossel 134 in den Niederdruckablauf entweichen kann und sich das Einspritzventilglied 116 in Figur 1 nach oben bewegen kann, um die Einspritzöffnungen freizugeben. Um das Einspritzventilglied 116 und damit den Kraftstoffinjektor 110 erneut zu schließen, wird der Magnetaktor 148 abgeschaltet oder die Magnetkraft verringert, so dass, getrieben durch die Ventilfeder 158, der Ankerbolzen 164 wieder in seinen Sitz gepresst wird und sich im Steuerraum 124 erneut ein Hochdruck aufbauen kann. Das Einspritzventilglied 116 schließt dann wieder.When the hydraulic valve 146 is actuated, magnetic force is applied to the solenoid actuator 148. The armature plate 162 is rotated by the solenoid 152 in FIG FIG. 1 attracted to the top. The sickle plate 178, which is positively connected to the anchor bolt 164, acts as a driver and ensures that the anchor sleeve 170 is pulled by the anchor plate 162 with up. In this way, the sealing edge 174 is lifted from its seat on the sealing shoulder 130, so that pressure from the control chamber 124 can escape via the outlet throttle 134 in the low-pressure drain and the injection valve member 116 in FIG. 1 can move up to release the injection ports. To the injection valve member 116 and thus to close the fuel injector 110 again, the solenoid actuator 148 is turned off or the magnetic force is reduced, so that, driven by the valve spring 158, the anchor bolt 164 is pressed back into its seat and again in the control chamber 124 can build up a high pressure. The injection valve member 116 then closes again.

Die Restluftspaltscheibe 184 kann vorzugsweise unter der Sichelscheibe 178 eingeklemmter werden, so dass die Restluftspaltscheibe 184 durch die Sichelscheibe 178 in einer definierten Lage gehalten werden kann. Die Ankerplatte 162 wird zwischen den Einspritzungen mittels der Ankerfeder 160 in einer definierten Lage gehalten bzw. in eine derartige definierte Lage gebracht. Die Federkraft der Ankerfeder 160 soll dabei möglichst klein gewählt werden, vorzugsweise bei maximal 3 bis 4 Newton. Nachdem der Magnetaktor148 abgeschaltet bzw. in seiner Magnetkraft heruntergeschaltet ist, drückt die Ventilfeder 158 den Ankerbolzen 164, wie oben beschrieben, wieder in seinen Sitz. Sobald der Ankerbolzen 164 seinen Sitz erreicht hat, wird die Ankerplatte 162 aufgrund ihrer Trägheit sich weiter nach unten bewegen. Dieser Weg wird auch als Überhub bezeichnet und ist in Figur 1 mit a bezeichnet. Weitere Größen x (Dicke der Sichelscheibe 178), z (axiale Länge der Ankerplatte 162) und y (Abstand zwischen Oberkante der Sichelscheibe 178 und Unterseite der Ankerplatte 162) sind ebenfalls in Figur 1 definiert. Somit gilt, dass sich die Dicke x der Sichelscheibe 178 aus den Größen a, y und z zu x=a-y+z berechnet.The residual air gap disc 184 may preferably be clamped under the sickle disc 178 so that the residual air disc 184 may be held in a defined position by the sickle disc 178. The anchor plate 162 is held between the injections by means of the armature spring 160 in a defined position or brought into such a defined position. The spring force of the armature spring 160 should be chosen as small as possible, preferably at a maximum of 3 to 4 Newtons. After the solenoid actuator 148 is turned off or downshifted in its magnetic force, the valve spring 158 returns the anchor bolt 164 to its seat as described above. Once the anchor bolt 164 has reached its seat, the armature plate 162 will continue to move downwardly due to its inertia , This way is also referred to as overstroke and is in FIG. 1 denoted by a. Other sizes x (thickness of the sickle plate 178), z (axial length of the anchor plate 162) and y (distance between the upper edge of the sickle plate 178 and the underside of the anchor plate 162) are also in FIG. 1 Are defined. Thus, the thickness x of the sickle disk 178 is calculated from the quantities a, y and z as x = a-y + z.

