EP1259729A2 - Electromagnetic valve for controlling an injection valve of an internal combustion engine - Google Patents

Electromagnetic valve for controlling an injection valve of an internal combustion engine

Info

Publication number
EP1259729A2
EP1259729A2 EP01994586A EP01994586A EP1259729A2 EP 1259729 A2 EP1259729 A2 EP 1259729A2 EP 01994586 A EP01994586 A EP 01994586A EP 01994586 A EP01994586 A EP 01994586A EP 1259729 A2 EP1259729 A2 EP 1259729A2
Authority
EP
European Patent Office
Prior art keywords
armature
solenoid valve
anchor bolt
valve
plate
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.)
Granted
Application number
EP01994586A
Other languages
German (de)
French (fr)
Other versions
EP1259729B1 (en
Inventor
Rainer Haeberer
Hermann Koch-Grober
Holger Rapp
Christoffer Uhr
Andreas Rettich
Wolfgang Fleiner
Markus Rueckle
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
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Priority claimed from DE10113008A external-priority patent/DE10113008A1/en
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP1259729A2 publication Critical patent/EP1259729A2/en
Application granted granted Critical
Publication of EP1259729B1 publication Critical patent/EP1259729B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M47/00—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
    • F02M47/02—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure of accumulator-injector type, i.e. having fuel pressure of accumulator tending to open, and fuel pressure in other chamber tending to close, injection valves and having means for periodically releasing that closing pressure
    • F02M47/027—Electrically actuated valves draining the chamber to release the closing pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/0033—Lift valves, i.e. having a valve member that moves perpendicularly to the plane of the valve seat
    • F02M63/0036—Lift valves, i.e. having a valve member that moves perpendicularly to the plane of the valve seat with spherical or partly spherical shaped valve member ends
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/30—Fuel-injection apparatus having mechanical parts, the movement of which is damped
    • F02M2200/304—Fuel-injection apparatus having mechanical parts, the movement of which is damped using hydraulic means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/30—Fuel-injection apparatus having mechanical parts, the movement of which is damped
    • F02M2200/306—Fuel-injection apparatus having mechanical parts, the movement of which is damped using mechanical means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2547/00—Special features for fuel-injection valves actuated by fluid pressure
    • F02M2547/003—Valve inserts containing control chamber and valve piston

