EP3384149B1 - Fuel injector having a control valve - Google Patents

Fuel injector having a control valve Download PDF

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Publication number
EP3384149B1
EP3384149B1 EP16788726.4A EP16788726A EP3384149B1 EP 3384149 B1 EP3384149 B1 EP 3384149B1 EP 16788726 A EP16788726 A EP 16788726A EP 3384149 B1 EP3384149 B1 EP 3384149B1
Authority
EP
European Patent Office
Prior art keywords
armature
fuel injector
valve
magnet assembly
crown ring
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
EP16788726.4A
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German (de)
French (fr)
Other versions
EP3384149A1 (en
Inventor
Lars Olems
Dominik WURST
Helmut Clauss
Oezguer Tuerker
Christian Faltin
Michael WALDENMAIER
Thomas Nierychlo
Fabian FISCHER
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
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Filing date
Publication date
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Publication of EP3384149A1 publication Critical patent/EP3384149A1/en
Application granted granted Critical
Publication of EP3384149B1 publication Critical patent/EP3384149B1/en
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M47/00—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
    • F02M47/02—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure of accumulator-injector type, i.e. having fuel pressure of accumulator tending to open, and fuel pressure in other chamber tending to close, injection valves and having means for periodically releasing that closing pressure
    • F02M47/027—Electrically actuated valves draining the chamber to release the closing pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M51/00—Fuel-injection apparatus characterised by being operated electrically
    • F02M51/005—Arrangement of electrical wires and connections, e.g. wire harness, sockets, plugs; Arrangement of electronic control circuits in or on fuel injection apparatus
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/04—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series
    • F02M61/10—Other injectors with elongated valve bodies, i.e. of needle-valve type
    • F02M61/12—Other injectors with elongated valve bodies, i.e. of needle-valve type characterised by the provision of guiding or centring means for valve bodies
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/161—Means for adjusting injection-valve lift
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/007—Details not provided for in, or of interest apart from, the apparatus of the groups F02M63/0014 - F02M63/0059
    • F02M63/0073—Pressure balanced valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/90—Selection of particular materials
    • F02M2200/9053—Metals
    • F02M2200/9069—Non-magnetic metals
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/007—Details not provided for in, or of interest apart from, the apparatus of the groups F02M63/0014 - F02M63/0059
    • F02M63/0071—Details not provided for in, or of interest apart from, the apparatus of the groups F02M63/0014 - F02M63/0059 characterised by guiding or centering means in valves including the absence of any guiding means, e.g. "flying arrangements"