Der Überhub a wird durch den Überhubanschlag 182 begrenzt, welcher in diesem Fall durch die Schulter 180 an der Oberseite eines Bundes 186 der Ankerhülse 170 ausgebildet ist. Der Überhub a soll vorzugsweise nicht größer als 10 µm sein. Sollten in Einzelfällen die Toleranzen der Einzelteile der für den Überhub a relevanten Maße größer sein als es die Überhubtoleranz erfordert, so besteht die Möglichkeit, den Überhub a über einen Einstellring (Maßgruppen) einzustellen. In diesem Fall müssen vor der Montage die mit y und z bezeichneten Maße in Figur 1 gemessen werden und dann eine entsprechende Einstellscheibe 176 (Maß x in Figur 1) ausgewählt werden.The overstroke a is limited by the overstroke stop 182, which in this case is formed by the shoulder 180 at the top of a collar 186 of the anchor sleeve 170. The excess stroke a should preferably not be greater than 10 microns. If, in individual cases, the tolerances of the individual parts of the dimensions relevant to the overstroke are greater than the overtravel tolerance requires, it is possible to set the overstroke a via an adjusting ring (measuring groups). In this case, the dimensions marked y and z in FIG. 1 are measured and then a corresponding dial 176 (dimension x in FIG. 1 ) to be selected.

In Figur 3 ist ein zweites Ausführungsbeispiel eines erfindungsgemäßen Kraftstoffinjektors 110 dargestellt. Der Aufbau und die Funktionsweise des Kraftstoffinjektors 110 entsprechen zunächst weitgehend dem Aufbau und der Funktionsweise des Ausführungsbeispiels gemäß Figur 1, so dass weitgehend auf die obige Beschreibung verwiesen werden kann. Wiederum umfasst der Kraftstoffinjektor 110 einen Injektorkörper 114, in welchem ein Einspritzventilglied 116 mit einem Ventilkolben 118 gelagert ist. Oberhalb des Ventilkolbens 118 ist in einem Ventilstück 122 wiederum ein Steuerraum 124 ausgebildet, welcher über eine Zulaufdrossel 126 mit Hochdruck beaufschlagbar ist. Über eine Ablaufdrossel 134 in dem Ventilstück 122 ist der Steuerraum 124 wiederum druckentlastbar, wobei die Ablaufdrossel 134 in dem in Figur 3 dargestellten Ausführungsbeispiel, im Gegensatz zum Ausführungsbeispiel gemäß Figur 1, lediglich eine axiale Bohrung 136 umfasst. Diese axiale Bohrung 136 mündet im Innenraum einer zylinderhülsenförmigen Führung 188 des Ventilstücks 122 und ist durch das hydraulische Ventil 146 verschließbar bzw. freigebbar.In FIG. 3 a second embodiment of a fuel injector 110 according to the invention is shown. The structure and operation of the fuel injector 110 initially correspond largely to the structure and operation of the embodiment according to FIG. 1 , so that reference can be made largely to the above description. In turn, the fuel injector 110 comprises an injector body 114, in which an injection valve member 116 is mounted with a valve piston 118. Above the valve piston 118, in turn, a control chamber 124 is formed in a valve piece 122, which can be acted upon by an inlet throttle 126 with high pressure. About an outlet throttle 134 in the valve member 122, the control chamber 124 is again pressure relieved, the Outflow throttle 134 in the in FIG. 3 illustrated embodiment, in contrast to the embodiment according to FIG. 1 , only an axial bore 136 includes. This axial bore 136 opens into the interior of a cylindrical sleeve-shaped guide 188 of the valve piece 122 and can be closed or released by the hydraulic valve 146.

Das hydraulische Ventil 146 ist grundsätzlich ähnlich zu dem in Figur 1 dargestellten hydraulischen Ventil 146 dargestellt. Dabei ist in der Darstellung gemäß Figur 3 der Magnetaktor 148 lediglich teilweise dargestellt, wobei lediglich ein Teil des Magnetkerns 152 abgebildet ist. Die Magnetspule 150, welche beispielsweise analog zu Figur 1 ausgestaltet sein kann, ist in Figur 1 nicht gezeigt.The hydraulic valve 146 is basically similar to that in FIG FIG. 1 shown hydraulic valve 146 shown. It is in the illustration according to FIG. 3 the magnetic actuator 148 is shown only partially, with only part of the magnetic core 152 being depicted. The magnetic coil 150, which, for example, analogous to FIG. 1 can be designed, is in FIG. 1 Not shown.

