EP2207955B1 - Fuel overflow valve for a fuel injection system, and fuel injection system having a fuel overflow valve - Google Patents

Fuel overflow valve for a fuel injection system, and fuel injection system having a fuel overflow valve Download PDF

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Publication number
EP2207955B1
EP2207955B1 EP20080848181 EP08848181A EP2207955B1 EP 2207955 B1 EP2207955 B1 EP 2207955B1 EP 20080848181 EP20080848181 EP 20080848181 EP 08848181 A EP08848181 A EP 08848181A EP 2207955 B1 EP2207955 B1 EP 2207955B1
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EP
European Patent Office
Prior art keywords
valve
fuel
pressure
region
valve element
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Not-in-force
Application number
EP20080848181
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German (de)
French (fr)
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EP2207955A1 (en
Inventor
Volkhard Ammon
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
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Robert Bosch GmbH
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Publication of EP2207955A1 publication Critical patent/EP2207955A1/en
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Publication of EP2207955B1 publication Critical patent/EP2207955B1/en
Not-in-force legal-status Critical Current
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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
    • F02M37/00—Apparatus or systems for feeding liquid fuel from storage containers to carburettors or fuel-injection apparatus; Arrangements for purifying liquid fuel specially adapted for, or arranged on, internal-combustion engines
    • F02M37/0011—Constructional details; Manufacturing or assembly of elements of fuel systems; Materials therefor
    • F02M37/0023—Valves in the fuel supply and return system
    • F02M37/0029—Pressure regulator in the low pressure fuel system
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/7722—Line condition change responsive valves
    • Y10T137/7837—Direct response valves [i.e., check valve type]
    • Y10T137/7847—With leak passage
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/7722—Line condition change responsive valves
    • Y10T137/7837—Direct response valves [i.e., check valve type]
    • Y10T137/785—With retarder or dashpot

Definitions

  • the invention is based on a fuel spill valve for a fuel injector and a fuel injector with fuel spill valve according to the preamble of claim 1 and of claim 9.
  • Such a fuel spill valve and such a fuel injector is characterized by the DE 100 57 244 A1 known.
  • This fuel spill valve serves to limit the pressure in a low-pressure region of the fuel injection device.
  • the fuel overflow valve has a valve housing in which a valve member is arranged to be liftable.
  • the valve member is controlled in its stroke movement, the connection of an inlet from the low pressure area with a drain to a discharge area
  • the valve member is acted upon by a valve spring in the direction of a closed position in which the connection of the inlet is interrupted with the flow, and by the in the inlet prevailing pressure in the opening direction acted upon.
  • the connection of the inlet opens on the jacket of the valve member into the valve housing and the valve member forms with the connection of the inlet a slide valve.
  • the fuel injection device has a high-pressure pump through which fuel is conveyed under high pressure at least indirectly, for example via a reservoir, to at least one injector.
  • a feed pump delivers fuel to the high-pressure pump.
  • the high pressure pump has at least one in a drive region arranged drive in a lifting movement driven pump piston.
  • the low-pressure region of the fuel injection device extends between the feed pump and the high-pressure pump and in this there is a low pressure generated by the feed pump.
  • the low-pressure region is connected to the drive region of the high-pressure pump.
  • the volume of the drive range changes, since the outward stroke of the pump piston increases the volume of the drive portion and the inward stroke of the pump piston decreases the volume of the drive portion.
  • pressure fluctuations throughout the low pressure range are generated, which may affect the function of the fuel injection device.
  • the valve member of the fuel spill valve must be able to perform a large stroke, which also requires a large stroke of the valve spring. This in turn means that a large installation space for the valve spring is required and this is heavily loaded and therefore can break.
  • a valve which can be flowed through in two directions and in which there is no closed position.
  • a cylindrical part is provided which is slidably disposed in a first chamber and having a through opening.
  • a valve member is also provided, which is arranged in a second chamber and having a through opening.
  • the valve member is acted upon by a valve spring to a stop at the junction of the two chambers out.
