EP2156046B1 - Armature stroke adjustment for solenoid valve - Google Patents

Armature stroke adjustment for solenoid valve Download PDF

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Publication number
EP2156046B1
EP2156046B1 EP08750284A EP08750284A EP2156046B1 EP 2156046 B1 EP2156046 B1 EP 2156046B1 EP 08750284 A EP08750284 A EP 08750284A EP 08750284 A EP08750284 A EP 08750284A EP 2156046 B1 EP2156046 B1 EP 2156046B1
Authority
EP
European Patent Office
Prior art keywords
armature
fuel injector
guide sleeve
sealing seat
elevation
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Not-in-force
Application number
EP08750284A
Other languages
German (de)
French (fr)
Other versions
EP2156046A1 (en
Inventor
Holger Rapp
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
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Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP2156046A1 publication Critical patent/EP2156046A1/en
Application granted granted Critical
Publication of EP2156046B1 publication Critical patent/EP2156046B1/en
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • 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
    • F02M61/168—Assembling; Disassembling; Manufacturing; Adjusting
    • 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
    • F02M63/0003—Fuel-injection apparatus having a cyclically-operated valve for connecting a pressure source, e.g. constant pressure pump or accumulator, to an injection valve held closed mechanically, e.g. by springs, and automatically opened by fuel pressure
    • F02M63/0007—Fuel-injection apparatus having a cyclically-operated valve for connecting a pressure source, e.g. constant pressure pump or accumulator, to an injection valve held closed mechanically, e.g. by springs, and automatically opened by fuel pressure using electrically actuated valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/004—Sliding valves, e.g. spool valves, i.e. whereby the closing member has a sliding movement along a seat for opening and closing
    • F02M63/0042—Sliding valves, e.g. spool valves, i.e. whereby the closing member has a sliding movement along a seat for opening and closing combined with valve seats of the lift valve type
    • 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
    • F02M63/007—Details not provided for in, or of interest apart from, the apparatus of the groups F02M63/0014 - F02M63/0059
    • F02M63/0071—Details not provided for in, or of interest apart from, the apparatus of the groups F02M63/0014 - F02M63/0059 characterised by guiding or centering means in valves including the absence of any guiding means, e.g. "flying arrangements"
    • 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
    • F02M63/007—Details not provided for in, or of interest apart from, the apparatus of the groups F02M63/0014 - F02M63/0059
    • F02M63/0075—Stop members in valves, e.g. plates or disks limiting the movement of armature, valve or spring
    • 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
    • F02M63/007—Details not provided for in, or of interest apart from, the apparatus of the groups F02M63/0014 - F02M63/0059
    • F02M63/0077—Valve seat details
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/007—Details not provided for in, or of interest apart from, the apparatus of the groups F02M63/0014 - F02M63/0059
    • F02M63/0078—Valve member details, e.g. special shape, hollow or fuel passages in the valve member
    • F02M63/008—Hollow valve members, e.g. members internally guided
    • 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
    • F02M2200/80—Fuel injection apparatus manufacture, repair or assembly
    • F02M2200/8092—Fuel injection apparatus manufacture, repair or assembly adjusting or calibration
    • 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
    • F02M2200/90—Selection of particular materials
    • F02M2200/9053—Metals
    • F02M2200/9076—Non-ferrous metals
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0014—Valves characterised by the valve actuating means
    • F02M63/0015—Valves characterised by the valve actuating means electrical, e.g. using solenoid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/004—Sliding valves, e.g. spool valves, i.e. whereby the closing member has a sliding movement along a seat for opening and closing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/0043—Two-way valves