Wiederum umfasst der Magnetaktor 148 in dem Ausführungsbeispiel gemäß Figur 3 einen Magnetanker 154 mit einer Ankerplatte 162 und einem Ankerbolzen 164. Die Ankerplatte 162 ist wieder mit einem Ankerteller 166 und einem Führungsfortsatz 168 ausgestaltet. Der Führungsfortsatz 168 weist an seinem unteren Ende eine Verengung 190 auf, welche zylindrisch ausgestaltet ist und von ihrem Außendurchmesser her dem Innendurchmesser der Führung 188 entspricht. Der Führungsfortsatz 168 ist somit in der Führung 188 des Ventilstücks 122 geführt.Again, the magnetic actuator 148 in the embodiment of FIG FIG. 3 a magnet armature 154 with an anchor plate 162 and an anchor bolt 164. The anchor plate 162 is again configured with an anchor plate 166 and a guide extension 168. The guide extension 168 has at its lower end a constriction 190, which is cylindrical and corresponds to the inner diameter of the guide 188 from its outer diameter forth. The guide extension 168 is thus guided in the guide 188 of the valve piece 122.

Im zylindrischen Innenraum der Ankerplatte 162 ist der Ankerbolzen 164 abdichtend und in axialer Richtung bewegbar gelagert. Die Ankerhülse 170 ist wiederum rohrförmig ausgestaltet und weist an ihrem unteren Ende eine Sitzkante 192 auf, beispielsweise eine Beißkante, einen Flachsitz oder einen Kegelsitz, welche in dem in Figur 3 gezeigten geschlossenen Zustand auf einem Dichtsitz 194 im Inneren der Führung 188 des Ventilsitzes 122 aufsitzt und eine Mündung 140 der Ablaufdrossel 134 abdichtet.In the cylindrical interior of the anchor plate 162 of the anchor bolt 164 is sealingly mounted and movable in the axial direction. The anchor sleeve 170 is in turn designed tubular and has at its lower end a seat edge 192, for example, a biting edge, a flat seat or a conical seat, which in the in FIG. 3 shown closed state on a sealing seat 194 in the interior of the guide 188 of the valve seat 122 is seated and a mouth 140 of the outlet throttle 134 seals.

Im Inneren der rohrförmigen Ankerhülse 170 ist in dem in Figur 1 dargestellten Ausführungsbeispiel ein zylindrischer Druckstift 196 aufgenommen. Dieser zylindrische Druckstift stützt sich an seinem oberen Ende auf dem Magnetkern 152 oder einem anderen Teil des Magnetaktors 148 ab. Von seinem Außendurchmesser her entspricht der Druckstift 196 dem Innendurchmesser der rohrförmigen Ankerhülse 170, so dass die Ankerhülse 170 gleitend auf diesen Druckstift 196 gelagert ist, der Druckstift 196 jedoch eine druckdichte Abdichtung des Steuerraums 124 gewährleistet. Durch den hydraulischen Druck im Steuerraum 124, welcher sich durch die Ablaufdrossel 134 auf den Druckstift 196 überträgt, wird dieser Druckstift 196 nach oben gegen den Magnetkern 152 gedrückt.Inside the tubular anchor sleeve 170 is in the in FIG. 1 illustrated embodiment, a cylindrical pressure pin 196 added. This cylindrical pressure pin is supported at its upper end on the magnetic core 152 or another part of the magnetic actuator 148. From its outer diameter, the pressure pin 196 corresponds to the inner diameter of the tubular anchor sleeve 170, so that the anchor sleeve 170 is slidably mounted on this pressure pin 196, the pressure pin 196, however, ensures a pressure-tight seal of the control chamber 124. Due to the hydraulic pressure in the control chamber 124, which transmits through the outlet throttle 134 on the pressure pin 196, this pressure pin 196 is pressed up against the magnetic core 152.