  • the cylindrical part can come to rest on the valve member and cylindrical member and valve member are movable together against the valve spring.
  • the valve spring performs the same stroke as the valve member. Even if the cylindrical part bears against the valve member, the valve flows through the openings, so that this is not a closed position of the cylindrical part or of the valve member. This valve is thus not suitable as an overflow valve, since this has no closed position.
  • a feed pump which comprises a spring-loaded suction valve and a spring-loaded pressure valve.
  • valve springs By valve springs, the respective valve member of the suction valve or the pressure valve is acted upon in a closing direction to a valve seat.
  • the valve seats are each formed in a valve seat carrier. A movement of the valve member beyond its closed position determined by the system at the valve seat in the closing direction is not possible.
  • the conveying direction can be reversed by the normally acting as a suction valve acts as a pressure valve and the normally acting as a pressure valve valve acts as a suction valve.
  • valve springs are rendered ineffective by a displacement of the valve seat carrier and instead other valve springs are brought into abutment against the valve members.
  • the respective valve member of the suction valve and the pressure valve is acted upon in a closing direction to another valve seat.
  • the valve springs always execute the same stroke as the valve members.
  • An overflow valve is also known, which is designed as a seat valve, in which the valve member in its closed position acted upon by the valve spring comes into contact with a valve seat and can not move further in the closing direction beyond the valve seat.
  • the valve spring performs the same stroke as the valve member.
  • the fuel spill valve according to the invention with the features according to claim 1 has the advantage that the valve member can perform a larger stroke independently of the valve spring, whereby a better balance of the pressure fluctuations is possible.
  • the valve spring needs to perform only a limited stroke to move the valve member in its closed position, whereby the space of the Kraftstoffüberströmventils and the load of the valve spring can be kept low.
  • Corresponding advantages arise for the fuel injection device according to claim 9 whose function is improved by the reduced pressure fluctuations in the low-pressure region.
  • the embodiment according to claim 2 allows in a simple manner compared to the valve spring stroke enlarged stroke of the valve member. Due to the construction according to claim 3 damping of the lifting movement of the support member and thus the valve member and the valve spring is achieved, whereby the load on the valve spring is reduced.
  • the embodiment of claim 5 also allows damping of the lifting movement of the support member and thus the valve member and the valve spring.
  • the embodiment of claim 7 or 8 allows without changes to the valve housing a two-stage design of the fuel spill valve.
  • FIG. 1 a fuel injection device in a simplified schematic representation
  • FIG. 2 a fuel overflow valve of the fuel injection device according to a first embodiment in the closed state in a longitudinal section with a valve member in a first position
  • FIG. 3 the fuel spill valve in the closed state with the valve member in a second position
  • FIG. 4 the fuel spill valve in the open state
  • FIG. 5 the fuel spill valve according to a second embodiment in the closed state.
  • FIG. 1 a fuel injection device for an internal combustion engine is shown.
  • the fuel injection device has a feed pump 10, which draws fuel from a fuel reservoir 12 and conveys it to the suction side of a high-pressure pump 14. From the feed pump 10, the fuel is compressed to a delivery pressure of, for example, about 4 to 6 bar.
  • the feed pump 10 may be driven electrically or mechanically.
  • a fuel metering device 16 may be arranged, through which the of the High pressure pump 14 sucked and funded under high pressure fuel quantity can be variably adjusted.
  • the fuel metering device 16 may be a proportional valve that can set different flow cross sections, or a clocked valve and is controlled mechanically or electrically by an electronic control device 17.
  • the high-pressure pump 14 has a housing 18 in which a rotationally driven drive shaft 20 is arranged in an interior 19.
  • the interior 19 of the housing 18 with the drive shaft 20 forms a drive region of the high pressure pump 14.
  • the drive shaft 20 has at least one cam 22 or eccentric, wherein the cam 22 may be formed as a multiple cam.
  • the high-pressure pump has at least one or more pump elements 24, each having a pump piston 26, which is indirectly driven by the cam 22 of the drive shaft 20 in a lifting movement in at least approximately radial direction to the axis of rotation of the drive shaft 20.
