EP2409308B1 - Residual air split disc - Google Patents

Residual air split disc Download PDF

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Publication number
EP2409308B1
EP2409308B1 EP10703242.7A EP10703242A EP2409308B1 EP 2409308 B1 EP2409308 B1 EP 2409308B1 EP 10703242 A EP10703242 A EP 10703242A EP 2409308 B1 EP2409308 B1 EP 2409308B1
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EP
European Patent Office
Prior art keywords
residual air
magnet
air gap
air split
split disc
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.)
Active
Application number
EP10703242.7A
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German (de)
French (fr)
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EP2409308A1 (en
Inventor
Andreas Rettich
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication of EP2409308A1 publication Critical patent/EP2409308A1/en
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Classifications

    • H—ELECTRICITY
    • H01—ELECTRIC ELEMENTS
    • H01F—MAGNETS; INDUCTANCES; TRANSFORMERS; SELECTION OF MATERIALS FOR THEIR MAGNETIC PROPERTIES
    • H01F7/00—Magnets
    • H01F7/06—Electromagnets; Actuators including electromagnets
    • H01F7/08—Electromagnets; Actuators including electromagnets with armatures
    • H01F7/081—Magnetic constructions
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M47/00—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
    • F02M47/02—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure of accumulator-injector type, i.e. having fuel pressure of accumulator tending to open, and fuel pressure in other chamber tending to close, injection valves and having means for periodically releasing that closing pressure
    • F02M47/027—Electrically actuated valves draining the chamber to release the closing pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0014—Valves characterised by the valve actuating means
    • F02M63/0015—Valves characterised by the valve actuating means electrical, e.g. using solenoid
    • F02M63/0017—Valves characterised by the valve actuating means electrical, e.g. using solenoid using electromagnetic operating means
    • F02M63/0021—Valves characterised by the valve actuating means electrical, e.g. using solenoid using electromagnetic operating means characterised by the arrangement of mobile armatures
    • 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
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/07—Fuel-injection apparatus having means for avoiding sticking of valve or armature, e.g. preventing hydraulic or magnetic sticking of parts
    • 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
    • F02M2200/9069—Non-magnetic metals
    • H—ELECTRICITY
    • H01—ELECTRIC ELEMENTS
    • H01F—MAGNETS; INDUCTANCES; TRANSFORMERS; SELECTION OF MATERIALS FOR THEIR MAGNETIC PROPERTIES
    • H01F7/00—Magnets
    • H01F7/06—Electromagnets; Actuators including electromagnets
    • H01F7/08—Electromagnets; Actuators including electromagnets with armatures
    • H01F7/16—Rectilinearly-movable armatures
    • H01F2007/1661—Electromagnets or actuators with anti-stick disc
    • H—ELECTRICITY
    • H01—ELECTRIC ELEMENTS
    • H01F—MAGNETS; INDUCTANCES; TRANSFORMERS; SELECTION OF MATERIALS FOR THEIR MAGNETIC PROPERTIES
    • H01F7/00—Magnets
    • H01F7/06—Electromagnets; Actuators including electromagnets
    • H01F7/08—Electromagnets; Actuators including electromagnets with armatures
    • H01F7/088—Electromagnets; Actuators including electromagnets with armatures provided with means for absorbing shocks