Wiederum weist der Ankerbolzen 164 an seinem oberen, dem Steuerraum 124 abgewandten Ende einen Mitnehmer in Form eines Bundes auf. Dieser Bund kann beispielsweise wiederum als Einstellscheibe 176 oder als Sichelscheibe 178 ausgestaltet sein und kann beispielsweise wiederum kraftschlüssig mit der Ankerhülse 170 verbunden sein. Alternativ oder zusätzlich kann der Bund auch auf andere Weise ausgestaltet sein, beispielsweise als Bestandteil der Ankerhülse 170 selbst. Unter der Sichelscheibe 178 kann wiederum eine Restluftspaltscheibe 184 angeordnet sein.Again, the anchor bolt 164 at its upper, the control chamber 124 opposite end on a driver in the form of a federal government. For example, this covenant can turn be configured as a dial 176 or a sickle disc 178 and, for example, in turn, be positively connected to the anchor sleeve 170. Alternatively or additionally, the collar can also be configured in other ways, for example as part of the anchor sleeve 170 itself. Under the sickle plate 178, in turn, a residual air gap disc 184 can be arranged.

Die Funktionsweise des Kraftstoffinjektors 110 gemäß dem in Figur 3 dargestellten Ausführungsbeispiel entspricht weitgehend der Funktionsweise des Ausführungsbeispiels gemäß Figur 1. Wiederum handelt es sich bei dem eingesetzten hydraulischen Ventil 146 um ein druckausgeglichenes Ventil, da keine hydraulischen Kräfte in axialer Richtung auf den Magnetanker 154 wirken. Sobald der Magnetaktor 148 bestromt wird, wird die Ankerplatte 162 durch die Magnetspule 150 angezogen und nach oben bewegt. Durch den Bund in Form der Sichelscheibe 178 an dem Ankerbolzen 164 wird auch der Ankerbolzen 164 von der Ankerplatte 162 mit nach oben gezogen. Die Einklemmung der Restluftspaltscheibe 184 dient wiederum dazu, diese in einer definierten Position zu halten.The operation of the fuel injector 110 according to the in FIG. 3 illustrated embodiment largely corresponds to the operation of the embodiment according to FIG. 1 , Again, the hydraulic valve 146 used is a pressure compensated valve because no hydraulic forces are acting on the armature 154 in the axial direction. As soon as the magnetic actuator 148 is energized, the armature plate 162 is attracted by the magnetic coil 150 and moved upward. Due to the collar in the form of the sickle plate 178 on the anchor bolt 164 and the anchor bolt 164 is pulled by the anchor plate 162 with up. The entrapment of the residual air gap disc 184 again serves to hold it in a defined position.

Die Ankerplatte 162 wird bei der beschriebenen Aufwärtsbewegung durch die Führung 188 an dem Führungsfortsatz 168 geführt. Mittels der Ankerfeder 160 wird die Ankerplatte 162 in einer definierten Lage positioniert. Wiederum sollte die Federkraft der Ankerfeder 160 so klein wie möglich gewählt werden, beispielsweise wiederum bei maximal 3 bis 4 Newton. Durch diese Aufwärtsbewegung des Ankerbolzens 164 wird die Mündung 140 freigegeben und der Steuerraum 124 wird druckentlastet, so dass sich das Einspritzventilglied 116 nach oben bewegen kann und die mindestens eine Einspritzöffnung freigeben kann.The anchor plate 162 is guided in the described upward movement by the guide 188 on the guide extension 168. By means of the armature spring 160, the anchor plate 162 is positioned in a defined position. Again, the spring force of the armature spring 160 should be as small as possible, for example, again at a maximum of 3 to 4 Newtons. By this upward movement of the anchor bolt 164, the mouth 140 is released and the control chamber 124 is depressurized, so that the injection valve member 116 can move upwards and can release at least one injection port.