  • the pump piston 26 is tightly guided in a cylinder bore 28 and bounded with its side facing away from the drive shaft 20 a pump working space 30.
  • the pump working chamber 30 has via an opening into the pump working chamber 30 inlet valve 32 a connection with the fuel inlet from the feed pump 10 ago.
  • the pump working chamber 30 also has, via an outlet valve 34 opening out of the pump working chamber 30, a connection to an outlet, which is connected, for example, to a high-pressure accumulator 110.
  • One or preferably a plurality of injectors 120 arranged on the cylinders of the internal combustion engine are connected to the high-pressure accumulator 110, through which fuel is injected into the cylinders of the internal combustion engine.
  • the high-pressure accumulator 110 can also be dispensed with, with the high-pressure pump 14 then being connected to the injectors 120 via hydraulic lines.
  • the pump piston 26 moves into the interior 19 and sucks in fuel from the feed pump 10 via the open inlet valve 32 forth in the pump work chamber 30 at.
  • the pump piston 26 moves out of the interior 19 and delivers fuel under high pressure from the pump working chamber 30 via the open outlet valve 34 into the high-pressure accumulator 110 or to the injectors 120.
  • the region between the feed pump 10 and the fuel metering device 16 forms a low-pressure region in which the pressure generated by the feed pump 10 prevails.
  • a fuel overflow valve 36 is provided, by which the pressure in the low-pressure region is limited.
  • the fuel spill valve 36 opens when the pressure in the low pressure region exceeds its opening pressure and via the open Kraftstoffüberströmventil 36 funded by the feed pump 10, but not sucked by the high pressure pump 14 fuel quantity is diverted into a discharge area, which is for example a return 11 to the fuel tank 12.
  • the fuel spill valve 36 includes a tubular valve housing 38 that includes a smaller diameter tubular portion 39 and a larger diameter tubular portion 40.
  • a piston-shaped valve member 42 is slidably guided in a longitudinal bore 41.
  • In section 39 of the valve housing 38 at least one opening 43 is provided, which connects the longitudinal bore 41 with the outer jacket of the portion 39.
  • the opening 43 is preferably formed as a bore, wherein, for example, two diametrically opposite holes 43 are provided. Via the openings 43, the longitudinal bore 41 with a discharge area, for example, a return to the fuel tank 12 connectable.
  • the pressure prevailing in the low-pressure region acts via its open end also in the longitudinal bore 41 of the valve housing 38 and thus on the end face of the valve member 42.
  • the open end of the longitudinal bore 41 thus forms an inlet from the low-pressure region into the fuel spill valve 36.
  • the valve member 42 the openings Covered 43, so the inlet, so the low pressure area is separated from the discharge area and when the valve member 42, the openings 43 at least partially releases, so is the inlet, so the low pressure area, with connected to the discharge area.
  • the valve member 42 thus forms with the openings 43 a slide valve.
  • a filter screen 44 can be arranged on the valve housing 38, by which it is prevented that dirt particles can enter the longitudinal bore 41 from the low-pressure region.
  • the filter screen 44 may be fixed by means of an annular fastening element 45 on the valve housing 38, wherein the fastening element may be connected, for example by a flange with the valve housing 38.
  • a valve spring 48 is arranged, which acts via a support member 50 on the valve member 42.
  • the support member 50 is cup-shaped, with its bottom 52 facing the valve member 42 and the open side facing away from the valve member 42.
  • the support member 50 is slidably guided in the longitudinal bore 46 and projects into this from the open side thereof designed as a helical compression spring valve spring 48, which rests against the bottom 52.
  • the valve member 42 remote from the end of the longitudinal bore 46 of the valve housing 38 is closed by means of an insert member 54, which also serves as a support for the valve spring 48.
  • the insert member 54 may be like the support member 50 cup-shaped, with its open end facing the valve member 42 and the valve spring 48 protrudes into the insert member 54 and is supported on the bottom thereof.