Definitions

  • DE 196 50 865 A1 describes a solenoid valve for controlling the fuel pressure in a control chamber of an injection valve, such as a common rail high-pressure accumulator injection system. About the fuel pressure in the control chamber, a lifting movement of a valve piston is controlled, with which an injection port of the injection valve can be opened or closed.
  • the solenoid valve comprises an electromagnet, a movable armature and a valve member moved with the armature and acted upon by a valve closing spring in the closing direction, which valve member cooperates with the valve seat of the solenoid valve and thus controls the fuel drain from the control chamber.
  • the armature of the solenoid valve is designed as a two-part armature, so as to reduce the moving mass of the armature / valve member assembly and thus the bouncing kinetic energy.
  • the two-piece armature includes an anchor bolt and an armature plate slidably received on the armature bolt against the force of a return spring in the closing direction of the valve member under the action of its inertial mass. This is secured by means of a locking washer and a surrounding locking sleeve on the anchor bolt.
  • Additional damping devices are used, including one moving with the anchor plate and one fixed part.
  • the armature plate movable portion includes a fixed portion facing shoulder for damping the ringing of the armature plate upon dynamic displacement to effect the same.
  • the other part of the damping device is formed on a stationary part of the solenoid valve as an overstroke. This limits the maximum path length by which the anchor plate can move on the anchor bolt in the axial direction.
  • the overstroke stop may be formed by an end face of a bolt which guides the anchor bolt, is fixedly arranged in the solenoid valve, or by a part which is disposed in front of the slider, for example a disk.
  • the residual air gap is adjusted by means of a residual air gap disc made of non-magnetic metal foil.
  • the residual air gap disc made of non-magnetic metal foil is placed on the magnet armature during assembly of the armature assembly and held down by a spring plate with the solenoid valve spring. This ensures that the thin metal foil, which represents the residual air gap disc, always assumes a defined position or follows the movement of the armature.
  • a compromise must always be made between the strength or stability and the hydraulic requirements. Since the residual air gap disk is fixed in the center of the armature, a connection to the magnetic inner pole is to be established, which extends over the spring space.
  • Magnet assemblies according to the preamble of claim 1 are made US5238224A1 and US5918818A1 known.
  • the present invention has for its object to provide a residual air gap disc that can be used on solenoid valves, without the outflow of the return amount is hindered.
  • the geometry of e.g. made of non-magnetic metal foil manufacturable residual air gap significantly simplified.
  • This is according to the invention no longer, as in previous embodiments, fixed on the spring plate on the anchor. This results in a simplification of the assembly process.
  • the inventively proposed residual air gap disc no longer covers, not even partially, the spring chamber and thus does not hinder the flow of the tax or the leakage amount in the direction of the low-pressure side return.
  • the cross section of the return geometry in the armature and in the magnet is independent of the position of the residual air gap disk.
  • the inventively proposed residual air gap disc is designed as a simple disc with a slit, which serves to avoid deformation executed.
  • a plurality of radial slots may be formed with a slot length which is smaller than the width of the annular-shaped residual air gap disc.
  • the inventively proposed residual air gap disc is inserted between the magnetic core and the magnet sleeve and fixed by the magnetic core.
  • the inner diameter of the inventively proposed residual air gap disc is chosen to be as large as possible, so that the inner pole of the magnetic coil, which is embedded in the magnetic core, is not covered, whereas the outer pole of the magnetic core is covered by the annular-shaped residual air gap disc.
  • the inventively proposed residual air gap disk can be very easily inserted in the assembly of the armature assembly between the magnetic core and an annular extending grip on the underside of the magnet sleeve and fixed very easy and captive during assembly.
  • the representation according to FIG. 1 is to take a schematic representation of a magnetic group of a fuel injector.
  • a magnet assembly 10 which facilitates the actuation of a fuel injector, e.g. A fuel injector for a high-pressure accumulator injection system (common rail) is inserted in an injector body 12 of the fuel injector.
  • the magnet assembly 10 is located opposite an armature 14, the plan side 16 is acted upon by a solenoid valve spring 18.
  • an adjustment ring is designated, which serves to adjust the solenoid valve.
  • the adjusting ring 20 rests in the injector body 12 and at the same time serves as a support for a magnetic sleeve 32.
  • the magnetic sleeve 32 serves to receive a magnetic core 22.
  • the magnetic core 22 in turn encloses a magnetic coil 24.
  • the magnetic core 22 is on a front side 26, that of the plan side 16 the armature 14 is opposite, open and divided by the position of the coil 24 in an inner pole 28 and an outer pole 30.
  • FIG. 1 shows that the magnetic sleeve 32 encloses the magnetic core 22 with its inner side 36.
  • the magnet sleeve 32 is with one in FIG. 1 Not shown clamping nut attached to the injector body 12 of the fuel injector.
  • the magnetic core 22 is fixed within the magnet assembly, for example via a flange or a welded joint.
  • the magnetic core 22 of the magnet group 10 comprises a passage opening in which on the one hand the solenoid valve spring 18, which acts on the armature 14 on the plan side 16, is arranged, and on the other hand serves as return 40, via the controlled upon actuation of the solenoid valve from a control chamber of the fuel injector Control amount or leakage in the low-pressure side return of a fuel injection system, for example, flows back.
  • FIG. 1 shows that a residual air gap disk 44 is clamped at a clamping point 42 between the end face 26 of the magnetic core 22 and the upper side of the overlap 34 of the magnet sleeve 32.
  • a residual air gap disk 44 is clamped at a clamping point 42 between the end face 26 of the magnetic core 22 and the upper side of the overlap 34 of the magnet sleeve 32.
  • the residual air gap disk 44 is no longer on the plan side 16 of the armature 14, for example. attached by a spring plate or the like, but assigned in departure from the previous practice of the end face 26 of the magnetic core 22 of the magnet assembly 10.
  • FIG. 1 shows that in an embodiment of the residual air gap disc 44 in the form of a circular ring, see illustration according to the Figures 2 and 3 , the inner pole 28 of the magnetic core 22 remains free, while the outer pole 30 of the magnetic core 22 is covered by the residual air gap disc 44.
  • the residual air gap disc 44 no longer obscures, not even partially, the spring space, ie the passage opening in the low-pressure side return 40 and thus no longer impedes the outflow of the control or leakage amount in the low-pressure side return 40.
  • the cross section of the return geometry, ie the low-pressure side return 40 in the magnet assembly 10 is independent of the position of the proposed inventions residual air disc 44th Mit Reference numerals 38 are anchor slots, by which the control of leakage or control amount in the low-pressure side return is improved.
  • the armature slots 38 the control amount or the leakage amount of the passage opening of the magnetic core 22 flow, in which the solenoid valve spring 18 is located.
  • FIG. 2 shows that the residual air gap disc 44 shown there is formed as a circular ring 48.
  • a circular ring width of the circular ring 58 is indicated by reference numeral 54.
  • An inner diameter 50 of the formed as a circular ring 48 residual air gap disc 44 is dimensioned such that it exceeds the outer diameter of the inner pole 28 of the magnetic core 22 of the magnet assembly 10, further, the inner diameter 50 of the annulus 48 is designed so that the magnetic coil 24 is not substantially through the made of non-magnetic material, for example, formed as a metal foil formed Restluftspaltfrac 44.
  • the inner diameter of the bore of the annular-shaped residual air gap disc 44 is at most as large as the inner diameter of the outer pole 30 or the outer diameter of the coil space in which the magnetic coil 24 is accommodated.
  • residual air gap disc 44 comprises a continuous single slot 46.
  • the slot is used to prevent deformation during assembly of the non-magnetic metallic foil material produced residual air gap disk 44 in the clamping point 42 between the end face 26 of the magnetic core 22 and the overlap 34 of the magnet sleeve 32nd
  • the representation according to FIG. 3 is a further embodiment of a trained as a circular ring residual air disc to remove.
  • FIG. 3 In contrast to the representation according to FIG. 2 , in which the formed as a circular ring 48 residual air gap disc 44 is provided with a single slot 46, is at the in FIG. 3 shown further embodiment of the formed as a circular ring 48 residual air gap disc an internal slit 56 is formed.
  • a number of slots 60 extend in the radial direction. As shown in the illustration FIG. 3 As can be seen, the slots 60 are not continuous, but have a slot length 58 which is dimensioned smaller than the annular width 54.
  • the annulus width 54 represents the difference between the outer diameter 52 and the inner diameter 50 of the annulus 48. Between the end of the slot 60th and the outer diameter 52 of the circular ring 48 thus remains a web width 62, so that, as shown in FIG FIG. 1 a continuous in the circumferential direction fixation of the present invention proposed residual air gap disc 44 at the clamping point 42 between the overlap 34 of the magnet sleeve 32 and the end face 26 of the magnetic core 22 can be achieved.

