EP2466108B1 - Fuel injector valve - Google Patents

Fuel injector valve Download PDF

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Publication number
EP2466108B1
EP2466108B1 EP20110193679 EP11193679A EP2466108B1 EP 2466108 B1 EP2466108 B1 EP 2466108B1 EP 20110193679 EP20110193679 EP 20110193679 EP 11193679 A EP11193679 A EP 11193679A EP 2466108 B1 EP2466108 B1 EP 2466108B1
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EP
European Patent Office
Prior art keywords
valve
sealing
fuel
sealing bushing
fuel injection
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Not-in-force
Application number
EP20110193679
Other languages
German (de)
French (fr)
Other versions
EP2466108A1 (en
Inventor
Andreas Gruenberger
Marco Stieber
Dieter Junger
Jens-Peter Nagel
Michael Kurrle
Udo Schaich
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
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Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP2466108A1 publication Critical patent/EP2466108A1/en
Application granted granted Critical
Publication of EP2466108B1 publication Critical patent/EP2466108B1/en
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M47/00—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
    • F02M47/02—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure of accumulator-injector type, i.e. having fuel pressure of accumulator tending to open, and fuel pressure in other chamber tending to close, injection valves and having means for periodically releasing that closing pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/0033—Lift valves, i.e. having a valve member that moves perpendicularly to the plane of the valve seat
    • F02M63/0035—Poppet valves, i.e. having a mushroom-shaped valve member that moves perpendicularly to the plane of the valve seat
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/007—Details not provided for in, or of interest apart from, the apparatus of the groups F02M63/0014 - F02M63/0059
    • F02M63/0071—Details not provided for in, or of interest apart from, the apparatus of the groups F02M63/0014 - F02M63/0059 characterised by guiding or centering means in valves including the absence of any guiding means, e.g. "flying arrangements"
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/007—Details not provided for in, or of interest apart from, the apparatus of the groups F02M63/0014 - F02M63/0059
    • F02M63/0073—Pressure balanced valves