Definitions

  • Out DE 196 50 865 A1 or EP 890 730 A2 is a solenoid valve for controlling the fuel pressure in a control chamber of an injection valve, such as for common-rail injection systems, known. About the fuel pressure in the control chamber, a stroke movement of a valve piston is controlled, with which an injection port of the injection valve is opened or closed.
  • the solenoid valve comprises an electromagnet, a movable armature and a valve which is moved with the armature and acted upon by a valve closing spring in the closing direction, which cooperates with the valve seat of the solenoid valve and thus controls the fuel drain from a control chamber.
  • the hydraulic coupler comprises a coupler sleeve with an internal bore in which the valve piston is guided.
  • the diameter of the coupler sleeve is larger than the outer diameter of the needle-shaped injection valve member.
  • the coupler sleeve rests on a nozzle body at its lower end with a sealing edge formed on its end face and encloses a coupler volume.
  • the coupler sleeve is employed in the idle state with a small, applied via a coil spring force to an end face of the nozzle needle.
  • the coupler sleeve or the coupler is surrounded by fuel under system pressure.
  • system pressure is meant the fuel pressure level generated in a fuel injection system, such as via a high pressure pump, within a high pressure reservoir body (common rail).
  • the armature stroke is the free distance that the anchor between its position in the Quiescent state, usually defined by the contact of the armature and a valve piece on the sealing seat, as well as an anchor position on an upper stroke stop is available.
  • the armature stroke is thus affected by the distance between the sealing seat formed in the valve piece and an upper stroke stop.
  • the stroke stop for the armature is carried out in many cases as close to the sealing seat, so for example below the magnetically active armature region.
  • this has the consequence that the armature must have a collar on its shaft, and consequently the magnetically active region of the armature must be carried out in a separate part, which only after the assembly of the armature guide, which in this case contains the upper stroke stop, is joined with the shank part of the anchor. Joining can be done either detachable or non-detachable.
  • the upper stroke stop is to be arranged above the anchor guide.
  • Common here are the versions of a Hubanschlages on the magnetic core, so for example directly via an inserted between the armature and core residual air gap foil or on a sleeve which is supported on a discharge pipe arranged above the core.
  • results for the distance between the sealing seat in the valve piece and the upper stroke stop a considerably longer and therefore also much tolerance-sensitive tolerance chain.
  • the position of the sealing seat in the holding body of the fuel injector may shift by a few microns under the influence of the system pressure below the sealing seat, whereas the position of the upper lifting stop relative to the holding body remains unaffected by the system pressure.
  • the present invention has for its object to make the distance between a sealing seat and a stroke stop of a solenoid valve for actuating a fuel injector unaffected by system pressure, which is applied to the fuel injector.
  • a force-balanced valve which has a one- or multi-part armature
  • a guide sleeve on the one hand has a support portion on which the magnetic core of the solenoid valve rests, and on the other hand comprises a guide portion, within which an anchor plate with a is guided on this trained sleeve-shaped approach.
  • the upper stroke stop for the armature of the inventively proposed solenoid valve, in particular arranged in this armature assembly is formed on the magnetic core and can be realized for example via a stop which is formed by an inserted between the armature plate and magnetic core residual air gap disc.
  • the guide sleeve lies with its lower end face on the valve piece, on which the sealing seat is formed, while the magnetic core is supported on an upper, for example, annular support surface by the guide sleeve.
  • the axial distance between the sealing seat in the valve piece and the bearing surface of the guide sleeve on the valve piece can be denoted by y 1 , the height of the guide sleeve with y 2 .
  • y 1 the height of the guide sleeve with y 2 .
  • the magnet core in the assembled state of the fuel injector, is pressed by an elastically designed spring element against the support surface, which may be designed to be annular, for example, the guide sleeve.
  • the spring element is supported for example on the inside of a lid, with which the solenoid valve is closed in the head region of the fuel injector.
  • the discharge nozzle, which limits the cavity in which the elastic spring element is received, is fixed, for example by means of a magnetic clamping nut on the holding body of the fuel injector.
  • the guide sleeve can be made of a non-magnetic material, wherein for adjusting the armature stroke (AH) between the guide sleeve and the magnetic core or between the guide sleeve and the magnet piece a shim can be inserted, which in turn can be made of a non-magnetic material.
  • AH armature stroke
  • the upper stroke stop of the armature of the solenoid valve on the magnetic core via the interposition of a residual air circuit between the lower end face of the magnetic core and the upper plan side of the armature assembly represents only one possible embodiment.
  • the anchor can also fully or partially strike directly on the magnetic core of the solenoid valve and / or a residual air gap can be represented via a step introduced into the armature or via a coating of the armature or of its end face assigning the magnetic core or the magnetic core end face which assigns the armature plate.
  • the armature stroke can be adjusted by the fact that the guide sleeve is guided via a non-positive, preferably slightly elastic designed connection with the valve piece.
  • a non-positive, preferably slightly elastic designed connection with the valve piece for example, offers a dome-shaped elevation within the valve piece, in the center of which runs a discharge channel through which the amount discharged from the control chamber when the sealing seat is opened emerges.
  • the lateral boundary of this dome-shaped elevation may be formed for example in the form of a Morse taper, so that the guide sleeve which receives the armature of the inventively proposed solenoid valve can be added in the form of a press fit on Morse taper with slight expansion of its lower portion.
  • the armature stroke (AH) can be adjusted very simply by providing the guide sleeve and the armature-in this example with the return pulley-the pressing force for the guide sleeve is increased until the distance between the upper end face of the support section , That is, the annular support surface for the magnetic core and one of the front side of the residual air gap disc has reached a target value.
  • This setpoint results from the desired value of the armature stroke as well as a lead which takes into account the elastic deformation of the bushing during the joining process.
  • the guide sleeve can be screwed onto the valve piece and the armature stroke can be adjusted by varying the tightening torque of this screw connection.
  • FIG. 1 The representation according to FIG. 1 a solenoid valve according to the prior art can be seen.
  • a fuel injector 10 as shown in FIG. 1 includes a holding body 12 in which a solenoid valve 14 is received.
  • the solenoid valve 14 is enclosed by a sleeve 16 which is closed by a cover 18 which can be secured to the sleeve 16 with a nut or the like.
  • the solenoid valve 14 is shown in FIG FIG. 1 executed symmetrically to the axis 20.
  • the solenoid valve 14 comprises a magnetic core 22 which receives a closing spring 28. Furthermore, a magnetic coil 26 is embedded in the magnetic core 22 of the solenoid valve 14.
  • the armature plate 32 of the armature assembly 30 is acted upon by the closing spring 28 is opposite the lower end face of the magnetic core 22 is an anchor plate 32 of an armature assembly. From the illustration according to FIG. 1 is further removed that it is in the armature assembly 30 of the solenoid valve 14 as shown in FIG FIG. 1 is a multi-part formed anchor assembly 30, wherein the anchor plate 32 is slidably mounted on the anchor bolt 34.
  • the armature plate 32 which is guided on the lateral surface of the anchor bolt 34, is pretensioned via an armature spring 36, which is supported on an armature guide 38.
  • the armature guide 38 also has an armature lifting stop 40, against which a collar extending in the circumferential direction on the armature bolt 34 abuts.
  • a closing element 44 At the bottom of the collar on the anchor bolt 34 is a receptacle for a closing element 44, which in the illustration in accordance with FIG. 1 is formed spherical.
  • the ball-shaped closure member 44 closes a drain passage in a valve piece 46, in which a control chamber for actuating a in FIG. 1 not shown, preferably needle-shaped injection valve member is received.
  • FIG. 1 The representation according to FIG. 1 can also be seen that the armature guide 38 is fixed by means of a valve clamping screw 48 in the holding body 12 of the fuel injector 10.
  • a valve clamping screw 48 In the foot of the armature guide 38, within which the anchor bolt 34 is displaceably guided, there is at least one discharge bore 50, via which with open sealing seat 42 from the formed in the valve piece 46 control chamber fuel in the low pressure region, ie the return 24 in the head region of the fuel injector 10th flows in.
  • FIG. 2 shows a first embodiment of the present invention proposed solenoid valve.
  • the fuel injector 10 in the head region comprises the solenoid valve 14, which has the magnetic core 22 and the magnetic core 26 embedded in the magnetic coil 26, which cooperates with the armature assembly 30.
  • the armature assembly 30, in turn, includes the armature plate 32, whose face side 74 faces the lower end face of the magnetic core 22. This is traversed by a passage opening which receives the closing spring 28 which extends on a pin 20 symmetrical to the pressure pin 92. Above the pressure pin 92 is a discharge nozzle 66, via which discharged amount flows into the low-pressure region of the fuel injector 10.
  • FIG. 2 can be seen that the magnetic core 22 is biased on the one hand via an elastic biasing member 70, and on the other hand rests on an annular bearing surface 98 of a guide sleeve 60.
  • the guide sleeve 60 in turn comprises in addition to a direction indicated by reference numeral 62 support portion formed in a smaller diameter guide portion 64 within which a sleeve-shaped projection of the anchor plate 32 is received.
  • the support portion 62 of the guide sleeve 60 defines an armature space 78; a lying outside the outer periphery of the guide sleeve 60 space represents a Abgresraum 80.
  • the carrier sleeve 60 is received with its guide portion 64 for the sleeve-shaped projection of the anchor plate 32 at a survey 104 of the valve member 46.
  • the survey 104 according to this embodiment has a cylindrical outer surface on which the guide portion 64 of the guide sleeve 60 is fixed, for example by forming a press or shrink fit 100.
  • the guide portion 64 of the guide sleeve 60 rests with its lower end face on a flat surface 96 of the valve piece.
  • the elevation 104 of the valve piece 46 is traversed by a flow channel 84 in which an outlet throttle 88 is received. About the drain passage 84 with the discharge throttle 88 received therein is formed in the valve piece 46, in FIG. 2 but not shown control room pressure relieved.
  • FIG. 2 shows that the sleeve-shaped projection of the anchor plate 32, which is the valve member in this embodiment of the solenoid valve 14, a sealing seat 42, 86 of the solenoid valve 14 closes.
  • the designated by reference numeral 94 on the underside of the sleeve-shaped projection of the anchor plate 32 rests on a seat 90 at the top of the elevation 104 of the valve member 46 and closes the seat 42, 86. Due to the closed seat 42, 86 exits no discarded amount the drainage channel 84 from.
  • a residual air gap disk 76 is applied to the plan side 74 of the anchor plate 32, which is opposite to the lower end face of the magnetic core 22.
  • the guide sleeve 60 rests with its lower end face on the flat surface 96 of the valve member 46
  • the magnetic core 22 rests on the annularly configured bearing surface of the guide sleeve 60.
  • the axial distance between the sealing seat 42, 86 and the bearing point of the guide sleeve 60 on the flat surface 96 of the valve member 46 is denoted by y 1 .
  • the height of the guide sleeve 60 is dimensioned with the dimension y 2 .
  • the distance between the sealing seat 42, 86 and the armature, ie the anchor plate 32 and the upper end face of resting on the flat side 74 of the anchor plate 32 residual air gap disk 76 is denoted by x. Consequently, the armature stroke AH results from the difference between the distance y and the distance x.
  • the magnetic core 22 is pressed by the elastic spring element 70 against the end face, ie the annular support surface 98 of the guide sleeve 60.
  • the elastic spring element 70 in turn is supported on the drain neck 66.
  • the drain pipe 66 is in turn fixed to the holding body 12, for example via an in FIG. 2 not shown magnetic clamping nut.
  • valve piece 46 in the holding body 12 under the influence of the system pressure by a few microns up or down, so the magnetic core 22 is necessarily displaced axially by the same amount. It only changes the distance between the top End face of the magnetic core 22 and the lower end face of the downcomer 66. This affects the biasing force slightly, with which the elastic spring member 70, the magnetic core 22 of the guide sleeve 60 holds down. The measure y and thus the armature stroke AH remain constant.
  • the guide sleeve 60 may be made of a non-magnetic material, as well as a set for adjusting the armature stroke AH between the guide sleeve 60 and the magnetic core 22 and / or between the guide sleeve 60 and the valve member 46 shim also made of a non-magnetic material can be.
  • the game between the anchor bolt 34 and the central bore of the guide sleeve 60 can be chosen relatively large, so that no further Guide the anchor bolt 34 within the guide portion 64 of the guide sleeve 60 is done.
  • FIG. 2 Furthermore, it can be seen, there is a ring-shaped drainage gap 72 between the inside of the holding body 12 and the outer periphery of the magnetic core 22, via which the discharged into the discharge chamber 80 amount, for example, the discharge nozzle 66 can flow.
  • a ring-shaped drainage gap 72 between the inside of the holding body 12 and the outer periphery of the magnetic core 22, via which the discharged into the discharge chamber 80 amount, for example, the discharge nozzle 66 can flow.
  • annular run-off gap discrete drainage channels, it may be a drainage channel, it may be formed a plurality of drainage channels instead of the drainage channel 72 in ring form.
  • FIG. 2 shows that in this embodiment, the stop of the armature 32 takes place on the magnetic core 22 via the residual air gap disk 76.
  • the armature 32 may strike the full or partial area directly on the magnetic core 22 and / or there may be a residual air gap via an introduced into the anchor, ie the anchor plate 32 stage and / or a coating of the plan side 74 of the anchor plate 32 and / or this assigning end face of the magnetic core 22 are shown.
  • connection to the return line 24 can be represented by a bore in the discharge nozzle 66, as well as the return 24 can be attached elsewhere, if this proves favorable or necessary for the particular application.
  • FIG. 3 is a further embodiment of the valve proposed by the invention can be seen.
  • FIG. 3 shows that the armature 32, symmetrically formed to the axis 20, has a through hole into which the in FIG. 2 shown pressure pin 92 is recessed, so that a pressure and force balanced solenoid valve 14 is obtained.
  • On the plan side 74 of the anchor plate 32 is the already described residual air gap disc 76.
  • the upper end face of the residual air gap disc 76 has to this opposite - in FIG. 3 only indicated - end face of the magnetic core 22 to the armature hub 102 forming distance, as in FIG. 3 outlined.
  • the armature 32 is according to the embodiment in FIG. 3 enclosed by the guide sleeve 60.
  • the guide sleeve 60 includes the support portion 62 and the guide portion 64.
  • the guide sleeve 60 is fixed with press fit or shrink fit 100 on a configured as Morse taper 118 with respect to the outer surface elevation 104 of the valve member 46.
  • the armature stroke AH can be adjusted very simply by inserting the guide sleeve 60, the armature 32 and - in the example shown here - also the residual air gap disc 76 already inserted and now the pressing force acting on the guide sleeve 60 is increased until the distance between the upper end face of the guide sleeve 60 and the residual air gap disc 76 has reached its desired value.
  • This setpoint results from the desired value of the armature stroke AH and a lead, which takes into account the elastic deformation of the guide sleeve 60 during the joining process.
  • the pressing force during the joining process must be significantly higher than the biasing force which is applied via the biasing member 70, with which the magnetic core 22 in operation later against the in FIG. 3 illustrated annular support surface 98 is pressed at the upper end of the support portion 62.
  • FIG. 3 shows further that the sealing seat 42, 86 is formed between the seat surface 90 of the Morsekegel 118 survey 104 and the end face 94 of the sleeve-shaped projection of the anchor plate 32.
  • the sealing seat 42, 86 located laterally in the wall of the guide sleeve 60 in the support portion 64 at least one discharge bore 82, via which the amount diverted when opening the sealing seat 42, 86 in the discharge chamber 80 is passed.
  • FIG. 3 shows that the elevation 104 on its outer circumferential surface has a slightly conical contour 106 which defines the Morse taper 118. Its cone angle in turn causes the radial expansion 108 of the guide portion 64 in the lower region of the guide sleeve 60th
  • FIG. 4 shows a further embodiment of the invention proposed solution for a solenoid valve.
  • FIG. 4 shows that on the outer circumference of the elevation 104 of the valve member 46, a threaded portion is mounted, which forms a threaded connection 112 with an internal thread, which is formed below the guide portion 64 of the guide sleeve 60.
  • the guide sleeve 60 in whose guide portion 64 of the sleeve-shaped projection of the anchor plate 32 is guided, on the one hand via the screw 112 connected to the survey 104 on the valve piece 46 and on the other hand is supported via a support 116 with the interposition of an elastic region 114 on the flat surface 96 of Valve piece 46 from.
  • the guide sleeve 60 When in connection with FIG. 4 shown solution, the guide sleeve 60 is screwed onto the valve member 46 and secured by the screw 112 with this.
  • the armature stroke AH can be changed by varying the tightening torque of this screw 112.

Abstract

Fuel injector (10) having a holding body (12), into which a solenoid valve (14) is let which actuates an injection valve element of preferably needle-shaped configuration and has an armature assembly (30) which has an armature plate (32) and an armature stroke stop (40), and a sealing seat (42) is opened or closed by the armature assembly (30). A magnetic core (22) of the solenoid valve (14) is supported on a guide sleeve (60, 62, 64) which for its part is received on the valve element (46) such that it encloses a sealing seat (42, 86).