Definitions

  • Solenoid valve for controlling an injection valve of an internal combustion engine
  • the invention relates to a solenoid valve for controlling an injection valve of an internal combustion engine according to the preamble of claim 1.
  • Such a solenoid valve is used to control the fuel pressure in the control pressure chamber of an injection valve, for example an injector of a common rail injection system.
  • the movement of a valve piston, with which an injection opening of the injection valve is opened or closed, is controlled via the fuel pressure in the control pressure chamber.
  • the known solenoid valve has an electromagnet arranged in a housing part, a movable armature and a control valve member which is moved with the armature and acted upon by a closing spring in the closing direction and which cooperates with a valve seat of the solenoid valve and thus controls the fuel outflow from the control pressure chamber.
  • solenoid valves The disadvantage of solenoid valves is the so-called anchor bounce.
  • the armature, and with it the control valve member is accelerated from the closing spring of the solenoid valve to the valve seat in order to close a fuel outlet channel from the control pressure chamber.
  • the impact of the control valve member on the valve seat can result in disadvantageous swinging and / or bouncing of the control valve member on the valve seat, as a result of which the control of the injection process is impaired.
  • the armature is therefore made in two parts with an armature bolt and an armature plate slidably mounted on the armature bolt, so that the armature plate moves further against the tension force of a return spring when the control valve member impacts the valve seat.
  • the return spring then conveys the anchor plate back to its starting position at a stop of the anchor bolt.
  • the two-part design of the armature reduces the effectively braked mass and thus the kinetic energy causing the bouncing of the armature hitting the valve seat, but the armature plate can disadvantageously oscillate on the armature bolt after the solenoid valve has closed.
  • DE 197 08 104 AI proposes using an overstroke stop which limits the path length by which the anchor plate can move on the anchor bolt.
  • the overstroke stop is arranged in a fixed manner in the housing of the solenoid valve between the anchor plate and a slide piece guiding the anchor bolt.
  • the overstroke stop By means of the overstroke stop, the reverberation time of the anchor plate is shortened, but the required overstroke distance of the anchor plate must be during the installation of the Solenoid valve can be set in the housing of the solenoid valve. This requires a complex change in the manufacturing process, since the manufacturing facilities have to be retrofitted accordingly.
  • the solenoid valve according to the invention with the characterizing features of claim 1 avoids the disadvantages occurring in the prior art.
  • the armature with the armature plate, armature bolt, return spring and overstroke stop can advantageously be preassembled outside the assembly line of the injection valve and the required displacement path of the armature plate on the armature bolt can be set outside the housing of the injection valve.
  • the pre-assembled armature assembly can then be installed in the housing of the solenoid valve. A complex conversion of the assembly line is not necessary.
  • the return spring which presses the anchor plate with a first end in its rest position against a first stop on the anchor bolt, is not fixedly supported with the second end in the solenoid valve housing, but rather on one fixed to the anchor bolt and moved with the anchor bolt Supporting part is also advantageously achieved that the return spring does not counteract the closing spring of the solenoid valve acting on the anchor bolt.
  • the spring tension of the closing spring of the solenoid valve can therefore be designed to be lower. Since the return spring no longer counteracts the closing spring, the return spring no longer has any influence on the dynamic behavior of the anchor bolt.
  • the anchor bolt is slidably mounted in an opening of a slider which is fixed in the housing of the solenoid valve and for the side of the slider facing the anchor plate to be provided with a recess in which the support part fixed to the anchor bolt is arranged, wherein the outer contour of the support part is spaced from the inner contour of the recess by a gap.
  • FIG. 1 shows a cross section through the upper part of a fuel injection valve known from the prior art with a solenoid valve
  • FIG. 2 shows a partial area of the solenoid valve known from the prior art with an over-stroke adjusting disk
  • FIG. 3 shows a cross section through the armature assembly with slide piece according to a first embodiment of the invention
  • FIG. 4 shows a cross section through the armature assembly with slide piece according to a second embodiment of the invention.
  • Fig. 5 shows a cross section through the armature assembly with slider according to a third embodiment of the invention.
  • Fig. 1 shows the upper part of a fuel injection valve 1 known from the prior art, which is for use is determined in a fuel injection system which is equipped with a high-pressure fuel reservoir which is continuously supplied with high-pressure fuel by a high-pressure feed pump.
  • the fuel injector 1 shown has a valve housing 4 with a longitudinal bore 5, in which a valve piston 6 is arranged, which acts with its one end on a valve needle arranged in a nozzle body, not shown.
  • the valve needle is arranged in a pressure chamber which is supplied with fuel under high pressure via a pressure bore 8.
  • the valve needle is raised against the closing force of a spring by the high force of fuel which acts constantly on a pressure shoulder of the valve needle in the pressure chamber.
  • the fuel is then injected into the combustion chamber of the internal combustion engine through an injection opening which is then connected to the pressure chamber.
  • the valve needle is pressed into the valve seat of the injection valve in the closing direction and the injection process is ended.
  • valve piston 6 is guided at its end facing away from the valve needle in a cylinder bore 11 which is introduced into a valve piece 12 which is inserted into the valve housing 4.
  • a valve piece 12 which is inserted into the valve housing 4.
  • the end face 13 of the valve piston 6 is guided at its end facing away from the valve needle in a cylinder bore 11 which is introduced into a valve piece 12 which is inserted into the valve housing 4.
  • Valve piston 6 a control pressure chamber 14, which is connected via an inlet channel to a high-pressure fuel connection.
  • the inlet channel is essentially made up of three parts.
  • a bore leading radially through the wall of the valve piece 12, the inner walls of which form an inlet throttle 15 over part of its length, is constantly connected to an annular space 16 surrounding the valve piece on the circumference, which annular space in turn is in constant connection via a fuel filter inserted into the inlet channel with the high-pressure fuel connection of a connection piece 9 which can be screwed into the valve housing 4.
  • the annular space 16 is sealed to the longitudinal bore 5 via a sealing ring 39.
  • the control pressure chamber 14 is exposed to the high fuel pressure prevailing in the high-pressure fuel reservoir via the inlet throttle 15.
  • a bore running in the valve piece 12 which forms a fuel outlet channel 17 provided with an outlet throttle 18, which opens into a relief chamber 19, which is connected to a low-pressure fuel connection 10, which in turn is not further illustrated manner is connected to a fuel return of the injection valve 1.
  • the fuel drain channel 17 emerges from the valve piece 12 in the region of a conically countersunk part 21 of the outer end face of the valve piece 12.
  • the valve piece 12 is firmly clamped to the valve housing 4 in a flange area 22 via a screw member 23.
  • a valve seat 24 is formed in the conical part 21, with which a control valve member 25 of a solenoid valve 30 controlling the injection valve interacts.
  • the control valve member 25 is coupled to a two-part armature in the form of an armature bolt 27 and an armature plate 28, which armature interacts with an electromagnet 29 of the solenoid valve 30.
  • the solenoid valve 30 further comprises a housing part 60 which accommodates the electromagnet and which is firmly connected to the valve housing 4 via screwable connecting means 7.
  • the anchor plate 28 is dynamically slidably supported on the anchor bolt 27 under the action of its inertial mass against the biasing force of a return spring 35 and is pressed by this return spring in the idle state against a sickle disk 26 fixed on the anchor bolt.
  • the return spring 35 is supported in a housing-fixed manner on a flange 32 of a sliding piece 34 guiding the anchor bolt 27, which with this flange lies between a spacer disk 38 placed on the valve piece 12 and the screw member 23 in the valve housing is firmly clamped.
  • the armature bolt 27 and with it the armature disk 28 and the control valve member 25 coupled to the armature bolt are constantly acted upon in the closing direction by a closing spring 31 which is fixed to the housing, so that the control valve member 25 normally bears against the valve seat 24 in the closed position.
  • a closing spring 31 which is fixed to the housing, so that the control valve member 25 normally bears against the valve seat 24 in the closed position.
  • the armature plate 28 is attracted by the electromagnet and the drain channel 17 is opened toward the relief chamber 19.
  • annular shoulder 33 on the armature bolt 27 which strikes the flange 32 when the electromagnet is excited and thus limits the opening stroke of the control valve member 25.
  • the spacer 38 arranged between the flange 32 and the valve piece 12 serves to adjust the opening stroke.
  • the opening stroke of the control valve member 25 is adjusted by a stop element arranged between the armature plate 28 and the electromagnet 29.
  • the opening and closing of the injection valve is controlled by the solenoid valve 30 as described below.
  • the anchor bolt 27 is constantly acted upon by the closing spring 31 in the closing direction, so that the control valve member 25 rests on the valve seat 24 in the closed position when the electromagnet is not energized, and the control pressure chamber 14 is closed to the relief side 19, so that the high one there via the inlet channel very quickly Builds up pressure that is also present in the high-pressure fuel reservoir.
  • the pressure in the control pressure chamber 14 generates a closing force on the valve piston 6 and thus in FIG.
  • Control pressure chamber 14 very quickly, since this via the throttle 15 is decoupled from the high pressure side. As a result, the force acting on the valve needle in the opening direction outweighs the high fuel pressure applied to the valve needle, so that the valve needle moves upwards and at the same time the at least one injection opening toward it
  • the control valve member reverts as a result of the impact of the anchor bolt on the valve seat causing an elastic deformation thereof, which acts as an energy store, part of the energy being transferred to the control valve member, which then bounces off the valve seat 24 together with the anchor bolt.
  • the known solenoid valve shown in FIG. 1 therefore uses a two-part armature with an armature plate 28 decoupled from the armature pin 27. In this way, the mass impinging on the valve seat as a whole can be reduced, but the armature plate 28 can oscillate in a disadvantageous manner. For this reason, an overstroke adjusting disk 70 arranged between the armature plate 28 and the sliding sleeve 34 is provided in the known solenoid valve, as shown in FIG. 2.
  • the overtravel 70 limits the displacement of the anchor plate 28 on the anchor bolt 27 to the dimension d.
  • the swinging of the anchor plate 28 is reduced by the overtravel 70 and the anchor plate 28 returns to its initial position at the stop 26 faster.
  • the spacer 38, the slider 34 and the overtravel 70 are fixed in place in the solenoid valve housing. stressed.
  • the overtravel distance d in the solenoid valves known in the prior art must therefore be set during the assembly in the solenoid valve housing via the thickness of the related overtravel adjusting disc. In some embodiments, however, the thickness of the overtravel adjusting disc also influences the distance of the armature plate 28 from the electromagnet 29. This is the case when, for example, the end face of the solenoid valve housing 60 is clamped against the flange 32.
  • Fig. 3 shows a first embodiment of the solenoid valve according to the invention. Only the slider 34 and the anchor with anchor bolt 27, anchor plate 28 and return spring 35 are shown. The same parts are provided with the same reference numerals.
  • the armature assembly shown can be used, for example, in the solenoid valve housing 60 shown in FIG. 1.
  • An important difference from the known arrangement shown in FIG. 2 is that a support part 50 is provided in place of the overtravel adjusting disk which is arranged in a fixed manner in the solenoid valve housing and is firmly connected to the anchor bolt 27.
  • a disk fixed to the anchor bolt 27 can be provided as the supporting part.
  • the washer is pushed onto the anchor bolt 27 and then firmly connected to the anchor bolt by, for example, welding or gluing. Other types of fastening such as shrinking on are also possible.
  • the support part 50 is welded to the anchor bolt 27 on the side 59 facing away from the anchor plate.
  • the weld seam 51 on the underside 59 of the support part 50 can be seen in FIG. 1.
  • the return spring 35 is supported with one end 61 on the anchor plate 28 and with its other end 62 on the side 57 of the support part 50 which faces the anchor plate 28.
  • the anchor plate 28 When manufacturing the anchor assembly, the anchor plate 28 is first pushed onto the anchor bolt 27 until the anchor plate strikes a head 55 of the anchor bolt.
  • the head 55 replaces the sickle disk 26 in FIGS. 1 and 2 and, like this, serves as a stop for the anchor plate.
  • the return spring 35 is then pushed over the guide stub 65 of the anchor plate 28 until its end 61 abuts the anchor plate.
  • the disk-shaped support part 50 is pushed so far onto the anchor bolt 27 that the required overtravel distance d remains between the mutually facing sides 57 and 58 of the support part 50 and the guide stub 65. Finally, the support part 50 is fixed in this position on the anchor bolt 27.
  • the anchor assembly consisting of anchor bolt 27, anchor plate 28, return spring 35 and support member 50 is then inserted into the slider 34.
  • the anchor bolt 27 is inserted into a central bore 68 of the slider 34.
  • the slider 34 can already be clamped with the flange 36 in the housing 60 of the solenoid valve.
  • no annular shoulder 33 is provided, which limits the opening stroke of the anchor bolt by a stop on the slide piece 34. Instead, the opening stroke is limited by a stop of the armature bolt head 55 on the electromagnet or a projection of the electromagnet. This is necessary so that the anchor bolt 27 in FIG. 3 can be inserted into the slider 34 from above.
  • FIG. 3 deviating from the known arrangement shown in FIG. 2
  • the side of the slider 34 facing the support part 50 has a recess 52 into which the support part engages.
  • the lower end 67 of the anchor bolt 27 acts on the control valve member 25, which is pressed against the valve seat 24 by the closing force of the spring 31 when the electromagnet is not energized.
  • the side 59 of the support part 50 facing away from the anchor plate 28 and the weld seam 51 are spaced apart from the inner wall of the recess 52 by a gap.
  • the support part 50 which is moved with the anchor bolt, is prevented from striking the inner wall of the recess 52, since such a striking could result in the control valve member 25 not coming into contact with the valve seat 24.
  • the recess 52 is therefore designed in such a way that it can also accommodate the weld seam 51 and is always at a distance from it.
  • the lower side 59 of the support part 50 approaches the inner wall of the cylindrical recess 52 of the slider 34 when the solenoid valve closes, creating a hydraulic damping space.
  • the fuel compressed between the support part 50 and the recess 52 which can only escape laterally through the gap, advantageously dampens the impact of the anchor bolt 27 and the control valve member 25 coupled to the valve seat 24.
  • Gap between the anchor plate 28 and the support member 50 held fuel exerts a counterforce that counteracts the movement of the anchor plate.
  • the compensating movement of the anchor plate 28 is therefore limited by the position of the support part on the anchor bolt 27, which leads to a reversal of movement after previous damping and thus to a reduction in the ringing process.
  • FIG. 4 shows a further exemplary embodiment of the invention, which differs from the exemplary embodiment shown in FIG. 3 in that the supporting part 50 is positively fixed on the anchor bolt 27.
  • the support part 50 is designed as a sickle disk with an open recess 56 which is pushed laterally onto the anchor bolt with the open end.
  • the anchor bolt 27 has a circumferential groove 54, in which the inner contour of the recess 56 of the sickle disk 50 engages in a form-fitting manner.
  • the crescent disk 50 pushed onto the anchor bolt is secured in its position perpendicular to the anchor bolt by the recess 52 of the slider 34.
  • the path length by which the anchor bolt is displaced in the axial direction when the solenoid valve is opened and closed is significantly smaller than the depth of the recess 52, so that the sickle disk 50 cannot accidentally slip out of its position on the anchor bolt 27.
  • FIG. 5 shows a third exemplary embodiment, which shows a modification of the exemplary embodiment illustrated in FIG. 4.
  • the support part 50 is again designed as a sickle disk, which is pushed with the open end, not shown, onto a section 72 of the anchor bolt 27.
  • the diameter of the section 72 is made smaller than the diameter of the section of the anchor bolt 27 guided in the slider 34 and is delimited from it by a circumferential shoulder 71.
  • the return spring 35 is supported at one end on the anchor plate 28. The return spring 35 presses the other end Sickle disc 50 against the circumferential shoulder 71 formed on the anchor bolt 27.
  • the anchor assembly can be inserted as a preassembled unit in the slide 34, the anchor bolt 27 being inserted into the opening 68 and the sickle disc 50 at least partially penetrating into the recess 52. Due to the inner contour of the recess 52, the sickle plate 50 is secured against lateral slipping off the anchor bolt.