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

Description

Stand der TechnikState of the art

DE 196 50 865 A1 beschreibt ein Magnetventil zur Steuerung des Kraftstoffdruckes in einem Steuerraum eines Einspritzventiles, so z.B. eines Common-Rail-Hochdruckspeichereinspritzsystems. Über den Kraftstoffdruck im Steuerraum wird eine Hubbewegung eines Ventilkolbens gesteuert, mit dem eine Einspritzöffnung des Einspritzventiles geöffnet oder geschlossen werden kann. Das Magnetventil umfasst einen Elektromagneten, einen beweglichen Anker und ein mit dem Anker bewegtes und von einer Ventilschließfeder in Schließrichtung beaufschlagtes Ventilglied, welches mit dem Ventilsitz des Magnetventils zusammenwirkt und so den Kraftstoffabfluss aus dem Steuerraum steuert. DE 196 50 865 A1 describes a solenoid valve for controlling the fuel pressure in a control chamber of an injection valve, such as a common rail high-pressure accumulator injection system. About the fuel pressure in the control chamber, a lifting movement of a valve piston is controlled, with which an injection port of the injection valve can be opened or closed. The solenoid valve comprises an electromagnet, a movable armature and a valve member moved with the armature and acted upon by a valve closing spring in the closing direction, which valve member cooperates with the valve seat of the solenoid valve and thus controls the fuel drain from the control chamber.

Bei bekannten Magnetventilen wirkt sich nachteilig das im Betrieb auftretende Schwingen des Ankers und/oder Prellen des Ventilgliedes aus. Gemäß der Lösungen aus DE 196 50 865 A1 und DE 195 08 104 A1 ist der Anker des Magnetventils als zweiteiliger Magnetanker ausgebildet, um so die bewegte Masse der Baueinheit Anker/Ventilglied und damit die das Prellen verursachende kinetische Energie zu verringern. Der zweiteilige Anker umfasst einen Ankerbolzen und eine auf dem Ankerbolzen gegen die Kraft einer Rückstellfeder in Schließrichtung des Ventilgliedes unter Einwirkung ihrer trägen Masse verschiebbar aufgenommene Ankerplatte. Diese ist mittels einer Sicherungsscheibe und einer diese umgebenden Sicherungshülse am Ankerbolzen gesichert.In known solenoid valves, the swing occurring during operation of the armature and / or bouncing of the valve member has a disadvantageous effect. According to the solutions out DE 196 50 865 A1 and DE 195 08 104 A1 the armature of the solenoid valve is designed as a two-part armature, so as to reduce the moving mass of the armature / valve member assembly and thus the bouncing kinetic energy. The two-piece armature includes an anchor bolt and an armature plate slidably received on the armature bolt against the force of a return spring in the closing direction of the valve member under the action of its inertial mass. This is secured by means of a locking washer and a surrounding locking sleeve on the anchor bolt.

Zusätzliche Dämpfungseinrichtungen werden eingesetzt, umfassend einen mit der Ankerplatte bewegten und einen ortsfesten Teil. Der mit der Ankerplatte bewegbare Teil umfasst einen dem ortsfesten Teil zugewandten Ansatz, um eine Dämpfung des Nachschwingens der Ankerplatte bei dynamischer Verschiebung derselben zu bewirken. Der andere Teil der Dämpfungseinrichtung ist an einem ortsfest angeordneten Teil des Magnetventils als ein Überhubanschlag ausgebildet. Dieser begrenzt die maximale Weglänge, um die sich die Ankerplatte an dem Ankerbolzen in axialer Richtung bewegen kann. Der Überhubanschlag kann durch eine Stirnseite eines den Ankerbolzen führenden, ortsfest im Magnetventil angeordneten Gleitstücks oder durch ein dem Gleitstück vorgelagertes Teil, so z.B. eine Scheibe, gebildet sein. Bei Annäherung des mit der Ankerplatte bewegten Ansatzes an diesen Überhubanschlag entsteht zwischen den einander zugewandten Flächen ein hydraulischer Dämpfungsraum. Der in dem hydraulischen Dämpfungsraum vorhandene Kraftstoff erzeugt eine Gegenkraft, die der Bewegung der Ankerplatte entgegenwirkt, so dass ein Nachschwingen der Ankerplatte stark gedämpft wird.Additional damping devices are used, including one moving with the anchor plate and one fixed part. The armature plate movable portion includes a fixed portion facing shoulder for damping the ringing of the armature plate upon dynamic displacement to effect the same. The other part of the damping device is formed on a stationary part of the solenoid valve as an overstroke. This limits the maximum path length by which the anchor plate can move on the anchor bolt in the axial direction. The overstroke stop may be formed by an end face of a bolt which guides the anchor bolt, is fixedly arranged in the solenoid valve, or by a part which is disposed in front of the slider, for example a disk. When approaching the moving with the anchor plate approach to this Überhubanschlag arises between the facing surfaces of a hydraulic damping chamber. The existing in the hydraulic damping chamber fuel generates a counterforce, which counteracts the movement of the armature plate, so that a ringing of the armature plate is strongly attenuated.

