EP2466108A1 - Soupape d'injection de combustible - Google Patents

Soupape d'injection de combustible Download PDF

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Publication number
EP2466108A1
EP2466108A1 EP11193679A EP11193679A EP2466108A1 EP 2466108 A1 EP2466108 A1 EP 2466108A1 EP 11193679 A EP11193679 A EP 11193679A EP 11193679 A EP11193679 A EP 11193679A EP 2466108 A1 EP2466108 A1 EP 2466108A1
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EP
European Patent Office
Prior art keywords
valve
sealing
fuel
fuel injection
sealing bush
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP11193679A
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German (de)
English (en)
Other versions
EP2466108B1 (fr
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
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP2466108A1 publication Critical patent/EP2466108A1/fr
Application granted granted Critical
Publication of EP2466108B1 publication Critical patent/EP2466108B1/fr
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.
  • 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)
EP20110193679 2010-12-20 2011-12-15 Soupape d'injection de combustible Not-in-force EP2466108B1 (fr)

Applications Claiming Priority (1)

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

Publications (2)

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

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EP20110193679 Not-in-force EP2466108B1 (fr) 2010-12-20 2011-12-15 Soupape d'injection de combustible

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EP (1) EP2466108B1 (fr)
DE (1) DE102010063540A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102852684A (zh) * 2012-10-12 2013-01-02 福建省莆田市中涵机动力有限公司 共轨喷油器压力平衡式外密封平面控制阀
WO2013072115A1 (fr) * 2011-11-15 2013-05-23 Robert Bosch Gmbh Injecteur de carburant, en particulier injecteur à rampe commune

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102011078400A1 (de) 2011-06-30 2013-01-03 Robert Bosch Gmbh Kraftstoffinjektor

Citations (5)

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Publication number Priority date Publication date Assignee Title
DE10353169A1 (de) 2003-11-14 2005-06-16 Robert Bosch Gmbh Injektor zur Einspritzung von Kraftstoff in Brennräume von Brennkraftmaschinen, insbesondere piezogesteuerter Common-Rail-Injektor
EP2148080A1 (fr) * 2008-07-23 2010-01-27 Robert Bosch GmbH Dispositif de ventilation d'injection de carburant
DE102009001100A1 (de) * 2009-02-24 2010-08-26 Robert Bosch Gmbh Kraftstoffeinspritzventil
DE102009001099A1 (de) * 2009-02-24 2010-08-26 Robert Bosch Gmbh Kraftstoffeinspritzventil
EP2339164A1 (fr) * 2009-12-23 2011-06-29 Robert Bosch GmbH Injecteur de carburant à compensation de pression doté d'une dérivation et d'un volume d'espace de soupape minimisé

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10353169A1 (de) 2003-11-14 2005-06-16 Robert Bosch Gmbh Injektor zur Einspritzung von Kraftstoff in Brennräume von Brennkraftmaschinen, insbesondere piezogesteuerter Common-Rail-Injektor
EP2148080A1 (fr) * 2008-07-23 2010-01-27 Robert Bosch GmbH Dispositif de ventilation d'injection de carburant
DE102009001100A1 (de) * 2009-02-24 2010-08-26 Robert Bosch Gmbh Kraftstoffeinspritzventil
DE102009001099A1 (de) * 2009-02-24 2010-08-26 Robert Bosch Gmbh Kraftstoffeinspritzventil
EP2339164A1 (fr) * 2009-12-23 2011-06-29 Robert Bosch GmbH Injecteur de carburant à compensation de pression doté d'une dérivation et d'un volume d'espace de soupape minimisé

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2013072115A1 (fr) * 2011-11-15 2013-05-23 Robert Bosch Gmbh Injecteur de carburant, en particulier injecteur à rampe commune
CN102852684A (zh) * 2012-10-12 2013-01-02 福建省莆田市中涵机动力有限公司 共轨喷油器压力平衡式外密封平面控制阀
CN102852684B (zh) * 2012-10-12 2014-09-17 福建省莆田市中涵机动力有限公司 共轨喷油器压力平衡式外密封平面控制阀

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DE102010063540A1 (de) 2012-06-21

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