Definitions

  • the invention relates to a fuel injector for injecting fuel into the combustion chamber of an internal combustion engine, the fuel injector having a control valve.
  • Fuel injectors with control valves are widely known from the prior art, for example from the published patent application DE 196 50 865 A1 , DE 102007025614 A1 and US 2006/138374 A1 .
  • the known fuel injector for injecting fuel into the combustion chamber of an internal combustion engine comprises a control valve and an injection valve member.
  • the injection valve member delimits a control chamber and is guided in the fuel injector in a longitudinally movable manner.
  • the injection valve member opens and blocks at least one injection opening into the combustion chamber due to its movement.
  • the control valve controls the pressure in the control chamber and comprises a magnet assembly, an armature, a valve piece and a valve seat formed on the valve piece.
  • An armature plate arranged on the armature can be controlled by the magnet assembly. The armature interacts at least indirectly with the valve seat to relieve the control space.
  • the known fuel injector has a comparatively complex armature stroke setting.
  • the armature stroke is the path between the closed position and the maximum open position, i.e. the axial distance between the valve seat and the magnet assembly reduced by the components of the armature arranged in between, including an optional closing body. This happens on the one hand in a series production the assembly of the fuel injector to high tolerance-related variations in the armature stroke. On the other hand, thermal expansions occur during operation due to temperature loads, which result in a change in the armature stroke with the temperature. The function of the entire fuel injection valve is therefore no longer robust above the operating temperature.
  • the armature stroke of the fuel injector according to the invention is almost constant over the operating temperature. Furthermore, comparatively few components are involved in the anchor stroke adjustment, so that the tolerance error of the anchor stroke during assembly is minimized. This improves the functionality of the entire fuel injector and makes it more robust.
  • the fuel injector comprises a control valve and an injection valve member.
  • the injection valve member delimits a control chamber and is guided in the fuel injector in a longitudinally movable manner.
  • the injection valve member opens and blocks at least one injection opening into the combustion chamber due to its movement.
  • the control valve controls the pressure in the control room.
  • the control valve comprises a magnet assembly, an armature, a valve piece and a valve seat formed on the valve piece.
  • the armature comprises an armature plate, the armature plate being controllable by the magnet assembly. The armature interacts at least indirectly with the valve seat to relieve the control space. A crown ring is clamped between the valve piece and the magnet assembly.
  • the crown ring thus defines, possibly together with other components, the distance between the valve piece with the valve seat on the one hand and the magnet assembly on the other.
  • the two fixed positions for the armature stroke are thus defined in a simple manner and tolerance fluctuations are accordingly minimized.
  • the Thermal expansion coefficients of anchor and crown ring are taken into account.
  • a cylindrical outer surface is formed on the valve piece.
  • the crown ring is positioned on this lateral surface coaxially with the valve seat. Due to the coaxiality, the crown ring is optimally aligned with the valve piece and the valve seat, so the power flow is very homogeneous, so that there is no tilting or misalignment of the clamped components.
  • the rotational symmetry can be largely preserved.
  • a cylindrical guide surface is formed on the crown ring.
  • the armature is guided longitudinally in this guide surface.
  • the crown ring has another function: it radially aligns the anchor or positions it coaxially with the valve seat.
  • the closing function of the control valve and its service life are optimized; there are no malfunctions or misalignments of the control valve. Skewing the armature usually means increased wear on the control valve.
  • an anchor stroke adjusting disc is clamped between the crown ring and the valve piece.
  • the anchor stroke shim is easier to manufacture than the crown ring. Therefore, the anchor stroke adjusting disc can also be manufactured more easily with different disc thicknesses, which are then installed depending on the tolerance chain of the components involved to adjust the anchor stroke.
  • the crown ring can therefore be manufactured inexpensively at only a single height.
  • the armature stroke adjusting disk is clamped between the crown ring and the magnet assembly.
  • a plate groove is formed in the anchor plate.
  • the crown ring has a crown, the crown protruding through the plate groove.
  • the control valve - especially in the area of the anchor and crown ring - is very space-saving. It is not necessary to reach around the anchor.
  • the crown ring preferably also fulfills the function of securing against rotation, that is to say rotation of the anchor plate or of the anchor about its longitudinal axis is prevented.
  • a bearing recess is formed in the crown.
  • a rolling element is mounted in the bearing recess, the rolling element interacting with the plate groove.
  • the rolling element is preferably designed spherical.
  • the armature plate or armature thus rolls on the rolling element during the opening and closing of the control valve. The friction that occurs is minimal due to the theoretical point support and constant over the service life.
  • the anti-rotation device is therefore designed to be very low-friction and energy-saving.
  • the rolling element is advantageously made of an amagnetic material, preferably a ceramic. As a result, the rolling element is not subject to any electromagnetic forces caused by the magnetic assembly.
  • a residual air gap disc is arranged between the magnet assembly and the armature plate. This avoids so-called sticking between the armature plate and the magnet assembly in the maximum opening position, that is, with the maximum armature stroke.
  • the residual air gap disk is preferably not magnetic.
  • the material of the crown ring has a greater coefficient of thermal expansion than the material of the anchor and the crown ring is arranged at least partially radially surrounding the anchor.
  • the armature is therefore subject to a greater temperature load during operation due to the rapidly flowing and high-pressure fuel. Due to the larger thermal expansion coefficient of the crown ring, the different length changes occur Temperature loads compensated. This minimizes the thermal stresses that occur in the control valve.
  • the crown ring surrounds the anchor on the outside. As a result, the crown ring virtually engages around the anchor. The anchor can thus remain geometrically unchanged; the electromagnetic force acting on the armature or the armature plate is therefore not influenced by the crown ring.
  • the material of the crown ring is advantageously non-magnetic.
  • the crown ring is preferably made of an austenitic sintered steel or a ceramic. As a result, the crown ring does not negatively influence the magnetic field of the magnetic assembly. The magnetic force on the anchor plate is therefore not falsified.
  • the magnet assembly is clamped to the crown ring by means of a tension spring. This is a very simple and efficient bracing. This eliminates the need for additional complex screw connections inside the fuel injector.
  • the magnetic assembly can be electrically contacted by at least one contact pin. Furthermore, the at least one contact pin has a slide seat. As a result, the magnet assembly can be axially variably positioned during assembly without the electrical contact being lost.
  • the armature is acted upon by a spring in the direction of the valve seat.
  • this is a simple and inexpensive design for pressing the armature or the closing body against the valve seat in the closed position.
  • the control valve closes very quickly and efficiently.
  • an anchor bolt protrudes through the anchor.
  • the hydraulically resulting force on the armature can be reduced in the axial direction or even set to zero.
  • a pressure or force-balanced control valve can thus be implemented. Accordingly, for example, the magnet assembly and the spring can be downsized, since only smaller forces are required to move the armature.
  • the anchor bolt and the valve seat preferably have almost the same diameter. As a result, a pressure or force-balanced control valve is realized.
  • a fuel injector 100 can be seen in a schematic manner, as is known from the prior art.
  • the fuel injector 100 is used to inject fuel into the combustion chamber of an internal combustion engine.
  • the fuel injector 100 comprises a holding body 10 and a control valve 1 with a magnet assembly 2 and a magnetic core 3 arranged therein.
  • An injection valve member 11, which is movably received in the holding body 10, can be actuated via the control valve 1.
  • the injection valve member 11 - generally needle-shaped - opens or closes injection openings 13 in the combustion chamber of the internal combustion engine at an end of the fuel injector 100 on a nozzle body 12, so that fuel can be injected into the combustion chamber if necessary.
  • the nozzle body 12 is screwed to the holding body 10 in a media-tight manner by a clamping nut 14.
  • the control valve 1 comprises a valve piece 4, which is installed in the holding body 10 and has a control chamber 15 for actuating the injection valve member 11, the opening or closing of which is controlled by the control valve 1.
  • the control valve 1 thus controls the pressure in the control chamber 15.
  • the mode of operation of the fuel injector 100 is such that when the pressure in the control chamber 15 is reduced, the injection valve member 11 pushes into the control chamber 15 and thus releases the injection openings 13 and that when the pressure increases in the Control chamber 15 this hydraulic pressure pushes the injection valve member 11 in the direction of the combustion chamber and thereby the injection openings 13 are closed.
  • injection valve member 11 can also be made in several parts.
  • Fig. 2 shows a control valve 1 according to the invention in longitudinal section, only the essential areas being shown. At the bottom of the Fig. 2 one can still see the injection valve member 11 guided in the valve piece 4, which is moved in the axial direction of the fuel injector 100 by the pressure change in the control chamber 15.
  • the valve piece 4 is clamped in the holding body 10.
  • the control chamber 15 is connected to a valve chamber 17 by an outlet throttle 16 formed in the valve piece 4.
  • the valve chamber 17 can be connected to a low-pressure chamber 18 by the control valve 1, the low-pressure chamber 18 opening into a return system (not shown) of the fuel injector 100.
  • the valve chamber 17 is delimited by the valve piece 4, an at least partially sleeve-shaped armature 5 and an armature bolt 6.
  • the low-pressure chamber 18 is delimited by the valve piece 4 and the armature 5.
  • the armature 5 interacts with a valve seat 7 formed on the valve piece 4. If the armature 5 rests on the valve seat 7, then a hydraulic connection is separated from the valve chamber 17 to the low-pressure chamber 18; If the armature 5 is lifted off the valve seat 7, the hydraulic connection from the valve chamber 17 to the low-pressure chamber 18 is opened.
  • the anchor bolt 6 is at least partially arranged in a bore in the anchor 5 and thus guides the anchor 5 in a longitudinally movable manner.
  • the armature bolt 6 further delimits the valve space 17 and thus serves to equalize the pressure of the armature 5.
  • the armature 5 is of sleeve-shaped design, at least in its area adjacent to the valve space 17, and can thus be designed to be pressure or force balanced by the valve seat 7 having almost the same diameter has as the armature pin 6.
  • the bore of the armature 5, through which the armature pin 6 projects must have the same diameter as the valve seat 7. Then the hydraulically resulting force on the armature 5 in the axial direction is zero.
  • the control valve 1 is then referred to as force-balanced or pressure-balanced.
  • the longitudinal movement of the armature 5 can alternatively also be guided by a valve piece neck 41 of the valve piece 4.
  • the armature 5 is acted upon by a spring 8 and is pressed by it against the valve seat 7.
  • a support ring 81 is optionally arranged between the armature 5 and the spring 8, the support ring 81 preferably serving to adjust the force of the spring 8.
  • the magnet assembly 2 with the magnet core 3 arranged therein is arranged on the side of the armature 5 opposite the valve chamber 17 and optionally surrounded by a magnet sleeve (not shown). When the magnetic core 3 is energized by contact pins 31, an electromagnetic force is exerted on an armature plate 50 of the armature 5, so that the armature 5 is lifted from the valve seat 7 against the force of the spring 8.
  • the magnet assembly 2 is supported directly on the valve piece 4 via a crown ring 20 and an anchor stroke adjusting disk 21.
  • an end face 40 is formed on the valve piece 4, which cooperates with the anchor stroke adjusting disk 21.
  • the crown ring 20 is then clamped to the magnet assembly 2, at least one crown 29 being formed or arranged on the crown ring 20.
  • the anchor plate 50 has at least one plate groove 54 through which the crown 29 is guided in the axial direction. The crown 29 thus interacts with the magnet assembly 2 or is clamped to it.
  • the magnetic assembly 2 in turn is pressed against the crown 29 by a tension spring 22.
  • the tension spring 22 can, as in the Fig. 2 shown, be designed as a plate spring, alternatively also with opposite curvature. However, the tension spring 22 can also be designed as any spring, for example as a wave spring.
  • a locking ring 24 serves as an assembly aid so that the magnet assembly 2 does not fall out of the fuel injector 100 during assembly.
  • a residual air gap disk 23 is arranged on the outside between the magnet assembly 2 and the armature 5 and prevents the armature 5 from sticking to the magnet assembly 2.
  • the residual air gap disk 23 can also be designed on the inside; then it would be arranged between the inner pole of the magnet assembly 2 and the armature plate 50.
  • armature stroke that is, the path that the armature 5 can perform during its opening and closing movements between the valve seat 7 and the residual air gap disk 23
  • a corresponding armature stroke adjusting disk 21 is used, adapted to the relevant dimensions of the control valve 1.
  • the crown ring 20 and the anchor stroke adjusting disk 21 can also be made in one piece; accordingly, the armature stroke would then be adjusted over the axial length of the crown ring 20.
  • the crown ring 20 can advantageously be designed as an austenitic sintered part in order not to impair the magnetic flux of the magnet assembly 2.
  • a ceramic sintered part can also be used.
  • the Fig. 3 shows the section AA of the Fig. 2 through the control valve 1.
  • the armature 5 is longitudinally movable on the anchor bolt 6, that is perpendicular to the cutting plane.
  • the anchor plate 50 of the armature 5 has three anchor wings 51, 52, 53, each of which has a circular segment shape.
  • a plate groove 54, 55, 56 of the anchor plate 50 is formed between each two anchor wings.
  • one crown 29 of the crown ring 20 is arranged in a plate groove 54, 55, 56, so that the three crowns 29 protrude through the anchor plate 50 and thus contact the magnet assembly 2 in the assembled state.
  • the crown ring 20 can have any number of crowns 29.
  • the crowns 29 serve not only to brace or position the magnet assembly 2, but also to prevent the armature plate 50 or the armature 5 from rotating. Unnecessary rotation of the armature 5 and thus also additional wear are thereby avoided.
  • Fig. 4 shows a further embodiment of the control valve 1 according to the invention in longitudinal section, wherein only the essential differences to the embodiment of the Fig. 2 to be received.
  • the armature 5 is guided in a longitudinally movable manner by the armature bolt 6, or alternatively by the valve piece neck 41.
  • the armature 5 is guided in the embodiment of FIG Fig. 4 through the crown ring 20.
  • a collar 42 is arranged on the valve piece 4, which inside the Valve space 17 limited.
  • the crown ring 20 is at least radially fixed on an outer lateral surface 43 of the collar 42 via an inner positioning surface 27 formed on it, so that it is preferably arranged concentrically with the valve seat 7. In alternative embodiments, however, the positioning surface 27 can also be on the outside and thus the outer surface 43 can be on the inside.
  • the collar 42 is compared to the valve neck 41 of the Fig. 2 shorter because it no longer has a guiding function for anchor 5.
  • the crown ring 20 is at least partially radially surrounding the armature 5.
  • the crown ring 20 also has an inner guide surface 28 with which the armature 5 is guided in a longitudinally movable manner.
  • the positioning surface 27 and the guide surface 28 are the same inner lateral surface of the crown ring 20, the positioning surface 27 and the guide surface 28 being arranged one above the other when viewed in the axial direction.
  • At least one drain hole 26 is formed in the crown ring 20, which is part of the low-pressure chamber 18 and thus connects the valve chamber 17 to the low-pressure system or return system of the fuel injector 100.
  • the contact pins 31 in the embodiment of FIG Fig. 4 have a slide seat 31a, by means of which the axial length of the contact pin 31 is designed to be variable, so that the magnet assembly 2 can be correctly positioned axially during the assembly process without the electrical contacting of the magnetic core 3 being interrupted.
  • the crown ring 20 and the anchor stroke adjusting disc 21 can be made in one piece.
  • Fig. 5 shows yet another embodiment of the control valve 1 according to the invention in longitudinal section, wherein only the essential differences to the embodiments of the Fig. 2 and Fig. 4 to be received.
  • the armature 5 is guided by the crown ring 20 or by the guide surface 28 of the crown ring 20 Fig. 4 , the positioning surface 27 of the crown ring 20th at least radially fixed on the collar 42 of the valve piece 4 or arranged with very little play.
  • the crown 29 is not guided through a plate groove in the anchor plate 50, but surrounds or surrounds the anchor plate 50 on the outside.
  • the anchor plate 50 can be designed as a complete circular ring without grooves.
  • the radial dimension of the crown 29 may be increased.
  • Outflow holes 25 are formed in the crown 29 or in the crown ring 20 and are part of the low-pressure chamber 18.
  • the outflow holes 25 can also be omitted if the flow gaps on the outside of the crown ring 20 or the crown 29 have a sufficient flow cross section.
  • the armature stroke adjusting disk 21 is clamped between the crown 29 and the magnet assembly 2.
  • the armature stroke adjusting disk 21 can either be clamped between the crown 29 and the magnet assembly 2, or between the crown ring 20 and the valve piece 4, or can be embodied in one piece together with the valve piece 4.
  • the residual air gap disk 23 is arranged on the inner pole of the magnet assembly 2 between the latter and the armature plate 50, the radial positioning of the residual air gap disk 23 being freely selectable for all embodiments.
  • the fuel injector 100 of the embodiment of FIG Fig. 5 also has a spring adjusting washer 80, which is used to adjust the tension spring 22.
  • the holding body 10 is screwed to a holding body head 9 by means of a union nut 9a with the spring adjusting disk 80 being interposed.
  • a stop surface 9b is formed on the holding body head 9, on which both the spring 8 and the tension spring 22 and the anchor bolt 6 are preferably supported.
  • the stop surface 9b is positioned via the valve piece 4, the holding body 10, the spring adjusting washer 80 and the holding body head 9.
  • a lower stop for the magnet assembly 2 is defined via the valve piece 4, the crown ring 20 and the armature stroke adjusting disk 21.
  • An upper distance between the Magnet assembly 2 and the stop surface 9b are now adjusted by the spring adjusting disk 80 in such a way that the force of the tension spring 80 is also adjusted thereby.
  • the force of the spring 8 is set using the support ring 81.
  • the spring 8 tensioned between the armature 5 - or the support ring 81 - and the stop surface 9b can be very well adjusted in terms of its spring force or its spring travel by the height of the Support rings 81 can be set.
  • Fig. 6 shows a detail of a further embodiment of the control valve 1 according to the invention in longitudinal section.
  • the design of the Fig. 6 a spherical closing body 60, which is positioned in a receiving piece 61.
  • the receiving piece 61 is arranged between the armature 5 and the closing body 60 and is acted upon by the armature 5, the guide surface 28 of the crown ring 20 guiding the armature 5 in a longitudinally movable manner. Due to the spherical closing body 60, the control valve 1 is no longer force balanced in this embodiment.
  • the components armature 5, receptacle 61 and closing body 60 can also be made in one or two parts in alternative designs.
  • the crown ring 20 is clamped between a shoulder 49 formed on the valve piece 4 and the magnet assembly 2, optionally with the interposition of the armature stroke adjusting disk 21.
  • the outer surface 43 of the valve piece 4 is on the inside and the positioning surface 27 of the crown ring 20 is on the outside.
  • the crown ring 20 is thereby positioned coaxially to the valve piece 4 and consequently coaxially to the valve seat 7.
  • the lateral surface 43 can also be designed on the outside and the positioning surface 27 on the inside.
  • the crown ring 20 has two crowns 29 which protrude through two plate grooves 54, 55 of the anchor plate 5.
  • any number of crowns 29 and plate grooves 54, 55, 56 can be used.
  • the crown ring 20 can also be designed to surround the armature 5 on the outside, as in FIG Fig. 5 shown.
  • Fig. 7 shows a further embodiment of the control valve 1, only the essential areas being shown.
  • the crown ring 20 of the execution of the Fig.7a / Fig.7b advantageously has three crowns 29, in principle any number of crowns 29 can be used.
  • the anchor plate 50 has a corresponding number of plate grooves 54, 55, 56 through which the crowns 29 are guided in the axial direction.
  • the crowns 29 cooperate on the end face with the magnet assembly 2, not shown, or are braced with the latter.
  • a bearing recess 59 is formed in each of the crowns 29.
  • the bearing recesses 59 are designed in the form of a clamp, in such a way that they are open in the circumferential direction of the crown ring 20 and to the magnet assembly 2.
  • the bearing recesses 59 serve to receive rolling elements 58, which are preferably spherical; As a result, the bearing recesses 59 perform the function of bearing cages.
  • the rolling elements 58 are dimensioned and positioned in the bearing recesses 59 in such a way that they interact with the plate grooves 54, 55, 56 of the anchor plate 50, specifically in both circumferential directions, that is to say tangentially, so that each rolling element 58 can transmit rotational forces in both directions.
  • the armature 5 is therefore guided almost smoothly by the rolling elements 58.
  • the anti-rotation device of the anchor plate 50 or of the armature 5 is thus designed to be very low-friction and low-wear, since the armature 5 rolls on the rolling elements 58 virtually over its plate grooves 54, 55, 56.
  • the rolling elements 58 are preferably made of an amagnetic material, for example a ceramic, so that they are not influenced by the electromagnetic forces of the magnet assembly 2.
  • the Fig. 8 shows one to Fig. 7 alternative rotation lock of the anchor plate 50.
  • the bearing recesses 59 are in the embodiment of the Fig. 8 Pot-shaped, each with an open end in the circumferential direction of the armature 5.
  • a rolling element 58 is positioned in each case in a bearing recess 59 such that it cooperates with a flank of the corresponding plate groove 54, 55, 56 at the open end of the bearing recess 59.
  • the anchor plate 50 is supported on a plate groove 54, 55, 56 in a circumferential direction, but not in the opposite oriented circumferential direction. Therefore, at least one further rolling element 58 is required, which also supports the armature plate 50 in the opposite oriented circumferential direction.
  • the crown ring preferably has a different shape than in FIGS Fig.8a / Fig.8b shown, an even number of crowns 29, so that the rolling elements 58 arranged in the associated bearing recesses 59 each support the anchor plate 50 in pairs in both circumferential directions.
  • the rolling elements 58 are supported by the crowns 29 in the radial direction.
  • the radial direction to the outside can also be supported by a further component, for example by the residual air gap disk 23, if this, as in the exemplary embodiment in FIG Fig. 6 is arranged.
  • the mode of operation of the fuel injector 100 according to the invention is as follows: The injections via the injection openings 13 into the combustion chamber of the internal combustion engine are caused by the longitudinal movement of the or multi-part injection valve member 11, the longitudinal movements of which are in turn controlled by the control valve 1, the control valve 1 being controlled by the magnet assembly 2.
  • the injection valve member 11 is guided in the valve piece 4 at its end opposite the injection openings 13 and delimits the control chamber 15 there.
  • the magnet assembly 2 When the magnetic core 3 is energized, the magnet assembly 2 exerts an attractive force on the armature 5 and moves it away from the valve seat 7 against the force of the spring 8. The hydraulic connection from the valve chamber 17 to the low-pressure chamber 18 is thereby opened and the control chamber 15 is consequently relieved. The hydraulically closing force in the control chamber 15 on the injection valve member 11 in the direction of the injection openings 13 is reduced and the injection valve member 11 releases the injection openings 13 so that the fuel injector 100 injects into the combustion chamber of the internal combustion engine.
  • the components of the control valve 1 that have an influence on the stroke of the armature 5 are reduced: the axial distance between the valve seat 7 and the magnet assembly 2 is defined by the valve piece 4, crown ring 20 and optionally armature stroke adjusting disk 21. If the effective length of the armature 5 and, if appropriate, the height of the residual air gap disk 23 are subtracted from this, the maximum possible armature stroke is obtained.
  • the pressure and temperature dependency of the anchor stroke is reduced; the two components determining the axial length are the armature 5 and the crown ring 20.
  • the armature 5 heats up dynamically faster than the crown ring 20.
  • the material of the crown ring 20 is selected such that it has a greater coefficient of thermal expansion than the material of the armature 5 Coefficient of thermal expansion of the crown ring 20 can be compensated.
  • the material of the crown ring 20 is advantageously selected such that it does not impair the magnetic flux of the magnetic assembly 2, for example made of austenitic steel or a ceramic.
  • the crowns 29 of the crown ring 20 protruding through the anchor plate 50 also have a function for securing the anchor plate 50 or the anchor 5 against rotation.
  • the use of rolling elements 58 makes this rotation lock particularly low-friction.

