EP2466108A1 - Fuel injector valve - Google Patents
Fuel injector valve Download PDFInfo
- 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
- Authority
- 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
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Classifications
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- 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
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- 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
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- 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"
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- 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)
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- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Fuel-Injection Apparatus (AREA)
Abstract
Description
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
Der aus der
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.
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
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
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.
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:
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Fig. 1 ein Brennstoffeinspritzventil in einer auszugsweisen, schematischen Schnittdarstellung entsprechend einem ersten Ausführungsbeispiel der Erfindung; -
Fig. 2 den inFig. 1 mit II bezeichneten Ausschnitt des Brennstoffeinspritzventils entsprechend dem ersten Ausführungsbeispiel der Erfindung; -
Fig. 3 den inFig. 1 mit III bezeichneten Ausschnitt des Brennstoffeinspritzventils entsprechend dem ersten Ausführungsbeispiel der Erfindung; -
Fig. 4 den inFig. 1 mit IV bezeichneten Ausschnitt des Brennstoffeinspritzventils entsprechend einem zweiten Ausführungsbeispiel der Erfindung; -
Fig. 5 den inFig. 4 dargestellten Ausschnitt des Brennstoffeinspritzventils entsprechend einem dritten Ausführungsbeispiel der Erfindung; -
Fig. 6 eine auszugsweise Darstellung des inFig. 1 gezeigten Brennstoffeinspritzventils entsprechend einem vierten Ausführungsbeispiel der Erfindung und -
Fig. 7 eine auszugsweise Darstellung des inFig. 1 gezeigten Brennstoffeinspritzventils entsprechend einem fünften Ausführungsbeispiel der Erfindung.
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Fig. 1 a fuel injection valve in an excerpt, schematic sectional view according to a first embodiment of the invention; -
Fig. 2 the inFig. 1 labeled II section of the fuel injection valve according to the first embodiment of the invention; -
Fig. 3 the inFig. 1 labeled III section of the fuel injection valve according to the first embodiment of the invention; -
Fig. 4 the inFig. 1 labeled IV section of the fuel injection valve according to a second embodiment of the invention; -
Fig. 5 the inFig. 4 illustrated section of the fuel injection valve according to a third embodiment of the invention; -
Fig. 6 a partial representation of the inFig. 1 shown fuel injection valve according to a fourth embodiment of the invention and -
Fig. 7 a partial representation of the inFig. 1 shown fuel injection valve according to a fifth embodiment of the invention.
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
Außerdem weist die Drosselplatte 2 eine von der Stirnseite 4 abgewandte weitere Stirnseite 6 auf.In addition, the
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
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
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
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
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
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
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
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
Außerdem weist die Dichtbuchse 19 an einer der Dichtfläche 18 zugewandten Stirnseite 50 eine umlaufende Beißkante 51 (
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
Der Dichtsitz 42 ist hierbei kreislinienförmig ausgestaltet und bezüglich der Längsachse 23 zentriert.The sealing
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
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
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
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
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
Bei dem anhand der
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
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
Die Erfindung ist nicht auf die beschriebenen Ausführungsbeispiele beschränkt.The invention is not limited to the described embodiments.
Claims (14)
dadurch gekennzeichnet,
dass in dem Ventilraum (16) eine Dichtbuchse (19) angeordnet ist, in der der Ventilbolzen (20) geführt ist, dass die Dichtbuchse (19) einerseits im Bereich der Ventilsitzfläche (41) abgestützt ist und dass die Dichtbuchse (19) andererseits an einer Dichtfläche (18) abgestützt ist, die der Ventilsitzfläche (41) gegenüberliegt.Fuel injection valve (1), in particular injector for fuel injection systems of air-compressing, self-igniting internal combustion engines, with a control valve (15) and a control chamber (8), wherein the control chamber (8) via a drain bore (25) with a valve chamber (16) of the control valve (15 ), wherein in the valve space (16) a valve pin (20) is arranged and wherein the valve pin (20) has a valve body (21) which cooperates with a valve seat surface (41),
characterized,
in that a sealing bush (19) is arranged in the valve space (16) in which the sealing bush (19) is supported on the one hand in the region of the valve seat surface (41) and on the other hand on the sealing bush (19) a sealing surface (18) is supported, which is opposite to the valve seat surface (41).
dadurch gekennzeichnet,
dass die Dichtbuchse (19) an einer der Dichtfläche (18) zugewandten Stirnseite (50) eine umlaufende Beißkante (51) aufweist, mit der Dichtbuchse (19) an der Dichtfläche (18) anliegt.Fuel injection valve according to claim 1,
characterized,
that the sealing sleeve (19) on one of the sealing surface (18) facing the end face (50) has a peripheral biting edge (51), with the sealing sleeve (19) at the sealing surface (18) abuts.