Description

Stand der TechnikState of the art

Aus DE 196 50 865 A1 oder EP 890 730 A2 ist ein Magnetventil zur Steuerung des Kraftstoffdruckes in einem Steuerraum eines Einspritzventiles, so zum Beispiel für Common-Rail-Einspritzsysteme, bekannt. Über den Kraftstoffdruck im Steuerraum wird eine Hubbewegung eines Ventilkolbens gesteuert, mit dem eine Einspritzöffnung des Einspritzventils geöffnet oder geschlossen wird. Das Magnetventil umfasst einen Elektromagneten, einen beweglichen Anker und ein mit dem Anker bewegtes und von einem Ventilschließfeder in Schließrichtung beaufschlagtes Ventil, das mit dem Ventilsitz des Magnetventiles zusammenwirkt und so den Kraftstoffabfluss aus einem Steuerraum steuert.Out DE 196 50 865 A1 or EP 890 730 A2 is a solenoid valve for controlling the fuel pressure in a control chamber of an injection valve, such as for common-rail injection systems, known. About the fuel pressure in the control chamber, a stroke movement of a valve piston is controlled, with which an injection port of the injection valve is opened or closed. The solenoid valve comprises an electromagnet, a movable armature and a valve which is moved with the armature and acted upon by a valve closing spring in the closing direction, which cooperates with the valve seat of the solenoid valve and thus controls the fuel drain from a control chamber.

Bei einem derzeit eingesetzten, leckagefrei ausgebildeten Kraftstoffinjektor, der mittels eines Magnetventiles betätigt wird, erfolgt die Kopplung zwischen einem Ventilkolben und einem nadelförmig ausgebildeten Einspritzventilglied über einen hydraulischen Koppler. Der hydraulische Koppler umfasst eine Kopplerhülse mit einer Innenbohrung, in welcher der Ventilkolben geführt ist. Der Durchmesser der Kopplerhülse ist größer als der Außendurchmesser des nadelförmig ausgebildeten Einspritzventilgliedes. Die Kopplerhülse liegt an ihrem unteren Ende mit einer an deren Stirnseite ausgebildeten Dichtkante auf einen Düsenkörper auf und schließt ein Kopplervolumen ein. Die Kopplerhülse wird im Ruhezustand mit einer geringen, über eine Spiralfeder aufgebrachten Kraft an eine Stirnfläche der Düsennadel angestellt. Die Kopplerhülse bzw. der Koppler ist von unter Systemdruck stehendem Kraftstoff umgeben. Unter Systemdruck ist das Kraftstoffdruckniveau zu verstehen, welches in einem Kraftstoffeinspritzsystem, so zum Beispiel über eine Hochdruckpumpe, innerhalb eines Hochdruckspeicherkörpers (Common-Rail) erzeugt wird.In a currently used, leak-free designed fuel injector, which is actuated by means of a solenoid valve, the coupling between a valve piston and a needle-shaped injection valve member via a hydraulic coupler. The hydraulic coupler comprises a coupler sleeve with an internal bore in which the valve piston is guided. The diameter of the coupler sleeve is larger than the outer diameter of the needle-shaped injection valve member. The coupler sleeve rests on a nozzle body at its lower end with a sealing edge formed on its end face and encloses a coupler volume. The coupler sleeve is employed in the idle state with a small, applied via a coil spring force to an end face of the nozzle needle. The coupler sleeve or the coupler is surrounded by fuel under system pressure. By system pressure is meant the fuel pressure level generated in a fuel injection system, such as via a high pressure pump, within a high pressure reservoir body (common rail).

Bei heute eingesetzten, mittels eines Elektromagneten betätigten Kraftstoffinjektoren kommt der genauen und robusten, d.h. reproduzierbaren Einstellung des Ankerhubes einer Ankerbaugruppe innerhalb des Magnetventiles eine entscheidende Bedeutung zu. Unter dem Ankerhub ist die freie Wegstrecke zu verstehen, die dem Anker zwischen seiner Position im Ruhezustand, üblicherweise definiert durch den Kontakt des Ankers und einem Ventilstück am Dichtsitz, sowie einer Ankerposition an einem oberen Hubanschlag zur Verfügung steht. Der Ankerhub wird folglich beeinflusst vom Abstand zwischen dem Dichtsitz, der im Ventilstück ausgebildet ist, und einem oberen Hubanschlag.Used today, actuated by an electromagnet fuel injectors of the exact and robust, ie reproducible adjustment of the armature stroke of an armature assembly within the solenoid valve is crucial. The armature stroke is the free distance that the anchor between its position in the Quiescent state, usually defined by the contact of the armature and a valve piece on the sealing seat, as well as an anchor position on an upper stroke stop is available. The armature stroke is thus affected by the distance between the sealing seat formed in the valve piece and an upper stroke stop.

Um eine möglichst genaue und robuste Einstellung dieses Ankerhubes zu ermöglichen, wird der Hubanschlag für den Anker in vielen Fällen möglichst nahe am Dichtsitz ausgeführt, so zum Beispiel unterhalb des magnetisch aktiven Ankerbereiches. Dies hat jedoch zur Folge, dass der Anker an seinem Schaft einen Bund aufweisen muss, und infolgedessen der magnetisch aktive Bereich des Ankers in einem separaten Teil ausgeführt werden muss, welches erst nach der Montage der Ankerführung, welche in diesem Fall den oberen Hubanschlag enthält, mit dem Schaftteil des Ankers gefügt wird. Das Fügen kann entweder lösbar oder auch unlösbar erfolgen.In order to enable the most accurate and robust adjustment of this armature stroke, the stroke stop for the armature is carried out in many cases as close to the sealing seat, so for example below the magnetically active armature region. However, this has the consequence that the armature must have a collar on its shaft, and consequently the magnetically active region of the armature must be carried out in a separate part, which only after the assembly of the armature guide, which in this case contains the upper stroke stop, is joined with the shank part of the anchor. Joining can be done either detachable or non-detachable.

Bei einteilig ausgebildeten Ankern, was aus Kosten- und Montagegründen in vielen Fällen erwünscht ist, ist der obere Hubanschlag oberhalb der Ankerführung anzuordnen. Gängig sind hier die Ausführungen eines Hubanschlages am Magnetkern, so zum Beispiel direkt über eine zwischen Anker und Kern eingelegte Restluftspaltfolie oder an einer Hülse, welche sich an einem oberhalb des Kerns angeordneten Ablaufstutzen abstützt. In diesem Falle ergibt sich für den Abstand zwischen dem Dichtsitz im Ventilstück und dem oberen Hubanschlag eine erheblich längere und daher auch wesentlich toleranzempfindlichere Toleranzkette. Insbesondere kann sich die Position des Dichtsitzes im Haltekörper des Kraftstoffinjektors unter dem Einfluss des unterhalb des Dichtsitzes anstehenden Systemdrucks um einige µm verschieben, während hingegen die Position des oberen Hubanschlages gegenüber dem Haltekörper vom Systemdruck unbeeinflusst bleibt. In der Folge ergibt sich eine Reduktion des Ankerhubes bei steigendem Systemdruck, was durch eine Erhöhung des Ankerhub-Einstellwerts im drucklosen Zustand kompensiert werden muss. Um diese Kompensation durch Erhöhung des Ankerhub-Einstellwerts zu erreichen, muss die Bewegung des Dichtsitzes im Haltekörper unter dem Einfluss des anstehenden Systemdrucks bekannt sein, was jedoch nicht immer der Fall ist.In one-piece anchors, which is desirable in many cases for cost and installation reasons, the upper stroke stop is to be arranged above the anchor guide. Common here are the versions of a Hubanschlages on the magnetic core, so for example directly via an inserted between the armature and core residual air gap foil or on a sleeve which is supported on a discharge pipe arranged above the core. In this case, results for the distance between the sealing seat in the valve piece and the upper stroke stop a considerably longer and therefore also much tolerance-sensitive tolerance chain. In particular, the position of the sealing seat in the holding body of the fuel injector may shift by a few microns under the influence of the system pressure below the sealing seat, whereas the position of the upper lifting stop relative to the holding body remains unaffected by the system pressure. As a result, there is a reduction of the armature stroke with increasing system pressure, which must be compensated by an increase in the armature stroke adjustment value in the unpressurized state. To achieve this compensation by increasing the armature stroke adjustment value, the movement of the sealing seat in the holding body must be known under the influence of the pending system pressure, which is not always the case.

Offenbarung der ErfindungDisclosure of the invention

Der vorliegenden Erfindung liegt die Aufgabe zugrunde, den Abstand zwischen einem Dichtsitz und einem Hubanschlag eines Magnetventiles zur Betätigung eines Kraftstoffinjektors unbeeinflusst von Systemdruck, mit dem der Kraftstoffinjektor beaufschlagt ist, zu gestalten.The present invention has for its object to make the distance between a sealing seat and a stroke stop of a solenoid valve for actuating a fuel injector unaffected by system pressure, which is applied to the fuel injector.

Es wird vorgeschlagen, insbesondere an einem kraftausgeglichenen Ventil, welches einen ein- oder mehrteiligen Anker aufweist, eine Führungshülse vorzusehen, die einerseits einen Trägerabschnitt aufweist, auf welchem der Magnetkern des Magnetventiles ruht, und welche andererseits einen Führungsabschnitt umfasst, innerhalb dessen eine Ankerplatte mit einem an dieser ausgebildeten hülsenförmigen Ansatz geführt ist. Der obere Hubanschlag für den Anker des erfindungsgemäß vorgeschlagenen Magnetventiles, insbesondere der in diesem angeordneten Ankerbaugruppe, ist am Magnetkern ausgebildet und kann zum Beispiel über einen Anschlag realisiert werden, der durch eine zwischen Ankerplatte und Magnetkern eingelegte Restluftspaltscheibe gebildet wird. Die Führungshülse liegt mit ihrer unteren Stirnfläche auf dem Ventilstück auf, an welchem der Dichtsitz ausgebildet ist, während der Magnetkern auf einer oberen, beispielsweise ringförmig verlaufenden Auflagefläche durch die Führungshülse abgestützt ist.It is proposed, in particular on a force-balanced valve, which has a one- or multi-part armature, to provide a guide sleeve, on the one hand has a support portion on which the magnetic core of the solenoid valve rests, and on the other hand comprises a guide portion, within which an anchor plate with a is guided on this trained sleeve-shaped approach. The upper stroke stop for the armature of the inventively proposed solenoid valve, in particular arranged in this armature assembly is formed on the magnetic core and can be realized for example via a stop which is formed by an inserted between the armature plate and magnetic core residual air gap disc. The guide sleeve lies with its lower end face on the valve piece, on which the sealing seat is formed, while the magnetic core is supported on an upper, for example, annular support surface by the guide sleeve.