Zur Beendigung des Einspritzvorgangs kann der Magnetaktor 148 abgeschaltet oder in eine geringere Bestromung geschaltet werden. Dadurch drückt die Ventilfeder 158 den Ankerbolzen 164 wieder in seinen Sitz. Sobald der Ankerbolzen den Sitz erreicht hat, wird die Mündung 140 verschlossen, und der Steuerraum 124 wird wieder über die Zulaufdrossel 126 mit Hochdruck beaufschlagt, so dass sich das Einspritzventilglied 116 wieder nach unten bewegt und die mindestens eine Einspritzöffnung verschließt.To complete the injection process, the solenoid actuator 148 can be switched off or switched to a lower current. As a result, the valve spring 158 pushes the anchor bolt 164 back into its seat. Once the anchor bolt has reached the seat, the mouth 140 is closed, and the control chamber 124 is again acted upon by the inlet throttle 126 with high pressure, so that the injection valve member 116 back down moves and closes the at least one injection port.

Sobald der Ankerbolzen 164 seinen Sitz erreicht hat, wird wiederum die Ankerplatte 162 aufgrund ihrer Trägheit sich weiter nach unten bewegen, so dass wiederum ein Überhub a entsteht.Once the anchor bolt 164 has reached its seat, in turn, the armature plate 162 will continue to move down due to their inertia, so that in turn an overstroke a arises.

Dieser Überhub a wird durch einen Überhubanschlag 182 begrenzt. Dieser Überhubanschlag 182 ist in dem dargestellten Ausführungsbeispiel durch die Oberkante der Führung 188 ausgebildet. Optional kann jedoch zwischen der Führung 188 und einer Schulter 198 am Ende der Verengung 190 des Führungsfortsatzes 168 der Ankerplatte 162 ein auswechselbarer Überhubanschlag 182 in Form eines Einstellrings 200 vorgesehen sein, wie dies in Figur 3 angedeutet ist. Dieser Einstellring 200 kann insbesondere als auswechselbarer Einstellring ausgestaltet sein, so dass der Überhubanschlag 182 als auswechselbarerer Überhubanschlag 182 ausgestaltet sein kann. Auch andere Ausgestaltungen des Überhubanschlags 182 sind denkbar, beispielsweise indem die Schulter 180 nicht an dem Führungsfortsatz 168 der Ankerplatte 162 ausgebildet wird, sondern beispielsweise an der Führung 188. Auch andere Arten des Überhubsanschlags oder Kombinationen derartiger Überhubanschläge sind denkbar. Insgesamt sollte der Überhub a vorzugsweise wiederum nicht größer als 10 µm sein. Der minimale Überhub a wird durch den maximalen Verschleiß bzw. die dadurch entstehende Ankerhubdrift im Ventilsitz begrenzt. Typischerweise liegt der Verschleiß bzw. die Ankerhubdrift bei weniger als 4 µm, womit die Untergrenze des Überhubs a bei ca. 5 µm liegen kann.This overstroke a is limited by an overstroke stop 182. This overstroke stop 182 is formed by the upper edge of the guide 188 in the illustrated embodiment. Optionally, however, may be between the guide 188 and a shoulder 198 at the end the constriction 190 of the guide extension 168 of the anchor plate 162 a replaceable overstroke stop 182 may be provided in the form of an adjusting ring 200, as shown in FIG FIG. 3 is indicated. This adjusting ring 200 may in particular be configured as a replaceable adjusting ring, so that the overstroke stop 182 may be configured as a replaceable overstroke stop 182. Other embodiments of the overstroke stop 182 are conceivable, for example in that the shoulder 180 is not formed on the guide extension 168 of the anchor plate 162, but for example on the guide 188. Other types of overstroke stop or combinations of such overstroke stops are conceivable. Overall, the excess lift a should preferably again be no greater than 10 microns. The minimum overtravel a is limited by the maximum wear or the resulting anchor stroke drift in the valve seat. Typically, the wear or the Ankerhubdrift is less than 4 microns, so that the lower limit of the excess stroke a can be about 5 microns.