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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)

Description

Die Erfindung betrifft einen Kraftstoffinjektor zum Einspritzen von Kraftstoff in den Brennraum einer Brennkraftmaschine, wobei der Kraftstoffinjektor ein Steuerventil aufweist. Stand der TechnikThe invention relates to a fuel injector for injecting fuel into the combustion chamber of an internal combustion engine, the fuel injector having a control valve. State of the art

Kraftstoffinjektoren mit Steuerventilen sind vielfach aus dem Stand der Technik bekannt, beispielsweise aus der Offenlegungsschrift DE 196 50 865 A1 , DE 102007025614 A1 und US 2006/138374 A1 .Fuel injectors with control valves are widely known from the prior art, for example from the published patent application DE 196 50 865 A1 , DE 102007025614 A1 and US 2006/138374 A1 .

Der bekannte Kraftstoffinjektor zum Einspritzen von Kraftstoff in den Brennraum einer Brennkraftmaschine umfasst ein Steuerventil und ein Einspritzventilglied. Das Einspritzventilglied begrenzt einen Steuerraum und ist längsbeweglich in dem Kraftstoffinjektor geführt. Das Einspritzventilglied öffnet und sperrt durch seine Bewegung zumindest eine Einspritzöffnung in den Brennraum. Das Steuerventil steuert den Druck in dem Steuerraum und umfasst eine Magnetbaugruppe, einen Anker, ein Ventilstück und einen an dem Ventilstück ausgebildeten Ventilsitz. Eine an dem Anker angeordnete Ankerplatte ist von der Magnetbaugruppe ansteuerbar. Der Anker wirkt zumindest mittelbar mit dem Ventilsitz zum Entlasten des Steuerraums zusammen.The known fuel injector for injecting fuel into the combustion chamber of an internal combustion engine comprises a control valve and an injection valve member. The injection valve member delimits a control chamber and is guided in the fuel injector in a longitudinally movable manner. The injection valve member opens and blocks at least one injection opening into the combustion chamber due to its movement. The control valve controls the pressure in the control chamber and comprises a magnet assembly, an armature, a valve piece and a valve seat formed on the valve piece. An armature plate arranged on the armature can be controlled by the magnet assembly. The armature interacts at least indirectly with the valve seat to relieve the control space.

Der bekannte Kraftstoffstoffinjektor weist eine vergleichsweise aufwändige Ankerhubeinstellung auf. Der Ankerhub ist dabei der Weg zwischen Schließstellung und maximaler Öffnungsstellung, also der axiale Abstand zwischen dem Ventilsitz und der Magnetbaugruppe reduziert um die dazwischen angeordneten Bauteile des Ankers einschließlich eines optionalen Schließkörpers. Dadurch kommt es zum einen in einer Serienfertigung während der Montage des Kraftstoffinjektors zu toleranzbedingten hohen Streuungen des Ankerhubs. Zum anderen kommt es während des Betriebs aufgrund von Temperaturlasten zu Wärmeausdehnungen, die eine Änderung des Ankerhubs mit der Temperatur zur Folge haben. Die Funktion des gesamten Kraftstoffeinspritzventils ist dadurch über der Betriebstemperatur nicht mehr robust.The known fuel injector has a comparatively complex armature stroke setting. The armature stroke is the path between the closed position and the maximum open position, i.e. the axial distance between the valve seat and the magnet assembly reduced by the components of the armature arranged in between, including an optional closing body. This happens on the one hand in a series production the assembly of the fuel injector to high tolerance-related variations in the armature stroke. On the other hand, thermal expansions occur during operation due to temperature loads, which result in a change in the armature stroke with the temperature. The function of the entire fuel injection valve is therefore no longer robust above the operating temperature.

Offenbarung der ErfindungDisclosure of the invention

Demgegenüber ist der Ankerhub des erfindungsgemäßen Kraftstoffinjektors über die Betriebstemperatur nahezu konstant. Weiterhin sind an der Ankerhubeinstellung vergleichsweise wenig Bauteile beteiligt, so dass der Toleranzfehler des Ankerhubs während der Montage minimiert ist. Die Funktionalität des gesamten Kraftstoffinjektors ist dadurch verbessert und robuster gestaltet.In contrast, the armature stroke of the fuel injector according to the invention is almost constant over the operating temperature. Furthermore, comparatively few components are involved in the anchor stroke adjustment, so that the tolerance error of the anchor stroke during assembly is minimized. This improves the functionality of the entire fuel injector and makes it more robust.

Dazu umfasst der Kraftstoffinjektor ein Steuerventil und ein Einspritzventilglied. Das Einspritzventilglied begrenzt einen Steuerraum und ist längsbeweglich in dem Kraftstoffinjektor geführt. Das Einspritzventilglied öffnet und sperrt durch seine Bewegung zumindest eine Einspritzöffnung in den Brennraum. Das Steuerventil steuert den Druck in dem Steuerraum. Das Steuerventil umfasst eine Magnetbaugruppe, einen Anker, ein Ventilstück und einen an dem Ventilstück ausgebildeten Ventilsitz. Der Anker umfasst eine Ankerplatte, wobei die Ankerplatte von der Magnetbaugruppe ansteuerbar ist. Der Anker wirkt zumindest mittelbar mit dem Ventilsitz zum Entlasten des Steuerraums zusammen. Ein Kronenring ist zwischen dem Ventilstück und der Magnetbaugruppe verspannt.For this purpose, the fuel injector comprises a control valve and an injection valve member. The injection valve member delimits a control chamber and is guided in the fuel injector in a longitudinally movable manner. The injection valve member opens and blocks at least one injection opening into the combustion chamber due to its movement. The control valve controls the pressure in the control room. The control valve comprises a magnet assembly, an armature, a valve piece and a valve seat formed on the valve piece. The armature comprises an armature plate, the armature plate being controllable by the magnet assembly. The armature interacts at least indirectly with the valve seat to relieve the control space. A crown ring is clamped between the valve piece and the magnet assembly.

Der Kronenring definiert somit, gegebenenfalls zusammen mit weiteren Bauteilen, den Abstand zwischen dem Ventilstück mit dem Ventilsitz einerseits und der Magnetbaugruppe andererseits. Die beiden Fixpositionen für den Ankerhub sind dadurch auf einfache Art und Weise festgelegt und dementsprechend Toleranzschwankungen minimiert. Für die Änderung des Ankerhubs über den Betriebstemperaturen müssen so vorwiegend lediglich die Wärmeausdehnungskoeffizienten von Anker und Kronenring berücksichtigt werden.The crown ring thus defines, possibly together with other components, the distance between the valve piece with the valve seat on the one hand and the magnet assembly on the other. The two fixed positions for the armature stroke are thus defined in a simple manner and tolerance fluctuations are accordingly minimized. For the change of the armature stroke above the operating temperatures, only the Thermal expansion coefficients of anchor and crown ring are taken into account.

In einer vorteilhaften Weiterbildung ist an dem Ventilstück eine zylindrische Mantelfläche ausgebildet. Der Kronenring ist auf dieser Mantelfläche koaxial zu dem Ventilsitz positioniert. Durch die Koaxialität ist der Kronenring optimal zu dem Ventilstück und dem Ventilsitz ausgerichtet, dementsprechend ist der Kraftfluss sehr homogen, so dass es zu keinen Verkippungen bzw. Schiefstellungen der verspannten Bauteile kommt. Die Rotationssymmetrie kann so weitestgehend erhalten werden.In an advantageous development, a cylindrical outer surface is formed on the valve piece. The crown ring is positioned on this lateral surface coaxially with the valve seat. Due to the coaxiality, the crown ring is optimally aligned with the valve piece and the valve seat, so the power flow is very homogeneous, so that there is no tilting or misalignment of the clamped components. The rotational symmetry can be largely preserved.

In einer vorteilhaften Weiterbildung ist an dem Kronenring eine zylindrische Führungsfläche ausgebildet. Der Anker ist längsbeweglich in dieser Führungsfläche geführt. Dadurch kommt dem Kronenring eine weitere Funktion zu: er richtet den Anker radial aus bzw. positioniert ihn koaxial zum Ventilsitz. So sind die Schließfunktion des Steuerventils und seine Lebensdauer optimiert; es kommt zu keinen Funktionsstörungen oder Schiefständen des Steuerventils. Ein Schiefstand des Ankers bedeutet in der Regel erhöhten Verschleiß des Steuerventils.In an advantageous development, a cylindrical guide surface is formed on the crown ring. The armature is guided longitudinally in this guide surface. This means that the crown ring has another function: it radially aligns the anchor or positions it coaxially with the valve seat. The closing function of the control valve and its service life are optimized; there are no malfunctions or misalignments of the control valve. Skewing the armature usually means increased wear on the control valve.

In vorteilhaften Ausführungen ist eine Ankerhubeinstellscheibe zwischen dem Kronenring und dem Ventilstück verspannt. Die Ankerhubeinstellscheibe ist einfacher zu fertigen als der Kronenring. Daher kann die Ankerhubeinstellscheibe auch einfacher mit unterschiedlichen Scheibendicken gefertigt werden, welche dann je nach Toleranzkette der beteiligten Bauteile zur Einstellung des Ankerhubs gezielt verbaut werden. Der Kronenring kann demzufolge kostengünstig in nur einer einzigen Höhe gefertigt werden. In einer alternativen Ausführung ist die Ankerhubeinstellscheibe zwischen dem Kronenring und der Magnetbaugruppe verspannt.In advantageous embodiments, an anchor stroke adjusting disc is clamped between the crown ring and the valve piece. The anchor stroke shim is easier to manufacture than the crown ring. Therefore, the anchor stroke adjusting disc can also be manufactured more easily with different disc thicknesses, which are then installed depending on the tolerance chain of the components involved to adjust the anchor stroke. The crown ring can therefore be manufactured inexpensively at only a single height. In an alternative embodiment, the armature stroke adjusting disk is clamped between the crown ring and the magnet assembly.

Gemäß einer ersten erfindungsgemäßen Alternative ist in der Ankerplatte eine Plattennut ausgebildet. Der Kronenring weist eine Krone auf, wobei die Krone durch die Plattennut ragt. Dadurch ist das Steuerventil - speziell im Bereich Anker und Kronenring - sehr bauraumsparend ausgeführt. Eine Umgreifung des Ankers ist nicht erforderlich. Vorzugsweise erfüllt der Kronenring dabei auch die Funktion einer Verdrehsicherung, das heißt eine Rotation der Ankerplatte bzw. des Ankers um seine Längsachse wird verhindert.According to a first alternative according to the invention, a plate groove is formed in the anchor plate. The crown ring has a crown, the crown protruding through the plate groove. As a result, the control valve - especially in the area of the anchor and crown ring - is very space-saving. It is not necessary to reach around the anchor. The crown ring preferably also fulfills the function of securing against rotation, that is to say rotation of the anchor plate or of the anchor about its longitudinal axis is prevented.

In einer vorteilhaften Weiterbildung ist in der Krone eine Lagerausnehmung ausgebildet. In der Lagerausnehmung ist ein Wälzkörper gelagert, wobei der Wälzkörper mit der Plattennut zusammenwirkt. Vorzugsweise ist der Wälzkörper dabei kugelförmig gestaltet. Die Ankerplatte bzw. der Anker rollt somit während des Öffnens und Schließens des Steuerventils auf dem Wälzkörper ab. Die auftretende Reibung ist aufgrund der theoretischen Punktauflage minimal und über die Lebensdauer konstant. Die Verdrehsicherung ist dadurch sehr reibungsarm und energiesparend ausgeführt.In an advantageous development, a bearing recess is formed in the crown. A rolling element is mounted in the bearing recess, the rolling element interacting with the plate groove. The rolling element is preferably designed spherical. The armature plate or armature thus rolls on the rolling element during the opening and closing of the control valve. The friction that occurs is minimal due to the theoretical point support and constant over the service life. The anti-rotation device is therefore designed to be very low-friction and energy-saving.