Definitions

  • the invention relates to a fuel injection valve, in particular an injector for fuel injection systems of internal combustion engines. Specifically, the invention relates to the field of injectors for fuel injection systems of air compressing, self-igniting internal combustion engines.
  • An injector for injecting fuel into combustion chambers of internal combustion engines has a piezoelectric actuator arranged in an injector body, which actuates a control valve accommodated in a valve plate.
  • a nozzle body is provided, at the combustion chamber end of which a nozzle outlet is formed.
  • a nozzle needle is axially movable or actuated in a longitudinal recess of the nozzle body.
  • a rearward, remote from the nozzle outlet end of the longitudinal recess, arranged between the nozzle body and the control valve throttle plate is provided which forms an opening stop for the nozzle needle.
  • the throttle disk acts in this case with the rear side, facing away from the nozzle outlet end face of the nozzle needle and thus limits the opening stroke of the nozzle needle. Further, a control space is formed between the rear nozzle needle end surface and the throttle disk, which is in hydraulic communication with a pressure port serving the fuel supply.
  • a cylindrical holding body is arranged, which receives a booster piston and the valve plate containing the control valve.
  • a valve pin is arranged with a valve body. The valve pin with the valve body has a mushroom-shaped configuration. In this case, the valve body is acted upon by a valve spring against a valve seat surface.
  • the valve chamber is connected on the one hand via a throttle bore, which serves as an inlet and outlet throttle, with the control room.
  • a throttle bore which serves as an inlet and outlet throttle
  • the valve space of the control valve via a bore serving as a bypass connected to a high pressure fuel space.
  • the bypass bore can be closed by actuating the valve pin.
  • the from the DE 103 53 169 A1 known injector has the disadvantage that due to the pressurized under the valve seat surface, the valve opening force increases with the fuel pressure. A pressure increase beyond 2000 bar is not possible. Furthermore, a relatively large volume of the valve space is required to accommodate the provided in the valve chamber components of the control valve. This results in a correspondingly large amount of reflux of fuel to a low pressure return. This refluxing amount of fuel must be replenished from the high-pressure chamber. This deteriorates the efficiency and makes a correspondingly high-pressure pump required. In addition, the bypass hole is required to achieve a sufficiently fast closing behavior when operating the nozzle needle.
  • a fuel injection valve which has a control valve with a longitudinally movable by an actuator valve member.
  • the valve member is guided in a sleeve which is arranged in a valve chamber formed in the fuel injection valve.
  • the fuel injection valve according to the invention with the features of claim 1 has the advantage that an improved design of the control valve is made possible.
  • a reduction of the volume of the valve space is possible, whereby in particular the injector function and the smallest quantity capability can be improved.
  • a cost advantage can be achieved because assembly and adjustment steps in the manufacture of the fuel injection valve can be simplified or possibly also omitted.
  • the sealing bush has a peripheral biting edge on one of the sealing surface facing the end face, with which the sealing bush rests against the sealing surface. This ensures a reliable seal. In this way, according to a fuel pressure, an admission of the sealing bush against the sealing surface can be achieved.
  • the sealing bushing in the region of the valve seat surface has a contact surface and that the contact surface has a contour which is at least partially designed in accordance with a spherical surface.
  • a valve plate is provided, that the valve space is at least partially configured in the valve plate, that the valve seat surface is configured on the valve plate and that the valve plate has an at least partially conical contact surface on which the sealing bush is supported with its contact surface is. In this way, a tangential abutment of the partially conical abutment surface on the abutment surface of the sealing bush, which is partially designed in accordance with a convex torus segment, can be achieved.
  • the partially conical contact surface of the valve plate may comprise the valve seat surface. This simplifies the design of the valve plate at the same time the lowest position tolerance between the valve pin and the sealing bush, whereby the valve tightness is improved.
  • a fuel passage is formed on the sealing bush, that between a outer side of the sealing bush and an inner wall of the valve chamber, a fuel gap is configured and that the fuel passage allows fuel flow from the fuel gap to a sealing seat between the valve seat surface and the valve body of the valve pin ,
  • the fuel passage is formed by at least one passage gap, which is designed between the sealing bush and a sealing bush facing the bearing surface on the valve plate. In this way, a fuel flow to the sealing seat is made possible, so that when the valve pin is actuated, fuel can flow away via the open sealing seat to a low-pressure return or the like. As a result, a pressure drop in the control chamber for actuating a nozzle needle is achieved.
  • a fuel gap is configured and that a diameter of a sealing seat between the valve body and the valve seat surface is greater than a diameter of a guide bore of the sealing bush, in which the valve pin is guided.
  • This can be achieved by the pressure of the fuel in the fuel gap between the Valve body of the valve pin and the sealing bush a hydraulic closing force are exerted on the valve pin with its valve body to urge the valve body against the valve seat surface.
  • This hydraulic closing force can act in addition to a valve spring.
  • the sealing bush is fitted in an unpressurized mounting state with an axial transition fit in the valve chamber.
  • the transition fit can in this case be designed so that both a slight oversize between the biting edge and the sealing surface and a small game can be provided at this point.
  • a certain installation tolerance is specified and also possible.
  • the biting edge of the sealing bush is applied in the pressureless state instead of a spring force by their form-fitting installation condition on the sealing surface.
  • the sealing bushing is designed such that the sealing bushing can be acted upon by a pressure which can be built up via the drainage bore from the control chamber in the valve space against the sealing surface. In this case, a hydraulic force is generated on the sealing bush, which is directed to the sealing surface.
  • the sealing bush has an annular recess on an outer side of the sealing bush.
  • the annular recess of the sealing bush is associated with a recess of the valve plate, into which via a drain hole of a throttle plate fuel is feasible, and that the annular recess of the sealing bush forms an annular space connected to the recess of the valve plate, via which the in the recess of the throttle plate feasible fuel is circumferentially distributable. In this way, the one-sided flow from the recess of the valve plate can be distributed uniformly over the entire circumference of the sealing bushing.
  • the sealing bush in the region of the valve body of the valve pin has a plurality of through-flow bores extending from an outer side of the sealing bush to a fuel gap formed between the valve body of the valve pin and the sealing bush. This allows a design with an axial projection, in which the sealing bush is already pressed in the assembled state with a biting edge against the sealing surface.
  • Fig. 1 shows a first embodiment of a fuel injection valve 1 of the invention in a schematic, partial sectional view.
  • the fuel injection valve 1 can serve in particular as an injector for fuel injection systems of air-compressing, self-igniting internal combustion engines.
  • a preferred use of the fuel injection valve 1 is for a fuel injection system with a common rail that leads Diesel fuel under high pressure to a plurality of fuel injection valves 1.
  • the fuel injection valve 1 according to the invention is also suitable for other applications.
  • the fuel injection valve 1 has a housing in which a throttle plate 2 and a valve plate 3 are arranged.
  • the throttle plate 2 has an end face 4.
  • the valve plate 3 has a front side 5.
  • the throttle plate 2 rests with its end face 4 on the end face 5 of the valve plate 3.
  • a control chamber 8 During operation of the fuel injection valve 1, fuel is led into a control chamber 8 from a fuel line guided through the fuel injection valve 1 via a channel section 7, which is guided through the throttle plate 2.
  • the channel section 7 has an inlet throttle 9 configured in the throttle plate 2.
  • the control chamber 8 is bounded on the one hand by an end face 6 of the throttle plate 2 and on the other hand by an end face 10 of a nozzle needle 11 and laterally by a sleeve 12.
  • the sleeve 12 is in this case on the end face 6 of the throttle plate 2.
  • the nozzle needle 11 According to the pressure in the control chamber 8, the nozzle needle 11 is acted upon in a closing direction 13 or opened against the closing direction 13.
  • the pressure of the fuel in the control chamber 8 acts against a fuel pressure in a fuel chamber 14 and a valve spring tension.
  • the control valve 15 has a valve chamber 16 which is configured in this embodiment in the valve plate 3.
  • the valve chamber 16 is in this case bounded by an inner wall 17, which is configured on the valve plate 3, and a sealing surface 18, which is part of the end face 4 of the throttle plate 2.
  • a sealing bushing 19 and at least partially a valve pin 20 are arranged with a valve body 21.
  • the valve pin 20 is in this case guided in a guide bore 22 of the sealing bushing 19.
  • the control valve 15 has a longitudinal axis 23 along which the valve pin 20 with the valve body 21 can be actuated.
  • the valve plate 3 has a recess 24 into which a drain hole 25 opens.
  • the drain hole 25 is connected via the recess 24 on the one hand with the valve chamber 16.
  • the drain hole 25 opens into the control chamber 8.
  • the drain hole 25 has an outlet throttle 26.
  • the drain hole 25 connects the control chamber 8 with the valve chamber 16.
  • the drain hole 25 with the outlet throttle 26 is configured in this embodiment in the throttle plate 2.
  • a pressure-relieved space 27 is configured, which is connected via a return passage 28 with a low pressure return or the like.
  • a stop pin 29 is arranged, which comprises a part-spherical bearing part 30.
  • the stop pin 29 is mounted on a bearing surface 31.
  • the stop pin 29 is pivotally mounted to achieve a tolerance compensation.
  • a parallel alignment of the stop pin 29 with respect to the longitudinal axis 23 is made possible during operation.
  • a shim 33 is arranged, which is acted upon by a arranged in the pressure-relieved space 27 valve spring 34.
  • valve pin 20 is thus acted upon by the valve spring 34 with the valve body 21 in a closing direction 35. Further, a gap 36 is predetermined between the shim 33 and the stop pin 29, whose height limits a stroke of the valve body 21. By the thickness of the shim 33 thus a specification of the maximum stroke of the valve body 21 is possible.
  • the valve plate 3 has a partially conical contact surface 40. Further, a valve seat surface 41 is configured on the valve plate 3. In this embodiment, the valve seat surface 41 is part of the conical abutment surface 40.
  • the valve body 21 of the valve pin 20 cooperates with the valve seat surface 41 to form a sealing seat 42. In the unactuated state of the control valve 15, the sealing seat 42 is closed.
  • the force of the valve spring 34 in the closing direction 35 acts on the one hand.
  • a hydraulic force due to the pressure of the fuel acts in the closing direction 35 during operation.
  • a fuel gap 44 is formed between the inner wall 17 and an outer side 43 of the sealing bush 19, a fuel gap 44 is formed.
  • the fuel gap 44 is configured as an annular fuel gap 44. Via the fuel gap 44, the fuel passes from the drain hole 25 to a passage gap 45 in the region of the conical contact surface 40. Via the passage gap 45, the fuel passes into a fuel gap 46, which is configured between the sealing bush 19 and the valve body 21.
  • the sealing bushing 19 has a peripheral biting edge 51 on a front side 50 facing the sealing surface 18 (FIG. Fig. 3 ), with the sealing bush 19 against the sealing surface 18 of the throttle plate 2.
  • the fuel gap 44 is sealed off from the pressure-relieved space 27. Due to the pressure of the fuel, which acts in the region of the passage gap 45 on the sealing bushing 19, the sealing bush 19 is acted against the closing direction 35. This increases with increasing pressure of the fuel, the sealing effect between the sealing bushing 19 and the sealing surface 18th
  • the sealing bush 19 has a contact surface 55 assigned to the conical bearing surface.
  • the contact surface 55 has a contour 56, which is designed in accordance with a spherical surface 56, as illustrated by the broken line 56.
  • the contact surface 56 is oriented tangentially to the contact surface 55 of the sealing bushing 19 at the contact point.
  • the spherical contour 56 of the contact surface 55 is characterized by a radius 57, wherein the center 58 is preferably located on the longitudinal axis 23 and has approximately the same center as the valve pin seat of the valve pin 20. This avoids that when aligning the sealing bushing 19, for example Tolerance compensation or in cooperation with a plastication on the biting edge 51, an overdetermination between the centered on the valve seat 42 valve pin 20 and the centered sealing bushing 19 occurs.
  • the sealing seat 42 is in this case designed in a circular shape and centered with respect to the longitudinal axis 23.
  • the conical abutment surface 40 does not necessarily pass smoothly into the valve seat surface 41.
  • the valve seat surface 41 may also have a small offset to the conical bearing surface 40.
  • the valve seat surface 41 is configured advantageously as a partially conical valve seat surface 41.
  • the sealing bush 19 is set in places with respect to the conical bearing surface 40. This can also be provided in several places. As a result, the contact surface 55, which is located on the spherical surface contour 56, interrupted in places. At such a passage gap 45, an unthrottled cross section is preferably predetermined. In this case, a parallel gap 45 is preferably formed to the conical bearing surface 40.
  • the sealing bush 19 is thus supported on the one hand in the region of the valve seat surface 41 and on the other hand in the region of the sealing surface 18, which lies opposite the valve seat surface 41.
  • the biting edge 51 of the sealing bushing 19 is thus applied in the pressureless state instead of a spring force by their positive installation condition to the sealing surface 18 of the throttle plate 2.
  • the installation tolerance of the sealing bushing 19 in the recess of the valve plate 3, which forms the valve chamber 16 is designed in the pressureless mounting state as a transition fit, so that both slight excess between the biting edge 51 and the sealing surface 18 of the throttle plate 2 and a small game can be provided ,
  • the leakage gaps are only very small or only effective for a short time. This is ensured in particular by the fact that with increasing fuel pressure in the valve chamber 16, the biting edge 51 of the sealing bushing 19 is pressed by the pressure force against the sealing surface 18 of the throttle plate 2 and thereby a leak-free seal is ensured. If no further energy is supplied, for example, because an engine is turned off, then the sealing bush 19 is still on the sealing surface 18 of the throttle plate 2, as by the stop process relatively slowly sinking pressure of the fuel in the common rail or the like, the sealing bushing 19 continue is pressed by the pressure force to the throttle plate 2. This is particularly advantageous in a start-stop operation.
  • the actuation of the valve pin 20 with the valve body 21 is effected by an actuator 62, which acts on a transition piece 59 against the closing direction 35.
  • the actuator 62 may be configured as a piezoelectric actuator 62 or as a magnetic actuator 62.
  • Fig. 2 shows the in Fig. 1 labeled II section of the fuel injection valve 1 of the embodiment.
  • a contact point 63 is provided, on which the conical abutment surface 40 contacts the abutment surface 55 configured in accordance with the spherical surface contour 56.
  • This contact point 63 allows in the initial state, a support of the sealing bushing 19 in order to achieve a tightness in the region of the biting edge 51.
  • the contact between the abutment surface 55 and the conical abutment surface 40 does not continue uninterruptedly in the circumferential direction about the longitudinal axis 23, since one or more interruptions in the form of passage gaps 45 are provided.
  • Fuel flow from the fuel gap 44 to the sealing seat 42 allows.
  • the fuel gap 44 may extend over an edge 59 of the sealing bushing 19. This is made possible by a recessed portion 60 in the conical bearing surface 40 of the valve plate 3.
  • the pressure of the fuel on the flank 49 can act to generate circumferentially a hydraulic force against the closing direction 35, which acts on the biting edge 51 against the sealing surface 18.
  • Fig. 3 shows the in Fig. 1 labeled III section of the fuel injection valve 1 of the first embodiment.
  • the biting edge 51 is in this case designed as a circular biting edge 51, which is centered with respect to the longitudinal axis 23.
  • a diameter 61 of the circular biting edge 51 is in this case set relatively large, that is significantly larger than the diameter 48 of the guide bore 22 and almost as large as a diameter of the sealing bushing 19 on the outer side 43. In this way, with respect to the pressure-relieved space 27 is a relative large hydraulic force against the closing direction 35 achieved by the pressure of the fuel.
  • Fig. 4 shows the in Fig. 1 labeled IV section of the fuel injection valve 1 according to a second embodiment.
  • the valve pin 20 has a pin 65 with a ball cap 66.
  • the bearing part 30 is mounted on the bearing surface 31. In this case, the bearing part 30 is in the pressure-relieved space 27.
  • the bearing part 30 has a flat stroke stop 67.
  • the ball cap 66 of the pin 65 faces the planar stroke stop 67 of the bearing part 30. This results in an approximately punctiform contact point 68, with which the ball cap 66 abuts against the stroke stop 67.
  • the spherical radius of the ball cap 66 is given by the Hertzian pressing condition.
  • a disc 69 which is also located in the pressure-relieved space 27 of the throttle plate 2, serves to support the valve spring 34 to ensure a provision of the valve pin 20 with its valve body 21.
  • the pin 65 extends through a bore 70 of the disc 69th
  • Fig. 5 shows the in Fig. 4 shown section of the fuel injection valve 1 according to a third embodiment.
  • the valve pin 20 is located on a valve pin 20 facing flat end face 71 of the shim 69.
  • a side facing away from the end face 71 further end face 72 of Shim 69 faces the stop pin 29.
  • the end face 72 the stroke stop 67 of the stop pin 29 faces, which is formed by a ball cap 73 of the stop pin 29.
  • an approximately punctiform bearing point 68 between the shim 69 and the ball cap 73 of the stop pin 29 is formed.
  • a spherical surface contact 68 is formed, which ensures a permanently stable stroke stop 67.
  • FIGS. 4 and 5 also described variations of a planar configuration of the stroke stop 67 of the stop pin 29 and the end face 72 of the shim 69 may be provided. Specifically, slightly concave surfaces may be formed.
  • the stroke adjustment can be based on the Fig. 4 described embodiment also on the height of the stop pin 29 and in the basis of the Fig. 5 described embodiment of the thickness of the shim 69 and / or the height of the stop pin 29 be predetermined.
  • the shim 69 is preferably formed as a sheet metal stamping.
  • Fig. 6 shows that in Fig. 1 shown fuel injector 1 according to a fourth embodiment in a partial, schematic sectional view.
  • the sealing bush 19 on its outer side 43 an annular recess 74.
  • the annular recess 74 may in this case be configured as a ring recess 74 and / or as an annular groove 74.
  • the recess 24 of the valve plate 3 is designed as a spout 24.
  • the annular recess 74 is provided at the height of the spout 24 on the outer side 43 of the sealing bushing 19.
  • the one-sided flow from the spout 24 is circumferentially distributed in an annular space 74 formed by the annular recess 74 with respect to the inner wall 17 of the valve plate 3.
  • the annular space 75 is in this case connected to the spout 24.
  • the narrow collar 76 is dimensioned such that due to the small radial gap between the narrow collar 76 and the inner wall 17 of the valve plate 3 no function-relevant throttling with respect to the outlet throttle 26 occurs.
  • the narrow collar 76 is located between the annular recess 74 and the valve seat surface 41st
  • the flow gap 44 continues.
  • the axial naturalström lake 77 are in this case blended with the annular recess 74.
  • the recesses formed by the axial flow-through surfaces 77 with respect to the inner wall 17 of the valve plate 3 connect the annular recess 74 with the flow gap 44.
  • the narrow flange 76 can thus be interrupted via the axial flow-through surface 77 in order to achieve an advantageous fuel flow.
  • Fig. 7 shows that in Fig. 1 shown fuel injector 1 according to a fifth embodiment in a partial, schematic sectional view.
  • the annular recess 74 is provided at the height of the spout 24.
  • the one-sided flow from the spout 24 is evenly distributed over the entire circumference.
  • the fuel flows to the sealing seat 42 from the annular recess 74 in the direction of the valve seat surface 41.
  • the fuel inlet to the sealing seat 42 takes place via a plurality of flow holes 78, 79, which are distributed uniformly over the circumference, as well as via the extended fuel gap 46
  • Installation of the sealing bushing 19 on the contact surface 40 of the valve plate 3 is configured in this embodiment with an axial projection, so that the sealing bushing 19 is already pressed in the assembled state with its biting edge 51 against the sealing surface 18.
  • the conical design of the conical bearing surface 40 results in a concentric position of the sealing bushing 19 for the sealing seat 42.
  • the positive and non-positive fixation of the sealing bush 19 enables the transverse forces caused by the pressure waves to be reliably absorbed. This allows the reduction of the flow gap 44, whereby the remaining volume of the valve chamber 16 can be functionally reduced.
  • the flow holes 78, 79 extend from the outer side 43 of the sealing bush 19 to the fuel gap 46 formed between the valve body 21 of the valve pin 20 and the sealing bushing 19.
  • the flow bores 78, 79 are in this case configured in the region of the valve body 21 of the valve pin 20 on the sealing bushing 19. As a result, open the flow holes 78, 79 on the outside 43 of the sealing bushing 19 in a recessed portion 60 of the valve plate 3, in which the fuel gap 46 expands.

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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

Stand der TechnikState of the art

Die Erfindung betrifft ein Brennstoffeinspritzventil, insbesondere einen Injektor für Brennstoffeinspritzanlagen von Brennkraftmaschinen. Speziell betrifft die Erfindung das Gebiet der Injektoren für Brennstoffeinspritzanlagen von luftverdichtenden, selbstzündenden Brennkraftmaschinen.The invention relates to a fuel injection valve, in particular an injector for fuel injection systems of internal combustion engines. Specifically, the invention relates to the field of injectors for fuel injection systems of air compressing, self-igniting internal combustion engines.