Der axiale Abstand zwischen dem Dichtsitz im Ventilstück und der Auflagefläche der Führungshülse am Ventilstück lässt sich mit y1 bezeichnen, die Höhe der Führungshülse mit y2. Damit ergibt sich der Abstand zwischen dem Dichtsitz im Ventilstück und der unteren Stirnfläche des Magnetkernes zu y = y2 - y1. Der Abstand zwischen dem Dichtsitz am Anker und der oberen Stirnfläche der auf dem Anker aufgelegten Restluftspaltscheibe sei x, so dass sich folglich der Ankerhub AH aus der Differenz zwischen y und x ergibt. Demzufolge gehen nur die Maße y1, y2 sowie x in den Ankerhub (AH) ein.The axial distance between the sealing seat in the valve piece and the bearing surface of the guide sleeve on the valve piece can be denoted by y 1 , the height of the guide sleeve with y 2 . This results in the distance between the sealing seat in the valve piece and the lower end face of the magnetic core to y = y 2 - y. 1 Let the distance between the sealing seat on the armature and the upper end face of the residual air gap disk placed on the armature be x, so that consequently the armature stroke AH results from the difference between y and x. As a result, only the dimensions y 1 , y 2 and x enter the armature stroke (AH).

Dabei wird erfindungsgemäß im montierten Zustand des Kraftstoffinjektors, der Magnetkern durch ein elastisch ausgebildetes Federelement gegen die Auflagefläche, die beispielsweise ringförmig gestaltet sein kann, der Führungshülse gedrückt. Das Federelement stützt sich zum Beispiel an der Innenseite eines Deckels ab, mit welchem das Magnetventil im Kopfbereich des Kraftstoffinjektors verschlossen ist. Der Ablaufstutzen, welcher den Hohlraum, in dem das elastische Federelement aufgenommen ist, begrenzt, ist zum Beispiel mittels einer Magnetspannmutter am Haltekörper des Kraftstoffinjektors fixiert.According to the invention, in the assembled state of the fuel injector, the magnet core is pressed by an elastically designed spring element against the support surface, which may be designed to be annular, for example, the guide sleeve. The spring element is supported for example on the inside of a lid, with which the solenoid valve is closed in the head region of the fuel injector. The discharge nozzle, which limits the cavity in which the elastic spring element is received, is fixed, for example by means of a magnetic clamping nut on the holding body of the fuel injector.

Verschiebt sich nun das innerhalb des Haltekörpers angeordnete Ventilstück, an dem der Dichtsitz ausgebildet ist, unter dem Einfluss des Systemdrucks um einige µm, sei es nach oben oder sei es nach unten, so wird auch der Magnetkern des Magnetventils um dasselbe Maß in axiale Richtung verschoben. Bei dieser Verschiebung ändert sich lediglich der Abstand zwischen der oberen Stirnfläche des Magnetkerns und der unteren Stirnfläche des Ablaufstutzens. Dadurch ändert sich geringfügig die Vorspannkraft, mit der das Federelement den Magnetkern auf der Buchse niederhält. Das Maß y, d.h. die Differenz y2 abzüglich des Maßes y1 hingegen bleibt konstant.Shifts now arranged within the holding body valve piece on which the sealing seat is formed, under the influence of the system pressure by a few microns, be it up or down, so the magnetic core of the solenoid valve is shifted by the same amount in the axial direction , With this displacement, only the distance between the upper end face of the magnetic core and the lower end face of the downcomer changes. As a result, slightly changes the biasing force with which the spring element holds down the magnetic core on the socket. The measure y, ie the difference y 2 minus the measure y 1, on the other hand, remains constant.

Die Führungshülse kann aus einem nicht magnetischen Material hergestellt werden, wobei zur Einstellung des Ankerhubes (AH) zwischen der Führungshülse und dem Magnetkern oder zwischen der Führungshülse und dem Magnetstück eine Einstellscheibe eingelegt sein kann, die wiederum auch aus einem nicht magnetischen Material hergestellt werden kann.The guide sleeve can be made of a non-magnetic material, wherein for adjusting the armature stroke (AH) between the guide sleeve and the magnetic core or between the guide sleeve and the magnet piece a shim can be inserted, which in turn can be made of a non-magnetic material.

Bei Magnetventilen, bei denen eine Führung des Ankers in der Zentralbohrung der Führungshülse nicht erforderlich ist, da der Anker bereits anderweitig geführt ist, kann das Spiel zwischen dem Anker und der Zentralbohrung der Führungshülse sehr groß gewählt werden, so dass es keiner weiteren Führung innerhalb der Führungshülse bedarf.In solenoid valves in which a guide of the armature in the central bore of the guide sleeve is not required because the anchor is already performed elsewhere, the game between the anchor and the central bore of the guide sleeve can be made very large, so that there is no further guidance within the Guide sleeve required.

Der obere Hubanschlag des Ankers des Magnetventils am Magnetkern über die Zwischenschaltung einer Restluftschaltscheibe zwischen der unteren Stirnfläche des Magnetkerns und der oberen Planseite der Ankerbaugruppe, stellt lediglich eine mögliche Ausführungsvariante dar. Stattdessen kann der Anker auch voll- oder teilflächig direkt am Magnetkern des Magnetventils anschlagen und/oder es kann ein Restluftspalt über eine in den Anker eingebrachte Stufe oder über eine Beschichtung des Ankers bzw. von dessen dem Magnetkern zuweisender Stirnseite oder der Magnetkernstirnfläche, welche der Ankerplatte zuweist, dargestellt werden.The upper stroke stop of the armature of the solenoid valve on the magnetic core via the interposition of a residual air circuit between the lower end face of the magnetic core and the upper plan side of the armature assembly, represents only one possible embodiment. Instead, the anchor can also fully or partially strike directly on the magnetic core of the solenoid valve and / or a residual air gap can be represented via a step introduced into the armature or via a coating of the armature or of its end face assigning the magnetic core or the magnetic core end face which assigns the armature plate.

In fertigungstechnisch besonders einfacher Weise lässt sich der Ankerhub dadurch einstellen, dass die Führungshülse über eine kraftschlüssige, bevorzugt leicht elastisch ausgelegte Verbindung mit dem Ventilstück geführt ist. Dazu bietet sich beispielsweise eine domförmige Erhebung innerhalb des Ventilstückes an, in deren Zentrum ein Ablaufkanal verläuft, durch welchen die aus dem Steuerraum bei Öffnen des Dichtsitzes abgesteuerte Menge austritt. Die seitliche Begrenzung dieser domförmig ausgebildeten Erhebung kann beispielsweise in Form eines Morsekegels ausgebildet sein, so dass die Führungshülse, die den Anker des erfindungsgemäß vorgeschlagenen Magnetventils aufnimmt, in Form eines Presssitzes am Morsekegel unter leichter Aufweitung ihres unteren Abschnittes gefügt werden kann. Bei dieser Befestigungsmöglichkeit lässt sich der Ankerhub (AH) sehr einfach dadurch einstellen, dass beim Führen der Führungshülse und des Ankers -im hier dargelegten Beispiel mit Rücklaufscheibe ausgestattet - die Aufpresskraft für die Führungshülse solange erhöht wird, bis der Abstand zwischen der oberen Stirnfläche des Trägerabschnittes, d.h. die ringförmig verlaufende Auflagefläche für den Magnetkern und eine von der Stirnseite der Restluftspaltscheibe einen Sollwert erreicht hat. Dieser Sollwert ergibt sich aus dem Sollwert des Ankerhubes sowie einem Vorhalt, welche die elastische Verformung der Buchse während des Fügeprozesses berücksichtigt.In manufacturing technology particularly simple manner, the armature stroke can be adjusted by the fact that the guide sleeve is guided via a non-positive, preferably slightly elastic designed connection with the valve piece. For this purpose, for example, offers a dome-shaped elevation within the valve piece, in the center of which runs a discharge channel through which the amount discharged from the control chamber when the sealing seat is opened emerges. The lateral boundary of this dome-shaped elevation may be formed for example in the form of a Morse taper, so that the guide sleeve which receives the armature of the inventively proposed solenoid valve can be added in the form of a press fit on Morse taper with slight expansion of its lower portion. With this mounting option, the armature stroke (AH) can be adjusted very simply by providing the guide sleeve and the armature-in this example with the return pulley-the pressing force for the guide sleeve is increased until the distance between the upper end face of the support section , That is, the annular support surface for the magnetic core and one of the front side of the residual air gap disc has reached a target value. This setpoint results from the desired value of the armature stroke as well as a lead which takes into account the elastic deformation of the bushing during the joining process.

Alternativ kann die Führungshülse auf das Ventilstück aufgeschraubt sein und der Ankerhub durch Variation des Anzugdrehmomentes dieser Schraubverbindung eingestellt werden.Alternatively, the guide sleeve can be screwed onto the valve piece and the armature stroke can be adjusted by varying the tightening torque of this screw connection.

Bei der erfindungsgemäß vorgeschlagenen Ankerbaugruppe, unter Verwendung der Führungshülse für den Fall, dass eine Zentrierung des Ankeraußendurchmessers zum Dichtsitz im Ventilstück nicht erforderlich ist, kann auf die Zentrierung verzichtet werden. Erfolgt die Ableitung eines Absteuervolumens bei offenem Ventil aus dem Raum zwischen Dichtsitz und Führungshülse über eine oder mehrere radial in der Wand der Führungshülse ausgebildeten Absteuerbohrungen, oder nach unten über Anschlüsse am Ventilstückaußendurchmesser unterhalb des Dichtsitzes, so wird das Absteuervolumen nicht mehr - wie bei heutigen Ventilen üblich - in den inneren Ankerraum eingeleitet. Folglich unterbleibt in diesen Fällen auch die schlagartige Änderung des Volumenstromes durch den Luftspalt zwischen Anker und Magnetkern, der bei heutigen Magnetventilen zu Störkräften auf den Anker führt. Die erfindungsgemäß vorgeschlagene Lösung bietet eine erheblich verbesserte Robustheit des Magnetventils gegenüber dem zum Beispiel im Niederdruckbereich, d.h. im Rücklauf herrschenden Kraftstoffgegendruck und damit ein noch besseres reproduzierbares Öffnungs- und Schließverhalten der Ankerbaugruppe und damit des Magnetventils zur Betätigung eines Kraftstoffinjektors.In the inventively proposed anchor assembly, using the guide sleeve in the event that a centering of the Ankeraußendurchmessers to the sealing seat in the valve piece is not required, can be dispensed with the centering. If the discharge of a Absteuervolumens with open valve from the space between the sealing seat and guide sleeve over one or more radially formed in the wall of the guide sleeve Absteuerbohrungen, or down via connections on Ventilstückaußendurchmesser below the sealing seat, the Absteuervolumen is no longer - as in today's valves usual - introduced into the inner armature space. Consequently, in these cases, the abrupt change of the volume flow through the air gap between the armature and the magnetic core, which leads to disturbing forces on the armature in today's solenoid valves, is also omitted in these cases. The solution proposed according to the invention offers a considerably improved robustness of the solenoid valve compared to, for example, the low pressure range, i. in the return prevailing fuel back pressure and thus an even better reproducible opening and closing behavior of the armature assembly and thus the solenoid valve for actuating a fuel injector.