Vorteilhafterweise ist der Wälzkörper aus einem amagnetischen Material, vorzugsweise einer Keramik, ausgeführt. Dadurch unterliegt der Wälzkörper keinen durch die Magnetbaugruppe hervorgerufenen elektromagnetischen Kräften.The rolling element is advantageously made of an amagnetic material, preferably a ceramic. As a result, the rolling element is not subject to any electromagnetic forces caused by the magnetic assembly.

In vorteilhaften Ausführungen ist zwischen der Magnetbaugruppe und der Ankerplatte eine Restluftspaltscheibe angeordnet. Dadurch wird ein sogenanntes Verkleben zwischen der Ankerplatte und der Magnetbaugruppe in maximaler Öffnungsstellung, also bei maximalem Ankerhub, vermieden. Vorzugsweise ist die Restluftspaltscheibe dabei nicht magnetisch.In advantageous embodiments, a residual air gap disc is arranged between the magnet assembly and the armature plate. This avoids so-called sticking between the armature plate and the magnet assembly in the maximum opening position, that is, with the maximum armature stroke. The residual air gap disk is preferably not magnetic.

Gemäß einer zweiten erfindungsgemäßen Alternative weist das Material des Kronenrings einen größeren Wärmeausdehnungskoeffizienten auf als das Material des Ankers und ist der Kronenring den Anker zumindest teilweise radial umgebend angeordnet. Der Anker unterliegt demzufolge im Betrieb einer größeren Temperaturlast aufgrund des schnell abströmenden und unter Hochdruck stehenden Kraftstoffs. Durch den größeren Wärmeausdehnungskoeffizienten des Kronenrings werden bezüglich der auftretenden Längenänderungen die unterschiedlichen Temperaturlasten kompensiert. Die im Steuerventil auftretenden thermischen Spannungen werden dadurch minimiert. Gemäß dieser zweiten erfindungsgemäßen Alternative umgibt der Kronenring den Anker außen. Dadurch umgreift der Kronenring den Anker quasi. Der Anker kann so geometrisch unverändert bleiben; die auf den Anker bzw. die Ankerplatte wirkende elektromagnetische Kraft wird somit durch den Kronenring nicht beeinflusst.According to a second alternative according to the invention, the material of the crown ring has a greater coefficient of thermal expansion than the material of the anchor and the crown ring is arranged at least partially radially surrounding the anchor. The armature is therefore subject to a greater temperature load during operation due to the rapidly flowing and high-pressure fuel. Due to the larger thermal expansion coefficient of the crown ring, the different length changes occur Temperature loads compensated. This minimizes the thermal stresses that occur in the control valve. According to this second alternative according to the invention, the crown ring surrounds the anchor on the outside. As a result, the crown ring virtually engages around the anchor. The anchor can thus remain geometrically unchanged; the electromagnetic force acting on the armature or the armature plate is therefore not influenced by the crown ring.

Vorteilhafterweise ist das Material des Kronenrings amagnetisch. Vorzugsweise ist der Kronenring aus einem austenitischem Sinterstahl oder einer Keramik gefertigt. Dadurch beeinflusst der Kronenring das Magnetfeld der Magnetbaugruppe nicht negativ. Die magnetische Kraft auf die Ankerplatte wird somit nicht verfälscht.The material of the crown ring is advantageously non-magnetic. The crown ring is preferably made of an austenitic sintered steel or a ceramic. As a result, the crown ring does not negatively influence the magnetic field of the magnetic assembly. The magnetic force on the anchor plate is therefore not falsified.

In vorteilhaften Ausführungen ist die Magnetbaugruppe mittels einer Spannfeder mit dem Kronenring verspannt. Dies ist eine sehr einfache und effiziente Verspannung. Auf zusätzliche aufwändige Schraubverbindungen im Inneren des Kraftstoffinjektors kann dadurch verzichtet werden.In advantageous embodiments, the magnet assembly is clamped to the crown ring by means of a tension spring. This is a very simple and efficient bracing. This eliminates the need for additional complex screw connections inside the fuel injector.

In vorteilhaften Weiterbildungen ist die Magnetbaugruppe von zumindest einem Kontaktstift elektrisch kontaktierbar. Weiterhin weist der zumindest eine Kontaktstift einen Schiebersitz auf. Dadurch kann die Magnetbaugruppe in der Montage axial variabel positioniert werden, ohne dass die elektrische Kontaktierung dabei verloren geht.In advantageous developments, the magnetic assembly can be electrically contacted by at least one contact pin. Furthermore, the at least one contact pin has a slide seat. As a result, the magnet assembly can be axially variably positioned during assembly without the electrical contact being lost.

In vorteilhaften Ausführungen ist der Anker von einer Feder in Richtung des Ventilsitzes beaufschlagt. Dies ist zum einen eine einfache und kostengünstige Ausführung, um den Anker bzw. den Schließkörper gegen den Ventilsitz in Schließstellung zu drücken. Zum anderen erfolgt der Schließvorgang des Steuerventils so sehr schnell und effizient.In advantageous embodiments, the armature is acted upon by a spring in the direction of the valve seat. On the one hand, this is a simple and inexpensive design for pressing the armature or the closing body against the valve seat in the closed position. On the other hand, the control valve closes very quickly and efficiently.

In vorteilhaften Weiterbildungen ragt ein Ankerbolzen durch den Anker. Dadurch kann die hydraulisch resultierende Kraft auf den Anker in axialer Richtung verringert oder sogar auf Null gesetzt werden. Somit kann ein druck- bzw. kraftausgeglichenes Steuerventil realisiert werden. Dementsprechend können beispielsweise die Magnetbaugruppe und die Feder verkleinert werden, da zur Bewegung des Ankers nur mehr geringere Kräfte erforderlich sind.In advantageous developments, an anchor bolt protrudes through the anchor. As a result, the hydraulically resulting force on the armature can be reduced in the axial direction or even set to zero. A pressure or force-balanced control valve can thus be implemented. Accordingly, for example, the magnet assembly and the spring can be downsized, since only smaller forces are required to move the armature.

Vorzugsweise weisen der Ankerbolzen und der Ventilsitz nahezu den gleichen Durchmesser auf. Dadurch ist ein druck- bzw. kraftausgeglichenes Steuerventil realisiert.The anchor bolt and the valve seat preferably have almost the same diameter. As a result, a pressure or force-balanced control valve is realized.

Kurze Beschreibung der ZeichnungenBrief description of the drawings

Anhand der Zeichnung wird die Erfindung nachstehend eingehender beschrieben.The invention is described in more detail below with reference to the drawing.

Es zeigt:

Figur 1
eine schematische Darstellung eines Kraftstoffinjektors aus dem Stand der Technik,
Figur 2
ein erfindungsgemäßes Steuerventil im Längsschnitt, wobei nur die wesentlichen Bereiche dargestellt sind,
Figur 3
den Schnitt A-A der Figur 2 durch das Steuerventil des Kraftstoffinjektors,
Figur 4
ein erfindungsgemäßes Steuerventil im Längsschnitt in einer weiteren Ausführungsform, wobei nur die wesentlichen Bereiche dargestellt sind,
Figur 5
ein erfindungsgemäßes Steuerventil im Längsschnitt in noch einer weiteren Ausführungsform, wobei nur die wesentlichen Bereiche dargestellt sind,
Figur 6
ein erfindungsgemäßes Steuerventil im Längsschnitt in noch einer weiteren Ausführungsform, wobei nur die wesentlichen Bereiche dargestellt sind,
Figur 7a
ein erfindungsgemäßes Steuerventil in perspektivischer Ansicht mit geschnittenem Anker in noch einer weiteren Ausführungsform, wobei nur die wesentlichen Bereiche dargestellt sind,
Figur 7b
die Draufsicht auf die Ausführungsform der Figur 7a, wobei nur die wesentlichen Bereiche dargestellt sind.
Figur 8a
ein erfindungsgemäßes Steuerventil im Schnitt in noch einer weiteren Ausführungsform, wobei nur die wesentlichen Bereiche dargestellt sind,
Figur 8b
die Draufsicht auf die Ausführungsform der Figur 8a, wobei nur die wesentlichen Bereiche dargestellt sind.
It shows:
Figure 1
1 shows a schematic illustration of a fuel injector from the prior art,
Figure 2
a control valve according to the invention in longitudinal section, only the essential areas are shown,
Figure 3
the section AA the Figure 2 through the control valve of the fuel injector,
Figure 4
a control valve according to the invention in longitudinal section in a further embodiment, only the essential areas are shown,
Figure 5
a control valve according to the invention in longitudinal section in yet another embodiment, only the essential areas are shown,
Figure 6
a control valve according to the invention in longitudinal section in yet another embodiment, only the essential areas are shown,
Figure 7a
a control valve according to the invention in a perspective view with a cut armature in yet another embodiment, only the essential areas being shown,
Figure 7b
the top view of the embodiment of the Figure 7a , where only the essential areas are shown.
Figure 8a
a control valve according to the invention in section in yet another embodiment, only the essential areas are shown,
Figure 8b
the top view of the embodiment of the Figure 8a , where only the essential areas are shown.

Beschreibungdescription

Fig.1 ist in schematischer Weise ein Kraftstoffinjektor 100 zu entnehmen, wie er aus dem Stand der Technik bekannt ist. Mit dem Kraftstoffinjektor 100 wird Kraftstoff in den Brennraum einer Brennkraftmaschine eingespritzt. Der Kraftstoffinjektor 100 umfasst einen Haltekörper 10 und ein Steuerventil 1 mit einer Magnetbaugruppe 2 und einem darin angeordneten Magnetkern 3. Über das Steuerventil 1 ist ein beweglich im Haltekörper 10 aufgenommenes Einspritzventilglied 11 betätigbar. Fig. 1 a fuel injector 100 can be seen in a schematic manner, as is known from the prior art. The fuel injector 100 is used to inject fuel into the combustion chamber of an internal combustion engine. The fuel injector 100 comprises a holding body 10 and a control valve 1 with a magnet assembly 2 and a magnetic core 3 arranged therein. An injection valve member 11, which is movably received in the holding body 10, can be actuated via the control valve 1.

Das Einspritzventilglied 11 - im Allgemeinen nadelförmig ausgebildet - gibt an einem brennraumseitigen Ende des Kraftstoffinjektors 100 an einem Düsenkörper 12 ausgebildete Einspritzöffnungen 13 in den Brennraum der Brennkraftmaschine frei oder verschließt diese, so dass Kraftstoff bei Bedarf in den Brennraum eingespritzt werden kann. Der Düsenkörper 12 ist durch eine Spannmutter 14 mit dem Haltekörper 10 mediendicht verschraubt.The injection valve member 11 - generally needle-shaped - opens or closes injection openings 13 in the combustion chamber of the internal combustion engine at an end of the fuel injector 100 on a nozzle body 12, so that fuel can be injected into the combustion chamber if necessary. The nozzle body 12 is screwed to the holding body 10 in a media-tight manner by a clamping nut 14.

Das Steuerventil 1 umfasst ein Ventilstück 4, das in den Haltekörper 10 eingebaut ist und einen Steuerraum 15 zur Betätigung des Einspritzventilgliedes 11 aufweist, dessen Öffnen bzw. Verschließen durch das Steuerventil 1 gesteuert wird. Das Steuerventil 1 steuert so den Druck in dem Steuerraum 15. Die Funktionsweise des Kraftstoffinjektors 100 ist dabei so, dass sich bei einer Druckreduzierung im Steuerraum 15 das Einspritzventilglied 11 in den Steuerraum 15 schiebt und damit die Einspritzöffnungen 13 frei gibt und dass bei einer Druckerhöhung im Steuerraum 15 dieser hydraulische Druck das Einspritzventilglied 11 in Richtung des Brennraums drückt und dadurch die Einspritzöffnungen 13 verschlossen werden.The control valve 1 comprises a valve piece 4, which is installed in the holding body 10 and has a control chamber 15 for actuating the injection valve member 11, the opening or closing of which is controlled by the control valve 1. The control valve 1 thus controls the pressure in the control chamber 15. The mode of operation of the fuel injector 100 is such that when the pressure in the control chamber 15 is reduced, the injection valve member 11 pushes into the control chamber 15 and thus releases the injection openings 13 and that when the pressure increases in the Control chamber 15 this hydraulic pressure pushes the injection valve member 11 in the direction of the combustion chamber and thereby the injection openings 13 are closed.