Aus der DE 103 53 169 R1 ist ein Injektor zur Einspritzung von Kraftstoff in Brennräume von Brennkraftmaschinen bekannt. Der bekannte Injektor weist einen in einem Injektorkörper angeordneten Piezoaktor auf, der ein in einer Ventilplatte aufgenommenes Steuerventil betätigt. Außerdem ist ein Düsenkörper vorgesehen, an dessen brennraumseitigen Ende ein Düsenaustritt ausgebildet ist. Eine Düsennadel ist in einer Längsausnehmung des Düsenkörpers axial beweglich beziehungsweise betätigbar angeordnet. Des weiteren ist eine das rückwärtige, vom Düsenaustritt abgewandte Ende der Längsausnehmung abschließende, zwischen Düsenkörper und Steuerventil angeordnete Drosselscheibe vorgesehen, die einen Offnungsanschlag für die Düsennadel bildet. Die Drosselscheibe wirkt hierbei mit der rückseitigen, vom Düsenaustritt abgewandten Stirnfläche der Düsennadel zusammen und begrenzt damit den Öffnungshub der Düsennadel. Ferner ist ein Steuerraum zwischen der rückwärtigen Düsennadel-Stirnfläche und der Drosselscheibe ausgebildet, der mit einem der Kraftstoffzuführung dienenden Druckanschluss in hydraulischer Verbindung steht. Im Injektorkörper ist ein zylindrischer Haltekörper angeordnet, der einen Übersetzerkolben und die das Steuerventil enthaltene Ventilplatte aufnimmt. In einem Ventilraum des Steuerventils ist ein Ventilbolzen mit einem Ventilkörper angeordnet. Der Ventilbolzen mit dem Ventilkörper weist eine pilzförmige Ausgestaltung auf. Hierbei wird der Ventilkörper von einer Ventilfeder gegen eine Ventilsitzfläche beaufschlagt. Der Ventilraum wird einerseits über eine Drosselbohrung, die als Zu- und Ablaufdrossel dient, mit dem Steuerraum verbunden. Andererseits wird der Ventilraum des Steuerventils über eine als Bypass dienende Bohrung mit einem unter Hochdruck stehenden Brennstoffraum verbunden. Die Bypass-Bohrung ist hierbei durch Betätigen des Ventilbolzens verschließbar.From the DE 103 53 169 R1 An injector for injecting fuel into combustion chambers of internal combustion engines is known. The known injector has a piezoelectric actuator arranged in an injector body, which actuates a control valve accommodated in a valve plate. In addition, a nozzle body is provided, at the combustion chamber end of which a nozzle outlet is formed. A nozzle needle is axially movable or actuated in a longitudinal recess of the nozzle body. Furthermore, a rearward, remote from the nozzle outlet end of the longitudinal recess, arranged between the nozzle body and the control valve throttle plate is provided which forms an opening stop for the nozzle needle. The throttle disk acts in this case with the rear side, facing away from the nozzle outlet end face of the nozzle needle and thus limits the opening stroke of the nozzle needle. Further, a control space is formed between the rear nozzle needle end surface and the throttle disk, which is in hydraulic communication with a pressure port serving the fuel supply. In the injector body, a cylindrical holding body is arranged, which receives a booster piston and the valve plate containing the control valve. In a valve chamber of the control valve, a valve pin is arranged with a valve body. The valve pin with the valve body has a mushroom-shaped configuration. In this case, the valve body is acted upon by a valve spring against a valve seat surface. The valve chamber is connected on the one hand via a throttle bore, which serves as an inlet and outlet throttle, with the control room. On the other hand, the valve space of the control valve via a bore serving as a bypass connected to a high pressure fuel space. The bypass bore can be closed by actuating the valve pin.

Der aus der DE 103 53 169 A1 bekannte Injektor hat den Nachteil, dass aufgrund der unterhalb des Ventilsitzes druckbeaufschlagten Fläche, die Ventilöffnungskraft mit dem Brennstoffdruck zunimmt. Eine Drucksteigerung über 2000 bar hinaus ist nicht möglich. Weiterhin ist ein relativ großes Volumen des Ventilraums erforderlich ist, um die im Ventilraum vorgesehenen Komponenten des Steuerventils aufzunehmen. Hierdurch ergibt sich eine entsprechend große Rückflussmenge an Brennstoff zu einem Niederdruckrücklauf. Diese rückfließende Brennstoffmenge muss aus dem Hochdruckraum wieder aufgefüllt werden. Dies verschlechtert den Wirkungsgrad und macht eine entsprechend leistungsfähige Hochdruckpumpe erforderlich. Außerdem ist die Bypass-Bohrung erforderlich, um ein ausreichend schnelles Schließverhalten beim Betätigen der Düsennadel zu erzielen.The from the DE 103 53 169 A1 known injector has the disadvantage that due to the pressurized under the valve seat surface, the valve opening force increases with the fuel pressure. A pressure increase beyond 2000 bar is not possible. Furthermore, a relatively large volume of the valve space is required to accommodate the provided in the valve chamber components of the control valve. This results in a correspondingly large amount of reflux of fuel to a low pressure return. This refluxing amount of fuel must be replenished from the high-pressure chamber. This deteriorates the efficiency and makes a correspondingly high-pressure pump required. In addition, the bypass hole is required to achieve a sufficiently fast closing behavior when operating the nozzle needle.

Außerdem besteht der Nachteil, dass bei einem großen Ventilraumvolumen die Dynamik und damit eine Kleinstmengenfähigkeit verschlechtert wird.In addition, there is the disadvantage that with a large valve space volume, the dynamics and thus a small quantity capability is impaired.

Aus der DE 10 2009 001 099 A1 ist darüber hinaus ein Kraftstoffeinspritzventil bekannt, das ein Steuerventil mit einem durch einen Aktor längsbeweglichen Ventilglied aufweist. Das Ventilglied ist in einer Hülse geführt, die in einem im Kraftstoffeinspritzventil ausgebildeten Ventilraum angeordnet ist.From the DE 10 2009 001 099 A1 In addition, a fuel injection valve is known, which has a control valve with a longitudinally movable by an actuator valve member. The valve member is guided in a sleeve which is arranged in a valve chamber formed in the fuel injection valve.

Offenbarung der ErfindungDisclosure of the invention

Das erfindungsgemäße Brennstoffeinspritzventil mit den Merkmalen des Anspruchs 1 hat den Vorteil, dass eine verbesserte Ausgestaltung des Steuerventils ermöglicht ist. Insbesondere ist eine Reduzierung des Volumens des Ventilraums möglich, wodurch insbesondere die Injektorfunktion und die Kleinstmengenfähigkeit verbessert werden können. Außerdem kann gegebenenfalls ein Kostenvorteil erzielt werden, da Montage- und Einstellschritte bei der Herstellung des Brennstoffeinspritzventils vereinfacht werden oder gegebenenfalls auch entfallen können.The fuel injection valve according to the invention with the features of claim 1 has the advantage that an improved design of the control valve is made possible. In particular, a reduction of the volume of the valve space is possible, whereby in particular the injector function and the smallest quantity capability can be improved. In addition, if necessary, a cost advantage can be achieved because assembly and adjustment steps in the manufacture of the fuel injection valve can be simplified or possibly also omitted.

Durch die in den Unteransprüchen aufgeführten Maßnahmen sind vorteilhafte Weiterbildungen des im Anspruch 1 angegebenen Brennstoffeinspritzventils möglich.The measures listed in the dependent claims advantageous developments of the fuel injection valve specified in claim 1 are possible.

Vorteilhaft ist es, dass die Dichtbuchse an einer der Dichtfläche zugewandten Stirnseite eine umlaufende Beißkante aufweist, mit der die Dichtbuchse an der Dichtfläche anliegt. Hierdurch ist eine zuverlässige Abdichtung gewährleistet. Hierdurch kann entsprechend einem Brennstoffdruck eine Beaufschlagung der Dichtbuchse gegen die Dichtfläche erzielt werden.It is advantageous that the sealing bush has a peripheral biting edge on one of the sealing surface facing the end face, with which the sealing bush rests against the sealing surface. This ensures a reliable seal. In this way, according to a fuel pressure, an admission of the sealing bush against the sealing surface can be achieved.

Vorteilhaft ist es, dass die Dichtbuchse im Bereich der Ventilsitzfläche eine Anlagefläche aufweist und dass die Anlagefläche eine Kontur aufweist, die zumindest teilweise entsprechend einer Kugeloberfläche ausgestaltet ist. Ferner ist es hierbei vorteilhaft, dass eine Ventilplatte vorgesehen ist, dass der Ventilraum zumindest teilweise in der Ventilplatte ausgestaltet ist, dass die Ventilsitzfläche an der Ventilplatte ausgestaltet ist und dass die Ventilplatte eine zumindest teilweise kegelförmige Anlagefläche aufweist, an der die Dichtbuchse mit ihrer Anlagefläche abgestützt ist. Hierdurch kann eine tangentiale Anlage der teilweise kegelförmigen Anlagefläche an der teilweise entsprechend einem balligen Torussegment ausgestalteten Anlagefläche der Dichtbuchse erzielt werden. Hierdurch ist ein vorteilhaftes Ausrichten der Dichtbuchse beziehungsweise ein Toleranzausgleich möglich. Dies ergibt sich insbesondere in einer Zusammenwirkung mit der Abstützung der Dichtbuchse an ihrer Beißkante an der Dichtfläche. In vorteilhafter Weise kann die teilweise kegelförmige Anlagefläche der Ventilplatte die Ventilsitzfläche umfassen. Dadurch vereinfacht sich die Ausgestaltung der Ventilplatte bei gleichzeitig geringster Positionstoleranz zwischen dem Ventilbolzen und der Dichtbuchse, wodurch die Ventildichtheit verbessert wird.It is advantageous that the sealing bushing in the region of the valve seat surface has a contact surface and that the contact surface has a contour which is at least partially designed in accordance with a spherical surface. Furthermore, it is advantageous in this case that a valve plate is provided, that the valve space is at least partially configured in the valve plate, that the valve seat surface is configured on the valve plate and that the valve plate has an at least partially conical contact surface on which the sealing bush is supported with its contact surface is. In this way, a tangential abutment of the partially conical abutment surface on the abutment surface of the sealing bush, which is partially designed in accordance with a convex torus segment, can be achieved. As a result, an advantageous alignment of the sealing bush or a tolerance compensation is possible. This results in particular in a cooperation with the support of the sealing bushing at its biting edge on the sealing surface. Advantageously, the partially conical contact surface of the valve plate may comprise the valve seat surface. This simplifies the design of the valve plate at the same time the lowest position tolerance between the valve pin and the sealing bush, whereby the valve tightness is improved.

Vorteilhaft ist es auch, dass ein Brennstoffdurchgang an der Dichtbuchse ausgestaltet ist, dass zwischen einer Außenseite der Dichtbuchse und einer Innenwand des Ventilraums ein Brennstoffspalt ausgestaltet ist und dass der Brennstoffdurchgang einen Brennstofffluss von dem Brennstoffspalt zu einem Dichtsitz zwischen der Ventilsitzfläche und dem Ventilkörper des Ventilbolzens ermöglicht. Hierbei ist es ferner vorteilhaft, dass der Brennstoffdurchgang durch zumindest einen Durchgangsspalt gebildet ist, der zwischen der Dichtbuchse und einer der Dichtbuchse zugewandten Anlagefläche an der Ventilplatte ausgestaltet ist. Hierdurch wird ein Brennstofffluss zu dem Dichtsitz ermöglicht, so dass beim Betätigen des Ventilbolzens Brennstoff über den geöffneten Dichtsitz zu einem Niederdruckrücklauf oder dergleichen abfließen kann. Dadurch wird ein Druckabfall im Steuerraum zum Betätigen einer Düsennadel erzielt. Außerdem kann durch den Druck des Brennstoffs im Durchgangsspalt, der zwischen der Dichtbuchse und der Anlagefläche ausgebildet ist, eine Beaufschlagung der Dichtbuchse erfolgen, so dass die Dichtbuchse mit ihrer Beißkante gegen die Dichtfläche gepresst wird. Hierdurch ist eine zuverlässige Abdichtung zwischen der Beißkante und der Dichtfläche gewährleistet.It is also advantageous that a fuel passage is formed on the sealing bush, that between a outer side of the sealing bush and an inner wall of the valve chamber, a fuel gap is configured and that the fuel passage allows fuel flow from the fuel gap to a sealing seat between the valve seat surface and the valve body of the valve pin , Here, it is also advantageous that the fuel passage is formed by at least one passage gap, which is designed between the sealing bush and a sealing bush facing the bearing surface on the valve plate. In this way, a fuel flow to the sealing seat is made possible, so that when the valve pin is actuated, fuel can flow away via the open sealing seat to a low-pressure return or the like. As a result, a pressure drop in the control chamber for actuating a nozzle needle is achieved. In addition, by the pressure of the fuel in the passage gap, which is formed between the sealing bush and the contact surface, an impingement of the sealing bushing take place, so that the sealing bush is pressed with its biting edge against the sealing surface. As a result, a reliable seal between the biting edge and the sealing surface is ensured.