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

Abstract

The invention relates to an electromagnetic valve for controlling an injection valve of an internal combustion engine, comprising an electromagnet (29), a moving armature with an armature plate (28) and an armature pin (27); and a control valve member (25) which is moved with the armature and which interacts with a valve seat (24), for opening and closing a fuel drainage channel (17) of a control pressure chamber (14) of the injection valve (1). The armature plate (28) is mounted in such a way that under the influence of its inert mass, the armature plate can slide on the armature pin in the closing direction of the control valve member (25), in the opposite direction to the clamping force of a return spring (35) which acts on the armature plate. The inventive electromagnetic valve also comprises a hydraulic damping device with which the post-oscillation of the armature plate (28) after its dynamic displacement on the armature pin (27) can be damped. In order to simplify the assembly and reduce a disadvantageous post-oscillation process of the armature plate, the invention provides that the return spring (35) is supported on a support part (50) which is situated on the armature pin (27) and which is moved with said armature pin, by the end (62) of the return spring facing away from the armature plate (28). Said support part (50) also forms part (57) of the damping device.

Description

Magnetventil zur Steuerung eines Einspritzventils einer BrennkraftmaschineSolenoid valve for controlling an injection valve of an internal combustion engine
Stand der TechnikState of the art
Die Erfindung betrifft ein Magnetventil zur Steuerung eines Einspritzventils einer Brennkraftmaschine nach dem Oberbegriff des Anspruchs 1.The invention relates to a solenoid valve for controlling an injection valve of an internal combustion engine according to the preamble of claim 1.
Ein solches, beispielsweise aus der DE 197 08 104 AI bekanntes Magnetventil wird zur Steuerung des Kraftstoffdrucks im Steuerdruckraum eines Einspritzventils, beispielsweise eines Injektors einer Common-Rail-Einspritzanlage verwandt. Über den Kraftstoffdruck im Steuerdruckraum wird die Bewegung eines Ventilkolbens gesteuert, mit dem eine Einspritzöffnung des Einspritzventils geöffnet oder geschlossen wird. Das be- kannte Magnetventil weist einen in einem Gehäuseteil angeordneten Elektromagneten, einen beweglichen Anker und ein mit dem Anker bewegtes, von einer Schließfeder in Schließrichtung beaufschlagtes Steuerventilglied auf, das mit einem Ventilsitz des Magnetventils zusammenwirkt und so den Kraft- stoffabfluß aus dem Steuerdruckraum steuert. Ein bekannterSuch a solenoid valve, known for example from DE 197 08 104 AI, is used to control the fuel pressure in the control pressure chamber of an injection valve, for example an injector of a common rail injection system. The movement of a valve piston, with which an injection opening of the injection valve is opened or closed, is controlled via the fuel pressure in the control pressure chamber. The known solenoid valve has an electromagnet arranged in a housing part, a movable armature and a control valve member which is moved with the armature and acted upon by a closing spring in the closing direction and which cooperates with a valve seat of the solenoid valve and thus controls the fuel outflow from the control pressure chamber. A friend
Nachteil der Magnetventile besteht im sogenannten Ankerprel- len. Beim Abschalten des Magneten wird der Anker und mit ihm das Steuerventilglied von der Schließfeder des Magnetventils zum Ventilsitz hin beschleunigt, um einen Kraftstoffablauf- kanal aus dem Steuerdruckraum zu verschließen. Der Aufprall des Steuerventilgliedes am Ventilsitz kann ein nachteiliges Schwingen und/oder Prellen des Steuerventilgliedes am Ventilsitz zur Folge haben, wodurch die Steuerung des Ein- spritzvorgangs beeinträchtigt wird. Bei dem aus der DE 197 08 104 AI bekannten Magnetventil ist deshalb der Anker zweiteilig mit einem Ankerbolzen und einer auf dem Ankerbolzen gleitverschiebbar gelagerten Ankerplatte ausgeführt, so daß sich die Ankerplatte beim Aufprall des Steuerventilgliedes auf den Ventilsitz gegen die Spannkraft einer Rückholfeder weiterbewegt . Die Rückholfeder befördert die Ankerplatte anschließend wieder in ihre Ausgangsposition an einem Anschlag des Ankerbolzens zurück. Durch die zweiteilige Ausführung des Ankers wird zwar die effektiv abge- bremste Masse und damit die das Prellen verursachende kinetische Energie des auf den Ventilsitz auftreffenden Ankers verringert, jedoch kann die Ankerplatte nach dem Schließen des Magnetventils auf dem Ankerbolzen in nachteiliger Weise nachschwingen. Da ein Ansteuern des Magnetventils erst wie- der zu einer definierten Einspritzmenge führt, wenn die Ankerplatte nicht mehr nachschwingt, sind Maßnahmen erforderlich, um das Nachschwingen der Ankerplatte zu reduzieren. Dies ist insbesondere zur Darstellung kurzer zeitlicher Abstände zwischen beispielsweise einer Vor- und Haupteinsprit- zung erforderlich.The disadvantage of solenoid valves is the so-called anchor bounce. When the magnet is switched off, the armature, and with it the control valve member, is accelerated from the closing spring of the solenoid valve to the valve seat in order to close a fuel outlet channel from the control pressure chamber. The impact of the control valve member on the valve seat can result in disadvantageous swinging and / or bouncing of the control valve member on the valve seat, as a result of which the control of the injection process is impaired. In the solenoid valve known from DE 197 08 104 AI, the armature is therefore made in two parts with an armature bolt and an armature plate slidably mounted on the armature bolt, so that the armature plate moves further against the tension force of a return spring when the control valve member impacts the valve seat. The return spring then conveys the anchor plate back to its starting position at a stop of the anchor bolt. The two-part design of the armature reduces the effectively braked mass and thus the kinetic energy causing the bouncing of the armature hitting the valve seat, but the armature plate can disadvantageously oscillate on the armature bolt after the solenoid valve has closed. Since actuation of the solenoid valve only leads to a defined injection quantity when the armature plate no longer oscillates, measures are necessary to reduce the oscillation of the armature plate. This is particularly necessary to show short time intervals between, for example, a pre-injection and a main injection.
In der DE 197 08 104 AI wird zur Lösung dieses Problems vorgeschlagen, einen Überhubanschlag zu verwenden, welcher die Weglänge begrenzt, um den sich die Ankerplatte auf dem An- kerbolzen verschieben kann. Der Überhubanschlag ist zwischen der Ankerplatte und einem den Ankerbolzen führenden Gleitstück ortsfest im Gehäuse des Magnetventils angeordnet. Bei einer Annäherung der Ankerplatte an den Überhubanschlag entsteht zwischen den einander zugewandten ebenen Seiten der Ankerplatte und des Überhubanschlags ein hydraulischer Dämpfungsraum. Der in dem Dämpfungsraum enthaltene Kraftstoff erzeugt eine Kraft, die der Bewegung der Ankerplatte entgegenwirkt . Das Nachschwingen der Ankerplatte wird daher stark gedämpft . Mittels des Überhubanschlags wird zwar die Nach- schwingzeit der Ankerplatte verkürzt, jedoch muß der erforderliche Überhubweg der Ankerplatte während der Montage des Magnetventils im Gehäuse des Magnetventils eingestellt werden. Dies macht eine aufwendige Änderung des Herstellungsverfahrens erforderlich, da die Fertigungseinrichtungen entsprechend nachgerüstet werden müssen.To solve this problem, DE 197 08 104 AI proposes using an overstroke stop which limits the path length by which the anchor plate can move on the anchor bolt. The overstroke stop is arranged in a fixed manner in the housing of the solenoid valve between the anchor plate and a slide piece guiding the anchor bolt. When the anchor plate approaches the overtravel stop, a hydraulic damping space is created between the mutually facing flat sides of the anchor plate and the overtravel stop. The fuel contained in the damping chamber generates a force that counteracts the movement of the anchor plate. The swinging of the anchor plate is therefore strongly damped. By means of the overstroke stop, the reverberation time of the anchor plate is shortened, but the required overstroke distance of the anchor plate must be during the installation of the Solenoid valve can be set in the housing of the solenoid valve. This requires a complex change in the manufacturing process, since the manufacturing facilities have to be retrofitted accordingly.
Vorteile der ErfindungAdvantages of the invention