Generell kann dabei das Einspritzventilglied 11 auch mehrteilig ausgeführt sein.In general, the injection valve member 11 can also be made in several parts.

Fig.2 zeigt ein erfindungsgemäßes Steuerventil 1 im Längsschnitt, wobei nur die wesentlichen Bereiche dargestellt sind. Am unteren Rand der Fig.2 ist noch das in dem Ventilstück 4 geführte Einspritzventilglied 11 zu sehen, welches durch die Druckänderung im Steuerraum 15 in axialer Richtung des Kraftstoffinjektors 100 bewegt wird. Das Ventilstück 4 ist dabei in dem Haltekörper 10 verspannt. Der Steuerraum 15 ist durch eine in dem Ventilstück 4 ausgebildete Ablaufdrossel 16 mit einem Ventilraum 17 verbunden. Der Ventilraum 17 ist durch das Steuerventil 1 mit einem Niederdruckraum 18 verbindbar, wobei der Niederdruckraum 18 in ein nichtdargestelltes Rücklaufsystem des Kraftstoffinjektors 100 mündet. Fig. 2 shows a control valve 1 according to the invention in longitudinal section, only the essential areas being shown. At the bottom of the Fig. 2 one can still see the injection valve member 11 guided in the valve piece 4, which is moved in the axial direction of the fuel injector 100 by the pressure change in the control chamber 15. The valve piece 4 is clamped in the holding body 10. The control chamber 15 is connected to a valve chamber 17 by an outlet throttle 16 formed in the valve piece 4. The valve chamber 17 can be connected to a low-pressure chamber 18 by the control valve 1, the low-pressure chamber 18 opening into a return system (not shown) of the fuel injector 100.

Der Ventilraum 17 ist von dem Ventilstück 4, einem zumindest teilweise hülsenförmigen Anker 5 und einem Ankerbolzen 6 begrenzt. Der Niederdruckraum 18 ist von dem Ventilstück 4 und dem Anker 5 begrenzt. Der Anker 5 wirkt mit einem an dem Ventilstück 4 ausgebildeten Ventilsitz 7 zusammen. Liegt der Anker 5 an dem Ventilsitz 7 an, dann ist eine hydraulische Verbindung von dem Ventilraum 17 zu dem Niederdruckraum 18 getrennt; ist der Anker 5 von dem Ventilsitz 7 abgehoben, dann ist die hydraulische Verbindung von dem Ventilraum 17 zu dem Niederdruckraum 18 geöffnet.The valve chamber 17 is delimited by the valve piece 4, an at least partially sleeve-shaped armature 5 and an armature bolt 6. The low-pressure chamber 18 is delimited by the valve piece 4 and the armature 5. The armature 5 interacts with a valve seat 7 formed on the valve piece 4. If the armature 5 rests on the valve seat 7, then a hydraulic connection is separated from the valve chamber 17 to the low-pressure chamber 18; If the armature 5 is lifted off the valve seat 7, the hydraulic connection from the valve chamber 17 to the low-pressure chamber 18 is opened.

Der Ankerbolzen 6 ist zumindest teilweise in einer Bohrung des Ankers 5 angeordnet und führt so den Anker 5 längsbeweglich. Der Ankerbolzen 6 begrenzt weiterhin den Ventilraum 17 und dient somit einem Druckausgleich des Ankers 5. Demzufolge ist der Anker 5 zumindest in seinem dem Ventilraum 17 benachbarten Bereich hülsenförmig ausgeführt und kann so druck- bzw. kraftausgeglichen gestaltet werden, indem der Ventilsitz 7 nahezu denselben Durchmesser aufweist wie der Ankerbolzen 6. Genaugenommen muss die Bohrung des Ankers 5, durch welche der Ankerbolzen 6 ragt, denselben Durchmesser aufweisen wie der Ventilsitz 7. Dann ist die hydraulisch resultierende Kraft auf den Anker 5 in axialer Richtung gleich Null. Das Steuerventil 1 wird dann als kraftausgeglichen bzw. druckausgeglichen bezeichnet.The anchor bolt 6 is at least partially arranged in a bore in the anchor 5 and thus guides the anchor 5 in a longitudinally movable manner. The armature bolt 6 further delimits the valve space 17 and thus serves to equalize the pressure of the armature 5. Accordingly, the armature 5 is of sleeve-shaped design, at least in its area adjacent to the valve space 17, and can thus be designed to be pressure or force balanced by the valve seat 7 having almost the same diameter has as the armature pin 6. Strictly speaking, the bore of the armature 5, through which the armature pin 6 projects, must have the same diameter as the valve seat 7. Then the hydraulically resulting force on the armature 5 in the axial direction is zero. The control valve 1 is then referred to as force-balanced or pressure-balanced.

Die Längsbewegung des Ankers 5 kann alternativ auch von einem Ventilstückhals 41 des Ventilstücks 4 geführt werden.The longitudinal movement of the armature 5 can alternatively also be guided by a valve piece neck 41 of the valve piece 4.

Der Anker 5 ist von einer Feder 8 kraftbeaufschlagt und wird von dieser gegen den Ventilsitz 7 gedrückt. Optional ist dabei zwischen dem Anker 5 und der Feder 8 ein Auflagering 81 angeordnet, wobei der Auflagering 81 vorzugsweise der Einstellung der Kraft der Feder 8 dient. Die Magnetbaugruppe 2 mit dem darin angeordneten Magnetkern 3 ist an der dem Ventilraum 17 gegenüberliegenden Seite des Ankers 5 angeordnet und optional von einer nicht dargestellten Magnethülse umgeben. Bei Bestromung des Magnetkerns 3 durch Kontaktstifte 31 wird eine elektromagnetische Kraft auf eine Ankerplatte 50 des Ankers 5 ausgeübt, so dass der Anker 5 entgegen der Kraft der Feder 8 von dem Ventilsitz 7 abgehoben wird.The armature 5 is acted upon by a spring 8 and is pressed by it against the valve seat 7. A support ring 81 is optionally arranged between the armature 5 and the spring 8, the support ring 81 preferably serving to adjust the force of the spring 8. The magnet assembly 2 with the magnet core 3 arranged therein is arranged on the side of the armature 5 opposite the valve chamber 17 and optionally surrounded by a magnet sleeve (not shown). When the magnetic core 3 is energized by contact pins 31, an electromagnetic force is exerted on an armature plate 50 of the armature 5, so that the armature 5 is lifted from the valve seat 7 against the force of the spring 8.

Die Magnetbaugruppe 2 stützt sich über einen Kronenring 20 und eine Ankerhubeinstellscheibe 21 direkt auf dem Ventilstück 4 ab. Dazu ist an dem Ventilstück 4 eine Stirnfläche 40 ausgebildet, die mit der Ankerhubeinstellscheibe 21 zusammenwirkt. Der Kronenring 20 ist daran anschließend mit der Magnetbaugruppe 2 verspannt, wobei zumindest eine Krone 29 an dem Kronenring 20 ausgebildet bzw. angeordnet ist. Die Ankerplatte 50 weist zumindest eine Plattennut 54 auf, durch die in axialer Richtung die Krone 29 hindurchgeführt ist. Die Krone 29 wirkt so mit der Magnetbaugruppe 2 zusammen bzw. ist mit dieser verspannt.The magnet assembly 2 is supported directly on the valve piece 4 via a crown ring 20 and an anchor stroke adjusting disk 21. For this purpose, an end face 40 is formed on the valve piece 4, which cooperates with the anchor stroke adjusting disk 21. The crown ring 20 is then clamped to the magnet assembly 2, at least one crown 29 being formed or arranged on the crown ring 20. The anchor plate 50 has at least one plate groove 54 through which the crown 29 is guided in the axial direction. The crown 29 thus interacts with the magnet assembly 2 or is clamped to it.

Die Magnetbaugruppe 2 wiederum wird von einer Spannfeder 22 gegen die Krone 29 gedrückt. Die Spannfeder 22 kann dabei, wie in der Fig.2 dargestellt, als Tellerfeder ausgeführt sein, alternativ auch mit entgegengesetzter Wölbung. Die Spannfeder 22 kann jedoch auch als beliebige Feder ausgeführt sein, beispielsweise als Wellenfeder.The magnetic assembly 2 in turn is pressed against the crown 29 by a tension spring 22. The tension spring 22 can, as in the Fig. 2 shown, be designed as a plate spring, alternatively also with opposite curvature. However, the tension spring 22 can also be designed as any spring, for example as a wave spring.

Ein Sicherungsring 24 dient als Montagehilfe, damit die Magnetbaugruppe 2 während der Montage nicht aus dem Kraftstoffinjektor 100 fällt. Eine Restluftspaltscheibe 23 ist außenliegend zwischen der Magnetbaugruppe 2 und dem Anker 5 angeordnet und verhindert ein Haften des Ankers 5 an der Magnetbaugruppe 2. Alternativ kann die Restluftspaltscheibe 23 auch innenliegend ausgeführt sein; dann wäre sie zwischen dem Innenpol der Magnetbaugruppe 2 und der Ankerplatte 50 angeordnet.A locking ring 24 serves as an assembly aid so that the magnet assembly 2 does not fall out of the fuel injector 100 during assembly. A residual air gap disk 23 is arranged on the outside between the magnet assembly 2 and the armature 5 and prevents the armature 5 from sticking to the magnet assembly 2. Alternatively, the residual air gap disk 23 can also be designed on the inside; then it would be arranged between the inner pole of the magnet assembly 2 and the armature plate 50.

Zur Einstellung des Ankerhubs, also des Weges, den der Anker 5 bei seinen Öffnungs- und Schließbewegungen zwischen dem Ventilsitz 7 und der Restluftspaltscheibe 23 ausführen kann, wird den relevanten Maßen des Steuerventils 1 angepasst eine entsprechende Ankerhubeinstellscheibe 21 verwendet. In alternativen Ausführungen können der Kronenring 20 und die Ankerhubeinstellscheibe 21 auch einteilig ausgeführt sein; dementsprechend würde der Ankerhub dann über die axiale Länge des Kronenrings 20 eingestellt.To adjust the armature stroke, that is, the path that the armature 5 can perform during its opening and closing movements between the valve seat 7 and the residual air gap disk 23, a corresponding armature stroke adjusting disk 21 is used, adapted to the relevant dimensions of the control valve 1. In alternative embodiments, the crown ring 20 and the anchor stroke adjusting disk 21 can also be made in one piece; accordingly, the armature stroke would then be adjusted over the axial length of the crown ring 20.

Der Kronenring 20 kann vorteilhaft als austenitisches Sinterteil ausgeführt werden, um den Magnetfluss der Magnetbaugrupee2 nicht zu beeinträchtigen. Alternativ ist auch ein keramisches Sinterteil einsetzbar.The crown ring 20 can advantageously be designed as an austenitic sintered part in order not to impair the magnetic flux of the magnet assembly 2. Alternatively, a ceramic sintered part can also be used.

Die Fig.3 zeigt den Schnitt A-A der Fig.2 durch das Steuerventil 1. Der Anker 5 ist auf dem Ankerbolzen 6 längsbeweglich, also senkrecht zur Schnittebene, geführt. Die Ankerplatte 50 des Ankers 5 weist drei Ankerflügel 51, 52, 53 auf, die jeweils eine Kreissegmentform haben. Zwischen je zwei Ankerflügeln ist jeweils eine Plattennut 54, 55, 56 der Ankerplatte 50 ausgebildet. Jeweils eine Krone 29 des Kronenrings 20 ist in jeweils einer Plattennut 54, 55, 56 angeordnet, so dass die drei Kronen 29 durch die Ankerplatte 50 hindurch ragen und so im montierten Zustand die Magnetbaugruppe 2 kontaktieren. In alternativen Ausführungen kann der Kronenring 20 eine beliebige Anzahl von Kronen 29 aufweisen.The Fig. 3 shows the section AA of the Fig. 2 through the control valve 1. The armature 5 is longitudinally movable on the anchor bolt 6, that is perpendicular to the cutting plane. The anchor plate 50 of the armature 5 has three anchor wings 51, 52, 53, each of which has a circular segment shape. A plate groove 54, 55, 56 of the anchor plate 50 is formed between each two anchor wings. In each case one crown 29 of the crown ring 20 is arranged in a plate groove 54, 55, 56, so that the three crowns 29 protrude through the anchor plate 50 and thus contact the magnet assembly 2 in the assembled state. In alternative embodiments, the crown ring 20 can have any number of crowns 29.