Außerdem ist es vorteilhaft, dass zwischen der Dichtbuchse und dem Ventilkörper des Ventilbolzens ein Brennstoffspalt ausgestaltet ist und dass ein Durchmesser eines Dichtsitzes zwischen dem Ventilkörper und der Ventilsitzfläche größer ist als ein Durchmesser einer Führungsbohrung der Dichtbuchse, in der der Ventilbolzen geführt ist. Hierdurch kann durch den Druck des Brennstoffs im Brennstoffspalt zwischen dem Ventilkörper des Ventilbolzens und der Dichtbuchse eine hydraulische Schließkraft auf den Ventilbolzen mit seinem Ventilkörper ausgeübt werden, um den Ventilkörper gegen die Ventilsitzfläche zu beaufschlagen. Diese hydraulische Schließkraft kann hierbei zusätzlich zu einer Ventilfeder wirken.Moreover, it is advantageous that between the sealing bush and the valve body of the valve pin, a fuel gap is configured and that a diameter of a sealing seat between the valve body and the valve seat surface is greater than a diameter of a guide bore of the sealing bush, in which the valve pin is guided. This can be achieved by the pressure of the fuel in the fuel gap between the Valve body of the valve pin and the sealing bush a hydraulic closing force are exerted on the valve pin with its valve body to urge the valve body against the valve seat surface. This hydraulic closing force can act in addition to a valve spring.

Ferner ist es vorteilhaft, dass die Dichtbuchse in einem drucklosen Montagezustand mit einer axialen Übergangspassung in den Ventilraum eingepasst ist. Die Übergangspassung kann hierbei so ausgelegt sein, dass sowohl ein geringes Übermaß zwischen der Beißkante und der Dichtfläche als auch ein kleines Spiel an dieser Stelle vorgesehen sein kann. Hierbei ist eine gewisse Einbautoleranz vorgegeben und auch ermöglicht. Die Beißkante der Dichtbuchse wird im drucklosen Zustand anstelle einer Federkraft durch ihre formschlüssige Einbaubedingung an der Dichtfläche angelegt.Further, it is advantageous that the sealing bush is fitted in an unpressurized mounting state with an axial transition fit in the valve chamber. The transition fit can in this case be designed so that both a slight oversize between the biting edge and the sealing surface and a small game can be provided at this point. Here, a certain installation tolerance is specified and also possible. The biting edge of the sealing bush is applied in the pressureless state instead of a spring force by their form-fitting installation condition on the sealing surface.

Vorteilhaft ist es, dass die Dichtbuchse so ausgestaltet ist, dass die Dichtbuchse von einem über die Ablaufbohrung aus dem Steuerraum aufbaubaren Druck im Ventilraum gegen die Dichtfläche beaufschlagbar ist. Hierbei wird eine hydraulische Kraft auf die Dichtbuchse erzeugt, die auf die Dichtfläche gerichtet ist.It is advantageous that the sealing bushing is designed such that the sealing bushing can be acted upon by a pressure which can be built up via the drainage bore from the control chamber in the valve space against the sealing surface. In this case, a hydraulic force is generated on the sealing bush, which is directed to the sealing surface.

Vorteilhaft ist es, dass die Dichtbuchse an einer Außenseite der Dichtbuchse eine ringförmige Ausnehmung aufweist. Hierbei ist es ferner vorteilhaft, dass die ringförmige Ausnehmung der Dichtbuchse einer Ausnehmung der Ventilplatte zugeordnet ist, in die über eine Ablaufbohrung einer Drosselplatte Brennstoff führbar ist, und dass die ringförmige Ausnehmung der Dichtbuchse einen mit der Ausnehmung der Ventilplatte verbundenen Ringraum bildet, über den der in die Ausnehmung der Drosselplatte führbare Brennstoff umfänglich verteilbar ist. Hierdurch kann die einseitige Strömung aus der Ausnehmung der Ventilplatte gleichmäßig auf den gesamten Umfang der Dichtbuchse verteilt werden. Ferner ist es hierbei vorteilhaft, dass an der Außenseite der Dichtbuchse ein Bund und an dem Bund mehrere axiale Durchströmflächen ausgestaltet sind und dass die axialen Durchströmflächen mit der ringförmigen Ausnehmung der Dichtbuchse verschnitten sind. Hierdurch kann eine vorteilhafte Verbindung der ringförmigen Ausnehmung mit dem jenseits des Bundes vorgesehenen Strömungsspalt erreicht werden.It is advantageous that the sealing bush has an annular recess on an outer side of the sealing bush. In this case, it is also advantageous that the annular recess of the sealing bush is associated with a recess of the valve plate, into which via a drain hole of a throttle plate fuel is feasible, and that the annular recess of the sealing bush forms an annular space connected to the recess of the valve plate, via which the in the recess of the throttle plate feasible fuel is circumferentially distributable. In this way, the one-sided flow from the recess of the valve plate can be distributed uniformly over the entire circumference of the sealing bushing. Furthermore, it is advantageous in this case that on the outer side of the sealing bush, a collar and on the collar a plurality of axial flow areas are configured and that the axial flow areas are blended with the annular recess of the sealing bushing. As a result, an advantageous connection of the annular recess with the flow gap provided beyond the collar can be achieved.

Vorteilhaft ist es auch, dass die Dichtbuchse im Bereich des Ventilkörpers des Ventilbolzens mehrere Durchflussbohrungen aufweist, die sich von einer Außenseite der Dichtbuchse zu einem zwischen dem Ventilkörper des Ventilbolzens und der Dichtbuchse gebildeten Brennstoffspalt erstrecken. Dies ermöglicht eine Ausgestaltung mit einem axialen Überstand, bei der die Dichtbuchse bereits im Montagezustand mit einer Beißkante gegen die Dichtfläche gepresst wird.It is also advantageous that the sealing bush in the region of the valve body of the valve pin has a plurality of through-flow bores extending from an outer side of the sealing bush to a fuel gap formed between the valve body of the valve pin and the sealing bush. This allows a design with an axial projection, in which the sealing bush is already pressed in the assembled state with a biting edge against the sealing surface.

Kurze Beschreibung der ZeichnungenBrief description of the drawings

Bevorzugte Ausführungsbeispiele der Erfindung sind in der nachfolgenden Beschreibung unter Bezugnahme auf die beigefügten Zeichnungen, in denen sich entsprechende Elemente mit übereinstimmenden Bezugszeichen versehen sind, näher erläutert. Es zeigt:

  • Fig. 1 ein Brennstoffeinspritzventil in einer auszugsweisen, schematischen Schnittdarstellung entsprechend einem ersten Ausführungsbeispiel der Erfindung;
  • Fig. 2 den in Fig. 1 mit II bezeichneten Ausschnitt des Brennstoffeinspritzventils entsprechend dem ersten Ausführungsbeispiel der Erfindung;
  • Fig. 3 den in Fig. 1 mit III bezeichneten Ausschnitt des Brennstoffeinspritzventils entsprechend dem ersten Ausführungsbeispiel der Erfindung;
  • Fig. 4 den in Fig. 1 mit IV bezeichneten Ausschnitt des Brennstoffeinspritzventils entsprechend einem zweiten Ausführungsbeispiel der Erfindung;
  • Fig. 5 den in Fig. 4 dargestellten Ausschnitt des Brennstoffeinspritzventils entsprechend einem dritten Ausführungsbeispiel der Erfindung;
  • Fig. 6 eine auszugsweise Darstellung des in Fig. 1 gezeigten Brennstoffeinspritzventils entsprechend einem vierten Ausführungsbeispiel der Erfindung und
  • Fig. 7 eine auszugsweise Darstellung des in Fig. 1 gezeigten Brennstoffeinspritzventils entsprechend einem fünften Ausführungsbeispiel der Erfindung.
Preferred embodiments of the invention are explained in more detail in the following description with reference to the accompanying drawings, in which corresponding elements are provided with identical reference numerals. It shows:
  • Fig. 1 a fuel injection valve in an excerpt, schematic sectional view according to a first embodiment of the invention;
  • Fig. 2 the in Fig. 1 labeled II section of the fuel injection valve according to the first embodiment of the invention;
  • Fig. 3 the in Fig. 1 labeled III section of the fuel injection valve according to the first embodiment of the invention;
  • Fig. 4 the in Fig. 1 labeled IV section of the fuel injection valve according to a second embodiment of the invention;
  • Fig. 5 the in Fig. 4 illustrated section of the fuel injection valve according to a third embodiment of the invention;
  • Fig. 6 a partial representation of the in Fig. 1 shown fuel injection valve according to a fourth embodiment of the invention and
  • Fig. 7 a partial representation of the in Fig. 1 shown fuel injection valve according to a fifth embodiment of the invention.

Ausführungsformen der ErfindungEmbodiments of the invention

Fig. 1 zeigt ein erstes Ausführungsbeispiel eines Brennstoffeinspritzventils 1 der Erfindung in einer schematischen, auszugsweisen Schnittdarstellung. Das Brennstoffeinspritzventil 1 kann insbesondere als Injektor für Brennstoffeinspritzanlagen von luftverdichtenden, selbstzündenden Brennkraftmaschinen dienen. Ein bevorzugter Einsatz des Brennstoffeinspritzventils 1 besteht für eine rennstoffeinspritzanlage mit einem Common-Rail, das Dieselbrennstoff unter hohem Druck zu mehreren Brennstoffeinspritzventilen 1 führt. Das erfindungsgemäße Brennstoffeinspritzventil 1 eignet sich jedoch auch für andere Anwendungsfälle. Fig. 1 shows a first embodiment of a fuel injection valve 1 of the invention in a schematic, partial sectional view. The fuel injection valve 1 can serve in particular as an injector for fuel injection systems of air-compressing, self-igniting internal combustion engines. A preferred use of the fuel injection valve 1 is for a fuel injection system with a common rail that leads Diesel fuel under high pressure to a plurality of fuel injection valves 1. However, the fuel injection valve 1 according to the invention is also suitable for other applications.

Das Brennstoffeinspritzventil 1 weist ein Gehäuse auf, in dem eine Drosselplatte 2 und eine Ventilplatte 3 angeordnet sind. Hierbei weist die Drosselplatte 2 eine Stirnseite 4 auf. Ferner weist die Ventilplatte 3 eine Stirnseite 5 auf. Die Drosselplatte 2 liegt mit ihrer Stirnseite 4 an der Stirnseite 5 der Ventilplatte 3 an.The fuel injection valve 1 has a housing in which a throttle plate 2 and a valve plate 3 are arranged. In this case, the throttle plate 2 has an end face 4. Furthermore, the valve plate 3 has a front side 5. The throttle plate 2 rests with its end face 4 on the end face 5 of the valve plate 3.

Außerdem weist die Drosselplatte 2 eine von der Stirnseite 4 abgewandte weitere Stirnseite 6 auf.In addition, the throttle plate 2 facing away from the end face 4 more end face 6.