dadurch gekennzeichnet,
dass die Dichtbuchse (19) im Bereich der Ventilsitzfläche (41) eine Anlagefläche (55) aufweist und dass die Anlagefläche (55) eine Kontur (56) aufweist, die zumindest teilweise entsprechend einer Kugeloberfläche (56) ausgestaltet ist.Fuel injection valve according to claim 1 or 2,
characterized,
in that the sealing bush (19) has a contact surface (55) in the area of the valve seat surface (41) and in that the contact surface (55) has a contour (56) which is at least partially designed in accordance with a spherical surface (56).
dadurch gekennzeichnet,
dass eine Ventilplatte (3) vorgesehen ist, dass der Ventilraum (16) zumindest teilweise in der Ventilplatte (3) ausgestaltet ist, dass die Ventilsitzfläche (41) an der Ventilplatte (3) ausgestaltet ist und dass die Ventilplatte (3) eine zumindest teilweise kegelförmige Anlagefläche (40) aufweist, an der die Dichtbuchse (19) mit ihrer Anlagefläche (55) abgestützt ist.Fuel injection valve according to claim 3,
characterized,
in that a valve plate (3) is provided, that the valve space (16) is at least partially configured in the valve plate (3), that the valve seat surface (41) is configured on the valve plate (3), and that the valve plate (3) is at least partially Has conical bearing surface (40) on which the sealing bush (19) is supported with its contact surface (55).
dadurch gekennzeichnet,
dass die zumindest teilweise kegelförmige Anlagefläche (40) der Ventilplatte (3) die Ventilsitzfläche (41) umfasst.Fuel injection valve according to claim 4,
characterized,
that the at least partially conical contact surface (40) of the valve plate (3) comprises the valve seat surface (41).
dadurch gekennzeichnet,
dass ein Brennstoffdurchgang (45) an der Dichtbuchse (19) ausgestaltet ist, dass zwischen einer Außenseite (43) der Dichtbuchse (19) und einer Innenwand (17) des Ventilraums (16) ein Brennstoffspalt (44) ausgestaltet ist und dass der Brennstoffdurchgang (45) einen Brennstofffluss von dem Brennstoffspalt (44) zu einem Dichtsitz (42) zwischen der Ventilsitzfläche (41) und dem Ventilkörper (21) ermöglicht.Fuel injection valve according to one of claims 1 to 5,
characterized,
a fuel passage (45) is configured on the sealing bush (19) such that a fuel gap (44) is formed between an outer side (43) of the sealing bush (19) and an inner wall (17) of the valve space (16) and that the fuel passage ( 45) enables fuel flow from the fuel gap (44) to a sealing seat (42) between the valve seat surface (41) and the valve body (21).
dadurch gekennzeichnet,
dass der Brennstoffdurchgang (45) durch zumindest einen Durchgangsspalt (45) gebildet ist, der zwischen der Dichtbuchse (19) und einer der Dichtbuchse (19) zugewandten Anlagefläche (40) ausgebildet ist.Fuel injector according to claim 6,
characterized,
that the fuel passage (45) is formed by at least one passage gap (45) between the sealing bush (19) and one of the sealing bush (19) facing abutment surface (40) is formed.
dadurch gekennzeichnet,
dass zwischen der Dichtbuchse (19) und dem Ventilkörper (21) des Ventilbolzens (20) ein Brennstoffspalt (46) ausgestaltet ist und dass ein Durchmesser (49) eines Dichtsitzes (42) zwischen dem Ventilkörper (21) und der Ventilsitzfläche (41) größer ist als ein Durchmesser (48) der Führungsbohrung (22) der Dichtbuchse (19), in der der Ventilbolzen (20) geführt ist.Fuel injection valve according to one of claims 1 to 7,
characterized,
in that a fuel gap (46) is formed between the sealing bush (19) and the valve body (21) of the valve pin (20) and that a diameter (49) of a sealing seat (42) between the valve body (21) and the valve seat surface (41) is greater is as a diameter (48) of the guide bore (22) of the sealing bush (19) in which the valve pin (20) is guided.
dadurch gekennzeichnet,
dass die Dichtbuchse (19) in einem drucklosen Montagezustand mit einer axialen Übergangspassung in den Ventilraum (16) eingepasst ist.Fuel injection valve according to one of claims 1 to 8,
characterized,
in that the sealing bush (19) is fitted into the valve chamber (16) in an unpressurized mounting state with an axial transition fit.
dadurch gekennzeichnet,
dass die Dichtbuchse (19) so ausgestaltet ist, dass die Dichtbuchse (19) von einem über die Ablaufbohrung (25) aus dem Steuerraum (8) aufbaubaren Druck im Ventilraum (16) gegen die Dichtfläche (18) beaufschlagbar ist.Fuel injection valve according to one of claims 1 to 9,
characterized,
in that the sealing bush (19) is configured such that the sealing bush (19) can be acted upon by a pressure which can be built up in the valve space (16) against the sealing surface (18) via the drainage bore (25) from the control chamber (8).