  • the insert 54 is fixed in the longitudinal bore 46, for example, pressed into this.
  • the support member 50 and / or the insert 54 may be formed as a sheet metal part.
  • the support member 50 is not connected to the valve member 42 but comes only by the action of the valve spring 48 on the valve member 42 with its bottom 52 to the plant.
  • the support element 50 can perform a maximum stroke towards the valve member 42 which is limited by abutment of the support element 50 at an annular shoulder 56 formed at the transition from the longitudinal bore 46 to the smaller longitudinal bore 41.
  • In the bottom 52 of the support element 50 there is at least one opening 58 available with large cross section.
  • the Longitudinal bore 46 can be connected via at least one opening 62 opening onto the outer jacket of section 40 of valve housing 38 to a relief region, which can be, for example, a return to fuel tank 12.
  • a relief region which can be, for example, a return to fuel tank 12.
  • the support member 50 When the support member 50 is in abutment with the annular shoulder 56, it does not cover the opening 62, so that the longitudinal bore 46 is connected to the relief region.
  • the support member 50 moves from its abutment against the annular shoulder 56 into the longitudinal bore 46, it progressively covers the opening 62 and thus reduces the cross-section and possibly completely closed so that the longitudinal bore 46 only has a small throttling action Flow cross-section is connected to the discharge area or is separated from this.
  • the fuel spill valve 36 with the valve housing 38, the valve member 42, the valve spring 48, the support member 50 and the insert member 54 and the filter screen 44 forms a preassembled module which is inserted into a receiving housing 70.
  • the receiving housing 70 may be a separate housing or a part of the housing 18 of the high-pressure pump 14.
  • the function of the fuel overflow valve 36 will be explained in more detail below.
  • the length of the valve member 42 and the position of the annular shoulder 56 in the valve housing 38 to limit the stroke of the support member 50 are coordinated so that the valve member 42 at the voltage applied to the annular shoulder 56 support member 50, the openings 43 just covers and thus the connection of the low pressure area separates the discharge area.
  • the valve member 42 in FIG. 2 shown. Starting from this position, the valve member 42 can move even further towards the open end of the longitudinal bore 41, wherein the valve member 42 is no longer in contact with the support member 50 and the valve spring 48 thus no longer acts on the valve member 42.
  • valve member 42 is thus free to move in the longitudinal bore 41 according to the difference of acting on one end face pressure in the low pressure region and acting on the other end face pressure in the cylinder bore 46.
  • valve spring 48 By the valve spring 48, the valve member 42 can be moved to its closed position and Independently of the valve spring 48, the valve member 42 beyond its closed position still another run further stroke, which may be limited, for example by the filter screen 44 or the fastener 45, to prevent the valve member 42 moves out of the longitudinal bore 41 out. In this end position, the valve member 42 is in FIG. 3 shown.
  • the low-pressure region is separated from the relief region.
  • the valve member 42 is displaced against the force of the valve spring 48 in the longitudinal bore 41 so that the openings 43 are opened by the valve member 42 and the low-pressure region is connected to the relief region, so that from the low pressure area fuel can flow into the discharge area. In this open position, the valve member 42 is in FIG. 4 shown.
  • valve member 42 can nevertheless carry out a further stroke towards the open end of the longitudinal bore 41 and thus at least partially compensate for pressure and volume fluctuations in the low-pressure region.
  • the stroke that the support element 50 and the valve spring 48 perform is smaller than the possible stroke of the valve member 42. This leads to lower loads on the valve spring 48, which can be dimensioned correspondingly weaker.
  • the maximum stroke of the support member 50 and the valve member 42 and thus the maximum travel of the valve spring 48 is limited by the fact that the support member 50 comes to rest on the insert 54.
  • the valve spring 48 is preferably not yet compressed to block.
  • the at least one opening 58 in the bottom 52 of the support member 50 it is ensured that the valve member 42 can be easily detached from the support member 50 and again come to rest on this.
  • the at least one opening 60 in the support member 50 a pressure equalization between the two sides of the support member 50 is ensured so that it is in the fuel-filled Can move longitudinal bore 46.