Im Betrieb des Brennstoffeinspritzventils 1 wird von einer durch das Brennstoffeinspritzventil 1 geführten Brennstoffleitung über einen Kanalabschnitt 7, der durch die Drosselplatte 2 geführt ist, Brennstoff in einen Steuerraum 8 geführt. Hierbei weist der Kanalabschnitt 7 eine in der Drosselplatte 2 ausgestaltete Zulaufdrossel 9 auf. Der Steuerraum 8 ist einerseits durch eine Stirnseite 6 der Drosselplatte 2 und andererseits durch eine Stirnfläche 10 einer Düsennadel 11 sowie seitlich durch eine Hülse 12 begrenzt. Die Hülse 12 liegt hierbei an der Stirnseite 6 der Drosselplatte 2 an. Entsprechend dem Druck im Steuerraum 8 wird die Düsennadel 11 in einer Schließrichtung 13 beaufschlagt oder entgegen der Schließrichtung 13 geöffnet. Der Druck des Brennstoffs im Steuerraum 8 wirkt hierbei gegen einen Brennstoffdruck in einem Brennstoffraum 14 und eine Ventilfederspannung.During operation of the fuel injection valve 1, fuel is led into a control chamber 8 from a fuel line guided through the fuel injection valve 1 via a channel section 7, which is guided through the throttle plate 2. In this case, the channel section 7 has an inlet throttle 9 configured in the throttle plate 2. The control chamber 8 is bounded on the one hand by an end face 6 of the throttle plate 2 and on the other hand by an end face 10 of a nozzle needle 11 and laterally by a sleeve 12. The sleeve 12 is in this case on the end face 6 of the throttle plate 2. According to the pressure in the control chamber 8, the nozzle needle 11 is acted upon in a closing direction 13 or opened against the closing direction 13. The pressure of the fuel in the control chamber 8 acts against a fuel pressure in a fuel chamber 14 and a valve spring tension.

Zum Steuern des Brennstoffdrucks im Steuerraum 8 dient ein Steuerventil 15. Das Steuerventil 15 weist einen Ventilraum 16 auf, der in diesem Ausführungsbeispiel in der Ventilplatte 3 ausgestaltet ist. Der Ventilraum 16 ist hierbei durch eine Innenwand 17, die an der Ventilplatte 3 ausgestaltet ist, und eine Dichtfläche 18 begrenzt, die Teil der Stirnseite 4 der Drosselplatte 2 ist.For controlling the fuel pressure in the control chamber 8 is a control valve 15. The control valve 15 has a valve chamber 16 which is configured in this embodiment in the valve plate 3. The valve chamber 16 is in this case bounded by an inner wall 17, which is configured on the valve plate 3, and a sealing surface 18, which is part of the end face 4 of the throttle plate 2.

In dem Ventilraum 16 sind eine Dichtbuchse 19 und zumindest abschnittsweise ein Ventilbolzen 20 mit einem Ventilkörper 21 angeordnet. Der Ventilbolzen 20 ist hierbei in einer Führungsbohrung 22 der Dichtbuchse 19 geführt. Das Steuerventil 15 weist eine Längsachse 23 auf, entlang der der Ventilbolzen 20 mit dem Ventilkörper 21 betätigbar ist.In the valve chamber 16, a sealing bushing 19 and at least partially a valve pin 20 are arranged with a valve body 21. The valve pin 20 is in this case guided in a guide bore 22 of the sealing bushing 19. The control valve 15 has a longitudinal axis 23 along which the valve pin 20 with the valve body 21 can be actuated.

Die Ventilplatte 3 weist eine Ausnehmung 24 auf, in die eine Ablaufbohrung 25 mündet. Die Ablaufbohrung 25 ist über die Ausnehmung 24 einerseits mit dem Ventilraum 16 verbunden. Andererseits mündet die Ablaufbohrung 25 in den Steuerraum 8. Die Ablaufbohrung 25 weist eine Ablaufdrossel 26 auf. Somit verbindet die Ablaufbohrung 25 den Steuerraum 8 mit dem Ventilraum 16. Die Ablaufbohrung 25 mit der Ablaufdrossel 26 ist in diesem Ausführungsbeispiel in der Drosselplatte 2 ausgestaltet.The valve plate 3 has a recess 24 into which a drain hole 25 opens. The drain hole 25 is connected via the recess 24 on the one hand with the valve chamber 16. On the other hand, the drain hole 25 opens into the control chamber 8. The drain hole 25 has an outlet throttle 26. Thus, the drain hole 25 connects the control chamber 8 with the valve chamber 16. The drain hole 25 with the outlet throttle 26 is configured in this embodiment in the throttle plate 2.

In der Drosselplatte 2 ist außerdem ein druckentlasteter Raum 27 ausgestaltet, der über einen Rücklaufkanal 28 mit einem Niederdruckrücklauf oder dergleichen verbunden ist. In dem druckentlasteten Raum 27 ist ein Anschlagbolzen 29 angeordnet, der ein teilkugelförmiges Lagerteil 30 umfasst. An seinem Lagerteil 30 ist der Anschlagbolzen 29 an einer Lagerfläche 31 gelagert. Hierdurch ist der Anschlagbolzen 29 zum Erzielen eines Toleranzausgleichs verschwenkbar gelagert. Hierdurch ist im Betrieb eine parallele Ausrichtung des Anschlagbolzens 29 bezüglich der Längsachse 23 ermöglicht. An einem Ende 32 des Ventilbolzens 20 ist eine Einstellscheibe 33 angeordnet, die von einer in dem druckentlasteten Raum 27 angeordneten Ventilfeder 34 beaufschlagt ist. Über die Ventilfeder 34 ist somit der Ventilbolzen 20 mit dem Ventilkörper 21 in einer Schließrichtung 35 beaufschlagt. Ferner ist zwischen der Einstellscheibe 33 und dem Anschlagbolzen 29 ein Spalt 36 vorgegeben, dessen Höhe einen Hub des Ventilkörpers 21 begrenzt. Durch die Dicke der Einstellscheibe 33 ist somit eine Vorgabe des maximalen Hubs des Ventilkörpers 21 ermöglicht.In the throttle plate 2 also a pressure-relieved space 27 is configured, which is connected via a return passage 28 with a low pressure return or the like. In the pressure-relieved space 27 a stop pin 29 is arranged, which comprises a part-spherical bearing part 30. At its bearing part 30, the stop pin 29 is mounted on a bearing surface 31. As a result, the stop pin 29 is pivotally mounted to achieve a tolerance compensation. As a result, a parallel alignment of the stop pin 29 with respect to the longitudinal axis 23 is made possible during operation. At one end 32 of the valve pin 20, a shim 33 is arranged, which is acted upon by a arranged in the pressure-relieved space 27 valve spring 34. The valve pin 20 is thus acted upon by the valve spring 34 with the valve body 21 in a closing direction 35. Further, a gap 36 is predetermined between the shim 33 and the stop pin 29, whose height limits a stroke of the valve body 21. By the thickness of the shim 33 thus a specification of the maximum stroke of the valve body 21 is possible.

Die Ventilplatte 3 weist eine teilweise kegelförmige Anlagefläche 40 auf. Ferner ist an der Ventilplatte 3 eine Ventilsitzfläche 41 ausgestaltet. In diesem Ausführungsbeispiel ist die Ventilsitzfläche 41 Teil der kegelförmigen Anlagefläche 40. Der Ventilkörper 21 des Ventilbolzens 20 wirkt mit der Ventilsitzfläche 41 zu einem Dichtsitz 42 zusammen. Im unbetätigten Zustand des Steuerventils 15 ist der Dichtsitz 42 geschlossen. Hierbei wirkt zum einen die Kraft der Ventilfeder 34 in der Schließrichtung 35. Zum anderen wirkt im Betrieb eine durch den Druck des Brennstoffs bedingte hydraulische Kraft in der Schließrichtung 35.The valve plate 3 has a partially conical contact surface 40. Further, a valve seat surface 41 is configured on the valve plate 3. In this embodiment, the valve seat surface 41 is part of the conical abutment surface 40. The valve body 21 of the valve pin 20 cooperates with the valve seat surface 41 to form a sealing seat 42. In the unactuated state of the control valve 15, the sealing seat 42 is closed. On the one hand, the force of the valve spring 34 in the closing direction 35 acts on the one hand. On the other hand, a hydraulic force due to the pressure of the fuel acts in the closing direction 35 during operation.

Zwischen der Innenwand 17 und einer Außenseite 43 der Dichtbuchse 19 ist ein Brennstoffspalt 44 gebildet. In diesem Ausführungsbeispiel ist der Brennstoffspalt 44 als ringförmiger Brennstoffspalt 44 ausgestaltet. Über den Brennstoffspalt 44 gelangt der Brennstoff aus der Ablaufbohrung 25 zu einem Durchgangsspalt 45 im Bereich der kegelförmigen Anlagefläche 40. Über den Durchgangsspalt 45 gelangt der Brennstoff in einen Brennstoffspalt 46, der zwischen der Dichtbuchse 19 und dem Ventilkörper 21 ausgestaltet ist.Between the inner wall 17 and an outer side 43 of the sealing bush 19, a fuel gap 44 is formed. In this embodiment, the fuel gap 44 is configured as an annular fuel gap 44. Via the fuel gap 44, the fuel passes from the drain hole 25 to a passage gap 45 in the region of the conical contact surface 40. Via the passage gap 45, the fuel passes into a fuel gap 46, which is configured between the sealing bush 19 and the valve body 21.

Im Betrieb wird unter hohem Druck stehender Brennstoff über die Zulaufdrossel 9 in den Steuerraum 8 geführt. Somit stellt sich auch im Brennstoffspalt 44 ein hoher Brennstoffdruck ein. Somit ergibt sich auch im Durchgangsspalt 45 und im Brennstoffspalt 46 ein hoher Druck des dort vorgesehenen Brennstoffs. Auf Grund des geschlossenen Dichtsitzes 42 ist eine Abdichtung gegenüber einem Niederdruckraum 47 gewährleistet, der jenseits des Dichtsitzes 42 an den Ventilkörper 21 des Ventilbolzens 20 angrenzt. Da ein Durchmesser 48 des Ventilbolzens 20 kleiner ist als ein Durchmesser 49 des Dichtsitzes 42 ergibt sich durch den Druck des Brennstoffs eine hydraulische Schließkraft in der Schließrichtung 35.In operation, high-pressure fuel is fed via the inlet throttle 9 into the control chamber 8. Thus, also in the fuel gap 44, a high fuel pressure. Thus, also in the passage gap 45 and in the fuel gap 46 results in a high pressure of the fuel provided there. Due to the closed sealing seat 42 a seal against a low-pressure chamber 47 is ensured, the beyond the sealing seat 42 to the valve body 21 of the valve pin 20 adjacent. Since a diameter 48 of the valve pin 20 is smaller than a diameter 49 of the sealing seat 42 results from the pressure of the fuel, a hydraulic closing force in the closing direction 35th

Außerdem weist die Dichtbuchse 19 an einer der Dichtfläche 18 zugewandten Stirnseite 50 eine umlaufende Beißkante 51 (Fig. 3) auf, mit der Dichtbuchse 19 an der Dichtfläche 18 der Drosselplatte 2 anliegt. Hierdurch ist der Brennstoffspalt 44 gegenüber dem druckentlasteten Raum 27 abgedichtet. Auf Grund des Drucks des Brennstoffs, der im Bereich des Durchgangsspalts 45 auf die Dichtbuchse 19 einwirkt, wird die Dichtbuchse 19 entgegen der Schließrichtung 35 beaufschlagt. Dies verstärkt mit zunehmendem Druck des Brennstoffs die Dichtwirkung zwischen der Dichtbuchse 19 und der Dichtfläche 18.In addition, the sealing bushing 19 has a peripheral biting edge 51 on a front side 50 facing the sealing surface 18 (FIG. Fig. 3 ), with the sealing bush 19 against the sealing surface 18 of the throttle plate 2. As a result, the fuel gap 44 is sealed off from the pressure-relieved space 27. Due to the pressure of the fuel, which acts in the region of the passage gap 45 on the sealing bushing 19, the sealing bush 19 is acted against the closing direction 35. This increases with increasing pressure of the fuel, the sealing effect between the sealing bushing 19 and the sealing surface 18th