Kurze Beschreibung der ZeichnungenBrief description of the drawings

Nachstehend wird die Erfindung anhand der Zeichnung beschrieben:The invention will be described below with reference to the drawing:

Es zeigt:

Figur 1
ein Magnetventil gemäß des Standes der Technik mit sitznahem Ankerhubanschlag und zweiteilig ausgeführtem Anker,
Figur 2
eine erste Ausführungsform des erfindungsgemäß vorgeschlagenen Magnetventils mit Führungshülse,
Figur 3
eine weitere Ausführungsform der in Figur 2 dargestellten Ausführung des erfindungsgemäß vorgeschlagenen Magnetventils mit Führungshülse, die auf einen Morsekegel am Ventilstück aufgeschrumpft ist, und
Figur 4
eine weitere Ausführungsform der erfindungsgemäß vorgeschlagenen Führungshülse mit Fixierung mittels einer Schraubverbindung an einer domförmigen Erhebung des Ventilstückes im Sitzbereich.
It shows:
FIG. 1
a solenoid valve according to the prior art with seat close Ankerhubanschlag and two-piece executed anchor,
FIG. 2
A first embodiment of the inventively proposed solenoid valve with guide sleeve,
FIG. 3
another embodiment of in FIG. 2 illustrated embodiment of the present invention proposed solenoid valve with guide sleeve, which is shrunk onto a Morse taper on the valve piece, and
FIG. 4
a further embodiment of the present invention proposed guide sleeve with fixation by means of a screw connection to a dome-shaped elevation of the valve member in the seating area.

Ausführungsformen der ErfindungEmbodiments of the invention

Der Darstellung gemäß Figur 1 ist ein Magnetventil gemäß des Standes der Technik zu entnehmen.The representation according to FIG. 1 a solenoid valve according to the prior art can be seen.

Ein Kraftstoffinjektor 10 gemäß der Darstellung in Figur 1 umfasst einen Haltekörper 12, in dem ein Magnetventil 14 aufgenommen ist. Das Magnetventil 14 ist von einer Hülse 16 umschlossen, die durch einen Deckel 18 verschlossen ist, der mit einer Mutter oder dergleichen an der Hülse 16 befestigt werden kann. Das Magnetventil 14 ist gemäß der Darstellung in Figur 1 symmetrisch zur Achse 20 ausgeführt.A fuel injector 10 as shown in FIG FIG. 1 includes a holding body 12 in which a solenoid valve 14 is received. The solenoid valve 14 is enclosed by a sleeve 16 which is closed by a cover 18 which can be secured to the sleeve 16 with a nut or the like. The solenoid valve 14 is shown in FIG FIG. 1 executed symmetrically to the axis 20.

Das Magnetventil 14 umfasst einen Magnetkern 22, der eine Schließfeder 28 aufnimmt. Des Weiteren ist in den Magnetkern 22 des Magnetventils 14 eine Magnetspule 26 eingebettet. Der unteren Stirnseite des Magnetkerns 22 gegenüberliegend befindet sich eine Ankerplatte 32 einer Ankerbaugruppe 30. Die Ankerplatte 32 der Ankerbaugruppe 30 ist durch die Schließfeder 28 beaufschlagt. Aus der Darstellung gemäß Figur 1 ist weiter entnehmbar, dass es sich bei der Ankerbaugruppe 30 des Magnetventils 14 gemäß der Darstellung in Figur 1 um eine mehrteilig ausgebildete Ankerbaugruppe 30 handelt, bei der die Ankerplatte 32 verschiebbar am Ankerbolzen 34 gelagert ist. Figur 1 ist darüber hinaus entnehmbar, dass die an der Mantelfläche des Ankerbolzen 34 geführte Ankerplatte 32 über eine Ankerfeder 36 vorgespannt ist, die sich an einer Ankerführung 38 abstützt. Die Ankerführung 38 weist darüber hinaus einen Ankerhubanschlag 40 auf, an welcher ein in Umfangsrichtung sich am Ankerbolzen 34 erstreckender Bund anschlägt. An der Unterseite des Bundes am Ankerbolzen 34 befindet sich eine Aufnahme für ein Schließelement 44, welches in der Darstellung gemäß Figur 1 kugelförmig ausgebildet ist. Das kugelförmig ausgebildete Schließelement 44 verschließt einen Ablaufkanal in einem Ventilstück 46, in dem ein Steuerraum zur Betätigung eines in Figur 1 nicht dargestellten, bevorzugt nadelförmig ausgebildeten Einspritzventilgliedes aufgenommen ist. Der Darstellung gemäß Figur 1 lässt sich darüber hinaus entnehmen, dass die Ankerführung 38 mittels einer Ventilspannschraube 48 im Haltekörper 12 des Kraftstoffinjektors 10 befestigt ist. Im Fuße der Ankerführung 38, innerhalb der der Ankerbolzen 34 verschieblich geführt ist, befindet sich mindestens eine Abströmbohrung 50, über welche bei geöffnetem Dichtsitz 42 aus dem im Ventilstück 46 ausgebildeten Steuerraum austretender Kraftstoff in den Niederdruckbereich, d.h. dem Rücklauf 24 im Kopfbereich des Kraftstoffinjektors 10 zuströmt.The solenoid valve 14 comprises a magnetic core 22 which receives a closing spring 28. Furthermore, a magnetic coil 26 is embedded in the magnetic core 22 of the solenoid valve 14. The armature plate 32 of the armature assembly 30 is acted upon by the closing spring 28 is opposite the lower end face of the magnetic core 22 is an anchor plate 32 of an armature assembly. From the illustration according to FIG. 1 is further removed that it is in the armature assembly 30 of the solenoid valve 14 as shown in FIG FIG. 1 is a multi-part formed anchor assembly 30, wherein the anchor plate 32 is slidably mounted on the anchor bolt 34. FIG. 1 In addition, it can be seen that the armature plate 32, which is guided on the lateral surface of the anchor bolt 34, is pretensioned via an armature spring 36, which is supported on an armature guide 38. The armature guide 38 also has an armature lifting stop 40, against which a collar extending in the circumferential direction on the armature bolt 34 abuts. At the bottom of the collar on the anchor bolt 34 is a receptacle for a closing element 44, which in the illustration in accordance with FIG. 1 is formed spherical. The ball-shaped closure member 44 closes a drain passage in a valve piece 46, in which a control chamber for actuating a in FIG. 1 not shown, preferably needle-shaped injection valve member is received. The representation according to FIG. 1 can also be seen that the armature guide 38 is fixed by means of a valve clamping screw 48 in the holding body 12 of the fuel injector 10. In the foot of the armature guide 38, within which the anchor bolt 34 is displaceably guided, there is at least one discharge bore 50, via which with open sealing seat 42 from the formed in the valve piece 46 control chamber fuel in the low pressure region, ie the return 24 in the head region of the fuel injector 10th flows in.

Figur 2 zeigt eine erste Ausführungsform des erfindungsgemäß vorgeschlagenen Magnetventils. FIG. 2 shows a first embodiment of the present invention proposed solenoid valve.

Der Darstellung gemäß Figur 2 lässt sich entnehmen, dass der Kraftstoffinjektor 10 im Kopfbereich das Magnetventil 14 umfasst, welches den Magnetkern 22 sowie die in den Magnetkern 22 eingelassene Magnetspule 26 aufweist, welche mit der Ankerbaugruppe 30 zusammen wirkt. Die Ankerbaugruppe 30 wiederum umfasst die Ankerplatte 32, deren Planseite 74 der unteren Stirnseite des Magnetkerns 22 zugewandt ist. Dieser ist von einer Durchgangsöffnung durchzogen, welche die Schließfeder 28 aufnimmt, die an einem zur Achse 20 symmetrisch ausgebildeten Druckstift 92 verläuft. Oberhalb des Druckstiftes 92 befindet sich ein Ablaufstutzen 66, über welchen abgesteuerte Menge in den Niederdruckbereich des Kraftstoffinjektors 10 abströmt.The representation according to FIG. 2 It can be seen that the fuel injector 10 in the head region comprises the solenoid valve 14, which has the magnetic core 22 and the magnetic core 26 embedded in the magnetic coil 26, which cooperates with the armature assembly 30. The armature assembly 30, in turn, includes the armature plate 32, whose face side 74 faces the lower end face of the magnetic core 22. This is traversed by a passage opening which receives the closing spring 28 which extends on a pin 20 symmetrical to the pressure pin 92. Above the pressure pin 92 is a discharge nozzle 66, via which discharged amount flows into the low-pressure region of the fuel injector 10.

Darüber hinaus lässt sich Figur 2 entnehmen, dass der Magnetkern 22 einerseits über ein elastisches Vorspannelement 70 vorgespannt ist, und andererseits auf einer ringförmigen Auflagefläche 98 einer Führungshülse 60 aufliegt. Die Führungshülse 60 wiederum umfasst neben einem durch Bezugszeichen 62 angedeuteten Trägerabschnitt einen in geringerem Durchmesser ausgebildeten Führungsabschnitt 64, innerhalb dessen ein hülsenförmiger Ansatz der Ankerplatte 32 aufgenommen ist. Der Trägerabschnitt 62 der Führungshülse 60 begrenzt einen Ankerraum 78; ein außerhalb des Außenumfangs der Führungshülse 60 liegender Raum stellt einen Absteuerraum 80 dar.In addition, it can be FIG. 2 can be seen that the magnetic core 22 is biased on the one hand via an elastic biasing member 70, and on the other hand rests on an annular bearing surface 98 of a guide sleeve 60. The guide sleeve 60 in turn comprises in addition to a direction indicated by reference numeral 62 support portion formed in a smaller diameter guide portion 64 within which a sleeve-shaped projection of the anchor plate 32 is received. The support portion 62 of the guide sleeve 60 defines an armature space 78; a lying outside the outer periphery of the guide sleeve 60 space represents a Absteuerraum 80.