Für die bevorzugten Toleranzen kann wiederum auf das obige Ausführungsbeispiel gemäß Figur 1 beschrieben werden. Es sollten die Toleranzen der Einzelteile der für den Überhub a relevanten Maße im Einzelfall wiederum größer sein als erforderlich, so besteht wiederum die Möglichkeit, den Überhub a über einen zusätzlichen Einstellring, wie beispielsweise den Einstellring 182, 200, einzustellen. In diesem Fall müssten vor der Montage wiederum die in Figur 3 mit y und z bezeichneten Maße gemessen werden, so dass der Einstellring 200 mit dem Maß x entsprechend ausgewählt werden kann.For the preferred tolerances can turn to the above embodiment according to FIG. 1 to be discribed. The tolerances of the individual parts of the dimensions relevant to the overstroke a should in each case be greater than necessary in each case, so it is again possible to adjust the overstroke a via an additional adjusting ring, such as, for example, the adjusting ring 182, 200. In this case, before the assembly would have to turn into the FIG. 3 Measured with y and z dimensions are measured so that the adjustment ring 200 can be selected with the dimension x accordingly.

Claims (11)

  1. Fuel injector (110) for injecting fuel into the combustion chamber of an internal combustion engine, in particular for use in accumulator injection systems, comprising at least one injection valve member (116), which is movably mounted in an injector body (114) of the fuel injector (110), for closing off or opening up at least one injection opening, furthermore comprising at least one hydraulic valve (146), wherein the hydraulic valve (146) is designed to control a stroke of the injection valve member (116) by means of at least one control chamber (124), wherein the hydraulic valve (146) comprises a magnet actuator (148) with at least one magnet coil (150) and at least one magnet armature (154), wherein the magnet armature (154) comprises at least one armature plate (162), which interacts with the magnet actuator (148), and at least one armature pin (164), which is mounted so as to be movable relative to the armature plate (162) and which controls a pressure in the control chamber (124), characterized in that the armature pin (164) is designed as an armature sleeve (170), and in that the armature sleeve (170) is mounted slidingly in the axial direction on the armature plate (162).
  2. Fuel injector (110) according to Claim 1, wherein the armature pin (164) is loaded by means of a valve spring element (158) with a first force acting in a closing direction, wherein the armature plate (162) is loaded by means of an armature spring element (160) with a second force acting counter to the closing direction, wherein the second force is lower than the first force.
  3. Fuel injector (110) according to Claim 1, wherein a slidingly mounted pressure pin (196) is received in the armature sleeve (170) for the purpose of hydraulically sealing off the armature sleeve (170) on the side facing away from the control chamber (124).
  4. Fuel injector (110) according to Claim 1, furthermore comprising a valve piece (122), wherein the valve piece (122) comprises an outflow throttle (134) of the control chamber (124), wherein the valve piece (122) has a projection (132) which projects into the armature sleeve (170), in particular a projection (132) which is cylindrical at least in portions.
  5. Fuel injector (110) according to Claim 4, wherein a mouth (140) of the outflow throttle (134) is accommodated in the projection (132).
  6. Fuel injector (110) according to either of Claims 4 and 5, wherein the mouth (140) is accommodated in a circumferential constriction (142) of the projection (132).
  7. Fuel injector (110) according to one of Claims 4, 5 or 6, wherein the projection (132) comprises, on that side of the constriction (142) which is remote from the control chamber (124), a guide portion (144), wherein the outer diameter of the guide portion (144) is matched to the inner diameter of the armature sleeve (170).
  8. Fuel injector (110) according to Claim 1, wherein the armature pin (164) is at least partially surrounded, on a side remote from the control chamber (124), by an exchangeable adjusting disc (174), in particular a sickle-shaped disc (178), in order to permit adjustment of an overstroke of the hydraulic valve (146).
  9. Fuel injector (110) according to one of the preceding claims, wherein an overstroke stop (182), in particular an exchangeable overstroke stop (182), for limiting an overstroke of the hydraulic valve (146) is provided on that side of the armature plate (162) which is remote from the magnet actuator (148).
  10. Fuel injector (110) according to the preceding claim, wherein the armature plate (162) has, on its side remote from the magnet actuator (148), a guide extension (168), wherein the fuel injector (110) has a guide (188) for receiving the guide extension (168), wherein the at least one overstroke stop (182) is arranged between the guide (188) and the guide extension (168).
  11. Fuel injector (110) according to the preceding claim, wherein the guide (188) is formed as part of a valve piece (122), wherein the valve piece (122) comprises at least one outflow throttle (134) of the control chamber (124).
EP09769057A 2008-06-27 2009-04-27 Fuel injector with two-piece armature Active EP2307697B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE200810002717 DE102008002717A1 (en) 2008-06-27 2008-06-27 Fuel injector with two-part magnet armature
PCT/EP2009/055019 WO2009156208A1 (en) 2008-06-27 2009-04-27 Fuel injector with two-piece armature