Das erfindungsgemäße Magnetventil mit den kennzeichnenden Merkmalen des Anspruchs 1 vermeidet die im Stand der Technik auftretenden Nachteile. Vorteilhaft kann der Anker mit Ankerplatte, Ankerbolzen, Rückholfeder und Überhubanschlag außerhalb der Montagelinie des Einspritzventils vormontiert und der erforderliche Verschiebeweg der Ankerplatte auf dem Ankerbolzen außerhalb des Gehäuses des Einspritzventils ein- gestellt werden. Die vormontierte Ankerbaugruppe kann dann anschließend in das Gehäuse des Magnetventils eingebaut werden. Ein aufwendiger Umbau der Montagelinie ist nicht erforderlich. Dadurch, daß sich die Rückholfeder, welche die Ankerplatte mit einem ersten Ende in ihrer Ruhelage gegen ei- nen ersten Anschlag an dem Ankerbolzen andrückt, mit dem zweiten Ende nicht ortsfest im Magnetventilgehäuse abstützt, sondern an einem an dem Ankerbolzen festgelegten und mit dem Ankerbolzen bewegten Stützteil, wird außerdem vorteilhaft erreicht, daß die Rückholfeder der auf den Ankerbolzen ein- wirkenden Schließfeder des Magnetventils nicht entgegenwirkt. Die Federspannkraft der Schließfeder des Magnetventils kann daher geringer ausgelegt werden. Da die Rückholfeder der Schließfeder nicht mehr entgegenwirkt, hat die Rückholfeder keinen Einfluß mehr auf das dynamische Verhalten des Ankerbolzens.The solenoid valve according to the invention with the characterizing features of claim 1 avoids the disadvantages occurring in the prior art. The armature with the armature plate, armature bolt, return spring and overstroke stop can advantageously be preassembled outside the assembly line of the injection valve and the required displacement path of the armature plate on the armature bolt can be set outside the housing of the injection valve. The pre-assembled armature assembly can then be installed in the housing of the solenoid valve. A complex conversion of the assembly line is not necessary. Characterized in that the return spring, which presses the anchor plate with a first end in its rest position against a first stop on the anchor bolt, is not fixedly supported with the second end in the solenoid valve housing, but rather on one fixed to the anchor bolt and moved with the anchor bolt Supporting part is also advantageously achieved that the return spring does not counteract the closing spring of the solenoid valve acting on the anchor bolt. The spring tension of the closing spring of the solenoid valve can therefore be designed to be lower. Since the return spring no longer counteracts the closing spring, the return spring no longer has any influence on the dynamic behavior of the anchor bolt.
Vorteilhafte Ausführungsbeispiele und Weiterbildungen der Erfindung werden durch die in den Unter nsprüchen enthaltenen Merkmale ermöglicht. Besonders vorteilhaft ist es, den Ankerbolzen in einer Öffnung eines in dem Gehäuse des Magnetventils ortsfest angeordneten Gleitstücks gleitverschiebbar zu lagern und die der Ankerplatte zugewandten Seite des Gleitstücks mit einer Aus- nehmung zu versehen, in welcher das an dem Ankerbolzen festgelegte Stützteil angeordnet ist, wobei die Außenkontur des Stützteils durch einen Spalt von der Innenkontur der Ausnehmung beabstandet ist. Durch diese Maßnahmen wird erreicht, daß durch die Annäherung des Stützteils an die Innenwand der Ausnehmung des Gleitstücks ein hydraulischer Dämpfungsraum entsteht und der zwischen dem Stützteil und der Ausnehmung komprimierte Kraftstoff den Aufprall des mit dem Ankerbolzen gekoppelten Steuerventilgliedes auf den Ventilsitz zusätzlich dämpft .Advantageous exemplary embodiments and developments of the invention are made possible by the features contained in the subclaims. It is particularly advantageous for the anchor bolt to be slidably mounted in an opening of a slider which is fixed in the housing of the solenoid valve and for the side of the slider facing the anchor plate to be provided with a recess in which the support part fixed to the anchor bolt is arranged, wherein the outer contour of the support part is spaced from the inner contour of the recess by a gap. These measures ensure that the approach of the support part to the inner wall of the recess of the slider creates a hydraulic damping space and the compressed fuel between the support part and the recess additionally dampens the impact of the control valve member coupled to the anchor bolt on the valve seat.
Zeichnungendrawings
Ausführungsbeispiele der Erfindung sind in den Zeichnungen dargestellt und werden in der nachfolgenden Beschreibung er- läutert. Es zeigtExemplary embodiments of the invention are shown in the drawings and are explained in the following description. It shows
Fig. 1 einen Querschnitt durch den oberen Teil eines aus dem Stand der Technik bekannten Kraftstoffeinspritzventils mit einem Magnetventil, Fig. 2 einen Teilbereich des aus dem Stand der Technik be- kannten Magnetventils mit Überhubeinstellscheibe,1 shows a cross section through the upper part of a fuel injection valve known from the prior art with a solenoid valve, FIG. 2 shows a partial area of the solenoid valve known from the prior art with an over-stroke adjusting disk,
Fig. 3 einen Querschnitt durch die Ankerbaugruppe mit Gleitstück nach einem ersten Ausführungsbeispiel der Erfindung, Fig. 4 einen Querschnitt durch die Ankerbaugruppe mit Gleitstück nach einem zweiten Ausführungsbeispiel der Erfindung. Fig. 5 einen Querschnitt durch die Ankerbaugruppe mit Gleitstück nach einem dritten Ausführungsbeispiel der Erfindung.3 shows a cross section through the armature assembly with slide piece according to a first embodiment of the invention, FIG. 4 shows a cross section through the armature assembly with slide piece according to a second embodiment of the invention. Fig. 5 shows a cross section through the armature assembly with slider according to a third embodiment of the invention.
Beschreibung der AusführungsbeispieleDescription of the embodiments
Fig. 1 zeigt den oberen Teil eines aus dem Stand der Technik bekannten Kraftstoffeinspritzventils 1, welches zur Verwendung in einer Kraftstoffeinspritzanlage bestimmt ist, die mit einem Kraftstoffhochdruckspeicher ausgerüstet ist, der durch eine Hochdruckförderpumpe kontinuierlich mit Hochdruckkraftstoff versorgt wird. Das dargestellte Kraftstoffeinspritzventil 1 weist ein Ventilgehäuse 4 mit einer Längsbohrung 5 auf, in der ein Ventilkolben 6 angeordnet ist, der mit seinem einen Ende auf eine in einem nicht dargestellten Düsenkörper angeordnete Ventilnadel einwirkt . Die Ventilnadel ist in einem Druckraum angeordnet, der über eine Druckbohrung 8 mit unter Hochdruck stehendem Kraftstoff versorgt ist. Bei einer Öffnungshubbewegung des Ventilkolbens 6 wird die Ventilnadel durch den ständig an einer Druckschulter der Ventilnadel angreifenden Kraft- Stoffhochdruck im Druckraum entgegen der Schließkraft einer Feder angehoben. Durch eine dann mit dem Druckraum verbundene Einspritzöffnung erfolgt die Einspritzung des Kraftstoffs in den Brennraum der Brennkraftmaschine. Durch Absenken des Ventilkolbens 6 wird die Ventilnadel in Schließrichtung in den Ventilsitz des Einspritzventils gedrückt und der Einspritzvorgang beendet .Fig. 1 shows the upper part of a fuel injection valve 1 known from the prior art, which is for use is determined in a fuel injection system which is equipped with a high-pressure fuel reservoir which is continuously supplied with high-pressure fuel by a high-pressure feed pump. The fuel injector 1 shown has a valve housing 4 with a longitudinal bore 5, in which a valve piston 6 is arranged, which acts with its one end on a valve needle arranged in a nozzle body, not shown. The valve needle is arranged in a pressure chamber which is supplied with fuel under high pressure via a pressure bore 8. During an opening stroke movement of the valve piston 6, the valve needle is raised against the closing force of a spring by the high force of fuel which acts constantly on a pressure shoulder of the valve needle in the pressure chamber. The fuel is then injected into the combustion chamber of the internal combustion engine through an injection opening which is then connected to the pressure chamber. By lowering the valve piston 6, the valve needle is pressed into the valve seat of the injection valve in the closing direction and the injection process is ended.
Wie in Fig. 1 zu erkennen ist, wird der Ventilkolben 6 an seinem von der Ventilnadel abgewandten Ende in einer Zylinderbohrung 11 geführt, die in einem Ventilstück 12 eingebracht ist, welches in das Ventilgehäuse 4 eingesetzt ist. In der Zylinderbohrung 11 schließt die Stirnseite 13 desAs can be seen in FIG. 1, the valve piston 6 is guided at its end facing away from the valve needle in a cylinder bore 11 which is introduced into a valve piece 12 which is inserted into the valve housing 4. In the cylinder bore 11, the end face 13 of the