Die Trägerhülse 60 ist mit ihrem Führungsabschnitt 64 für den hülsenförmigen Ansatz der Ankerplatte 32 an einer Erhebung 104 des Ventilstücks 46 aufgenommen. Aus der Darstellung gemäß Figur 2 geht hervor, dass die Erhebung 104 gemäß dieser Ausführungsform eine zylindrische Mantelfläche aufweist, an der der Führungsabschnitt 64 der Führungshülse 60 beispielsweise durch Ausbildung eines Press- bzw. Schrumpfsitzes 100 fixiert ist. Der Führungsabschnitt 64 der Führungshülse 60 liegt mit seiner unteren Stirnfläche auf einer Planfläche 96 des Ventilstücks auf.The carrier sleeve 60 is received with its guide portion 64 for the sleeve-shaped projection of the anchor plate 32 at a survey 104 of the valve member 46. From the illustration according to FIG. 2 shows that the survey 104 according to this embodiment has a cylindrical outer surface on which the guide portion 64 of the guide sleeve 60 is fixed, for example by forming a press or shrink fit 100. The guide portion 64 of the guide sleeve 60 rests with its lower end face on a flat surface 96 of the valve piece.

Die Erhebung 104 des Ventilstücks 46 ist von einem Ablaufkanal 84 durchzogen, in dem eine Ablaufdrossel 88 aufgenommen ist. Über den Ablaufkanal 84 mit der darin aufgenommenen Ablaufdrossel 88 ist ein im Ventilstück 46 ausgebildeter, in Figur 2 jedoch nicht dargestellter Steuerraum druckentlastbar. Aus Figur 2 geht hervor, dass der hülsenförmige Ansatz der Ankerplatte 32, der in dieser Ausführungsform des Magnetventils 14 das Ventilglied darstellt, einen Dichtsitz 42, 86 des Magnetventils 14 verschließt. Die mit Bezugszeichen 94 bezeichnete Stirnfläche an der Unterseite des hülsenförmigen Ansatzes der Ankerplatte 32 liegt auf einer Sitzfläche 90 an der Oberseite der Erhebung 104 des Ventilstücks 46 an und verschließt den Sitz 42, 86. Aufgrund des verschlossenen Sitzes 42, 86 tritt keine abgesteuerte Menge aus dem Ablaufkanal 84 aus.The elevation 104 of the valve piece 46 is traversed by a flow channel 84 in which an outlet throttle 88 is received. About the drain passage 84 with the discharge throttle 88 received therein is formed in the valve piece 46, in FIG. 2 but not shown control room pressure relieved. Out FIG. 2 shows that the sleeve-shaped projection of the anchor plate 32, which is the valve member in this embodiment of the solenoid valve 14, a sealing seat 42, 86 of the solenoid valve 14 closes. The designated by reference numeral 94 on the underside of the sleeve-shaped projection of the anchor plate 32 rests on a seat 90 at the top of the elevation 104 of the valve member 46 and closes the seat 42, 86. Due to the closed seat 42, 86 exits no discarded amount the drainage channel 84 from.

Wird das Magnetventil 14 bei Bestromung der Magnetspule 26 geöffnet, strömt über den geöffneten Sitz 42, 86 abgesteuerte Menge über mindestens eine in der Wand des Führungsabschnittes 64 der Führungshülse 60 ausgebildete Abströmbohrung 82 in den Absteuerraum 80 ab. Die Ableitung eines beim Öffnen des Magnetventiles 14 abzusteuernden Volumens aus dem Raum zwischen dem Dichtsitz 42, 86 und der Führungshülse 60 über ein oder mehrere radiale Abströmbohrungen 82 oder alternativ auch Anschliffe am Außendurchmesser des Ventilstückes 46 unterhalb des Dichtsitzes 42, 86 vermeidet im Gegensatz zu heute eingesetzten Ventilen das Einleiten des Absteuervolumens in das Innere des Ankerraums 78. Folglich unterbleibt bei der in Figur 2 dargestellten Ausführungsform des der Erfindung zugrunde liegenden Gedankens, die schlagartige Änderung des Volumenstromes durch den Luftspalt zwischen dem Anker und dem Magnetkern 26, der bei heute eingesetzten Magnetventilen zu Störkräften führt, die auf die Ankerbaugruppe 30 wirken.When the solenoid valve 14 is opened when the solenoid coil 26 is energized, quantity discharged via the opened seat 42, 86 flows into the discharge chamber 80 via at least one outflow bore 82 formed in the wall of the guide section 64 of the guide sleeve 60. The derivation of a aufzusteuernden when opening the solenoid valve 14 volume from the space between the sealing seat 42, 86 and the guide sleeve 60 via one or more radial Abströmbohrungen 82 or alternatively polished on the outer diameter of the valve member 46 below the sealing seat 42, 86 avoids in contrast to today inserted valves, the introduction of the Absteuervolumens in the interior of the armature space 78. Consequently, omitted in the in FIG. 2 illustrated embodiment of the invention underlying idea, the sudden change of the flow through the air gap between the armature and the magnetic core 26, which leads to magnetic forces used today in the magnetic forces acting on the armature assembly 30.

Wie der Darstellung gemäß Figur 2 weiter entnommen werden kann, ist auf der Planseite 74 der Ankerplatte 32 eine Restluftspaltscheibe 76 aufgebracht, die der unteren Stirnseite des Magnetkernes 22 gegenüberliegt. Während die Führungshülse 60 mit ihrer unteren Stirnfläche auf der Planfläche 96 des Ventilstücks 46 aufliegt, liegt der Magnetkern 22 auf der ringförmig konfigurierten Auflagefläche der Führungshülse 60 auf. Der axiale Abstand zwischen dem Dichtsitz 42, 86 und der Auflagestelle der Führungshülse 60 auf der Planfläche 96 des Ventilstücks 46 ist mit y1 bezeichnet. Die Höhe der Führungshülse 60 ist mit dem Maß y2 bemaßt. Der Abstand zwischen dem Dichtsitz 42, 86 und der unteren Stirnseite des Magnetkerns 22 ergibt sich somit zu y = y2 - y1. Der Abstand zwischen dem Dichtsitz 42, 86 und dem Anker, d.h. der Ankerplatte 32 und der oberen Stirnfläche der auf der Planseite 74 der Ankerplatte 32 aufliegenden Restluftspaltscheibe 76, wird mit x bezeichnet. Demzufolge ergibt sich der Ankerhub AH aus der Differenz des Abstandes y und des Abstandes x.As shown in the illustration FIG. 2 can be further removed, a residual air gap disk 76 is applied to the plan side 74 of the anchor plate 32, which is opposite to the lower end face of the magnetic core 22. While the guide sleeve 60 rests with its lower end face on the flat surface 96 of the valve member 46, the magnetic core 22 rests on the annularly configured bearing surface of the guide sleeve 60. The axial distance between the sealing seat 42, 86 and the bearing point of the guide sleeve 60 on the flat surface 96 of the valve member 46 is denoted by y 1 . The height of the guide sleeve 60 is dimensioned with the dimension y 2 . The distance between the sealing seat 42, 86 and the lower end face of the magnetic core 22 thus results in y = y 2 -y 1 . The distance between the sealing seat 42, 86 and the armature, ie the anchor plate 32 and the upper end face of resting on the flat side 74 of the anchor plate 32 residual air gap disk 76 is denoted by x. Consequently, the armature stroke AH results from the difference between the distance y and the distance x.

Demzufolge gehen in den Ankerhub AH nur die Maße y1, y2 und x ein.Consequently, only the dimensions y 1 , y 2 and x enter into the armature stroke AH.

Im zusammengebauten Zustand des Kraftstoffinjektors wird der Magnetkern 22 durch das elastische Federelement 70 gegen die Stirnfläche, d.h. die ringförmig verlaufende Auflagefläche 98 der Führungshülse 60 gedrückt. Das elastische Federelement 70 wiederum stützt sich am Ablaufstutzen 66 ab. Der Ablaufstutzen 66 ist wiederum am Haltekörper 12 fixiert, beispielsweise über eine in Figur 2 nicht dargestellte Magnetspannmutter.In the assembled state of the fuel injector, the magnetic core 22 is pressed by the elastic spring element 70 against the end face, ie the annular support surface 98 of the guide sleeve 60. The elastic spring element 70 in turn is supported on the drain neck 66. The drain pipe 66 is in turn fixed to the holding body 12, for example via an in FIG. 2 not shown magnetic clamping nut.

Verschiebt sich nun Ventilstück 46 im Haltekörper 12 unter dem Einfluss des Systemdruckes um einige µm nach oben oder nach unten, so wird zwangsläufig der Magnetkern 22 um dasselbe Maß axial verschoben. Dabei ändert sich lediglich der Abstand zwischen der oberen Stirnfläche des Magnetkerns 22 und der unteren Stirnfläche des Ablaufstutzens 66. Dies beeinflusst die Vorspannkraft geringfügig, mit der das elastische Federelement 70 den Magnetkern 22 der Führungshülse 60 niederhält. Das Maß y und damit der Ankerhub AH bleiben dagegen konstant.Shifts now valve piece 46 in the holding body 12 under the influence of the system pressure by a few microns up or down, so the magnetic core 22 is necessarily displaced axially by the same amount. It only changes the distance between the top End face of the magnetic core 22 and the lower end face of the downcomer 66. This affects the biasing force slightly, with which the elastic spring member 70, the magnetic core 22 of the guide sleeve 60 holds down. The measure y and thus the armature stroke AH remain constant.