Die Kronen 29 dienen in einer vorteilhaften Weiterbildung nicht nur der Verspannung bzw. Positionierung der Magnetbaugruppe 2, sondern auch als Verdrehsicherung der Ankerplatte 50 bzw. des Ankers 5. Unnötige Rotation des Ankers 5 und damit auch zusätzlicher Verschleiß werden dadurch vermieden.In an advantageous further development, the crowns 29 serve not only to brace or position the magnet assembly 2, but also to prevent the armature plate 50 or the armature 5 from rotating. Unnecessary rotation of the armature 5 and thus also additional wear are thereby avoided.

Fig.4 zeigt ein weiteres Ausführungsbeispiel des erfindungsgemäßen Steuerventils 1 im Längsschnitt, wobei im Folgenden nur auf die wesentlichen Unterschiede zum Ausführungsbeispiel der Fig.2 eingegangen werden soll. Fig. 4 shows a further embodiment of the control valve 1 according to the invention in longitudinal section, wherein only the essential differences to the embodiment of the Fig. 2 to be received.

In der Ausführung der Fig.2 wird der Anker 5 von dem Ankerbolzen 6, oder alternativ von dem Ventilstückhals 41, längsbeweglich geführt. Die Führung des Ankers 5 erfolgt in dem Ausführungsbeispiel der Fig.4 durch den Kronenring 20. Dazu ist an dem Ventilstück 4 ein Kragen 42 angeordnet, welcher innen den Ventilraum 17 begrenzt. Auf einer äußeren Mantelfläche 43 des Kragens 42 ist der Kronenring 20 über eine an ihm ausgebildete innere Positionierfläche 27 zumindest radial fixiert, so dass er vorzugsweise konzentrisch zu dem Ventilsitz 7 angeordnet ist. In alternativen Ausführungen können die Positionierfläche 27 jedoch auch außenliegend und somit die Mantelfläche 43 innenliegend sein. Der Kragen 42 ist im Vergleich zum Ventilstückhals 41 der Fig.2 kürzer ausgeführt, da er keine Führungsfunktion für den Anker 5 mehr hat.In the execution of the Fig. 2 the armature 5 is guided in a longitudinally movable manner by the armature bolt 6, or alternatively by the valve piece neck 41. The armature 5 is guided in the embodiment of FIG Fig. 4 through the crown ring 20. For this purpose, a collar 42 is arranged on the valve piece 4, which inside the Valve space 17 limited. The crown ring 20 is at least radially fixed on an outer lateral surface 43 of the collar 42 via an inner positioning surface 27 formed on it, so that it is preferably arranged concentrically with the valve seat 7. In alternative embodiments, however, the positioning surface 27 can also be on the outside and thus the outer surface 43 can be on the inside. The collar 42 is compared to the valve neck 41 of the Fig. 2 shorter because it no longer has a guiding function for anchor 5.

Der Kronenring 20 ist den Anker 5 zumindest teilweise radial umgebend angeordnet. Der Kronenring 20 weist weiterhin eine innere Führungsfläche 28 auf, mit der der Anker 5 längsbeweglich geführt ist. In vorteilhaften Ausführungen sind die Positionierfläche 27 und die Führungsfläche 28 dieselbe innere Mantelfläche des Kronenrings 20, wobei die Positionierfläche 27 und die Führungsfläche 28 in axialer Richtung betrachtet übereinander angeordnet sind.The crown ring 20 is at least partially radially surrounding the armature 5. The crown ring 20 also has an inner guide surface 28 with which the armature 5 is guided in a longitudinally movable manner. In advantageous embodiments, the positioning surface 27 and the guide surface 28 are the same inner lateral surface of the crown ring 20, the positioning surface 27 and the guide surface 28 being arranged one above the other when viewed in the axial direction.

Weiterhin ist in dem Kronenring 20 zumindest eine Ablaufbohrung 26 ausgebildet, die Bestandteil des Niederdruckraums 18 ist und so den Ventilraum 17 mit dem Niederdrucksystem bzw. Rücklaufsystem des Kraftstoffinjektors 100 verbindet. Die Kontaktstifte 31 in der Ausführungsform der Fig.4 weisen einen Schiebersitz 31a auf, durch welchen die axiale Länge des Kontaktstiftes 31 variabel gestaltet ist, so dass die Magnetbaugruppe 2 während des Montageprozesses axial korrekt positioniert werden kann, ohne dass die elektrische Kontaktierung des Magnetkerns 3 unterbrochen wird.Furthermore, at least one drain hole 26 is formed in the crown ring 20, which is part of the low-pressure chamber 18 and thus connects the valve chamber 17 to the low-pressure system or return system of the fuel injector 100. The contact pins 31 in the embodiment of FIG Fig. 4 have a slide seat 31a, by means of which the axial length of the contact pin 31 is designed to be variable, so that the magnet assembly 2 can be correctly positioned axially during the assembly process without the electrical contacting of the magnetic core 3 being interrupted.

Auch in der in Fig.4 dargestellten Ausführung können der Kronenring 20 und die Ankerhubeinstellscheibe 21 einteilig ausgeführt sein.Also in the Fig. 4 shown embodiment, the crown ring 20 and the anchor stroke adjusting disc 21 can be made in one piece.

Fig.5 zeigt noch ein weiteres Ausführungsbeispiel des erfindungsgemäßen Steuerventils 1 im Längsschnitt, wobei im Folgenden nur auf die wesentlichen Unterschiede zu den Ausführungsbeispielen der Fig.2 und Fig.4 eingegangen werden soll. Fig. 5 shows yet another embodiment of the control valve 1 according to the invention in longitudinal section, wherein only the essential differences to the embodiments of the Fig. 2 and Fig. 4 to be received.

Auch im Ausführungsbeispiel der Fig.5 erfolgt die Führung des Ankers 5 durch den Kronenring 20 bzw. durch die Führungsfläche 28 des Kronenrings 20. Dazu ist, analog zur Ausführung der Fig.4 , die Positionierfläche 27 des Kronenrings 20 zumindest radial auf dem Kragen 42 des Ventilstücks 4 fixiert bzw. mit sehr geringem Spiel angeordnet.Also in the embodiment of the Fig. 5 the armature 5 is guided by the crown ring 20 or by the guide surface 28 of the crown ring 20 Fig. 4 , the positioning surface 27 of the crown ring 20th at least radially fixed on the collar 42 of the valve piece 4 or arranged with very little play.

In der Ausführung der Fig.5 ist die Krone 29 jedoch nicht durch eine Plattennut der Ankerplatte 50 hindurch geführt, sondern umgibt bzw. umgreift die Ankerplatte 50 außen. Dadurch kann die Ankerplatte 50 ohne Nuten als kompletter Kreisring ausgeführt werden. Das radiale Maß der Krone 29 wird jedoch gegebenenfalls vergrößert. In der Krone 29 bzw. im Kronenring 20 sind Abströmlöcher 25 ausgebildet, die Bestandteil des Niederdruckraums 18 sind. Optional können die Abströmlöcher 25 auch entfallen, wenn die Strömungsspalte auf der Außenseite des Kronenrings 20 bzw. der Krone 29 einen ausreichenden Strömungsquerschnitt aufweisen.In the execution of the Fig. 5 However, the crown 29 is not guided through a plate groove in the anchor plate 50, but surrounds or surrounds the anchor plate 50 on the outside. As a result, the anchor plate 50 can be designed as a complete circular ring without grooves. However, the radial dimension of the crown 29 may be increased. Outflow holes 25 are formed in the crown 29 or in the crown ring 20 and are part of the low-pressure chamber 18. Optionally, the outflow holes 25 can also be omitted if the flow gaps on the outside of the crown ring 20 or the crown 29 have a sufficient flow cross section.

Die Ankerhubeinstellscheibe 21 ist zwischen der Krone 29 und der Magnetbaugruppe 2 verspannt. In allen Ausführungsbeispielen kann die Ankerhubeinstellscheibe 21 jedoch entweder zwischen der Krone 29 und der Magnetbaugruppe 2 verspannt sein, oder zwischen dem Kronenring 20 und dem Ventilstück 4, oder zusammen mit dem Ventilstück 4 einteilig ausgeführt sein. Im Ausführungsbeispiel der Fig.5 ist ferner die Restluftspaltscheibe 23 am Innenpol der Magnetbaugruppe 2 zwischen dieser und der Ankerplatte 50 angeordnet, wobei die radiale Positionierung der Restluftspaltscheibe 23 für alle Ausführungsformen frei wählbar ist.The armature stroke adjusting disk 21 is clamped between the crown 29 and the magnet assembly 2. In all exemplary embodiments, however, the armature stroke adjusting disk 21 can either be clamped between the crown 29 and the magnet assembly 2, or between the crown ring 20 and the valve piece 4, or can be embodied in one piece together with the valve piece 4. In the embodiment of the Fig. 5 Furthermore, the residual air gap disk 23 is arranged on the inner pole of the magnet assembly 2 between the latter and the armature plate 50, the radial positioning of the residual air gap disk 23 being freely selectable for all embodiments.

Der Kraftstoffinjektor 100 des Ausführungsbeispiels der Fig.5 weist weiterhin eine Federeinstellscheibe 80 auf, die der Einstellung der Spannfeder 22 dient. Dazu ist der Haltekörper 10 unter Zwischenlage der Federeinstellscheibe 80 durch eine Überwurfmutter 9a mit einem Haltekörperkopf 9 verschraubt. An dem Haltekörperkopf 9 ist eine Anschlagfläche 9b ausgebildet, an der sich vorzugsweise sowohl die Feder 8 als auch die Spannfeder 22 und der Ankerbolzen 6 abstützen.The fuel injector 100 of the embodiment of FIG Fig. 5 also has a spring adjusting washer 80, which is used to adjust the tension spring 22. For this purpose, the holding body 10 is screwed to a holding body head 9 by means of a union nut 9a with the spring adjusting disk 80 being interposed. A stop surface 9b is formed on the holding body head 9, on which both the spring 8 and the tension spring 22 and the anchor bolt 6 are preferably supported.

Dadurch dass das Ventilstück 4 zum Haltekörper 10 fixiert ist, ist über Ventilstück 4, Haltekörper 10, Federeinstellscheibe 80 und Haltekörperkopf 9 die Anschlagfläche 9b positioniert. Andererseits ist über das Ventilstück 4, den den Kronenring 20 und die Ankerhubeinstellscheibe 21 ein unterer Anschlag für die Magnetbaugruppe 2 definiert. Ein oberer Abstand zwischen der Magnetbaugruppe 2 und der Anschlagfläche 9b wird nun durch die Federeinstellscheibe 80 so eingestellt, dass dadurch auch die Kraft der Spannfeder 80 eingestellt wird.Because the valve piece 4 is fixed to the holding body 10, the stop surface 9b is positioned via the valve piece 4, the holding body 10, the spring adjusting washer 80 and the holding body head 9. On the other hand, a lower stop for the magnet assembly 2 is defined via the valve piece 4, the crown ring 20 and the armature stroke adjusting disk 21. An upper distance between the Magnet assembly 2 and the stop surface 9b are now adjusted by the spring adjusting disk 80 in such a way that the force of the tension spring 80 is also adjusted thereby.

Weiterhin wird die Kraft der Feder 8 mit Hilfe des Auflagerings 81 eingestellt. So kann bei unbestromtem Magnetkern 3, also bei Anlage des Ankers 5 an den Ventilsitz 7, die zwischen dem Anker 5 - bzw. dem Auflagering 81 - und der Anschlagfläche 9b verspannte Feder 8 hinsichtlich ihrer Federkraft bzw. ihres Federwegs sehr gut durch die Höhe des Auflagerings 81 eingestellt werden.Furthermore, the force of the spring 8 is set using the support ring 81. Thus, when the magnetic core 3 is de-energized, i.e. when the armature 5 is in contact with the valve seat 7, the spring 8 tensioned between the armature 5 - or the support ring 81 - and the stop surface 9b can be very well adjusted in terms of its spring force or its spring travel by the height of the Support rings 81 can be set.

Fig.6 zeigt einen Ausschnitt eines weiteren Ausführungsbeispiels des erfindungsgemäßen Steuerventils 1 im Längsschnitt. Im Unterschied zu den vorhergehenden Ausführungsbeispielen weist die Ausführung der Fig.6 einen kugelförmigen Schließkörper 60 auf, der in einem Aufnahmestück 61 positioniert ist. Das Aufnahmestück 61 ist zwischen dem Anker 5 und dem Schließkörper 60 angeordnet und wird von dem Anker 5 kraftbeaufschlagt, wobei die Führungsfläche 28 des Kronenrings 20 den Anker 5 längsbeweglich führt. Aufgrund des kugelförmigen Schließkörpers 60 ist das Steuerventil 1 in dieser Ausführung nicht mehr kraftausgeglichen. Fig. 6 shows a detail of a further embodiment of the control valve 1 according to the invention in longitudinal section. In contrast to the previous exemplary embodiments, the design of the Fig. 6 a spherical closing body 60, which is positioned in a receiving piece 61. The receiving piece 61 is arranged between the armature 5 and the closing body 60 and is acted upon by the armature 5, the guide surface 28 of the crown ring 20 guiding the armature 5 in a longitudinally movable manner. Due to the spherical closing body 60, the control valve 1 is no longer force balanced in this embodiment.