Ventilkolbens 6 einen Steuerdruckraum 14 ein, der über einen Zulaufkanal mit einem Kraftstoffhochdruckanschluß verbunden ist. Der Zulaufkanal ist im wesentlichen dreiteilig ausgebildet . Eine radial durch die Wand des Ventilstücks 12 füh- rende Bohrung, deren Innenwände auf einem Teil ihrer Länge eine Zulaufdrossel 15 ausbilden, ist mit einem das Ventilstück umfangsseitig umgebenden Ringraum 16 ständig verbunden, welcher Ringraum wiederum über einen in den Zulaufkanal eingeschobenen Kraftstoffilter in ständiger Verbindung mit dem Kraftstoffhochdruckanschluß eines in das Ventilgehäuse 4 einschraubbaren Anschlußstutzens 9 steht. Der Ringraum 16 ist über einen Dichtring 39 zur Längsbohrung 5 abgedichtet. Über die Zulaufdrossel 15 ist der Steuerdruckraum 14 dem im Kraftstoffhochdruckspeicher herrschenden hohen Kraftstoffdruck ausgesetzt. Koaxial zum Ventilkolben 6 zweigt aus dem Steuerdruckraum 14 eine im Ventilstück 12 verlaufende Bohrung ab, die einen mit einer Ablaufdrossel 18 versehenen Kraftstoffablaufkanal 17 bildet, der in einen Entlastungsraum 19 einmündet, der mit einem Kraftstoffniederdruckan- schluß 10 verbunden ist, welcher wiederum in nicht weiter dargestellter Weise mit einem Kraftstoffrücklauf des Einspritzventils 1 verbunden ist. Der Austritt des Kraft- stoffablaufkanals 17 aus dem Ventilstück 12 erfolgt im Bereich eines kegelförmig angesenkten Teiles 21 der außenliegenden Stirnseite des Ventilstückes 12. Das Ventilstück 12 ist in einem Flanschbereich 22 fest über ein Schraubglied 23 mit dem Ventilgehäuse 4 verspannt .Valve piston 6 a control pressure chamber 14, which is connected via an inlet channel to a high-pressure fuel connection. The inlet channel is essentially made up of three parts. A bore leading radially through the wall of the valve piece 12, the inner walls of which form an inlet throttle 15 over part of its length, is constantly connected to an annular space 16 surrounding the valve piece on the circumference, which annular space in turn is in constant connection via a fuel filter inserted into the inlet channel with the high-pressure fuel connection of a connection piece 9 which can be screwed into the valve housing 4. The annular space 16 is sealed to the longitudinal bore 5 via a sealing ring 39. The control pressure chamber 14 is exposed to the high fuel pressure prevailing in the high-pressure fuel reservoir via the inlet throttle 15. Coaxial to the valve piston 6 branches off from the control pressure chamber 14, a bore running in the valve piece 12, which forms a fuel outlet channel 17 provided with an outlet throttle 18, which opens into a relief chamber 19, which is connected to a low-pressure fuel connection 10, which in turn is not further illustrated manner is connected to a fuel return of the injection valve 1. The fuel drain channel 17 emerges from the valve piece 12 in the region of a conically countersunk part 21 of the outer end face of the valve piece 12. The valve piece 12 is firmly clamped to the valve housing 4 in a flange area 22 via a screw member 23.
In dem kegelförmigen Teil 21 ist ein Ventilsitz 24 ausgebildet, mit dem ein Steuerventilglied 25 eines das Einspritz- ventil steuernden Magnetventils 30 zusammen wirkt. Das Steuerventilglied 25 ist mit einem zweiteiligen Anker in Form eines Ankerbolzens 27 und einer Ankerplatte 28 gekoppelt, welcher Anker mit einem Elektromagneten 29 des Magnetventils 30 zusammen wirkt. Das Magnetventil 30 umfaßt weiterhin ein den Elektromagneten bergendes Gehäuseteil 60, das mit dem Ventilgehäuse 4 über schraubbare Verbindungsmittel 7 fest verbunden ist . Bei dem bekannten Magnetventil ist die Ankerplatte 28 unter Einwirkung ihrer trägen Masse gegen die Vorspannkraft einer Rückholfeder 35 dynamisch verschiebbar auf dem Ankerbolzen 27 gelagert und wird durch diese Rückholfeder im Ruhezustand gegen eine am Ankerbolzen festgelegte Sichelscheibe 26 gedrückt. Mit ihrem anderen Ende stützt sich die Rückholfeder 35 gehäusefest an einem Flansch 32 eines den Ankerbolzen 27 führenden Gleitstücks 34 ab, das mit die- sem Flansch zwischen einer auf das Ventilstück 12 aufgelegten Distanzscheibe 38 und dem Schraubglied 23 im Ventilge- häuse fest eingespannt ist. Der Ankerbolzen 27 und mit ihm die Ankerscheibe 28 und das mit dem Ankerbolzen gekoppelte Steuerventilglied 25 sind ständig durch eine sich gehäusefest abstützende Schließfeder 31 in Schließrichtung beauf- schlagt, so daß das Steuerventilglied 25 normalerweise in Schließstellung am Ventilsitz 24 anliegt. Bei Erregung des Elektromagneten wird die Ankerplatte 28 vom Elektromagneten angezogen und dabei der Ablaufkanal 17 zum Entlastungsraum 19 hin geöffnet . Zwischen dem Steuerventilglied 25 und der Ankerplatte 28 befindet sich eine Ringschulter 33 am Ankerbolzen 27, die bei erregtem Elektromagneten am Flansch 32 anschlägt und so den Öffnungshub des Steuerventilglieds 25 begrenzt. Zur Einstellung des Öffnungshubes dient die zwischen dem Flansch 32 und dem Ventilstück 12 angeordnete Di- stanzscheibe 38. Bei anderen bekannten Magnetventilen wird der Öffnungshub des Steuerventilgliedes 25 durch ein zwischen der Ankerplatte 28 und dem Elektromagneten 29 angeordnetes Anschlagelement eingestellt .A valve seat 24 is formed in the conical part 21, with which a control valve member 25 of a solenoid valve 30 controlling the injection valve interacts. The control valve member 25 is coupled to a two-part armature in the form of an armature bolt 27 and an armature plate 28, which armature interacts with an electromagnet 29 of the solenoid valve 30. The solenoid valve 30 further comprises a housing part 60 which accommodates the electromagnet and which is firmly connected to the valve housing 4 via screwable connecting means 7. In the known solenoid valve, the anchor plate 28 is dynamically slidably supported on the anchor bolt 27 under the action of its inertial mass against the biasing force of a return spring 35 and is pressed by this return spring in the idle state against a sickle disk 26 fixed on the anchor bolt. With its other end, the return spring 35 is supported in a housing-fixed manner on a flange 32 of a sliding piece 34 guiding the anchor bolt 27, which with this flange lies between a spacer disk 38 placed on the valve piece 12 and the screw member 23 in the valve housing is firmly clamped. The armature bolt 27 and with it the armature disk 28 and the control valve member 25 coupled to the armature bolt are constantly acted upon in the closing direction by a closing spring 31 which is fixed to the housing, so that the control valve member 25 normally bears against the valve seat 24 in the closed position. When the electromagnet is excited, the armature plate 28 is attracted by the electromagnet and the drain channel 17 is opened toward the relief chamber 19. Between the control valve member 25 and the armature plate 28 there is an annular shoulder 33 on the armature bolt 27 which strikes the flange 32 when the electromagnet is excited and thus limits the opening stroke of the control valve member 25. The spacer 38 arranged between the flange 32 and the valve piece 12 serves to adjust the opening stroke. In other known solenoid valves, the opening stroke of the control valve member 25 is adjusted by a stop element arranged between the armature plate 28 and the electromagnet 29.
Das Öffnen und Schließen des Einspritzventils wird wie nachfolgend beschrieben von dem Magnetventil 30 gesteuert. Der Ankerbolzen 27 ist ständig durch die Schließfeder 31 in Schließrichtung beaufschlagt, so daß das Steuerventilglied 25 bei nicht erregtem Elektromagneten in Schließstellung am Ventilsitz 24 anliegt und der Steuerdruckraum 14 zur Entlastungsseite 19 hin verschlossen ist, so daß sich dort über den Zulaufkanal sehr schnell der hohe Druck aufbaut, der auch im Kraftstoffhochdruckspeicher ansteht. Über die Fläche der Stirnseite 13 erzeugt der Druck im Steuerdruckraum 14 eine Schließkraft auf den Ventilkolben 6 und die damit inThe opening and closing of the injection valve is controlled by the solenoid valve 30 as described below. The anchor bolt 27 is constantly acted upon by the closing spring 31 in the closing direction, so that the control valve member 25 rests on the valve seat 24 in the closed position when the electromagnet is not energized, and the control pressure chamber 14 is closed to the relief side 19, so that the high one there via the inlet channel very quickly Builds up pressure that is also present in the high-pressure fuel reservoir. The pressure in the control pressure chamber 14 generates a closing force on the valve piston 6 and thus in FIG
Verbindung stehende Ventilnadel, die größer ist als die andererseits in Öffnungsrichtung in Folge des anstehenden Hochdrucks wirkenden Kräfte . Wird der Steuerdruckraum 14 durch Öffnen des Magnetventils zur Entlastungsseite 19 hin geöffnet, baut sich der Druck in dem geringen Volumen desConnected valve needle, which is greater than the forces acting on the other hand in the opening direction due to the high pressure. If the control pressure chamber 14 is opened towards the relief side 19 by opening the solenoid valve, the pressure builds up in the small volume of the
Steuerdruckraumes 14 sehr schnell ab, da dieser über die Zu- laufdrossel 15 von der Hochdruckseite abgekoppelt ist. Infolgedessen überwiegt die auf die Ventilnadel in Öffnungs- richtung wirkende Kraft aus dem an der Ventilnadel anstehenden Kraftstoffhochdruck, so daß die Ventilnadel nach oben bewegt und dabei die wenigstens eine Einspritzöffnung zurControl pressure chamber 14 very quickly, since this via the throttle 15 is decoupled from the high pressure side. As a result, the force acting on the valve needle in the opening direction outweighs the high fuel pressure applied to the valve needle, so that the valve needle moves upwards and at the same time the at least one injection opening toward it
Einspritzung geöffnet wird. Schließt jedoch das Magnetventil 30 den Kraftstoffablaufkanal 17, kann der Druck im Steuerdruckraum 14 durch den über den Zulaufkanal 15 nachfließenden Kraftstoff wieder aufgebaut werden, so daß die ursprüng- liehe Schließkraft ansteht und die Ventilnadel des Kraftstoffeinspritzventils schließt.Injection is opened. However, if the solenoid valve 30 closes the fuel outlet channel 17, the pressure in the control pressure chamber 14 can be built up again by the fuel flowing in via the inlet channel 15, so that the original closing force is applied and the valve needle of the fuel injection valve closes.