Die Führungshülse 60 kann aus einem nicht magnetischen Material gefertigt sein, ebenso wie eine zur Einstellung des Ankerhubs AH zwischen der Führungshülse 60 und dem Magnetkern 22 und/oder zwischen der Führungshülse 60 und dem Ventilstück 46 angeordnete Einstellscheibe, die ebenfalls aus einem nicht magnetischen Material gefertigt sein kann.The guide sleeve 60 may be made of a non-magnetic material, as well as a set for adjusting the armature stroke AH between the guide sleeve 60 and the magnetic core 22 and / or between the guide sleeve 60 and the valve member 46 shim also made of a non-magnetic material can be.

Bei Magnetventilen, bei denen eine Führung des Ankers 32 in der Zentralbohrung der Führungshülse 60 nicht erforderlich ist, da der Anker bereits anderweitig geführt ist, kann das Spiel zwischen dem Ankerbolzen 34 und der Zentralbohrung der Führungshülse 60 relativ groß gewählt werden, so dass keine weitere Führung des Ankerbolzens 34 innerhalb des Führungsabschnittes 64 der Führungshülse 60 erfolgt.For solenoid valves in which a guide of the armature 32 in the central bore of the guide sleeve 60 is not required, since the armature is already performed elsewhere, the game between the anchor bolt 34 and the central bore of the guide sleeve 60 can be chosen relatively large, so that no further Guide the anchor bolt 34 within the guide portion 64 of the guide sleeve 60 is done.

Wie sich der Darstellung gemäß Figur 2 des Weiteren entnehmen lässt, befindet sich ein ringförmig ausgebildeter Ablaufspalt 72 zwischen der Innenseite des Haltekörpers 12 und dem Außenumfang des Magnetkerns 22, über welche die in den Absteuerraum 80 abgesteuerte Menge zum Beispiel dem Ablaufstutzen 66 zuströmen kann. Alternativ zu dem in Figur 2 mit Bezugszeichen 72 bezeichneten ringförmigen Ablaufspalt, können auch diskrete Ablaufkanäle, seien es ein Ablaufkanal, seien es mehrere Ablaufkanäle anstelle des Ablaufkanals 72 in Ringform gebildet sein.As the representation according to FIG. 2 Furthermore, it can be seen, there is a ring-shaped drainage gap 72 between the inside of the holding body 12 and the outer periphery of the magnetic core 22, via which the discharged into the discharge chamber 80 amount, for example, the discharge nozzle 66 can flow. Alternatively to the in FIG. 2 denoted by reference numeral 72 annular run-off gap, discrete drainage channels, it may be a drainage channel, it may be formed a plurality of drainage channels instead of the drainage channel 72 in ring form.

Aus Figur 2 geht hervor, dass in dieser Ausführungsform der Anschlag des Ankers 32 am Magnetkern 22 über die Restluftspaltscheibe 76 erfolgt. Alternativ kann der Anker 32 auch voll- oder teilflächig direkt am Magnetkern 22 anschlagen und/oder es kann ein Restluftspalt über eine in den Anker, d.h. die Ankerplatte 32 eingebrachte Stufe und/oder über eine Beschichtung der Planseite 74 der Ankerplatte 32 und/oder der diesem zuweisenden Stirnfläche des Magnetkerns 22 dargestellt werden.Out FIG. 2 shows that in this embodiment, the stop of the armature 32 takes place on the magnetic core 22 via the residual air gap disk 76. Alternatively, the armature 32 may strike the full or partial area directly on the magnetic core 22 and / or there may be a residual air gap via an introduced into the anchor, ie the anchor plate 32 stage and / or a coating of the plan side 74 of the anchor plate 32 and / or this assigning end face of the magnetic core 22 are shown.

In der Darstellung gemäß Figur 2 befindet sich im Druckstift 92 im oberen Bereich eine schräg angesetzte Bohrung, welche den Abfluss von Absteuer- und/oder Leckagemenge aus dem Absteuerraum 80 nach oben hin ermöglicht, wo sich in der Ausführungsform gemäß Figur 2 der Rücklauf 24 innerhalb des Ablaufstutzens 66 befindet. Alternativ dazu kann die Verbindung zum Rücklauf 24 durch eine Bohrung im Ablaufstutzen 66 dargestellt werden, ebenso kann auch der Rücklauf 24 an anderer Stelle angebracht werden, wenn sich dies für den jeweiligen Anwendungsfall günstig oder notwendig erweist.In the illustration according to FIG. 2 located in the pressure pin 92 in the upper region an obliquely set hole, which allows the outflow of Absteuer- and / or leakage amount from the Absteuerraum 80 upwards, where in the embodiment according to FIG. 2 the return 24 is located within the drain port 66. Alternatively, the connection to the return line 24 can be represented by a bore in the discharge nozzle 66, as well as the return 24 can be attached elsewhere, if this proves favorable or necessary for the particular application.

Figur 3 ist eine weitere Ausführungsform des erfindungsgemäß vorgeschlagenen Ventils zu entnehmen. FIG. 3 is a further embodiment of the valve proposed by the invention can be seen.

Aus der Darstellung gemäß Figur 3 geht hervor, dass der Anker 32, symmetrisch ausgebildet zur Achse 20, eine Durchgangsbohrung aufweist, in welche der in Figur 2 dargestellte Druckstift 92 eingelassen ist, so dass ein druck- und kraftausgeglichenes Magnetventil 14 erhalten wird. Auf der Planseite 74 der Ankerplatte 32 befindet sich die bereits beschriebene Restluftspaltscheibe 76. Die obere Stirnseite der Restluftspaltscheibe 76 weist zu dieser gegenüberliegenden - in Figur 3 nur angedeuteten - Stirnfläche des Magnetkernes 22 den den Ankerhub 102 bildenden Abstand auf, wie in Figur 3 skizziert. Der Anker 32 ist gemäß der Ausführungsform in Figur 3 von der Führungshülse 60 umschlossen. Die Führungshülse 60 umfasst den Trägerabschnitt 62 sowie den Führungsabschnitt 64. Im unteren Ende des Führungsabschnittes 64 ist die Führungshülse 60 mit Presssitz bzw. Schrumpfsitz 100 an einer als Morsekegel 118 bezüglich der Außenfläche ausgestalteten Erhebung 104 des Ventilstücks 46 fixiert. Durch diese Befestigungsmöglichkeit der Führungshülse 60, welche mit einer Aufweitung 108 des Führungsabschnittes 64 der Führungshülse 60 am unteren Ende einhergeht, lässt sich in vorteilhafter Weise der Ankerhub AH leicht einstellen. Aufgrund der der Führungshülse 60 innewohnenden Elastizität kann der Ankerhub AH sehr einfach dadurch eingestellt werden, dass beim Fügen der Führungshülse 60 der Anker 32 und - im hier dargestellten Beispiel - auch die Restluftspaltscheibe 76 bereits eingelegt sind und nun die auf die Führungshülse 60 wirkende Aufpresskraft solange erhöht wird, bis der Abstand zwischen der oberen Stirnfläche der Führungshülse 60 und der Restluftspaltscheibe 76 seinen Sollwert erreicht hat. Dieser Sollwert ergibt sich aus dem Sollwert des Ankerhubes AH sowie einem Vorhalt, welcher die elastische Verformung der Führungshülse 60 während des Fügeprozesses berücksichtigt. Die Aufpresskraft beim Fügeprozess muss dabei deutlich höher sein als die Vorspannkraft, welche über das Vorspannelement 70 aufgebracht wird, mit welcher der Magnetkern 22 im Betrieb später gegen die in Figur 3 dargestellte ringförmig verlaufende Auflagefläche 98 am oberen Ende des Trägerabschnittes 62 gedrückt wird.From the illustration according to FIG. 3 shows that the armature 32, symmetrically formed to the axis 20, has a through hole into which the in FIG. 2 shown pressure pin 92 is recessed, so that a pressure and force balanced solenoid valve 14 is obtained. On the plan side 74 of the anchor plate 32 is the already described residual air gap disc 76. The upper end face of the residual air gap disc 76 has to this opposite - in FIG. 3 only indicated - end face of the magnetic core 22 to the armature hub 102 forming distance, as in FIG. 3 outlined. The armature 32 is according to the embodiment in FIG FIG. 3 enclosed by the guide sleeve 60. The guide sleeve 60 includes the support portion 62 and the guide portion 64. In the lower end of the guide portion 64, the guide sleeve 60 is fixed with press fit or shrink fit 100 on a configured as Morse taper 118 with respect to the outer surface elevation 104 of the valve member 46. By this possibility of attachment of the guide sleeve 60, which is accompanied by an expansion 108 of the guide portion 64 of the guide sleeve 60 at the lower end, the armature stroke AH can be adjusted easily in an advantageous manner. Due to the inherent elasticity of the guide sleeve 60, the armature stroke AH can be adjusted very simply by inserting the guide sleeve 60, the armature 32 and - in the example shown here - also the residual air gap disc 76 already inserted and now the pressing force acting on the guide sleeve 60 is increased until the distance between the upper end face of the guide sleeve 60 and the residual air gap disc 76 has reached its desired value. This setpoint results from the desired value of the armature stroke AH and a lead, which takes into account the elastic deformation of the guide sleeve 60 during the joining process. The pressing force during the joining process must be significantly higher than the biasing force which is applied via the biasing member 70, with which the magnetic core 22 in operation later against the in FIG. 3 illustrated annular support surface 98 is pressed at the upper end of the support portion 62.

Figur 3 zeigt des Weiteren, dass der Dichtsitz 42, 86 zwischen der Sitzfläche 90 der mit Morsekegel 118 ausgeführten Erhebung 104 sowie der Stirnfläche 94 des hülsenförmigen Ansatzes der Ankerplatte 32 gebildet ist. Um den Aufbau eines nennenswerten hydraulischen Druckes zwischen dem Dichtsitz 42, 86 und der Führungshülse 60 zu verhindern, befindet sich seitlich in der Wand der Führungshülse 60 im Trägerabschnitt 64 mindestens eine Abströmbohrung 82, über welche die abgesteuerte Menge bei Öffnen des Dichtsitzes 42, 86 in den Absteuerraum 80 geleitet wird. FIG. 3 shows further that the sealing seat 42, 86 is formed between the seat surface 90 of the Morsekegel 118 survey 104 and the end face 94 of the sleeve-shaped projection of the anchor plate 32. In order to prevent the build-up of a significant hydraulic pressure between the sealing seat 42, 86 and the guide sleeve 60, located laterally in the wall of the guide sleeve 60 in the support portion 64 at least one discharge bore 82, via which the amount diverted when opening the sealing seat 42, 86 in the discharge chamber 80 is passed.