dadurch gekennzeichnet,
dass die Dichtbuchse (19) an einer Außenseite (43) der Dichtbuchse (19) eine ringförmige Ausnehmung (74) aufweist.Fuel injection valve according to one of claims 1 to 10,
characterized,
that the sealing sleeve (19) on an outer side (43) of the sealing bush (19) has an annular recess (74).
dadurch gekennzeichnet,
dass die ringförmige Ausnehmung (74) der Dichtbuchse (19) einer Ausnehmung (24) der Ventilplatte (3) zugeordnet ist, in die über eine Ablaufbohrung einer Drosselplatte (2) Brennstoff führbar ist, und dass die ringförmige Ausnehmung (74) der Dichtbuchse (19) einen mit der Ausnehmung (24) der Drosselplatte (2) verbundenen Ringraum (75) bildet, über den der in die Ausnehmung (24) der Drosselplatte (2) führbare Brennstoff umfänglich verteilbar ist.Fuel injection valve according to claim 11,
characterized,
in that the annular recess (74) of the sealing bush (19) is associated with a recess (24) of the valve plate (3) into which fuel can be guided via a drainage bore of a throttle plate (2), and in that the annular recess (74) of the sealing bushing ( 19) forms an annular space (75) connected to the recess (24) of the throttle plate (2) via which the fuel which can be guided into the recess (24) of the throttle plate (2) can be distributed circumferentially.
dadurch gekennzeichnet,
dass an der Außenseite (43) der Dichtbuchse (19) ein Bund (76) und an dem Bund (76) zumindest eine axiale Durchströmfläche (77) ausgestaltet sind und dass die axiale Durchströmfläche (77) mit der ringförmigen Ausnehmung (74) der Dichtbuchse (19) verschnitten ist.Fuel injection valve according to claim 11 or 12,
characterized,
in that on the outer side (43) of the sealing bushing (19) a collar (76) and on the collar (76) at least one axial Durchströmfläche (77) are configured and that the axial Durchströmfläche (77) with the annular recess (74) of the sealing bushing (19) is blended.
dadurch gekennzeichnet,
dass die Dichtbuchse (19) im Bereich des Ventilkörpers (21) des Ventilbolzens (20) zumindest eine Durchflussbohrung (78, 79) aufweist, die sich von einer Außenseite (43) der Dichtbuchse (19) zu einem zwischen dem Ventilkörper (21) des Ventilbolzens (20) und der Dichtbuchse (19) gebildeten Brennstoffspalt (76) erstreckt.Fuel injection valve according to one of claims 1 to 13,
characterized,
in that the sealing bush (19) in the region of the valve body (21) of the valve pin (20) has at least one flow bore (78, 79) extending from an outer side (43) of the sealing bush (19) to between the valve body (21) of the Valve pin (20) and the sealing bushing (19) formed fuel gap (76) extends.
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 true EP2466108A1 (en) | 2012-06-20 |
EP2466108B1 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) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN102852684A (en) * | 2012-10-12 | 2013-01-02 | 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 |
WO2013072115A1 (en) * | 2011-11-15 | 2013-05-23 | Robert Bosch Gmbh | Fuel injector, in particular a common rail injector |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102011078400A1 (en) | 2011-06-30 | 2013-01-03 | Robert Bosch Gmbh | fuel injector |
Citations (5)
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 |
EP2148080A1 (en) * | 2008-07-23 | 2010-01-27 | Robert Bosch GmbH | Fuel injection valve device |
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 |
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 |
EP2339164A1 (en) * | 2009-12-23 | 2011-06-29 | Robert Bosch GmbH | Pressure-equalised fuel injector with bypass and minimised valve area volumes |
-
2010
- 2010-12-20 DE DE201010063540 patent/DE102010063540A1/en not_active Withdrawn
-
2011
- 2011-12-15 EP EP20110193679 patent/EP2466108B1/en not_active Not-in-force
Patent Citations (5)
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 |
EP2148080A1 (en) * | 2008-07-23 | 2010-01-27 | Robert Bosch GmbH | Fuel injection valve device |
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 |
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 |
EP2339164A1 (en) * | 2009-12-23 | 2011-06-29 | Robert Bosch GmbH | Pressure-equalised fuel injector with bypass and minimised valve area volumes |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2013072115A1 (en) * | 2011-11-15 | 2013-05-23 | Robert Bosch Gmbh | Fuel injector, in particular a common rail injector |
CN102852684A (en) * | 2012-10-12 | 2013-01-02 | 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 |
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 |
Also Published As
Publication number | Publication date |
---|---|
EP2466108B1 (en) | 2014-11-12 |
DE102010063540A1 (en) | 2012-06-21 |
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