Beim Schließen des Magnetventils drückt die Schließfeder 31 den Ankerbolzen 27 mit dem Steuerventilglied 25 schlagartig gegen den Ventilsitz 24. Ein nachteiliges Abprellen oderWhen the solenoid valve closes, the closing spring 31 suddenly presses the anchor bolt 27 with the control valve member 25 against the valve seat 24. A disadvantageous bouncing off or
Nachschwingen des Steuerventilgliedes entsteht dadurch, daß der Aufschlag des Ankerbolzen am Ventilsitz eine elastische Verformung desselben bewirkt, welche als Energiespeicher wirkt, wobei ein Teil der Energie wiederum auf das Steuerven- tilglied übertragen wird, das dann zusammen mit dem Ankerbolzen vom Ventilsitz 24 abprellt. Das in Fig. 1 gezeigte bekannte Magnetventil verwendet daher einen zweiteiligen Anker mit einer vom Ankerbolzen 27 abgekoppelten Ankerplatte 28. Auf diese Weise läßt sich zwar die insgesamt auf den Ventil- sitz auftreffende Masse verringern, jedoch kann die Ankerplatte 28 in nachteiliger Weise nachschwingen. Aus diesem Grund ist bei dem bekannten Magnetventil eine zwischen der Ankerplatte 28 und der Gleithülse 34 angeordnete Überhubein- stellscheibe 70 vorgesehen, wie dies in Fig. 2 dargestellt ist. Die Überhubeinstellscheibe 70 beschränkt den Verschiebeweg der Ankerplatte 28 auf dem Ankerbolzen 27 auf das Maß d. Das Nachschwingen der Ankerplatte 28 wird durch die Überhubeinstellscheibe 70 reduziert und die Ankerplatte 28 gelangt schneller wieder in ihre Ausgangslage am Anschlag 26 zurück. Die Distanzscheibe 38, das Gleitstück 34 und die Überhubeinstellscheibe 70 werden im Magnetventilgehäuse ortsfest einge- spannt. Der Überhubweg d muß bei den im Stand der Technik bekannten Magnetventilen daher während der Montage im Magnet- ventilgehäuse über die Dicke der verwandten Überhubeinstell- scheibe eingestellt werden. In manchen Ausfuhrungsformen be- einflußt die Dicke der Überhubeinstellscheibe aber auch den Abstand der Ankerplatte 28 vom Elektromagneten 29. Dies ist der Fall, wenn beispielsweise die Stirnseite des Magnetventilgehäuses 60 gegen den Flansch 32 verspannt wird. In diesen Fällen wird an Stelle der Überhubeinstellscheibe eine innere und eine äußere Scheibe verwandt. Die Fertigung des Magnetventils und des mit dem Magnetventil versehenen Einspritzventils ist daher recht aufwendig und kompliziert. Eine Voreinstellung des Überhubweges beziehungsweise des Verschiebeweges d der Ankerplatte 28 auf dem Ankerbolzen 27 außerhalb des Ma- gentventilgehäuses 60 ist nicht möglich.The control valve member reverts as a result of the impact of the anchor bolt on the valve seat causing an elastic deformation thereof, which acts as an energy store, part of the energy being transferred to the control valve member, which then bounces off the valve seat 24 together with the anchor bolt. The known solenoid valve shown in FIG. 1 therefore uses a two-part armature with an armature plate 28 decoupled from the armature pin 27. In this way, the mass impinging on the valve seat as a whole can be reduced, but the armature plate 28 can oscillate in a disadvantageous manner. For this reason, an overstroke adjusting disk 70 arranged between the armature plate 28 and the sliding sleeve 34 is provided in the known solenoid valve, as shown in FIG. 2. The overtravel 70 limits the displacement of the anchor plate 28 on the anchor bolt 27 to the dimension d. The swinging of the anchor plate 28 is reduced by the overtravel 70 and the anchor plate 28 returns to its initial position at the stop 26 faster. The spacer 38, the slider 34 and the overtravel 70 are fixed in place in the solenoid valve housing. stressed. The overtravel distance d in the solenoid valves known in the prior art must therefore be set during the assembly in the solenoid valve housing via the thickness of the related overtravel adjusting disc. In some embodiments, however, the thickness of the overtravel adjusting disc also influences the distance of the armature plate 28 from the electromagnet 29. This is the case when, for example, the end face of the solenoid valve housing 60 is clamped against the flange 32. In these cases, an inner and an outer disc are used instead of the overtravel adjusting disc. The manufacture of the solenoid valve and the injection valve provided with the solenoid valve is therefore quite complex and complicated. It is not possible to preset the overstroke path or the displacement path d of the armature plate 28 on the armature bolt 27 outside the solenoid valve housing 60.
Fig. 3 zeigt ein erstes Ausführungsbeispiel des erfindungsgemäßen Magnetventils. Dargestellt ist nur das Gleitstück 34 und der Anker mit Ankerbolzen 27, Ankerplatte 28 und Rückhol- feder 35. Gleiche Teile sind mit gleichen Bezugszeichen versehen. Die dargestellte Ankerbaugruppe kann beispielsweise in das in Fig. 1 gezeigte Magnetventilgehäuse 60 eingesetzt werden. Ein wichtiger Unterschied zu der in Fig. 2 gezeigten bekannten Anordnung besteht darin, daß an Stelle der ortsfest im Magnetventilgehäuse angeordneten Überhubeinstellscheibe ein Stützteil 50 vorgesehen ist, das fest mit dem Ankerbolzen 27 verbunden ist. Als Stützteil kann beispielsweise eine an dem Ankerbolzen 27 festgelegte Scheibe vorgesehen sein. In dem Ausführungsbeispiel von Fig. 3 wird die Scheibe auf den Ankerbolzen 27 aufgeschoben und anschließend mit dem Ankerbolzen durch beispielsweise Schweißen oder Kleben fest verbunden. Auch andere Befestigungsarten wir Aufschrumpfen sind möglich. In einem bevorzugten Ausführungsbeispiel ist das Stützteil 50 auf der von der Ankerplatte abgewandten Seite 59 mit dem Ankerbolzen 27 verschweißt. Die Schweißnaht 51 auf der Unterseite 59 des Stützteils 50 ist in Fig. 1 erkennbar. Die Rückholfeder 35 stützt sich mit ihrem einen Ende 61 an der Ankerplatte 28 ab und mit ihrem anderen Ende 62 an derjenigen Seite 57 des Stützteils 50, welche der Ankerplatte 28 zugewandt ist .Fig. 3 shows a first embodiment of the solenoid valve according to the invention. Only the slider 34 and the anchor with anchor bolt 27, anchor plate 28 and return spring 35 are shown. The same parts are provided with the same reference numerals. The armature assembly shown can be used, for example, in the solenoid valve housing 60 shown in FIG. 1. An important difference from the known arrangement shown in FIG. 2 is that a support part 50 is provided in place of the overtravel adjusting disk which is arranged in a fixed manner in the solenoid valve housing and is firmly connected to the anchor bolt 27. For example, a disk fixed to the anchor bolt 27 can be provided as the supporting part. In the embodiment of FIG. 3, the washer is pushed onto the anchor bolt 27 and then firmly connected to the anchor bolt by, for example, welding or gluing. Other types of fastening such as shrinking on are also possible. In a preferred embodiment, the support part 50 is welded to the anchor bolt 27 on the side 59 facing away from the anchor plate. The weld seam 51 on the underside 59 of the support part 50 can be seen in FIG. 1. The return spring 35 is supported with one end 61 on the anchor plate 28 and with its other end 62 on the side 57 of the support part 50 which faces the anchor plate 28.
Bei der Herstellung der Ankerbaugruppe wird zunächst die Ankerplatte 28 auf den Ankerbolzen 27 aufgeschoben, bis die Ankerplatte an einem Kopf 55 des Ankerbolzens anschlägt. Der Kopf 55 ersetzt die Sichelscheibe 26 in Fig. 1 und 2 und dient wie diese als Anschlag für die Ankerplatte. Anschließend wird die Rückholfeder 35 über den Führungsstutzen 65 der Ankerplatte 28 geschoben, bis sie mit dem Ende 61 an der Ankerplatte anliegt . Zuletzt wird das scheibenförmige Stützteil 50 so weit auf den Ankerbolzen 27 geschoben, daß zwischen den einander zugewandten Seiten 57 und 58 des Stützteils 50 und des Führungsstutzens 65 der erforderliche Überhubweg d verbleibt. Schließlich wird das Stützteil 50 in dieser Position am Ankerbolzen 27 festgelegt. Die aus Ankerbolzen 27, Ankerplatte 28, Rückholfeder 35 und Stützteil 50 bestehende Anker- baugruppe wird anschließend in das Gleitstück 34 eingesetzt. Dabei wird der Ankerbolzen 27 in eine zentrale Bohrung 68 des Gleitstücks 34 eingesetzt. Das Gleitstück 34 kann bereits mit dem Flansch 36 im Gehäuse 60 des Magnetventils eingespannt sein. Wie in Fig. 3 weiterhin zu erkennen ist, ist abweichend von der in Fig. 2 dargestellten bekannten Anordnung keine Ringschulter 33 vorgesehen, welche durch einen Anschlag an dem Gleitstück 34 den Öffnungshub des Ankerbolzens begrenzt. Statt dessen wird der Öffnungshub durch einen Anschlag des Ankerbolzenkopfes 55 am Elektromagneten oder einem Vorsprung des Elektromagneten begrenzt. Dies ist erforderlich, damit der Ankerbolzen 27 in Fig. 3 von oben in das Gleitstück 34 eingesetzt werden kann. Wie in Fig. 3 weiterhin erkennbar ist, weist die dem Stützteil 50 zugewandte Seite des Gleitstücks 34 eine Ausnehmung 52 auf, in welche das Stützteil eingreift. Wie bereits oben ausführlich beschrieben wurde, wirkt im eingebauten Zustand das untere Ende 67 des Ankerbolzens 27 auf das Steuerventilglied 25 ein, welches bei nicht erregtem Elektromagneten durch die Schließkraft der Feder 31 gegen den Ventilsitz 24 gedrückt wird. In dieser Lage ist die von der Ankerplatte 28 abgewandte Seite 59 des Stützteils 50 und die Schweißnaht 51 von der Innenwand der Ausnehmung 52 durch einen Spalt beabstandet. Durch diese Maßnahme wird beim Schließen des Magnetventils ein Anstoßen des mit dem Ankerbolzen bewegten Stützteils 50 an der Innenwand der Ausnehmung 52 verhindert, da ein