Bei Magnetventilen zur Betätigung von Kraftstoffinjektoren an Kraftstoffeinspritzsystemen wird der Restluftspalt mittels einer Restluftspaltscheibe aus nicht-magnetischer Metallfolie eingestellt. Die aus nicht-magnetischer Metallfolie hergestellte Restluftspaltscheibe wird bei der Montage der Ankerbaugruppe auf den Magnetanker gelegt und über einen Federteller mit der Magnetventilfeder niedergehalten. Dadurch ist sichergestellt, dass die dünne Metallfolie, die die Restluftspaltscheibe darstellt, stets eine definierte Position einnimmt bzw. der Bewegung des Ankers folgt. Bei Gestaltung der Restluftspaltscheibe ist stets ein Kompromiss zwischen der Festigkeit bzw. Stabilität und den hydraulischen Anforderungen zu treffen. Da die Restluftspaltscheibe im Zentrum des Ankers fixiert wird, ist eine Verbindung zum Magnetinnenpol herzustellen, die sich über den Federraum erstreckt. Dieser jedoch stellt den Abfluss für die abgesteuerte Rücklaufmenge dar. Aufgrund dieses Konfliktes kann der Abfluss der Steuer- bzw. Leckagemenge nicht optimal gestaltet werden, so dass die sich einstellende Ankerbewegung nicht optimal ist. Dies bedeutet, dass der Anker kurz vor dem oberen Anschlag, d.h. an der diesem zuweisenden Stirnseite des Magnetkerns, stark gedämpft wird und diesen nicht erreicht bzw. erst dann erreicht, nachdem die Flüssigkeit, d.h. der abgesteuerte Kraftstoff, aus dem Spalt vollständig verdrängt ist.In solenoid valves for actuating fuel injectors on fuel injection systems, the residual air gap is adjusted by means of a residual air gap disc made of non-magnetic metal foil. The residual air gap disc made of non-magnetic metal foil is placed on the magnet armature during assembly of the armature assembly and held down by a spring plate with the solenoid valve spring. This ensures that the thin metal foil, which represents the residual air gap disc, always assumes a defined position or follows the movement of the armature. When designing the residual air gap disc, a compromise must always be made between the strength or stability and the hydraulic requirements. Since the residual air gap disk is fixed in the center of the armature, a connection to the magnetic inner pole is to be established, which extends over the spring space. However, this represents the outflow for the repelled return flow. Due to this conflict, the outflow of the control or leakage amount can not be optimally designed, so that the self-adjusting armature movement is not optimal. This means that the armature just before the top stop, i. at the assigning end face of the magnetic core, is strongly attenuated and not reached or only reached after the liquid, i. the discarded fuel is completely displaced from the gap.

Magnetbaugruppen gemäß des Oberbegriffs von Anspruch 1 sind aus US5238224A1 und US5918818A1 bekannt.Magnet assemblies according to the preamble of claim 1 are made US5238224A1 and US5918818A1 known.

Offenbarung der ErfindungDisclosure of the invention

Der vorliegenden Erfindung liegt die Aufgabe zugrunde, eine Restluftspaltscheibe bereitzustellen, die an Magnetventilen eingesetzt werden kann, ohne dass die Abströmung der Rücklaufmenge behindert wird.The present invention has for its object to provide a residual air gap disc that can be used on solenoid valves, without the outflow of the return amount is hindered.

Der erfindungsgemäß vorgeschlagenen Lösung folgend, wird die Geometrie der z.B. aus nicht-magnetischer Metallfolie herstellbaren Restluftspaltscheibe signifikant vereinfacht. Diese wird erfindungsgemäß nicht mehr, wie bei bisherigen Ausführungsvarianten, über den Federteller auf dem Anker fixiert. Dadurch ergibt sich eine Vereinfachung des Montageablaufs. Die erfindungsgemäß vorgeschlagene Restluftspaltscheibe verdeckt nicht mehr, auch nicht teilweise, den Federraum und behindert somit nicht das Abfließen der Steuer- bzw. der Leckagemenge in Richtung des niederdruckseitigen Rücklaufes. Der Querschnitt der Rücklaufgeometrie im Anker und im Magnet ist unabhängig von der Lage der Restluftspaltscheibe.Following the solution proposed by the invention, the geometry of e.g. made of non-magnetic metal foil manufacturable residual air gap significantly simplified. This is according to the invention no longer, as in previous embodiments, fixed on the spring plate on the anchor. This results in a simplification of the assembly process. The inventively proposed residual air gap disc no longer covers, not even partially, the spring chamber and thus does not hinder the flow of the tax or the leakage amount in the direction of the low-pressure side return. The cross section of the return geometry in the armature and in the magnet is independent of the position of the residual air gap disk.