Die Bauteile Anker 5, Aufnahmestück 61 und Schließkörper 60 können dabei in alternativen Ausführungen auch ein- oder zweiteilig ausgeführt werden.The components armature 5, receptacle 61 and closing body 60 can also be made in one or two parts in alternative designs.

Der Kronenring 20 ist zwischen einem an dem Ventilstück 4 ausgebildeten Absatz 49 und der Magnetbaugruppe 2 verspannt, optional unter Zwischenlage der Ankerhubeinstellscheibe 21. Dabei ist die Mantelfläche 43 des Ventilstücks 4 innenliegend und die Positionierfläche 27 des Kronenrings 20 außenliegend ausgeführt. Der Kronenring 20 ist dadurch koaxial zu dem Ventilstück 4 und demzufolge koaxial zu dem Ventilsitz 7 positioniert. Analog zu den vorangegangenen Beispielen können aber die Mantelfläche 43 auch außenliegend und die Positionierfläche 27 innenliegend ausgeführt sein.The crown ring 20 is clamped between a shoulder 49 formed on the valve piece 4 and the magnet assembly 2, optionally with the interposition of the armature stroke adjusting disk 21. The outer surface 43 of the valve piece 4 is on the inside and the positioning surface 27 of the crown ring 20 is on the outside. The crown ring 20 is thereby positioned coaxially to the valve piece 4 and consequently coaxially to the valve seat 7. Analogous to the preceding examples, the lateral surface 43 can also be designed on the outside and the positioning surface 27 on the inside.

In der Darstellung der Fig.6 sind nur die wesentlichen Bereiche gezeigt; es ist jedoch selbstverständlich, dass der Haltekörperkopf 9 zumindest mittelbar mit dem Ventilstück 4 verbunden ist, so dass auch eine Verspannung des Kronenrings 20 erfolgen kann.In the representation of the Fig. 6 only the essential areas are shown; However, it goes without saying that the holding body head 9 is at least indirectly connected to the valve piece 4, so that the crown ring 20 can also be braced.

Der Kronenring 20 weist in dieser Ausführung zwei Kronen 29 auf, die durch zwei Plattennuten 54, 55 der Ankerplatte 5 ragen. Alternativ können jedoch beliebige Anzahlen von Kronen 29 und Plattennuten 54, 55, 56 verwendet werden. Weiterhin kann der Kronenring 20 auch den Anker 5 außen umgebend gestaltet sein, wie in Fig.5 gezeigt.In this embodiment, the crown ring 20 has two crowns 29 which protrude through two plate grooves 54, 55 of the anchor plate 5. Alternatively, however, any number of crowns 29 and plate grooves 54, 55, 56 can be used. Furthermore, the crown ring 20 can also be designed to surround the armature 5 on the outside, as in FIG Fig. 5 shown.

Fiq.7 zeigt eine weitere Ausführungsform des Steuerventils 1, wobei nur die wesentlichen Bereiche dargestellt sind. Dabei zeigen die Fig.7a das Steuerventil 1 in perspektivischer Ansicht mit geschnittenem Anker 5 und die Fig.7b das Steuerventil 1 in Draufsicht auf die Ankerplatte 50. Fig. 7 shows a further embodiment of the control valve 1, only the essential areas being shown. The show Fig.7a the control valve 1 in a perspective view with a cut armature 5 and the Fig.7b the control valve 1 in plan view of the anchor plate 50.

Der Kronenring 20 der Ausführung der Fig.7a / Fig.7b weist vorteilhafterweise drei Kronen 29 auf, wobei prinzipiell eine beliebige Anzahl an Kronen 29 verwendet werden kann. Die Ankerplatte 50 weist eine entsprechende Anzahl von Plattennuten 54, 55, 56 auf, durch die in axialer Richtung die Kronen 29 hindurchgeführt sind. Die Kronen 29 wirken stirnseitig mit der nicht dargestellten Magnetbaugruppe 2 zusammen bzw. sind mit dieser verspannt.The crown ring 20 of the execution of the Fig.7a / Fig.7b advantageously has three crowns 29, in principle any number of crowns 29 can be used. The anchor plate 50 has a corresponding number of plate grooves 54, 55, 56 through which the crowns 29 are guided in the axial direction. The crowns 29 cooperate on the end face with the magnet assembly 2, not shown, or are braced with the latter.

In der Ausführungsform der Fiq.7 sind in den Kronen 29 jeweils eine Lagerausnehmung 59 ausgebildet. Die Lagerausnehmungen 59 sind klammerförmig gestaltet, und zwar derart, dass sie in Umfangsrichtung des Kronenrings 20 und zur Magnetbaugruppe 2 geöffnet sind. Die Lagerausnehmungen 59 dienen der Aufnahme von Wälzkörpern 58, die vorzugsweise kugelförmig ausgebildet sind; dadurch erfüllen die Lagerausnehmungen 59 die Funktion von Lagerkäfigen. Die Wälzkörper 58 sind so dimensioniert und in den Lagerausnehmungen 59 positioniert, dass sie mit den Plattennuten 54, 55, 56 der Ankerplatte 50 zusammenwirken, und zwar in beiden Umfangsrichtungen, also tangential, so dass jeder Wälzkörper 58 Rotationskräfte in beiden Richtungen übertragen kann. Der Anker 5 wird demzufolge von den Wälzkörpern 58 nahezu reibungslos geführt.In the embodiment of FIG. 7 , a bearing recess 59 is formed in each of the crowns 29. The bearing recesses 59 are designed in the form of a clamp, in such a way that they are open in the circumferential direction of the crown ring 20 and to the magnet assembly 2. The bearing recesses 59 serve to receive rolling elements 58, which are preferably spherical; As a result, the bearing recesses 59 perform the function of bearing cages. The rolling elements 58 are dimensioned and positioned in the bearing recesses 59 in such a way that they interact with the plate grooves 54, 55, 56 of the anchor plate 50, specifically in both circumferential directions, that is to say tangentially, so that each rolling element 58 can transmit rotational forces in both directions. The armature 5 is therefore guided almost smoothly by the rolling elements 58.

Die Verdrehsicherung der Ankerplatte 50 bzw. des Ankers 5 ist somit sehr reibungsarm und verschleißarm ausgeführt, da der Anker 5 quasi über seine Plattennuten 54, 55, 56 auf den Wälzkörpern 58 abrollt.The anti-rotation device of the anchor plate 50 or of the armature 5 is thus designed to be very low-friction and low-wear, since the armature 5 rolls on the rolling elements 58 virtually over its plate grooves 54, 55, 56.

Vorzugsweise sind die Wälzkörper 58 aus einem amagnetischen Material, beispielsweise einer Keramik, hergestellt, damit sie nicht durch die elektromagnetischen Kräfte der Magnetbaugruppe 2 beeinflusst werden.The rolling elements 58 are preferably made of an amagnetic material, for example a ceramic, so that they are not influenced by the electromagnetic forces of the magnet assembly 2.

Die Fig.8 zeigt eine zur Fig.7 alternative Verdrehsicherung der Ankerplatte 50. Dabei zeigen die Fig.8a das Steuerventil 1 in einem Längsschnitt im Bereich eines Wälzkörpers 58 und die Fig.8b das Steuerventil 1 in Draufsicht auf die Ankerplatte 50.The Fig. 8 shows one to Fig. 7 alternative rotation lock of the anchor plate 50. The show Fig.8a the control valve 1 in a longitudinal section in the region of a rolling element 58 and the Fig. 8b the control valve 1 in plan view of the anchor plate 50.

Die Lagerausnehmungen 59 sind in der Ausführungsform der Fig.8 topfförmig gestaltet, mit jeweils einem in Umfangsrichtung des Ankers 5 offenen Ende. Ein Wälzkörper 58 ist in jeweils einer Lagerausnehmung 59 so positioniert, dass er an dem offenen Ende der Lagerausnehmung 59 mit einer Flanke der entsprechenden Plattennut 54, 55, 56 zusammenwirkt. Dadurch wird die Ankerplatte 50 an einer Plattennut 54, 55, 56 in einer Umfangsrichtung gelagert, jedoch nicht in der entgegengesetzt orientierten Umfangsrichtung. Daher ist zumindest ein weiterer Wälzkörper 58 erforderlich, der die Ankerplatte 50 auch in der entgegengesetzt orientierten Umfangsrichtung lagert.The bearing recesses 59 are in the embodiment of the Fig. 8 Pot-shaped, each with an open end in the circumferential direction of the armature 5. A rolling element 58 is positioned in each case in a bearing recess 59 such that it cooperates with a flank of the corresponding plate groove 54, 55, 56 at the open end of the bearing recess 59. As a result, the anchor plate 50 is supported on a plate groove 54, 55, 56 in a circumferential direction, but not in the opposite oriented circumferential direction. Therefore, at least one further rolling element 58 is required, which also supports the armature plate 50 in the opposite oriented circumferential direction.

In den Ausführungsformen der Fig.8 sind somit mindestens zwei Kronen 29 mit jeweils einem darin angeordneten Wälzkörper 58 erforderlich, um eine reibungsminimierte Verdrehsicherung sicherzustellen. Vorzugsweise weist der Kronenring dabei, anders als in den Fig.8a / Fig.8b dargestellt, eine gerade Anzahl von Kronen 29 auf, so dass die in den zugehörigen Lagerausnehmungen 59 angeordneten Wälzkörper 58 die Ankerplatte 50 jeweils paarweise in beiden Umfangsrichtungen lagern.In the embodiments of the Fig. 8 Thus, at least two crowns 29, each with a rolling element 58 arranged therein, are required in order to ensure friction-minimizing rotation. The crown ring preferably has a different shape than in FIGS Fig.8a / Fig.8b shown, an even number of crowns 29, so that the rolling elements 58 arranged in the associated bearing recesses 59 each support the anchor plate 50 in pairs in both circumferential directions.

Die Wälzkörper 58 werden in radialer Richtung von den Kronen 29 gelagert. Alternativ kann die radiale Richtung nach außen auch von einem weiteren Bauteil gelagert werden, beispielsweise von der Restluftspaltscheibe 23, wenn diese wie im Ausführungsbeispiel der Fig.6 angeordnet ist.The rolling elements 58 are supported by the crowns 29 in the radial direction. Alternatively, the radial direction to the outside can also be supported by a further component, for example by the residual air gap disk 23, if this, as in the exemplary embodiment in FIG Fig. 6 is arranged.

Die Funktionsweise des erfindungsgemäßen Kraftstoffinjektors 100 ist wie folgt:
Die Einspritzungen über die Einspritzöffnungen 13 in den Brennraum der Brennkraftmaschine werden durch die Längsbewegung des ein- oder mehrteiligen Einspritzventilglieds 11 ausgeführt, dessen Längsbewegungen wiederum von dem Steuerventil 1 gesteuert werden, wobei das Steuerventil 1 von der Magnetbaugruppe 2 angesteuert wird. Das Einspritzventilglied 11 ist an seinem den Einspritzöffnungen 13 entgegengesetzten Ende im Ventilstück 4 längsbeweglich geführt und begrenzt dort den Steuerraum 15.The mode of operation of the fuel injector 100 according to the invention is as follows:
The injections via the injection openings 13 into the combustion chamber of the internal combustion engine are caused by the longitudinal movement of the or multi-part injection valve member 11, the longitudinal movements of which are in turn controlled by the control valve 1, the control valve 1 being controlled by the magnet assembly 2. The injection valve member 11 is guided in the valve piece 4 at its end opposite the injection openings 13 and delimits the control chamber 15 there.