Publications (2)

Publication Number Publication Date
EP2307697A1 EP2307697A1 (en) 2011-04-13
EP2307697B1 true EP2307697B1 (en) 2012-06-20

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EP (1) EP2307697B1 (en)
CN (1) CN102076950A (en)
DE (1) DE102008002717A1 (en)
RU (1) RU2517518C2 (en)
WO (1) WO2009156208A1 (en)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102010030393A1 (en) 2010-06-23 2011-12-29 Robert Bosch Gmbh Anchor element for magnet component of fuel injection valve of storage injection system to inject fuel into combustion chamber of internal combustion engine, has anchor plate comprising recesses that are limited by opposite edge surface
DE102014225323A1 (en) * 2014-12-09 2016-06-09 Robert Bosch Gmbh Shift or pressure control valve for a fuel injection system
DE102015213141A1 (en) * 2015-07-14 2017-01-19 Robert Bosch Gmbh Switching valve for a fuel injector and fuel injector
CN106050499B (en) * 2016-05-31 2017-05-24 清华大学 Electric control high-pressure oil sprayer with control valve with self-locking function
CN106014740B (en) * 2016-07-25 2018-12-11 成都威特电喷有限责任公司 Eliminate the control valve of valve rod axial force
DE102016219881B3 (en) 2016-10-12 2017-11-23 Continental Automotive Gmbh Operating a fuel injector with hydraulic stop
CN106837640B (en) * 2017-01-25 2019-04-26 中国第一汽车股份有限公司 The controllable common-rail injector of needle valve movement speed
KR20190134747A (en) * 2017-04-10 2019-12-04 스카이 포춘 스타 테크놀로지 리미티드 Fuel injector and fuel injection method

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Publication number Priority date Publication date Assignee Title
RU2029129C1 (en) * 1989-05-10 1995-02-20 Семенов Владимир Григорьевич Controlled nozzle for internal combustion engine
IT239878Y1 (en) * 1996-12-23 2001-03-13 Elasis Sistema Ricerca Fiat IMPROVEMENTS TO AN ELECTROMAGNETIC CONTROL DOSING VALVE FOR A FUEL INJECTOR.
RU2136949C1 (en) * 1998-02-16 1999-09-10 Коростышевский Исаак Матвеевич Electromagnetic fuel nozzle
DE19816315A1 (en) * 1998-04-11 1999-10-14 Bosch Gmbh Robert Fuel injector
DE102004050992A1 (en) * 2004-10-20 2006-04-27 Robert Bosch Gmbh Solenoid-operated fuel injector with hydraulic over-stroke stop
DE102006050042A1 (en) * 2006-10-24 2008-04-30 Robert Bosch Gmbh Injector, particularly common rail injector, for fuel injection in combustion chambers of internal-combustion engines, has actuator arranged in injector body, which is arranged to operate valve case of control valve
DE102006057935A1 (en) * 2006-12-08 2008-06-12 Robert Bosch Gmbh Fuel injection valve for internal combustion engines

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Publication number Publication date
RU2517518C2 (en) 2014-05-27
EP2307697A1 (en) 2011-04-13
RU2011102820A (en) 2012-08-10
WO2009156208A1 (en) 2009-12-30
CN102076950A (en) 2011-05-25
DE102008002717A1 (en) 2010-01-14

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