solches Anstoßen zur Folge haben könnte, daß das Steuerventilglied 25 am Ventilsitz 24 nicht zur Anlage gelangt. Die Ausnehmung 52 ist daher so gestaltet, daß sie auch die Schweißnaht 51 aufnehmen kann und immer ein Stück von dieser beabstandet ist.When manufacturing the anchor assembly, the anchor plate 28 is first pushed onto the anchor bolt 27 until the anchor plate strikes a head 55 of the anchor bolt. The head 55 replaces the sickle disk 26 in FIGS. 1 and 2 and, like this, serves as a stop for the anchor plate. The return spring 35 is then pushed over the guide stub 65 of the anchor plate 28 until its end 61 abuts the anchor plate. Finally, the disk-shaped support part 50 is pushed so far onto the anchor bolt 27 that the required overtravel distance d remains between the mutually facing sides 57 and 58 of the support part 50 and the guide stub 65. Finally, the support part 50 is fixed in this position on the anchor bolt 27. The anchor assembly consisting of anchor bolt 27, anchor plate 28, return spring 35 and support member 50 is then inserted into the slider 34. The anchor bolt 27 is inserted into a central bore 68 of the slider 34. The slider 34 can already be clamped with the flange 36 in the housing 60 of the solenoid valve. As can also be seen in FIG. 3, deviating from the known arrangement shown in FIG. 2, no annular shoulder 33 is provided, which limits the opening stroke of the anchor bolt by a stop on the slide piece 34. Instead, the opening stroke is limited by a stop of the armature bolt head 55 on the electromagnet or a projection of the electromagnet. This is necessary so that the anchor bolt 27 in FIG. 3 can be inserted into the slider 34 from above. As can also be seen in FIG. 3, the side of the slider 34 facing the support part 50 has a recess 52 into which the support part engages. As already described in detail above, in the installed state, the lower end 67 of the anchor bolt 27 acts on the control valve member 25, which is pressed against the valve seat 24 by the closing force of the spring 31 when the electromagnet is not energized. In this position, the side 59 of the support part 50 facing away from the anchor plate 28 and the weld seam 51 are spaced apart from the inner wall of the recess 52 by a gap. By this measure, when the solenoid valve closes, the support part 50, which is moved with the anchor bolt, is prevented from striking the inner wall of the recess 52, since such a striking could result in the control valve member 25 not coming into contact with the valve seat 24. The recess 52 is therefore designed in such a way that it can also accommodate the weld seam 51 and is always at a distance from it.
Wie weiterhin in Fig. 3 zu erkennen ist, entsteht durch die Annäherung der Unterseite 59 des Stützteils 50 an die Innenwand der zylindrischen Ausnehmung 52 des Gleitstücks 34 beim Schließen des Magnetventils ein hydraulischer Dämpfungsraum. Der zwischen dem Stützteil 50 und der Ausnehmung 52 komprimierte Kraftstoff, welcher nur seitlich durch den Spalt entweichen kann, dämpft in vorteilhafter Weise den Aufprall des Ankerbolzens 27 und des damit gekoppelten Steuerventilgliedes 25 auf den Ventilsitz 24.As can also be seen in FIG. 3, the lower side 59 of the support part 50 approaches the inner wall of the cylindrical recess 52 of the slider 34 when the solenoid valve closes, creating a hydraulic damping space. The fuel compressed between the support part 50 and the recess 52, which can only escape laterally through the gap, advantageously dampens the impact of the anchor bolt 27 and the control valve member 25 coupled to the valve seat 24.
Sobald der Ankerbolzen 27 und das Steuerventilglied 25 am Ventilsitz 24 zur Anlage gelangt sind, gleitet die Ankerplatte 28 bedingt durch ihre träge Masse entgegen der Spannkraft der Rückholfeder 35 auf dem Ankerbolzen nach unten. Zwischen der dem Stützteil 50 zugewandten unteren Stirnseite 58 der Ankerplatte 28 und der der Ankerplatte 28 zugewandten Seite 57 des in diesem Moment nicht mehr bewegten Stützteils 50 bildet sich bedingt durch die Annäherung der Ankerplatte 28 ein weiterer hydraulischer Dämpfungsraum aus. Der in demAs soon as the armature pin 27 and the control valve member 25 come to rest on the valve seat 24, the armature plate 28 slides downward on the armature pin due to its inert mass against the tension force of the return spring 35. A further hydraulic damping space is formed between the lower end face 58 of the anchor plate 28 facing the support part 50 and the side 57 facing the anchor plate 28 of the support part 50 which is no longer moving at this moment due to the approach of the anchor plate 28. The one in the
Spalt zwischen der Ankerplatte 28 und dem Stützteil 50 ent- haltene Kraftstoff bringt eine Gegenkraft auf, welche der Bewegung der Ankerplatte entgegenwirkt . Die Ausgleichsbewegung der Ankerplatte 28 wird daher durch die Position des Stützteils auf dem Ankerbolzen 27 begrenzt, was zu einer Bewe- gungsumkehr nach vorheriger Dämpfung und damit zu einer Reduzierung des Nachschwingvorgangs führt .Gap between the anchor plate 28 and the support member 50 held fuel exerts a counterforce that counteracts the movement of the anchor plate. The compensating movement of the anchor plate 28 is therefore limited by the position of the support part on the anchor bolt 27, which leads to a reversal of movement after previous damping and thus to a reduction in the ringing process.
Fig. 4 zeigt ein weiteres Ausführungsbeispiel der Erfindung, welches sich von dem in Fig. 3 gezeigten Ausführungsbeispiel dadurch unterscheidet, daß das Stützteil 50 formschlüssig an dem Ankerbolzen 27 festgelegt ist. Das Stützteil 50 ist in diesem Ausführungsbeispiel als Sichelscheibe mit einer offenen Aussparung 56 ausgebildet, welche mit dem offenen Ende seitlich auf den Ankerbolzen aufgeschoben wird. Der Ankerbol- zen 27 weist eine umlaufende Nut 54 auf, in welche die Innenkontur der Aussparung 56 der Sichelscheibe 50 formschlüssig eingreift. Die auf den Ankerbolzen aufgeschobene Sichelscheibe 50 ist senkrecht zum Ankerbolzen durch die Ausnehmung 52 des Gleitstücks 34 in ihrer Lage gesichert. Die Weglänge, um die der Ankerbolzen beim Öffnen und Schließen des Magnetventils in axialer Richtung verschoben wird, ist deutlich kleiner als die Tiefe der Ausnehmung 52, so daß die Sichelscheibe 50 nicht versehentlich aus ihrer Lage am Ankerbolzen 27 herausrutschen kann.FIG. 4 shows a further exemplary embodiment of the invention, which differs from the exemplary embodiment shown in FIG. 3 in that the supporting part 50 is positively fixed on the anchor bolt 27. In this exemplary embodiment, the support part 50 is designed as a sickle disk with an open recess 56 which is pushed laterally onto the anchor bolt with the open end. The anchor bolt 27 has a circumferential groove 54, in which the inner contour of the recess 56 of the sickle disk 50 engages in a form-fitting manner. The crescent disk 50 pushed onto the anchor bolt is secured in its position perpendicular to the anchor bolt by the recess 52 of the slider 34. The path length by which the anchor bolt is displaced in the axial direction when the solenoid valve is opened and closed is significantly smaller than the depth of the recess 52, so that the sickle disk 50 cannot accidentally slip out of its position on the anchor bolt 27.
Fig. 5 zeigt ein drittes Ausführungsbeispiel, welches eine Abwandlung des in Fig. 4 dargestellten Ausführungsbeispiels zeigt. Bei diesem Ausführungsbeispiel ist das Stützteil 50 wieder als Sichelscheibe ausgebildet, welche mit dem nicht gezeigten offenen Ende auf einen Abschnitt 72 des Ankerbolzens 27 aufgeschoben ist. Der Durchmesser des Abschnitts 72 ist kleiner ausgebildet als der Durchmesser des in dem Gleitstück 34 geführten Abschnitts des Ankerbolzens 27 und durch eine umlaufende Schulter 71 von diesem abgegrenzt. Die Rück- holfeder 35 stützt sich mit dem einen Ende an der Ankerplatte 28 ab. Mit dem anderen Ende drückt die Rückholfeder 35 die Sichelscheibe 50 gegen die an dem Ankerbolzen 27 ausgebildete umlaufende Schulter 71. Die Ankerbaugruppe kann als vormontierte Baueinheit in das Gleitstück 34 eingesetzt werden, wobei der Ankerbolzen 27 in die Öffnung 68 eingeführt wird und die Sichelscheibe 50 wenigstens teilweise in die Ausnehmung 52 eindringt . Durch die Innenkontur der Ausnehmung 52 ist die Sichelscheibe 50 gegen ein seitliches Abrutschen von dem Ankerbolzen gesichert. FIG. 5 shows a third exemplary embodiment, which shows a modification of the exemplary embodiment illustrated in FIG. 4. In this embodiment, the support part 50 is again designed as a sickle disk, which is pushed with the open end, not shown, onto a section 72 of the anchor bolt 27. The diameter of the section 72 is made smaller than the diameter of the section of the anchor bolt 27 guided in the slider 34 and is delimited from it by a circumferential shoulder 71. The return spring 35 is supported at one end on the anchor plate 28. The return spring 35 presses the other end Sickle disc 50 against the circumferential shoulder 71 formed on the anchor bolt 27. The anchor assembly can be inserted as a preassembled unit in the slide 34, the anchor bolt 27 being inserted into the opening 68 and the sickle disc 50 at least partially penetrating into the recess 52. Due to the inner contour of the recess 52, the sickle plate 50 is secured against lateral slipping off the anchor bolt.