Bei Bestromung des Magnetkerns 3 übt die Magnetbaugruppe 2 eine anziehende Kraft auf den Anker 5 aus und bewegt diesen entgegen der Kraft der Feder 8 vom Ventilsitz 7 weg. Die hydraulische Verbindung von dem Ventilraum 17 zu dem Niederdruckraum 18 wird dadurch geöffnet und der Steuerraum 15 demzufolge entlastet. Die hydraulisch schließende Kraft im Steuerraum 15 auf das Einspritzventilglied 11 in Richtung der Einspritzöffnungen 13 verringert sich und das Einspritzventilglied 11 gibt die Einspritzöffnungen 13 frei, so dass der Kraftstoffinjektor 100 in den Brennraum der Brennkraftmaschine einspritzt.When the magnetic core 3 is energized, the magnet assembly 2 exerts an attractive force on the armature 5 and moves it away from the valve seat 7 against the force of the spring 8. The hydraulic connection from the valve chamber 17 to the low-pressure chamber 18 is thereby opened and the control chamber 15 is consequently relieved. The hydraulically closing force in the control chamber 15 on the injection valve member 11 in the direction of the injection openings 13 is reduced and the injection valve member 11 releases the injection openings 13 so that the fuel injector 100 injects into the combustion chamber of the internal combustion engine.

Zur Beendigung des Einspritzvorgangs wird die Bestromung des Magnetkerns 3 aufgehoben, so dass der Anker 5 von der Feder 8 gegen den Ventilsitz 7 gedrückt wird. Die hydraulische Verbindung vom Ventilraum 17 zum Niederdruckraum 18 wird dadurch geschlossen und der Steuerraum 15 mit unter Hochdruck stehendem Kraftstoff über eine nicht dargestellte Zulaufdrossel befüllt. Dadurch erhöht sich die hydraulisch schließende Kraft im Steuerraum 15 auf das Einspritzventilglied 11 in Richtung der Einspritzöffnungen 13 wieder und das Einspritzventilglied 11 verschließt die Einspritzöffnungen 13.At the end of the injection process, the energization of the magnetic core 3 is released, so that the armature 5 is pressed by the spring 8 against the valve seat 7. The hydraulic connection from the valve chamber 17 to the low-pressure chamber 18 is thereby closed and the control chamber 15 is filled with fuel under high pressure via an inlet throttle, not shown. As a result, the hydraulically closing force in the control chamber 15 on the injection valve member 11 increases again in the direction of the injection openings 13 and the injection valve member 11 closes the injection openings 13.

Erfindungsgemäß sind die Bauteile des Steuerventils 1, die einen Einfluss auf den Hub des Ankers 5 haben, reduziert: durch Ventilstück 4, Kronenring 20 und gegebenenfalls Ankerhubeinstellscheibe 21 wird der axiale Abstand zwischen dem Ventilsitz 7 und der Magnetbaugruppe 2 definiert. Subtrahiert man davon die wirksame Länge des Ankers 5 und gegebenenfalls die Höhe der Restluftspaltscheibe 23, so erhält man den maximal möglichen Ankerhub. Durch die Reduzierung der am Ankerhub beteiligten Bauteile sind die Druck- und Temperaturabhängigkeit des Ankerhubs reduziert; die beiden die axiale Länge bestimmenden Bauteile sind dabei der Anker 5 und der Kronenring 20.According to the invention, the components of the control valve 1 that have an influence on the stroke of the armature 5 are reduced: the axial distance between the valve seat 7 and the magnet assembly 2 is defined by the valve piece 4, crown ring 20 and optionally armature stroke adjusting disk 21. If the effective length of the armature 5 and, if appropriate, the height of the residual air gap disk 23 are subtracted from this, the maximum possible armature stroke is obtained. By reducing the components involved in the anchor stroke, the pressure and temperature dependency of the anchor stroke is reduced; the two components determining the axial length are the armature 5 and the crown ring 20.

Bei durch den Ventilsitz 7 aus dem Steuerraum 15 abströmendem unter Hochdruck stehendem Kraftstoff erwärmt sich der Anker 5 dynamisch schneller als der Kronenring 20. Dadurch wird vorteilhafterweise das Material des Kronenrings 20 so gewählt, dass es einen größeren Wärmeausdehnungskoeffizienten besitzt als das Material des Ankers 5. Dadurch kann der Ankerhubverlust, der durch die unterschiedlichen Temperaturgradienten am Anker 5 und am Kronenring 20 entsteht, durch den Wärmeausdehnungskoeffizienten des Kronenrings 20 kompensiert werden.In the case of high-pressure fuel flowing out of the control chamber 15 through the valve seat 7, the armature 5 heats up dynamically faster than the crown ring 20. This advantageously means that the material of the crown ring 20 is selected such that it has a greater coefficient of thermal expansion than the material of the armature 5 Coefficient of thermal expansion of the crown ring 20 can be compensated.

Vorteilhafterweise wird das Material des Kronenrings 20 weiterhin so gewählt, dass es den Magnetfluss der Magnetbaugruppe 2 nicht beeinträchtigt, beispielsweise aus austenitischem Stahl oder aus einer Keramik.The material of the crown ring 20 is advantageously selected such that it does not impair the magnetic flux of the magnetic assembly 2, for example made of austenitic steel or a ceramic.

In vorteilhaften Weiterbildungen haben die durch die Ankerplatte 50 hindurch ragenden Kronen 29 des Kronenrings 20 auch eine Funktion zur Verdrehsicherung der Ankerplatte 50 bzw. des Ankers 5. Durch den Einsatz von Wälzkörpern 58 kann diese Verdrehsicherung besonders reibungsarm gestaltet werden.In advantageous developments, the crowns 29 of the crown ring 20 protruding through the anchor plate 50 also have a function for securing the anchor plate 50 or the anchor 5 against rotation. The use of rolling elements 58 makes this rotation lock particularly low-friction.

Claims (13)

  1. Fuel injector (100) for injecting fuel into the combustion chamber of an internal combustion engine, wherein the fuel injector (100) comprises a control valve (1) and an injection valve member (11), wherein the injection valve member (11) delimits a control chamber (15) and is guided in longitudinally movable fashion in the fuel injector (11) and, by means of its movement, opens and shuts off at least one injection opening (13) into the combustion chamber, wherein the control valve (1) controls the pressure in the control chamber (15), wherein the control valve (1) comprises a magnet assembly (2), an armature (5), a valve piece (4) and a valve seat (7) formed on the valve piece (4), wherein the armature (5) comprises an armature plate (50), wherein the armature plate (50) is actuatable by the magnet assembly (2), wherein the armature (5) interacts at least indirectly with the valve seat (7) for the purposes of relieving the control chamber (15) of pressure,
    wherein a crown ring (20) is braced between the valve piece (4) and the magnet assembly (2), characterized in that a plate groove (54) is formed in the armature plate (50), and in that the crown ring (20) has a crown (29), wherein the crown (29) projects through the plate groove (54).
  2. Fuel injector (100) according to Claim 1, characterized in that a bearing recess (59) is formed in the crown (29), wherein a rolling body (58) is mounted in the bearing recess (59), wherein the rolling body (58) interacts with the plate groove (54).
  3. Fuel injector (100) for injecting fuel into the combustion chamber of an internal combustion engine, wherein the fuel injector (100) comprises a control valve (1) and an injection valve member (11), wherein the injection valve member (11) delimits a control chamber (15) and is guided in longitudinally movable fashion in the fuel injector (11) and, by means of its movement, opens and shuts off at least one injection opening (13) into the combustion chamber, wherein the control valve (1) controls the pressure in the control chamber (15), wherein the control valve (1) comprises a magnet assembly (2), an armature (5), a valve piece (4) and a valve seat (7) formed on the valve piece (4), wherein the armature (5) comprises an armature plate (50), wherein the armature plate (50) is actuatable by the magnet assembly (2), wherein the armature (5) interacts at least indirectly with the valve seat (7) for the purposes of relieving the control chamber (15) of pressure,
    wherein a crown ring (20) is braced between the valve piece (4) and the magnet assembly (2), wherein the crown ring (20) surrounds the armature (5) at the outside, characterized in that the material of the crown ring (29) has a higher coefficient of thermal expansion than the material of the armature (5) .
  4. Fuel injector (100) according to any of Claims 1 to 3, characterized in that a cylindrical lateral surface (43) is formed on the valve piece (4), wherein the crown ring (20) is positioned on the lateral surface (43) coaxially with respect to the valve seat (7).
  5. Fuel injector (100) according to any of claims 1 to 4, characterized in that a cylindrical guide surface (28) is formed on the crown ring (20), wherein the armature (5) is guided in longitudinally movable fashion in the guide surface (28).
  6. Fuel injector (100) according to any of Claims 1 to 5, characterized in that an armature stroke setting disc (21) is braced between the crown ring (20) and the valve piece (4).
  7. Fuel injector (100) according to any of Claims 1 to 5, characterized in that an armature stroke setting disc (21) is braced between the crown ring (20) and the magnet assembly (2).
  8. Fuel injector (100) according to any of Claims 1 to 7, characterized in that a residual air gap disc (23) is arranged between the magnet assembly (2) and the armature plate (50).
  9. Fuel injector (100) according to any of Claims 1 to 8, characterized in that the material of the crown ring (29) is amagnetic, preferably is an austenitic sintered steel or a ceramic.
  10. Fuel injector (100) according to any of Claims 1 to 9, characterized in that the magnet assembly (2) is braced with the crown ring (20) by means of a bracing spring (22).
  11. Fuel injector (100) according to any of Claims 1 to 10, characterized in that the magnet assembly (2) is electrically contactable by at least one contact pin (31), and in that the at least one contact pin (31) has a sliding fit (31a).
  12. Fuel injector (100) according to any of Claims 1 to 11, characterized in that the armature (5) is acted on in the direction of the valve seat (7) by a spring (8) .
  13. Fuel injector (100) according to any of Claims 1 to 12, characterized in that an armature bolt (6) projects through the armature (5).
EP16788726.4A 2015-12-03 2016-11-02 Fuel injector having a control valve Active EP3384149B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102015224177.7A DE102015224177A1 (en) 2015-12-03 2015-12-03 Fuel injector with control valve
PCT/EP2016/076439 WO2017092955A1 (en) 2015-12-03 2016-11-02 Fuel injector having a control valve

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EP3384149A1 EP3384149A1 (en) 2018-10-10
EP3384149B1 true EP3384149B1 (en) 2020-05-06

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EP16788726.4A Active EP3384149B1 (en) 2015-12-03 2016-11-02 Fuel injector having a control valve

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EP (1) EP3384149B1 (en)
KR (1) KR102623972B1 (en)
CN (1) CN108291509B (en)
DE (1) DE102015224177A1 (en)
WO (1) WO2017092955A1 (en)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102016225948A1 (en) 2016-12-22 2018-06-28 Robert Bosch Gmbh fuel injector
CN111894776B (en) * 2020-07-06 2021-09-17 一汽解放汽车有限公司 Fuel injector

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Publication number Priority date Publication date Assignee Title
DE4013832A1 (en) * 1990-04-30 1991-10-31 Bosch Gmbh Robert ELECTROMAGNETICALLY ACTUABLE FUEL INJECTION VALVE
DE19650865A1 (en) 1996-12-07 1998-06-10 Bosch Gmbh Robert magnetic valve
DE10131201A1 (en) * 2001-06-28 2003-01-16 Bosch Gmbh Robert Solenoid valve for controlling an injection valve of an internal combustion engine
DE10240880B4 (en) * 2002-09-04 2016-12-01 Robert Bosch Gmbh Actuator connection to fuel injectors of internal combustion engines
US20060138374A1 (en) * 2004-04-14 2006-06-29 Lucas Michael A Solenoid actuated flow control valve including adjustable spacer
JP2006257874A (en) * 2004-04-30 2006-09-28 Denso Corp Injector
PT1734251E (en) * 2005-06-17 2007-03-30 Magneti Marelli Powertrain Spa Fuel injector
DE102007025614A1 (en) * 2007-06-01 2008-12-04 Robert Bosch Gmbh Armature stroke adjustment for solenoid valve
DE102007025961A1 (en) * 2007-06-04 2008-12-11 Robert Bosch Gmbh injector
DE102008005532A1 (en) * 2008-01-22 2009-07-23 Robert Bosch Gmbh Fuel injector whose control valve element has a support region
US8689772B2 (en) * 2011-05-19 2014-04-08 Caterpillar Inc. Fuel injector with telescoping armature overtravel feature
JP5689395B2 (en) * 2011-09-28 2015-03-25 ナブテスコ株式会社 solenoid valve
EP2713040B1 (en) * 2012-09-26 2017-06-07 Delphi International Operations Luxembourg S.à r.l. Electrical connector
GB201503158D0 (en) * 2015-02-25 2015-04-08 Delphi International Operations Luxembourg S.�.R.L. Control valve arrangement

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EP3384149A1 (en) 2018-10-10
KR102623972B1 (en) 2024-01-11
DE102015224177A1 (en) 2017-06-08
CN108291509A (en) 2018-07-17
KR20180090842A (en) 2018-08-13
WO2017092955A1 (en) 2017-06-08
CN108291509B (en) 2020-12-04

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