Die Dichtbuchse 19 weist im Bereich der Ventilsitzfläche 41 eine der kegelförmigen Anlagefläche zugeordnete Anlagefläche 55 auf. Die Anlagefläche 55 weist eine Kontur 56 auf, die entsprechend einer Kugeloberfläche 56 ausgestaltet ist, wie es durch die unterbrochen dargestellte Linie 56 veranschaulicht ist. Hierdurch ist die Anlagefläche 56 am Berührpunkt tangential zu der Anlagefläche 55 der Dichtbuchse 19 orientiert. Die kugelförmige Kontur 56 der Anlagefläche 55 ist durch einen Radius 57 gekennzeichnet, wobei der Mittelpunkt 58 vorzugsweise auf der Längsachse 23 liegt und den annähernd gleichen Mittelpunkt hat wie der Ventilbolzensitz des Ventilbolzens 20. Hierdurch wird vermieden, dass beim Ausrichten der Dichtbuchse 19, beispielsweise zum Toleranzausgleich beziehungsweise im Zusammenwirken mit einer Plastifizierung an der Beißkante 51, eine Überbestimmung zwischen dem am Ventilplattensitz 42 zentrierten Ventilbolzen 20 und der zentrierten Dichtbuchse 19 auftritt.In the region of the valve seat surface 41, the sealing bush 19 has a contact surface 55 assigned to the conical bearing surface. The contact surface 55 has a contour 56, which is designed in accordance with a spherical surface 56, as illustrated by the broken line 56. As a result, the contact surface 56 is oriented tangentially to the contact surface 55 of the sealing bushing 19 at the contact point. The spherical contour 56 of the contact surface 55 is characterized by a radius 57, wherein the center 58 is preferably located on the longitudinal axis 23 and has approximately the same center as the valve pin seat of the valve pin 20. This avoids that when aligning the sealing bushing 19, for example Tolerance compensation or in cooperation with a plastication on the biting edge 51, an overdetermination between the centered on the valve seat 42 valve pin 20 and the centered sealing bushing 19 occurs.

Der Dichtsitz 42 ist hierbei kreislinienförmig ausgestaltet und bezüglich der Längsachse 23 zentriert.The sealing seat 42 is in this case designed in a circular shape and centered with respect to the longitudinal axis 23.

Es ist anzumerken, dass die kegelförmige Anlagefläche 40 nicht notwendigerweise stufenlos in die Ventilsitzfläche 41 übergeht. Gegebenenfalls kann die Ventilsitzfläche 41 auch einen kleinen Versatz zu der kegelförmigen Anlagefläche 40 aufweisen. Die Ventilsitzfläche 41 ist in vorteilhafter Weise als teilweise kegelförmige Ventilsitzfläche 41 ausgestaltet.It should be noted that the conical abutment surface 40 does not necessarily pass smoothly into the valve seat surface 41. Optionally, the valve seat surface 41 may also have a small offset to the conical bearing surface 40. The valve seat surface 41 is configured advantageously as a partially conical valve seat surface 41.

Zur Bildung des Durchgangsspaltes 45 ist in diesem Ausführungsbeispiel die Dichtbuchse 19 stellenweise zurückgesetzt bezüglich der kegelförmigen Anlagefläche 40 ausgestaltet. Dies kann auch an mehreren Stellen vorgesehen sein. Hierdurch wird die Anlagefläche 55, die auf der Kugeloberflächenkontur 56 liegt, stellenweise unterbrochen. An solch einem Durchgangsspalt 45 ist vorzugsweise ein ungedrosselter Querschnitt vorgegeben. Hierbei ist vorzugsweise ein Parallelspalt 45 zu der kegelförmigen Anlagefläche 40 gebildet.In order to form the passage gap 45, in this embodiment the sealing bush 19 is set in places with respect to the conical bearing surface 40. This can also be provided in several places. As a result, the contact surface 55, which is located on the spherical surface contour 56, interrupted in places. At such a passage gap 45, an unthrottled cross section is preferably predetermined. In this case, a parallel gap 45 is preferably formed to the conical bearing surface 40.

Die Dichtbuchse 19 ist somit einerseits im Bereich der Ventilsitzfläche 41 und andererseits im Bereich der Dichtfläche 18 abgestützt, die der Ventilsitzfläche 41 gegenüber liegt. Die Beißkante 51 der Dichtbuchse 19 wird somit im drucklosen Zustand anstelle einer Federkraft durch ihre formschlüssige Einbaubedingung an die Dichtfläche 18 der Drosselplatte 2 angelegt. Die Einbautoleranz der Dichtbuchse 19 in der Ausnehmung der Ventilplatte 3, die den Ventilraum 16 bildet, ist im drucklosen Montagezustand als Übergangspassung ausgelegt, so dass sowohl geringes Übermaß zwischen der Beißkante 51 und der Dichtfläche 18 der Drosselplatte 2 als auch ein kleines Spiel vorgesehen sein kann.The sealing bush 19 is thus supported on the one hand in the region of the valve seat surface 41 and on the other hand in the region of the sealing surface 18, which lies opposite the valve seat surface 41. The biting edge 51 of the sealing bushing 19 is thus applied in the pressureless state instead of a spring force by their positive installation condition to the sealing surface 18 of the throttle plate 2. The installation tolerance of the sealing bushing 19 in the recess of the valve plate 3, which forms the valve chamber 16 is designed in the pressureless mounting state as a transition fit, so that both slight excess between the biting edge 51 and the sealing surface 18 of the throttle plate 2 and a small game can be provided ,

Um einen schnellen Druckaufbau während der Startphase zu ermöglichen, sind die Leckagespalte nur sehr klein oder nur kurzzeitig wirksam. Dies ist insbesondere dadurch gewährleistet, dass bei ansteigendem Brennstoffdruck im Ventilraum 16 die Beißkante 51 der Dichtbuchse 19 durch die Druckkraft gegen die Dichtfläche 18 der Drosselplatte 2 gepresst wird und dadurch eine leckagefreie Abdichtung gewährleistet ist. Wenn keine weitere Energie zugeführt wird, beispielsweise weil ein Motor abgestellt wird, dann liegt die Dichtbuchse 19 weiterhin an der Dichtfläche 18 der Drosselplatte 2 an, da durch den beim Abstellvorgang relativ langsam absinkenden Druck des Brennstoff im Common-Rail oder dergleichen die Dichtbuchse 19 weiterhin durch die Druckkraft an die Drosselplatte 2 gedrückt wird. Dies ist besonders bei einem Start-Stopp-Betrieb von Vorteil.In order to allow a quick build-up of pressure during the starting phase, the leakage gaps are only very small or only effective for a short time. This is ensured in particular by the fact that with increasing fuel pressure in the valve chamber 16, the biting edge 51 of the sealing bushing 19 is pressed by the pressure force against the sealing surface 18 of the throttle plate 2 and thereby a leak-free seal is ensured. If no further energy is supplied, for example, because an engine is turned off, then the sealing bush 19 is still on the sealing surface 18 of the throttle plate 2, as by the stop process relatively slowly sinking pressure of the fuel in the common rail or the like, the sealing bushing 19 continue is pressed by the pressure force to the throttle plate 2. This is particularly advantageous in a start-stop operation.

Die Betätigung des Ventilbolzens 20 mit dem Ventilkörper 21 erfolgt durch einen Aktor 62, der auf ein Übergangsstück 59 entgegen der Schließrichtung 35 einwirkt. Der Aktor 62 kann als Piezoaktor 62 oder auch als Magnetaktor 62 ausgestaltet sein.The actuation of the valve pin 20 with the valve body 21 is effected by an actuator 62, which acts on a transition piece 59 against the closing direction 35. The actuator 62 may be configured as a piezoelectric actuator 62 or as a magnetic actuator 62.

Fig. 2 zeigt den in Fig. 1 mit II bezeichneten Ausschnitt des Brennstoffeinspritzventils 1 des Ausführungsbeispiels. An der Anlagefläche 55 des Ventilkörpers 21 ist ein Berührpunkt 63 gegeben, an dem die kegelförmige Anlagefläche 40 die entsprechend der Kugeloberflächenkontur 56 ausgestaltete Anlagefläche 55 berührt. Dieser Berührpunkt 63 ermöglicht im Ausgangszustand eine Abstützung der Dichtbuchse 19, um eine Dichtheit im Bereich der Beißkante 51 zu erzielen. Hierbei setzt sich die Berührung zwischen der Anlagefläche 55 und der kegelförmigen Anlagefläche 40 in Umfangsrichtung um die Längsachse 23 nicht ununterbrochen fort, da ein oder mehrere Unterbrechungen in Form von Durchgangsspalten 45 vorgesehen sind. An diesen Durchgangsspalten 45 wird ein Brennstofffluss von dem Brennstoffspalt 44 zu dem Dichtsitz 42 ermöglicht. Allerdings kann sich der Brennstoffspalt 44 auch über eine Flanke 59 der Dichtbuchse 19 erstrecken. Dies ist durch einen zurückgesetzten Abschnitt 60 in der kegelförmigen Anlagefläche 40 der Ventilplatte 3 ermöglicht. Hierdurch kann der Druck des Brennstoffs an der Flanke 49 angreifen, um umfänglich eine hydraulische Kraft entgegen der Schließrichtung 35 zu erzeugen, die die Beißkante 51 gegen die Dichtfläche 18 beaufschlagt. Fig. 2 shows the in Fig. 1 labeled II section of the fuel injection valve 1 of the embodiment. On the abutment surface 55 of the valve body 21, a contact point 63 is provided, on which the conical abutment surface 40 contacts the abutment surface 55 configured in accordance with the spherical surface contour 56. This contact point 63 allows in the initial state, a support of the sealing bushing 19 in order to achieve a tightness in the region of the biting edge 51. In this case, the contact between the abutment surface 55 and the conical abutment surface 40 does not continue uninterruptedly in the circumferential direction about the longitudinal axis 23, since one or more interruptions in the form of passage gaps 45 are provided. At these passage gaps 45 is a Fuel flow from the fuel gap 44 to the sealing seat 42 allows. However, the fuel gap 44 may extend over an edge 59 of the sealing bushing 19. This is made possible by a recessed portion 60 in the conical bearing surface 40 of the valve plate 3. As a result, the pressure of the fuel on the flank 49 can act to generate circumferentially a hydraulic force against the closing direction 35, which acts on the biting edge 51 against the sealing surface 18.

Fig. 3 zeigt den in Fig. 1 mit III bezeichneten Ausschnitt des Brennstoffeinspritzventils 1 des ersten Ausführungsbeispiels. An der Stirnseite 50 weist die Dichtbuchse 19 die Beißkante 51 auf. Die Beißkante 51 ist hierbei als kreislinienförmige Beißkante 51 ausgestaltet, die bezüglich der Längsachse 23 zentriert ist. Ein Durchmesser 61 der kreislinienförmigen Beißkante 51 ist hierbei relativ groß vorgegeben, das heißt deutlich größer als der Durchmesser 48 der Führungsbohrung 22 und fast so groß wie ein Durchmesser der Dichtbuchse 19 an der Außenseite 43. Hierdurch wird in Bezug auf den druckentlasteten Raum 27 eine relativ große hydraulische Kraft entgegen der Schließrichtung 35 durch den Druck des Brennstoffs erzielt. Fig. 3 shows the in Fig. 1 labeled III section of the fuel injection valve 1 of the first embodiment. On the front side 50, the sealing bushing 19, the biting edge 51. The biting edge 51 is in this case designed as a circular biting edge 51, which is centered with respect to the longitudinal axis 23. A diameter 61 of the circular biting edge 51 is in this case set relatively large, that is significantly larger than the diameter 48 of the guide bore 22 and almost as large as a diameter of the sealing bushing 19 on the outer side 43. In this way, with respect to the pressure-relieved space 27 is a relative large hydraulic force against the closing direction 35 achieved by the pressure of the fuel.