Die erfindungsgemäß vorgeschlagene Restluftspaltscheibe wird als eine einfache Scheibe mit einer Schlitzung, die der Vermeidung von Verformungen dient, ausgeführt. Optional können auch mehrere radiale Schlitze mit einer Schlitzlänge ausgebildet sein, die kleiner ist als die Breite der kreisringförmig ausgebildeten Restluftspaltscheibe. Statt auf dem Anker bzw. der dem Magnetkern zuweisenden Planfläche des Ankers wird die erfindungsgemäß vorgeschlagene Restluftspaltscheibe zwischen dem Magnetkern und der Magnethülse eingelegt und durch den Magnetkern fixiert. Der Innendurchmesser der erfindungsgemäß vorgeschlagenen Restluftspaltscheibe wird so groß wie möglich gewählt, so dass der Innenpol der Magnetspule, die im Magnetkern eingelassen ist, nicht überdeckt wird, wohingegen der Außenpol des Magnetkerns durch die kreisringförmig ausgebildete Restluftspaltscheibe überdeckt ist.The inventively proposed residual air gap disc is designed as a simple disc with a slit, which serves to avoid deformation executed. Optionally, a plurality of radial slots may be formed with a slot length which is smaller than the width of the annular-shaped residual air gap disc. Instead of the armature or the magnetic core facing planar surface of the armature, the inventively proposed residual air gap disc is inserted between the magnetic core and the magnet sleeve and fixed by the magnetic core. The inner diameter of the inventively proposed residual air gap disc is chosen to be as large as possible, so that the inner pole of the magnetic coil, which is embedded in the magnetic core, is not covered, whereas the outer pole of the magnetic core is covered by the annular-shaped residual air gap disc.

Die erfindungsgemäß vorgeschlagene Restluftspaltscheibe kann bei der Montage der Ankerbaugruppe sehr einfach zwischen dem Magnetkern und einem kreisringförmig verlaufenden Übergriff an der Unterseite der Magnethülse eingelegt und bei der Montage sehr einfach und verliersicher fixiert werden.The inventively proposed residual air gap disk can be very easily inserted in the assembly of the armature assembly between the magnetic core and an annular extending grip on the underside of the magnet sleeve and fixed very easy and captive during assembly.

Kurze Beschreibung der ZeichnungenBrief description of the drawings

Anhand der Zeichnung wird die Erfindung nachstehend eingehender beschrieben.With reference to the drawing, the invention will be described below in more detail.

Es zeigt:

Figur 1
die kreisringförmig ausgebildete Restluftspaltscheibe, angeordnet zwischen Magnetkern und Magnethülse,
Figur 2
eine erste Ausführungsvariante der erfindungsgemäß vorgeschlagenen Restluftspaltscheibe und
Figur 3
eine weitere Ausführungsvariante der erfindungsgemäß vorgeschlagenen Restluftspaltscheibe.
It shows:
FIG. 1
the annular-shaped residual air gap disc, arranged between the magnetic core and the magnetic sleeve,
FIG. 2
a first embodiment of the present invention proposed residual air gap disc and
FIG. 3
a further embodiment of the inventively proposed residual air gap disc.

Ausführungsformenembodiments

Der Darstellung gemäß Figur 1 ist in schematischer Wiedergabe eine Magnetgruppe eines Kraftstoffinjektors zu entnehmen.The representation according to FIG. 1 is to take a schematic representation of a magnetic group of a fuel injector.

Eine Magnetbaugruppe 10, die der Betätigung eines Kraftstoffinjektors, z.B. eines Kraftstoffinjektors für ein Hochdruckspeichereinspritzsystem (Common-Rail) dient, ist in einen Injektorkörper 12 des Kraftstoffinjektors eingelassen. Der Magnetbaugruppe 10 gegenüberliegend befindet sich ein Anker 14, dessen Planseite 16 durch eine Magnetventilfeder 18 beaufschlagt ist. Mit Bezugszeichen 20 ist ein Einstellring bezeichnet, der zur Einstellung des Magnetventilhubes dient. Der Einstellring 20 liegt im Injektorkörper 12 auf und dient gleichzeitig als Auflage für eine Magnethülse 32. Die Magnethülse 32 dient der Aufnahme eines Magnetkerns 22. Der Magnetkern 22 seinerseits umschließt eine Magnetspule 24. Der Magnetkern 22 ist an einer Stirnseite 26, die der Planseite 16 des Ankers 14 gegenüberliegt, offen und durch die Lage der Spule 24 in einen Innenpol 28 und einen Außenpol 30 unterteilt.A magnet assembly 10 which facilitates the actuation of a fuel injector, e.g. A fuel injector for a high-pressure accumulator injection system (common rail) is inserted in an injector body 12 of the fuel injector. The magnet assembly 10 is located opposite an armature 14, the plan side 16 is acted upon by a solenoid valve spring 18. With reference numeral 20, an adjustment ring is designated, which serves to adjust the solenoid valve. The adjusting ring 20 rests in the injector body 12 and at the same time serves as a support for a magnetic sleeve 32. The magnetic sleeve 32 serves to receive a magnetic core 22. The magnetic core 22 in turn encloses a magnetic coil 24. The magnetic core 22 is on a front side 26, that of the plan side 16 the armature 14 is opposite, open and divided by the position of the coil 24 in an inner pole 28 and an outer pole 30.

Aus der Darstellung gemäß Figur 1 geht hervor, dass die Magnethülse 32 mit ihrer Innenseite 36 den Magnetkern 22 umschließt. Die Magnethülse 32 wird mit einer in Figur 1 nicht dargestellten Spannmutter am Injektorkörper 12 des Kraftstoffinjektors befestigt. Der Magnetkern 22 wird innerhalb der Magnetbaugruppe beispielsweise über eine Bördelung oder eine Schweißverbindung fixiert.From the illustration according to FIG. 1 shows that the magnetic sleeve 32 encloses the magnetic core 22 with its inner side 36. The magnet sleeve 32 is with one in FIG. 1 Not shown clamping nut attached to the injector body 12 of the fuel injector. The magnetic core 22 is fixed within the magnet assembly, for example via a flange or a welded joint.