Aus Figur 3 geht hervor, dass die Erhebung 104 an ihrer Außenmantelfläche eine leicht konische Kontur 106 aufweist, welche den Morsekegel 118 definiert. Dessen Kegelwinkel wiederum bewirkt die radiale Aufweitung 108 des Führungsabschnittes 64 im unteren Bereich der Führungshülse 60.Out FIG. 3 shows that the elevation 104 on its outer circumferential surface has a slightly conical contour 106 which defines the Morse taper 118. Its cone angle in turn causes the radial expansion 108 of the guide portion 64 in the lower region of the guide sleeve 60th

Figur 4 zeigt eine weitere Ausführungsform der erfindungsgemäß vorgeschlagenen Lösung für ein Magnetventil. FIG. 4 shows a further embodiment of the invention proposed solution for a solenoid valve.

Figur 4 zeigt, dass am Außenumfang der Erhebung 104 des Ventilstücks 46 ein Gewindeabschnitt angebracht ist, der mit einem Innengewinde, welches unterhalb des Führungsabschnittes 64 der Führungshülse 60 ausgebildet ist, eine Schraubverbindung 112 bildet. Die Führungshülse 60, in deren Führungsabschnitt 64 der hülsenförmige Ansatz der Ankerplatte 32 geführt ist, ist einerseits über die Schraubverbindung 112 mit der Erhebung 104 am Ventilstück 46 verbunden und stützt sich andererseits über eine Abstützung 116 unter Zwischenschaltung eines elastischen Bereiches 114 auf der Planfläche 96 des Ventilstücks 46 ab. Aus Figur 4, welche den Dichtsitz 42, 86 nur hälftig zeigt, geht des Weiteren hervor, dass der hülsenförmige Ansatz der Ankerplatte 32 mit seiner Stirnfläche 94 auf der Sitzfläche 90 am Dichtsitz 42, 86 aufliegt und den ebenfalls nur hälftig dargestellten Ablaufkanal 84 mit darin ausgebildeter Ablaufdrossel 88 verschließt, so dass keine Druckentlastung des Steuerraumes erfolgt. FIG. 4 shows that on the outer circumference of the elevation 104 of the valve member 46, a threaded portion is mounted, which forms a threaded connection 112 with an internal thread, which is formed below the guide portion 64 of the guide sleeve 60. The guide sleeve 60, in whose guide portion 64 of the sleeve-shaped projection of the anchor plate 32 is guided, on the one hand via the screw 112 connected to the survey 104 on the valve piece 46 and on the other hand is supported via a support 116 with the interposition of an elastic region 114 on the flat surface 96 of Valve piece 46 from. Out FIG. 4 which shows the sealing seat 42, 86 only in half, it is further apparent that the sleeve-shaped projection of the anchor plate 32 rests with its end face 94 on the seat surface 90 on the sealing seat 42, 86 and the likewise only halfway shown drainage channel 84 formed therein outlet throttle 88th closes, so that no pressure relief of the control room.

Bei der in Zusammenhang mit Figur 4 dargestellten Lösung ist die Führungshülse 60 auf das Ventilstück 46 aufgeschraubt und durch die Schraubverbindung 112 mit diesem befestigt. Der Ankerhub AH kann durch Variation des Anzugmomentes dieser Schraubverbindung 112 verändert werden.When in connection with FIG. 4 shown solution, the guide sleeve 60 is screwed onto the valve member 46 and secured by the screw 112 with this. The armature stroke AH can be changed by varying the tightening torque of this screw 112.

Claims (13)

  1. Fuel injector (10) having a holding body (12) into which is recessed a solenoid valve (14) which actuates a preferably needle-shaped injection valve member and which has an armature assembly (30) which has an armature plate (32) and an armature stroke stop (40), and a sealing seat (42) is opened or closed by the armature assembly (30), characterized in that a magnet core (22) of the solenoid valve (14) is preloaded at one side by means of an elastic preload element (70) and is supported at the other side on a guide sleeve (60, 62, 64) which receives a sleeve-shaped projection of the armature plate (32) and which itself is received on the valve piece (46) so as to surround a sealing seat (42, 86).
  2. Fuel injector (10) according to Claim 1, characterized in that the guide sleeve (60, 62, 64) is produced from a non-magnetic material and has a supporting portion (62) and a guide portion (64).
  3. Fuel injector (10) according to Claim 2, characterized in that the supporting portion (62) has an annularly running bearing surface (98) for the magnet core (22).
  4. Fuel injector (10) according to Claim 1, characterized in that the guide sleeve (60, 62, 64) is received in a non-positively locking manner (100, 112) on an elevation (104) on the valve piece (46).
  5. Fuel injector (10) according to Claim 4, characterized in that the guide sleeve (60) is received on the elevation (104) on the valve piece (46) with an interference or shrink fit (100).
  6. Fuel injector (10) according to Claim 1, characterized in that the guide sleeve (60, 62, 64) is received in a non-positively locking manner on an elevation (104) of the valve piece (46), on which elevation is formed a Morse taper (118) with a conicity (106).
  7. Fuel injector (10) according to Claim 4, characterized in that the guide sleeve (60, 62, 64) is fastened to the elevation (104) by means of a screw connection (112).
  8. Fuel injector (10) according to Claim 4, characterized in that the armature plate (32) has an end surface (94) which, in the region of the sealing seat (42, 86), forms the sealing seat (42, 86) with a seat surface (90) of the elevation (104).
  9. Fuel injector (10) according to Claim 8, characterized in that the guide portion (64) of the guide sleeve (60) radially surrounds the sealing seat (42, 86), and at least one outflow bore (82) is formed in the wall of the supporting portion (64), out of which outflow bore a spill quantity emerges into a spill chamber (80) when the sealing seat (42, 86) is open.
  10. Fuel injector (10) according to one or more of the preceding claims, characterized in that the spill quantity flows out of the spill chamber (80) via an outflow gap (72), along the magnet core (22) to an outflow pipe (66).
  11. Fuel injector (10) according to Claim 1, characterized in that the armature plate (32) has a through bore in which a pressure pin (92) is received.
  12. Fuel injector (10) according to Claim 11, characterized in that a continuous bore is arranged in the low-pressure-side region of the pressure pin (92), via which bore the spill quantity is conducted from the spill chamber (80) into the outflow pipe (66).
  13. Fuel injector (10) according to Claim 1, characterized in that an armature stroke (AH) of the armature plate (32) is defined by a height y2 of the guide sleeve (60), a spacing y1 between a planar surface (96) of the valve piece (46) and the seat surface (90) of the elevation (104), and the height of the armature plate (32) with sleeve-shaped projection together with a residual air gap disc (76).
EP08750284A 2007-06-01 2008-05-14 Armature stroke adjustment for solenoid valve Not-in-force EP2156046B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102007025614A DE102007025614A1 (en) 2007-06-01 2007-06-01 Armature stroke adjustment for solenoid valve
PCT/EP2008/055896 WO2008145514A1 (en) 2007-06-01 2008-05-14 Armature stroke adjustment for solenoid valve

Publications (2)

Publication Number Publication Date
EP2156046A1 EP2156046A1 (en) 2010-02-24
EP2156046B1 true EP2156046B1 (en) 2011-12-21

Family

ID=39720503

Family Applications (1)

Application Number Title Priority Date Filing Date
EP08750284A Not-in-force EP2156046B1 (en) 2007-06-01 2008-05-14 Armature stroke adjustment for solenoid valve

Country Status (5)

Country Link
EP (1) EP2156046B1 (en)
CN (1) CN101680406B (en)
AT (1) ATE538302T1 (en)
DE (1) DE102007025614A1 (en)
WO (1) WO2008145514A1 (en)

Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102007044355A1 (en) * 2007-06-21 2008-12-24 Robert Bosch Gmbh Control valve for a fuel injector and fuel injector
DE102007047152A1 (en) * 2007-10-02 2009-04-09 Robert Bosch Gmbh Injector with an annulus separate anchor space
DE102011078564A1 (en) * 2011-07-04 2013-01-10 Robert Bosch Gmbh Control valve for a fuel injector and fuel injector
CN104533679B (en) * 2014-12-30 2016-09-07 南岳电控（衡阳）工业技术股份有限公司 A kind of injector control valve and use the high pressure common rail fuel injection system of this injector control valve
DE102015224177A1 (en) * 2015-12-03 2017-06-08 Robert Bosch Gmbh Fuel injector with control valve
DE102016206180A1 (en) * 2016-04-13 2017-10-19 Robert Bosch Gmbh Valve, in particular suction valve, in a high-pressure pump of a fuel injection system
DE102016220912A1 (en) 2016-10-25 2018-04-26 Robert Bosch Gmbh Fuel injection valve
DE102016222871A1 (en) * 2016-11-21 2018-05-24 Robert Bosch Gmbh fuel injector
US20230003215A1 (en) * 2019-11-19 2023-01-05 Hitachi Astemo, Ltd. Electromagnetic valve mechanism and high-pressure fuel supply pump

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5082180A (en) * 1988-12-28 1992-01-21 Diesel Kiki Co., Ltd. Electromagnetic valve and unit fuel injector with electromagnetic valve
DE19650865A1 (en) * 1996-12-07 1998-06-10 Bosch Gmbh Robert magnetic valve
IT1293433B1 (en) * 1997-07-11 1999-03-01 Elasis Sistema Ricerca Fiat ADJUSTABLE DOSING VALVE FOR A FUEL INJECTOR FOR INTERNAL COMBUSTION ENGINES, AND RELEVANT ADJUSTMENT METHOD.
IT1296144B1 (en) * 1997-11-18 1999-06-09 Elasis Sistema Ricerca Fiat ADJUSTABLE DOSING VALVE FOR ONE FUEL INJECTOR FOR INTERNAL COMBUSTION ENGINES.
DE102006046898A1 (en) * 2006-10-04 2008-04-10 Robert Bosch Gmbh Throttle plate for solenoid valve
DE102006053128A1 (en) * 2006-11-10 2008-05-15 Robert Bosch Gmbh Injector for injecting fuel

Also Published As

Publication number Publication date
CN101680406B (en) 2012-08-08
EP2156046A1 (en) 2010-02-24
DE102007025614A1 (en) 2008-12-04
CN101680406A (en) 2010-03-24
WO2008145514A1 (en) 2008-12-04
ATE538302T1 (en) 2012-01-15

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