Fig. 4 zeigt den in Fig. 1 mit IV bezeichneten Ausschnitt des Brennstoffeinspritzventils 1 entsprechend einem zweiten Ausführungsbeispiel. In diesem Ausführungsbeispiel weist der Ventilbolzen 20 einen Zapfen 65 mit einer Kugelkappe 66 auf. Das Lagerteil 30 ist an der Lagerfläche 31 gelagert. Hierbei befindet sich das Lagerteil 30 in dem druckentlasteten Raum 27. Das Lagerteil 30 weist einen ebenen Hubanschlag 67 auf. Die Kugelkappe 66 des Zapfens 65 ist dem ebenen Hubanschlag 67 des Lagerteils 30 zugewandt. Hierdurch ergibt sich eine näherungsweise punktförmige Anlagestelle 68, mit der die Kugelkappe 66 an dem Hubanschlag 67 anschlägt. Der Kugelradius der Kugelkappe 66 ist durch die Hertzsche Pressbedingung vorgegeben. Um einen Kantenträger zu vermeiden, ist die Rechtwinkligkeit zwischen der ebenen Anschlagfläche 67 des als Hubanschlag dienenden Lagerteils und dem Ventilbolzen 20 in Abhängigkeit von einem Zapfendurchmesser des Zapfens 65 eingeschränkt. Die Hubeinstellung kann hierbei über die Höhe des Zapfens 65 erfolgen. Eine Scheibe 69, die sich ebenfalls in dem druckentlasteten Raum 27 der Drosselplatte 2 befindet, dient hierbei zur Abstützung der Ventilfeder 34, um eine Rückstellung des Ventilbolzens 20 mit seinem Ventilkörper 21 zu gewährleisten. Der Zapfen 65 erstreckt sich hierbei durch eine Bohrung 70 der Scheibe 69. Fig. 4 shows the in Fig. 1 labeled IV section of the fuel injection valve 1 according to a second embodiment. In this embodiment, the valve pin 20 has a pin 65 with a ball cap 66. The bearing part 30 is mounted on the bearing surface 31. In this case, the bearing part 30 is in the pressure-relieved space 27. The bearing part 30 has a flat stroke stop 67. The ball cap 66 of the pin 65 faces the planar stroke stop 67 of the bearing part 30. This results in an approximately punctiform contact point 68, with which the ball cap 66 abuts against the stroke stop 67. The spherical radius of the ball cap 66 is given by the Hertzian pressing condition. To avoid an edge support, the squareness between the flat stop surface 67 of the serving as a stroke stop bearing part and the valve pin 20 in response to a journal diameter of the pin 65 is limited. The stroke adjustment can take place here via the height of the pin 65. A disc 69, which is also located in the pressure-relieved space 27 of the throttle plate 2, serves to support the valve spring 34 to ensure a provision of the valve pin 20 with its valve body 21. The pin 65 extends through a bore 70 of the disc 69th

Fig. 5 zeigt den in Fig. 4 dargestellten Ausschnitt des Brennstoffeinspritzventils 1 entsprechend einem dritten Ausführungsbeispiel. In diesem Ausführungsbeispiel liegt der Ventilbolzen 20 an einer dem Ventilbolzen 20 zugewandten ebenen Stirnseite 71 der Einstellscheibe 69 an. Eine von der Stirnseite 71 abgewandte weitere Stirnseite 72 der Einstellscheibe 69 ist dem Anschlagbolzen 29 zugewandt. Hierbei ist die Stirnseite 72 dem Hubanschlag 67 des Anschlagbolzens 29 zugewandt, der durch eine Kugelkappe 73 des Anschlagbolzens 29 gebildet ist. Hierdurch ist eine näherungsweise punktförmige Anlagestelle 68 zwischen der Einstellscheibe 69 und der Kugelkappe 73 des Anschlagbolzens 29 gebildet. Dadurch ist ein Kugel-Flächenkontakt 68 gebildet, der einen dauerhaft stabilen Hubanschlag 67 gewährleistet. Fig. 5 shows the in Fig. 4 shown section of the fuel injection valve 1 according to a third embodiment. In this embodiment, the valve pin 20 is located on a valve pin 20 facing flat end face 71 of the shim 69. A side facing away from the end face 71 further end face 72 of Shim 69 faces the stop pin 29. Here, the end face 72 the stroke stop 67 of the stop pin 29 faces, which is formed by a ball cap 73 of the stop pin 29. As a result, an approximately punctiform bearing point 68 between the shim 69 and the ball cap 73 of the stop pin 29 is formed. As a result, a spherical surface contact 68 is formed, which ensures a permanently stable stroke stop 67.

Bei dem anhand der Figuren 4 und 5 beschriebenen Ausführungsbeispiel können auch Variationen von einer ebenen Ausgestaltung des Hubanschlags 67 des Anschlagbolzens 29 bzw. der Stirnseite 72 der Einstellscheibe 69 vorgesehen sein. Speziell können leicht konkave Flächen ausgebildet sein. Die Hubeinstellung kann bei dem anhand der Fig. 4 beschriebenen Ausführungsbeispiel auch über die Höhe des Anschlagbolzens 29 und bei dem anhand der Fig. 5 beschriebenen Ausführungsbeispiel über die Dicke der Einstellscheibe 69 und/oder die Höhe des Anschlagbolzens 29 vorgegeben sein. Die Einstellscheibe 69 ist vorzugsweise als Blechstanzteil ausgebildet.In the case of the FIGS. 4 and 5 also described variations of a planar configuration of the stroke stop 67 of the stop pin 29 and the end face 72 of the shim 69 may be provided. Specifically, slightly concave surfaces may be formed. The stroke adjustment can be based on the Fig. 4 described embodiment also on the height of the stop pin 29 and in the basis of the Fig. 5 described embodiment of the thickness of the shim 69 and / or the height of the stop pin 29 be predetermined. The shim 69 is preferably formed as a sheet metal stamping.

Fig. 6 zeigt das in Fig. 1 dargestellte Brennstoffeinspritzventil 1 entsprechend einem vierten Ausführungsbeispiel in einer auszugsweisen, schematischen Schnittdarstellung. In diesem Ausführungsbeispiel weist die Dichtbuchse 19 an ihrer Außenseite 43 eine ringförmige Ausnehmung 74 auf. Die ringförmige Ausnehmung 74 kann hierbei als Ringeinstich 74 und/oder als Ringnut 74 ausgestaltet sein. Die Ausnehmung 24 der Ventilplatte 3 ist als Schnaupe 24 ausgestaltet. Die ringförmige Ausnehmung 74 ist auf der Höhe der Schnaupe 24 an der Außenseite 43 der Dichtbuchse 19 vorgesehen. Über die ringförmige Ausnehmung 74 wird die einseitige Strömung aus der Schnaupe 24 umfänglich in einen durch die ringförmige Ausnehmung 74 in Bezug auf die Innenwand 17 der Ventilplatte 3 gebildeten Ringraum 74 verteilt. Der Ringraum 75 ist hierbei mit der Schnaupe 24 verbunden. Somit verteilt sich die einseitige Strömung des Brennstoffs, die über die Ablaufbohrung 25 der Drosselplatte 2 in die Schnaupe 24 geführt ist, aus der Schnaupe 24 gleichmäßig auf den gesamten Umfang. Direkt oberhalb der ringförmigen Ausnehmung 74 schließt sich ein schmaler Bund 76 der Dichtbuchse 19 mit kleinem Radialspalt in Bezug auf die Innenwand 17 an. Der schmale Bund 76 ist so bemessen, dass durch den kleinen Radialspalt zwischen dem schmalen Bund 76 und der Innenwand 17 der Ventilplatte 3 keine funktionsrelevante Drosselung gegenüber der Ablaufdrossel 26 auftritt. Der schmale Bund 76 befindet sich zwischen der ringförmigen Ausnehmung 74 und der Ventilsitzfläche 41. Fig. 6 shows that in Fig. 1 shown fuel injector 1 according to a fourth embodiment in a partial, schematic sectional view. In this embodiment, the sealing bush 19 on its outer side 43 an annular recess 74. The annular recess 74 may in this case be configured as a ring recess 74 and / or as an annular groove 74. The recess 24 of the valve plate 3 is designed as a spout 24. The annular recess 74 is provided at the height of the spout 24 on the outer side 43 of the sealing bushing 19. About the annular recess 74, the one-sided flow from the spout 24 is circumferentially distributed in an annular space 74 formed by the annular recess 74 with respect to the inner wall 17 of the valve plate 3. The annular space 75 is in this case connected to the spout 24. Thus, the unilateral flow of the fuel, which is guided via the drain hole 25 of the throttle plate 2 in the spout 24, distributed from the spout 24 evenly over the entire circumference. Directly above the annular recess 74 is followed by a narrow collar 76 of the sealing bush 19 with a small radial gap with respect to the inner wall 17 at. The narrow collar 76 is dimensioned such that due to the small radial gap between the narrow collar 76 and the inner wall 17 of the valve plate 3 no function-relevant throttling with respect to the outlet throttle 26 occurs. The narrow collar 76 is located between the annular recess 74 and the valve seat surface 41st

Oberhalb des schmalen Bundes 76, das heißt zwischen dem schmalen Bund 76 und der Ventilsitzfläche 41, setzt sich der Strömungsspalt 44 fort. Hierbei sind vorzugsweise gleichmäßig über den Umfang verteilte axiale Durchströmflächen 77 an der Außenseite 43 der Dichtbuchse 19 vorgesehen. Die axialen Durchströmflächen 77 sind hierbei mit der ringförmigen Ausnehmung 74 verschnitten. Die durch die axialen Durchströmflächen 77 in Bezug auf die Innenwand 17 der Ventilplatte 3 gebildeten Ausnehmungen verbinden die ringförmige Ausnehmung 74 mit dem Strömungsspalt 44. Über die axialen Durchströmfläche 77 kann somit der schmale Bund 76 unterbrochen werden, um eine vorteilhafte Brennstoffströmung zu erzielen.Above the narrow collar 76, that is, between the narrow collar 76 and the valve seat surface 41, the flow gap 44 continues. These are preferably evenly distributed over the circumference axial Durchströmflächen 77 provided on the outer side 43 of the sealing bushing 19. The axial Durchströmflächen 77 are in this case blended with the annular recess 74. The recesses formed by the axial flow-through surfaces 77 with respect to the inner wall 17 of the valve plate 3 connect the annular recess 74 with the flow gap 44. The narrow flange 76 can thus be interrupted via the axial flow-through surface 77 in order to achieve an advantageous fuel flow.

Durch die Anordnung des Bundes 76 direkt oberhalb der Schnaupe 24 werden Druckwellen, die in der Schnaupe 24 und der Bohrung 25 auftreten, in der Wirkfläche bis zum Bundende begrenzt und durch die anschließende Erweiterung im Spalt 44 schwächt sich die Druckwellenamplitude ab. Weiterhin werden die Druckwellen durch die Ausnehmungen, die durch die axialen Durchströmflächen 77 in Bezug auf die Innenwand 17 gebildet sind, auf den Umfang verteilt, so dass sich die resultierende Querkraft reduziert. Die reduzierte Querkraft ermöglicht eine stabile Position der Dichtbuchse 19, wodurch das axiale Spiel zwischen der Anlagefläche 55 der Dichtbuchse 19 und der Anlagefläche 40 der Ventilplatte 3 auf ein fertigungstechnisch einfacheres Maß vergrößert werden kann.Due to the arrangement of the collar 76 directly above the spout 24 pressure waves that occur in the spout 24 and the bore 25 are limited in the effective area to the collar end and the subsequent expansion in the gap 44, the pressure wave amplitude weakens. Furthermore, the pressure waves through the recesses, which are formed by the axial Durchströmflächen 77 with respect to the inner wall 17, distributed over the circumference, so that the resulting lateral force is reduced. The reduced lateral force allows a stable position of the sealing bushing 19, whereby the axial clearance between the contact surface 55 of the sealing bushing 19 and the contact surface 40 of the valve plate 3 can be increased to a manufacturing technology simpler measure.