Der Magnetkern 22 der Magnetgruppe 10 umfasst eine Durchgangsöffnung, in der einerseits die Magnetventilfeder 18, die den Anker 14 auf der Planseite 16 beaufschlagt, angeordnet ist, und die andererseits als Rücklauf 40 dient, über den bei Betätigung des Magnetventils aus einem Steuerraum des Kraftstoffinjektors abgesteuerte Steuermenge bzw. Leckage in den niederdruckseitigen Rücklauf eines Kraftstoffeinspritzsystems, um ein Beispiel nennen, zurückströmt.The magnetic core 22 of the magnet group 10 comprises a passage opening in which on the one hand the solenoid valve spring 18, which acts on the armature 14 on the plan side 16, is arranged, and on the other hand serves as return 40, via the controlled upon actuation of the solenoid valve from a control chamber of the fuel injector Control amount or leakage in the low-pressure side return of a fuel injection system, for example, flows back.

Aus der Darstellung gemäß Figur 1 geht hervor, dass eine Restluftspaltscheibe 44 an einer Einspannstelle 42 zwischen der Stirnseite 26 des Magnetkerns 22 und der Oberseite des Übergriffs 34 der Magnethülse 32 eingespannt ist. Vor Montage der Magnethülse 32 und des Magnetkerns 22 wird die z.B. als dünne Metallfolie aus nicht-magnetischem Material gefertigte, z.B. kreisförmige Restluftspaltscheibe 44 auf den Übergriff 34 in die Magnethülse 32 eingelegt, und anschließend der Magnetkern 22 mit der Magnetspule 24 montiert. Bei der Beaufschlagung einer Spannmutter mit einem definierten Anzugsmoment wird die Magnetbaugruppe im Injektorkörper 12 befestigt.From the illustration according to FIG. 1 shows that a residual air gap disk 44 is clamped at a clamping point 42 between the end face 26 of the magnetic core 22 and the upper side of the overlap 34 of the magnet sleeve 32. Before mounting the magnetic sleeve 32 and the magnetic core 22, for example, as a thin metal foil made of non-magnetic material, eg circular residual air gap disc 44 is placed on the overlap 34 in the magnetic sleeve 32, and then the magnetic core 22 is mounted with the magnetic coil 24. When a clamping nut is acted upon with a defined tightening torque, the magnet assembly is fastened in the injector body 12.

Mithin wird in Abkehr von bisher gängigen Prinzipien die Restluftspaltscheibe 44 nicht mehr auf der Planseite 16 des Ankers 14 z.B. durch einen Federteller oder dergleichen befestigt, sondern in Abkehr von der bisherigen Praxis der Stirnseite 26 des Magnetkerns 22 der Magnetbaugruppe 10 zugeordnet.Thus, in departure from previously common principles, the residual air gap disk 44 is no longer on the plan side 16 of the armature 14, for example. attached by a spring plate or the like, but assigned in departure from the previous practice of the end face 26 of the magnetic core 22 of the magnet assembly 10.

Aus der Darstellung gemäß Figur 1 geht hervor, dass in einer Ausführung der Restluftspaltscheibe 44 in Form eines Kreisrings, vergleiche Darstellung gemäß der Figuren 2 und 3, der Innenpol 28 des Magnetkerns 22 frei bleibt, während der Außenpol 30 des Magnetkerns 22 von der Restluftspaltscheibe 44 überdeckt ist. Die Restluftspaltscheibe 44 verdeckt nicht mehr, auch nicht teilweise, den Federraum, d.h. die Durchgangsöffnung in den niederdruckseitigen Rücklauf 40 und behindert somit nicht mehr den Abfluss der Steuer- bzw. Leckagemenge in den niederdruckseitigen Rücklauf 40. Der Querschnitt der Rücklaufgeometrie, d.h. des niederdruckseitigen Rücklaufs 40 in der Magnetbaugruppe 10 ist unabhängig von der Lage der erfindungsgemäß vorgeschlagenen Restluftspaltscheibe 44. Mit Bezugszeichen 38 sind Ankerschlitze bezeichnet, durch welche die Absteuerung von Leckage oder Steuermenge in den niederdruckseitigen Rücklauf verbessert wird. Über die Ankerschlitze 38 kann die Steuermenge bzw. die Leckagemenge der Durchgangsöffnung des Magnetkerns 22 zuströmen, in dem sich die Magnetventilfeder 18 befindet.From the illustration according to FIG. 1 shows that in an embodiment of the residual air gap disc 44 in the form of a circular ring, see illustration according to the Figures 2 and 3 , the inner pole 28 of the magnetic core 22 remains free, while the outer pole 30 of the magnetic core 22 is covered by the residual air gap disc 44. The residual air gap disc 44 no longer obscures, not even partially, the spring space, ie the passage opening in the low-pressure side return 40 and thus no longer impedes the outflow of the control or leakage amount in the low-pressure side return 40. The cross section of the return geometry, ie the low-pressure side return 40 in the magnet assembly 10 is independent of the position of the proposed inventions residual air disc 44th Mit Reference numerals 38 are anchor slots, by which the control of leakage or control amount in the low-pressure side return is improved. About the armature slots 38, the control amount or the leakage amount of the passage opening of the magnetic core 22 flow, in which the solenoid valve spring 18 is located.

Aus der Darstellung gemäß Figur 2 ist eine erste Ausführungsvariante der erfindungsgemäß vorgeschlagenen Restluftspaltscheibe zu entnehmen.From the illustration according to FIG. 2 is a first embodiment of the inventively proposed residual air gap disc can be seen.