Claims

Ansprüche Expectations
1. Magnetventil zur Steuerung eines Einspritzventils einer Brennkraftmaschine, umfassend einen Elektromagneten (29) , einen beweglichen Anker mit Ankerplatte (28) und Ankerbolzen1. Solenoid valve for controlling an injection valve of an internal combustion engine, comprising an electromagnet (29), a movable armature with an armature plate (28) and armature bolts
(27) und ein mit dem Anker bewegtes und mit einem Ventilsitz (24) zusammenwirkendes Steuerventilglied (25) zum Öffnen und(27) and a control valve member (25) which is moved with the armature and cooperates with a valve seat (24) for opening and
Schließen eines Kraftstoffablaufkanals (17) eines Steuerdruckraums (14) des Einspritzventils (1) , welche AnkerplatteClosing a fuel drain channel (17) of a control pressure chamber (14) of the injection valve (1), which anchor plate
(28) unter Einwirkung ihrer trägen Masse in Schließrichtung des Steuerventilgliedes (25) entgegen der Spannkraft einer auf die Ankerplatte (28) einwirkenden Rückholfeder (35) auf dem Ankerbolzen (27) gleitend verschiebbar gelagert ist, und mit einer hydraulischen Dämpfungseinrichtung, mit der ein Nachschwingen der Ankerplatte (28) bei ihrer dynamischen Verschiebung auf dem Ankerbolzen (27) dämpfbar ist, dadurch gekennzeichnet, daß sich die Rückholfeder (35) mit ihrem von der Ankerplatte (28) abgewandten Ende (62) an einem an dem Ankerbolzen (27) angeordneten und mit dem Ankerbolzen bewegten Stützteil (50) abstützt, welches Stützteil (50) zugleich einen Teil (57) der Dämpfungseinrichtung bildet.(28) under the action of their inertial mass in the closing direction of the control valve member (25) against the tension force of a return spring (35) acting on the anchor plate (28) is slidably mounted on the anchor bolt (27), and with a hydraulic damping device with which a The oscillation of the anchor plate (28) during its dynamic displacement on the anchor bolt (27) can be damped, characterized in that the return spring (35), with its end (62) facing away from the anchor plate (28), contacts one end of the anchor bolt (27). arranged and moved with the anchor bolt supporting part (50), which supporting part (50) also forms part (57) of the damping device.
2. Magnetventil nach Anspruch 1, dadurch gekennzeichnet, daß der Ankerbolzen (27) , die Ankerplatte (28) , die Rückholfeder (35) und das an dem Ankerbolzen festgelegte Stützteil (50) als vormontierte Ankerbaugruppe in das Magnetventilgehäuse (60) eingesetzt sind.2. Solenoid valve according to claim 1, characterized in that the armature bolt (27), the armature plate (28), the return spring (35) and the support member (50) fixed to the armature bolt are inserted as a preassembled armature assembly in the solenoid valve housing (60).
3. Magnetventil nach Anspruch 1 oder 2, dadurch gekennzeichnet, daß der Ankerbolzen (27) in einer Öffnung (68) eines in dem Gehäuse (60) des Magnetventils (30) ortsfest angeordne- ten Gleitstücks (34) gleitverschiebbar gelagert ist. 3. Solenoid valve according to claim 1 or 2, characterized in that the anchor bolt (27) in a hole (68) of a fixed in the housing (60) of the solenoid valve (30) slider (34) is slidably mounted.
4. Magnetventil nach Anspruch 3, dadurch gekennzeichnet, daß die der Ankerplatte (28) zugewandten Seite des Gleitstücks (34) eine Ausnehmung (52) aufweist, in der das an dem Ankerbolzen (27) angeordnete Stützteil (50) angeordnet ist, wobei die Außenkontur des Stützteils (50) durch einen Spalt von der Innenkontur der Ausnehmung (52) beabstandet ist.4. Solenoid valve according to claim 3, characterized in that the armature plate (28) facing side of the slider (34) has a recess (52) in which the on the armature bolt (27) arranged support member (50) is arranged, the The outer contour of the support part (50) is spaced from the inner contour of the recess (52) by a gap.
5. Magnetventil nach Anspruch 4, dadurch gekennzeichnet, daß der mit Kraftstoff gefüllte Spalt zwischen dem Stützteil (50) und der Innenwandung der Ausnehmung (52) eine weitere Dämpfungseinrichtung bildet, mittels der ein Anschlagen des mit dem Ankerbolzen (27) gekoppelten Steuerventilgliedes (25) am Ventilsitz (24) dämpfbar ist.5. Solenoid valve according to claim 4, characterized in that the fuel-filled gap between the support part (50) and the inner wall of the recess (52) forms a further damping device by means of which the control valve member (25) coupled to the anchor bolt (27) strikes ) can be damped on the valve seat (24).
6. Magnetventil nach einem der Ansprüche 1 bis 5, dadurch gekennzeichnet, daß das Stützteil (50) scheibenförmig ausgebildet ist.6. Solenoid valve according to one of claims 1 to 5, characterized in that the supporting part (50) is disc-shaped.
7. Magnetventil nach einem der Ansprüche 1 bis 6, dadurch gekennzeichnet, daß das Stützteil (50) durch Schweißen, Kleben, Löten oder Aufschrumpfen an dem Ankerbolzen (27) festgelegt ist.7. Solenoid valve according to one of claims 1 to 6, characterized in that the support part (50) is fixed by welding, gluing, soldering or shrinking on the anchor bolt (27).
8. Magnetventil nach einem der Ansprüche 1 bis 5, dadurch gekennzeichnet, daß das Stützteil (50) als Sichelscheibe ausgebildet ist.8. Solenoid valve according to one of claims 1 to 5, characterized in that the supporting part (50) is designed as a sickle disk.
9. Magnetventil nach Anspruch 8, dadurch gekennzeichnet, daß das Stützteil formschlüssig in einer umlaufenden Nut (54) des Ankerbolzens (27) festgelegt ist.9. Solenoid valve according to claim 8, characterized in that the supporting part is positively fixed in a circumferential groove (54) of the anchor bolt (27).
10. Magnetventil nach Anspruch 4 und 8, dadurch gekennzeichnet, daß die Sichelscheibe (50) seitlich auf einen nicht in dem Gleitstück (34) geführten Abschnitt (72) des Ankerbolzen (27) aufgeschoben ist und durch die Federkraft der Rückholfeder (35) gegen eine an dem Ankerbolzen (27) ausgebildete Schulter (71) angedrückt wird und durch die Innenkontur der Ausnehmung (52) in radialer Richtung gegen ein Abrutschen vom Ankerbolzen gesichert ist. 10. Solenoid valve according to claim 4 and 8, characterized in that the sickle disc (50) is pushed laterally onto a section (72) of the anchor bolt (27) which is not guided in the slide (34) and against the spring force of the return spring (35) one formed on the anchor bolt (27) Shoulder (71) is pressed and is secured by the inner contour of the recess (52) in the radial direction against slipping off the anchor bolt.
EP01994586A 2000-11-23 2001-11-16 Electromagnetic valve for controlling an injection valve of an internal combustion engine Expired - Lifetime EP1259729B1 (en)

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DE10058007 2000-11-23
DE10058007 2000-11-23
DE10113008A DE10113008A1 (en) 2000-11-23 2001-03-17 Solenoid valve for controlling an injection valve of an internal combustion engine
DE10113008 2001-03-17
PCT/DE2001/004318 WO2002042632A2 (en) 2000-11-23 2001-11-16 Electromagnetic valve for controlling an injection valve of an internal combustion engine

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US6796543B2 (en) 2004-09-28
ES2256333T3 (en) 2006-07-16
WO2002042632A3 (en) 2002-08-08
JP4138481B2 (en) 2008-08-27
DE50108770D1 (en) 2006-04-06
WO2002042632A2 (en) 2002-05-30
US20040026540A1 (en) 2004-02-12
EP1259729B1 (en) 2006-01-18
JP2004514823A (en) 2004-05-20

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