Fig. 7 zeigt das in Fig. 1 dargestellte Brennstoffeinspritzventil 1 entsprechend einem fünften Ausführungsbeispiel in einer auszugsweisen, schematischen Schnittdarstellung. In diesem Ausführungsbeispiel ist auf der Höhe der Schnaupe 24 die ringförmige Ausnehmung 74 vorgesehen. Über die ringförmige Ausnehmung 74 wird die einseitige Strömung aus der Schnaupe 24 gleichmäßig auf den gesamten Umfang verteilt. Über den Brennstoffspalt 44 strömt der Brennstoff im Betrieb von der ringförmigen Ausnehmung 74 in Richtung der Ventilsitzfläche 41. Der Brennstoffzulauf zum Dichtsitz 42 erfolgt in diesem Ausführungsbeispiel über mehrere vorzugsweise gleichmäßig über den Umfang verteilte Durchflussbohrungen 78, 79 sowie weiterführend über den erweiterten Brennstoffspalt 46. Die Anlage der Dichtbuchse 19 an der Anlagefläche 40 der Ventilplatte 3 ist in diesem Ausführungsbeispiel mit einem axialen Überstand ausgestaltet, so dass die Dichtbuchse 19 bereits im Montagezustand mit ihrer Beißkante 51 gegen die Dichtfläche 18 gepresst wird. Durch die kegelförmige Ausbildung der kegelförmigen Anlagefläche 40 ergibt sich eine zum Dichtsitz 42 konzentrische Position der Dichtbuchse 19. Durch die form- und kraftschlüssige Fixierung der Dichtbuchse 19 können die durch die Druckwellen verursachten Querkräfte sicher aufgefangen werden. Dies erlaubt die Verkleinerung des Strömungsspalts 44, wodurch sich das verbleibende Volumen des Ventilraums 16 funktionsrelevant verringern lässt. Die Durchflussbohrungen 78, 79 erstrecken sich von der Außenseite 43 der Dichtbuchse 19 zu dem zwischen dem Ventilkörper 21 des Ventilbolzens 20 und der Dichtbuchse 19 gebildeten Brennstoffspalt 46. Die Durchflussbohrungen 78, 79 sind hierbei im Bereich des Ventilkörpers 21 des Ventilbolzens 20 an der Dichtbuchse 19 ausgestaltet. Hierdurch münden die Durchflussbohrungen 78, 79 an der Außenseite 43 der Dichtbuchse 19 in einen zurückgesetzten Abschnitt 60 der Ventilplatte 3, in dem sich der Brennstoffspalt 46 erweitert. Fig. 7 shows that in Fig. 1 shown fuel injector 1 according to a fifth embodiment in a partial, schematic sectional view. In this embodiment, the annular recess 74 is provided at the height of the spout 24. About the annular recess 74, the one-sided flow from the spout 24 is evenly distributed over the entire circumference. During operation, the fuel flows to the sealing seat 42 from the annular recess 74 in the direction of the valve seat surface 41. The fuel inlet to the sealing seat 42 takes place via a plurality of flow holes 78, 79, which are distributed uniformly over the circumference, as well as via the extended fuel gap 46 Installation of the sealing bushing 19 on the contact surface 40 of the valve plate 3 is configured in this embodiment with an axial projection, so that the sealing bushing 19 is already pressed in the assembled state with its biting edge 51 against the sealing surface 18. The conical design of the conical bearing surface 40 results in a concentric position of the sealing bushing 19 for the sealing seat 42. The positive and non-positive fixation of the sealing bush 19 enables the transverse forces caused by the pressure waves to be reliably absorbed. This allows the reduction of the flow gap 44, whereby the remaining volume of the valve chamber 16 can be functionally reduced. The flow holes 78, 79 extend from the outer side 43 of the sealing bush 19 to the fuel gap 46 formed between the valve body 21 of the valve pin 20 and the sealing bushing 19. The flow bores 78, 79 are in this case configured in the region of the valve body 21 of the valve pin 20 on the sealing bushing 19. As a result, open the flow holes 78, 79 on the outside 43 of the sealing bushing 19 in a recessed portion 60 of the valve plate 3, in which the fuel gap 46 expands.

Die Erfindung ist nicht auf die beschriebenen Ausführungsbeispiele beschränkt.The invention is not limited to the described embodiments.

Claims (14)

  1. Fuel injection valve (1), in particular injector for fuel injection systems of air-compressing, autoignition internal combustion engines, having a control valve (15) and having a control chamber (8), wherein the control chamber (8) is connected via an outflow bore (25) to a valve chamber (16) of the control valve (15), wherein a valve pin (20) is arranged in the valve chamber (16), and wherein the valve pin (20) has a valve body (21) which interacts with a valve seat surface (41), wherein, in the valve chamber (16), there is arranged a sealing bushing (19) in which the valve pin (20) is guided, characterized in that the sealing bushing (19) is supported at one side in the region of the valve seat surface (41), and in that the sealing bushing (19) is supported at the other side against a sealing surface (18) situated opposite the valve seat surface (41).
  2. Fuel injection valve according to Claim 1,
    characterized
    in that the sealing bushing (19) has, on a face side (50) facing toward the sealing surface (18), an encircling biting edge (51) by which the sealing bushing (19) bears against the sealing surface (18).
  3. Fuel injection valve according to Claim 1 or 2,
    characterized
    in that the sealing bushing (19) has an abutment surface (55) in the region of the valve seat surface (41) and in that the abutment surface (55) has a contour (56) which is formed at least partially in a manner corresponding to a spherical surface (56).
  4. Fuel injection valve according to Claim 3,
    characterized
    in that a valve plate (3) is provided, in that the valve chamber (16) is formed at least partially in the valve plate (3), in that the valve seat surface (41) is formed on the valve plate (3), and in that the valve plate (3) has an at least partially conical abutment surface (40) against which the sealing bushing (19) is supported by way of its abutment surface (55).
  5. Fuel injection valve according to Claim 4,
    characterized
    in that the at least partially conical abutment surface (40) of the valve plate (3) surrounds the valve seat surface (41).
  6. Fuel injection valve according to one of Claims 1 to 5,
    characterized
    in that a fuel passage (45) is formed on the sealing bushing (19), in that a fuel gap (44) is formed between an outer side (43) of the sealing bushing (19) and an inner wall (17) of the valve chamber (16), and in that the fuel passage (45) permits a flow of fuel from the fuel gap (44) to a sealing seat (42) between the valve seat surface (41) and the valve body (21).
  7. Fuel injection valve according to Claim 6,
    characterized
    in that the fuel passage (45) is formed by at least one passage gap (45) formed between the sealing bushing (19) and an abutment surface (40) facing toward the sealing bushing (19).
  8. Fuel injection valve according to one of Claims 1 to 7,
    characterized
    in that a fuel gap (46) is formed between the sealing bushing (19) and the valve body (21) of the valve pin (20), and in that a diameter (49) of a sealing seat (42) between the valve body (21) and the valve seat surface (41) is greater than a diameter (48) of the guide bore (22), in which the valve pin (20) is guided, of the sealing bushing (19).
  9. Fuel injection valve according to one of Claims 1 to 8,
    characterized
    in that, in an unpressurized assembled state, the sealing bushing (19) is fitted into the valve chamber (16) with an axial transition fit.
  10. Fuel injection valve according to one of Claims 1 to 9,
    characterized
    in that the sealing bushing (19) is designed such that the sealing bushing (19) can be forced against the sealing surface (18) by a pressure that can be built up in the valve chamber (16) from the control chamber (8) via the outflow bore (25).
  11. Fuel injection valve according to one of Claims 1 to 10,
    characterized
    in that the sealing bushing (19) has, on an outer side (43) of the sealing bushing (19), an annular recess (74).
  12. Fuel injection valve according to Claim 11,
    characterized
    in that the annular recess (74) of the sealing bushing (19) is assigned to a recess (24) of the valve plate (3), into which recess fuel can be conducted via an outflow bore of a throttle plate (2), and in that the annular recess (74) of the sealing bushing (19) forms an annular chamber (75) which is connected to the recess (24) of the valve plate (3) and via which the fuel that can be conducted into the recess (24) of the valve plate (3) can be distributed circumferentially.
  13. Fuel injection valve according to Claim 11 or 12,
    characterized
    in that a collar (76) is formed on the outer side (43) of the sealing bushing (19), and at least one axial throughflow surface (77) is formed on the collar (76), and in that the axial throughflow surface (77) intersects the annular recess (74) of the sealing bushing (19).
  14. Fuel injection valve according to one of Claims 1 to 13,
    characterized
    in that the sealing bushing (19) has, in the region of the valve body (21) of the valve pin (20), at least one throughflow bore (78, 79) which extends from an outer side (43) of the sealing bushing (19) to a fuel gap (76) formed between the valve body (21) of the valve pin (20) and the sealing bushing (19).
EP20110193679 2010-12-20 2011-12-15 Fuel injector valve Not-in-force EP2466108B1 (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE201010063540 DE102010063540A1 (en) 2010-12-20 2010-12-20 Brennstoffeinspitzventil

Publications (2)

Publication Number Publication Date
EP2466108A1 EP2466108A1 (en) 2012-06-20
EP2466108B1 true EP2466108B1 (en) 2014-11-12

Family

ID=45346341

Family Applications (1)

Application Number Title Priority Date Filing Date
EP20110193679 Not-in-force EP2466108B1 (en) 2010-12-20 2011-12-15 Fuel injector valve

Country Status (2)

Country Link
EP (1) EP2466108B1 (en)
DE (1) DE102010063540A1 (en)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102011078400A1 (en) 2011-06-30 2013-01-03 Robert Bosch Gmbh fuel injector
DE102011086339A1 (en) * 2011-11-15 2013-05-16 Robert Bosch Gmbh Fuel injector, in particular common rail injector
CN102852684B (en) * 2012-10-12 2014-09-17 福建省莆田市中涵机动力有限公司 Pressure balancing type external sealing plane control valve of common-rail oil sprayer

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10353169A1 (en) 2003-11-14 2005-06-16 Robert Bosch Gmbh Injector for injecting fuel into combustion chambers of internal combustion engines, in particular piezo-controlled common rail injector
DE102008040637A1 (en) * 2008-07-23 2010-01-28 Robert Bosch Gmbh Fuel injection valve device
DE102009001099A1 (en) * 2009-02-24 2010-08-26 Robert Bosch Gmbh Fuel injection valve for internal-combustion engine, has valve unit partially guided in sleeve, and spring element surrounding sleeve and subjecting sleeve with compressive force for position fixation in axial and/or radial directions
DE102009001100A1 (en) * 2009-02-24 2010-08-26 Robert Bosch Gmbh Fuel i.e. diesel, injection valve for internal-combustion engine of motor vehicle, has spring element arranged between sleeve and valve unit such that spring element rests against front surface of sleeve and spring collar of valve unit
DE102009055267A1 (en) * 2009-12-23 2011-06-30 Robert Bosch GmbH, 70469 Pressure compensated fuel injector with bypass and minimized valve volume

Also Published As

Publication number Publication date
EP2466108A1 (en) 2012-06-20
DE102010063540A1 (en) 2012-06-21

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