Figur 2 zeigt, dass die dort dargestellte Restluftspaltscheibe 44 als Kreisring 48 ausgebildet ist. Eine Kreisringbreite des Kreisringes 58 ist durch Bezugszeichen 54 angedeutet. Ein Innendurchmesser 50 der als Kreisring 48 ausgebildeten Restluftspaltscheibe 44 ist so bemessen, dass dieser den Außendurchmesser des Innenpols 28 des Magnetkerns 22 der Magnetbaugruppe 10 übersteigt, des Weiteren ist der Innendurchmesser 50 des Kreisringes 48 so ausgelegt, dass auch die Magnetspule 24 im Wesentlichen nicht durch die aus amagnetischem Material gefertigte, als Metallfolie z.B. ausgebildete Restluftspaltscheibe 44 überdeckt ist. Bevorzugt ist der Innendurchmesser der Bohrung der kreisringförmig ausgebildeten Restluftspaltscheibe 44 maximal so groß wie der Innendurchmesser des Außenpoles 30 oder der Außendurchmesser des Spulenraumes, in dem die Magnetspule 24 aufgenommen ist. FIG. 2 shows that the residual air gap disc 44 shown there is formed as a circular ring 48. A circular ring width of the circular ring 58 is indicated by reference numeral 54. An inner diameter 50 of the formed as a circular ring 48 residual air gap disc 44 is dimensioned such that it exceeds the outer diameter of the inner pole 28 of the magnetic core 22 of the magnet assembly 10, further, the inner diameter 50 of the annulus 48 is designed so that the magnetic coil 24 is not substantially through the made of non-magnetic material, for example, formed as a metal foil formed Restluftspaltscheibe 44. Preferably, the inner diameter of the bore of the annular-shaped residual air gap disc 44 is at most as large as the inner diameter of the outer pole 30 or the outer diameter of the coil space in which the magnetic coil 24 is accommodated.

Der Darstellung gemäß Figur 2 ist des Weiteren zu entnehmen, dass die als Kreisring 48 ausgebildete Restluftspaltscheibe 44 einen durchgehenden Einzelschlitz 46 umfasst. Der Schlitz dient zur Vermeidung von Verformungen bei der Montage der aus nicht-magnetischem metallischen Folienmaterial gefertigten Restluftspaltscheibe 44 in der Einspannstelle 42 zwischen der Stirnseite 26 des Magnetkerns 22 und dem Übergriff 34 der Magnethülse 32.The representation according to FIG. 2 Furthermore, it can be seen that the formed as a circular ring 48 residual air gap disc 44 comprises a continuous single slot 46. The slot is used to prevent deformation during assembly of the non-magnetic metallic foil material produced residual air gap disk 44 in the clamping point 42 between the end face 26 of the magnetic core 22 and the overlap 34 of the magnet sleeve 32nd

Der Darstellung gemäß Figur 3 ist eine weitere Ausführungsvariante einer als Kreisring ausgebildeten Restluftspaltscheibe zu entnehmen.The representation according to FIG. 3 is a further embodiment of a trained as a circular ring residual air disc to remove.

Im Unterschied zur Darstellung gemäß Figur 2, in der die als Kreisring 48 ausgebildete Restluftspaltscheibe 44 mit einem Einzelschlitz 46 versehen ist, ist an der in Figur 3 dargestellten weiteren Ausführungsvariante der als Kreisring 48 ausgebildeten Restluftspaltscheibe eine innenliegende Schlitzung 56 ausgebildet.In contrast to the representation according to FIG. 2 , in which the formed as a circular ring 48 residual air gap disc 44 is provided with a single slot 46, is at the in FIG. 3 shown further embodiment of the formed as a circular ring 48 residual air gap disc an internal slit 56 is formed.

Ausgehend vom Innendurchmesser 50 des Kreisrings 48 erstreckt sich eine Anzahl von Schlitzen 60 in radiale Richtung. Wie aus der Darstellung gemäß Figur 3 hervorgeht, verlaufen die Schlitze 60 nicht durchgängig, sondern weisen eine Schlitzlänge 58 auf, die kleiner bemessen ist als die Kreisringbreite 54. Die Kreisringbreite 54 stellt die Differenz zwischen dem Außendurchmesser 52 und dem Innendurchmesser 50 des Kreisrings 48 dar. Zwischen dem Ende des Schlitzes 60 und dem Außendurchmesser 52 des Kreisrings 48 verbleibt demnach eine Stegbreite 62, so dass sich gemäß der Darstellung in Figur 1 eine in Umfangsrichtung kontinuierliche Fixierung der erfindungsgemäß vorgeschlagenen Restluftspaltscheibe 44 an der Einspannstelle 42 zwischen dem Übergriff 34 der Magnethülse 32 und der Stirnseite 26 des Magnetkerns 22 erreichen lässt.Starting from the inner diameter 50 of the annulus 48, a number of slots 60 extend in the radial direction. As shown in the illustration FIG. 3 As can be seen, the slots 60 are not continuous, but have a slot length 58 which is dimensioned smaller than the annular width 54. The annulus width 54 represents the difference between the outer diameter 52 and the inner diameter 50 of the annulus 48. Between the end of the slot 60th and the outer diameter 52 of the circular ring 48 thus remains a web width 62, so that, as shown in FIG FIG. 1 a continuous in the circumferential direction fixation of the present invention proposed residual air gap disc 44 at the clamping point 42 between the overlap 34 of the magnet sleeve 32 and the end face 26 of the magnetic core 22 can be achieved.

Wenngleich zeichnerisch nicht dargestellt, so ist auch eine Kombination der in Figuren 2 und 3 dargestellten Ausführungsvarianten der als Kreisring 48 ausgebildeten Restluftspaltscheibe 44 denkbar. So kann anstelle einer Vielzahl von nicht durchgängigen Schlitzen 60 gemäß der Ausführungsvariante in Figur 3 in dieser Ausführungsform des Kreisrings 48 auch ein durchgängiger Einzelschlitz 46 zum Ausgleich von Verformungen vorgesehen sein, so dass sich eine Kombination der Schlitzmuster der Ausführungsvarianten gemäß der Figuren 2 und 3 ergibt.Although not shown in the drawing, so is a combination of in Figures 2 and 3 illustrated embodiments of the designed as a circular ring 48 residual air gap disc 44 conceivable. Thus, instead of a plurality of non-continuous slots 60 according to the embodiment in FIG. 3 in this embodiment of the circular ring 48, a continuous single slot 46 may be provided to compensate for deformations, so that a combination of the slot pattern of the embodiments according to the Figures 2 and 3 results.

Verbleibt wie in Figur 3 dargestellt, am Ende der nicht durchgängigen Schlitze 60 eine Stegbreite 62 des Restluftspaltscheibenmaterials, so lässt sich diese wesentlich einfacher handhaben, insbesondere wesentlich einfacher vor Montage des Magnetkerns 22 in der Magnethülse 32 positionieren.Remains as in FIG. 3 shown, at the end of the non-continuous slots 60 a web width 62 of the Restlottspaltscheibenmaterials, these can be much easier to handle, in particular much easier to position before mounting the magnetic core 22 in the magnetic sleeve 32.

Claims (9)

  1. Magnet assembly (10) comprising a magnet core (22) and a magnet sleeve (32) accommodating the latter, one end face (26) of the magnet core (22) facing an armature (14, 16) and a residual air split disc (44) being inserted between the magnet core (22) and the magnet sleeve (32), characterized in that the magnet sleeve (32) has an overlap (34) engaging under the end face (26) of the magnet core (22).
  2. Magnet assembly (10) according to Claim 1, characterized in that the residual air split disc (44) is fixed at a clamping point (42) by the magnet core (22) in the magnet sleeve (32).
  3. Magnet assembly (10) according to Claim 1, characterized in that the residual air split disc (44) is made as a metallic foil of non-magnetic material.
  4. Magnet assembly (10) according to Claim 1, characterized in that the residual air split disc (44) is implemented as a circular ring (48).
  5. Magnet assembly (10) according to Claim 1, characterized in that an internal diameter (50) of the residual air split disc (44) is greater than an external diameter of an inner pole (28) of the magnet core (22).
  6. Magnet assembly (10) according to Claim 1, characterized in that the residual air split disc (44) has a continuous slit (46).
  7. Magnet assembly (10) according to Claim 1, characterized in that the residual air split disc (44) comprises internal slitting (56) made of a number of slits (60) originating from the internal diameter (50).
  8. Magnet assembly (10) according to Claim 8, characterized in that the slits (60) are implemented with a length (58) which is less than the difference between external diameter (52) and internal diameter (50) of the residual air split disc (44).
  9. Use of the magnet assembly (10) according to one or more of Claims 1 to 9 in a fuel injector of a fuel injection system.
EP10703242.7A 2009-03-20 2010-01-20 Residual air split disc Active EP2409308B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102009001706A DE102009001706A1 (en) 2009-03-20 2009-03-20 Residual air gap disc
PCT/EP2010/050630 WO2010105864A1 (en) 2009-03-20 2010-01-20 Residual air split disc

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EP2409308A1 EP2409308A1 (en) 2012-01-25
EP2409308B1 true EP2409308B1 (en) 2018-01-10

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EP (1) EP2409308B1 (en)
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DE (1) DE102009001706A1 (en)
RU (1) RU2525971C2 (en)
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EP2434503B1 (en) * 2010-09-27 2015-07-29 ABB Technology AG Magnetic actuator with a non-magnetic insert
DE102012206214A1 (en) 2012-04-16 2013-10-17 Robert Bosch Gmbh Magnet component for servo valve of common rail injector, has residue air gap disk formed as circular ring and fastened at anchor plate-side front end of magnetic core by firmly bonded connection portions using weld
DE102012206215A1 (en) 2012-04-16 2013-10-17 Robert Bosch Gmbh Magnetic assembly, in particular for a solenoid valve of a fuel injector
FR2991728B1 (en) * 2012-06-08 2016-04-29 Bosch Gmbh Robert ELECTROMAGNETIC VALVE OF FUEL INJECTION SYSTEM
DE102012214920A1 (en) * 2012-08-22 2014-02-27 Continental Automotive Gmbh Damping surface on valve components
DE102013212504A1 (en) * 2013-06-27 2014-12-31 Robert Bosch Gmbh Magnetic assembly for a fuel injector
DE102014215589A1 (en) 2014-02-10 2015-08-13 Robert Bosch Gmbh Residual air gap disk for a magnetic assembly of a solenoid valve and method for producing a residual air gap disk
DE102014207988B3 (en) * 2014-04-29 2015-09-10 Schaeffler Technologies AG & Co. KG Electromagnetic actuator
DE102015212130A1 (en) 2015-06-30 2017-01-05 Robert Bosch Gmbh Magnetic assembly and fuel injector with a magnetic assembly
TR201509949A2 (en) * 2015-08-11 2017-02-21 Bosch Sanayi Ve Tic A S A fuel injector with a new shim
DE102015223167A1 (en) * 2015-11-24 2017-05-24 Robert Bosch Gmbh Switching valve for a fuel injector and fuel injector
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RU2525971C2 (en) 2014-08-20
WO2010105864A1 (en) 2010-09-23
DE102009001706A1 (en) 2010-09-23
CN102362319A (en) 2012-02-22
CN102362319B (en) 2013-11-20
EP2409308A1 (en) 2012-01-25
RU2011142079A (en) 2013-04-27

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