  • a damping of the ⁇ réelleshubiolo the valve member 42 and the support member 50 is also achieved, whereby the load on the valve spring 48 is reduced, since the opening stroke is damped by the building up in the longitudinal bore 46 fuel pressure.
  • the fuel spill valve 36 is shown according to a second embodiment in which it opens in two stages and controls two connections of the low-pressure area.
  • the valve housing 38, the support member 50, the valve spring 48, the insert member 54 and the filter screen 44 and its fastening element 45 are formed identically as in the first embodiment.
  • the valve member 142 is deviating from the first embodiment, but the outer dimensions of the valve member 142, ie diameter and length, are identical to the first embodiment.
  • the valve member 142 is hollow and has a blind bore 176 extending from its end facing away from the valve spring 48, wherein the bottom 178 of the valve member 142 coming to rest on the support element 50 is designed to be closed.
  • At least one opening 180 for example in the form of a bore, through which the blind bore 176 is connected to the outer jacket of the valve member 142.
  • the opening 180 is preferably designed as a throttle bore with a defined cross-section.
  • the interior of the blind bore 176 is constantly acted upon by the pressure prevailing in the low-pressure region.
  • the valve member 142 effected by the valve spring 48 When the valve member 142 effected by the valve spring 48 is in its closed position, so are the openings 43 covered by this and the mouth of the opening 180 is located within the longitudinal bore 41 and is covered by this The low-pressure region is thus separated from the discharge areas. If the pressure in the low-pressure region is sufficient to move the valve member 142 against the force of the valve spring 48, the opening 180 initially emerges from the longitudinal bore 41 with a slight opening stroke of the valve member 142, so that the low-pressure region via the blind bore 176, the opening 180 and the at least one opening 60 in the support member 50 is connected to the opening 62 and can flow through this opening 62 fuel from the low pressure region.
  • the openings 43 are further covered by this small opening stroke of the valve member 142 through this and remain closed, so that no fuel can flow out of the low pressure region via the openings 43.
  • the openings 43 are released by this, so that fuel can flow from the low-pressure region via the openings 43 in the return line 11.
  • a use of the two-stage embodiment of the Kraftstoffüberströmventils 36 is advantageous in a fuel injection device in which only a portion of the funded by the feed pump 10 amount of fuel is supplied to the interior 19 of the high-pressure pump 14 for the lubrication and cooling of the drive. If the pressure prevailing in the low-pressure region is insufficient to open the fuel spill valve 36, the entire amount of fuel delivered by the feed pump 10 is supplied via the fuel metering device 16 to the high-pressure pump 14 for delivery.
  • the fuel overflow valve 36 opens in the first stage and that over the opening of the first stage from the blind bore 176, the opening 180, the at least one opening 60 in the support element 50 and the opening 62 outflowing fuel quantity is according to FIG. 1 fed via a line 13 to the interior 19.
  • the second stage opens at the fuel overflow valve 36, in that the valve member 142 releases the openings 43 and fuel can flow out of the low-pressure region via the return 11 into the fuel tank 12.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Safety Valves (AREA)

Description

Stand der TechnikState of the art

Die Erfindung geht aus von einem Kraftstoffüberströmventil für eine Kraftstoffeinspritzeinrichtung und einer Kraftstoffeinspritzeinrichtung mit Kraftstoffüberströmventil nach der Gattung des Anspruchs 1 bzw. des Anspruchs 9.The invention is based on a fuel spill valve for a fuel injector and a fuel injector with fuel spill valve according to the preamble of claim 1 and of claim 9.

Ein solches Kraftstoffüberströmventil und eine solche Kraftstoffeinspritzeinrichtung ist durch die DE 100 57 244 A1 bekannt. Dieses Kraftstoffüberströmventil dient zur Druckbegrenzung in einem Niederdruckbereich der Kraftstoffeinspritzeinrichtung. Das Kraftstoffüberströmventil weist ein Ventilgehäuse auf, in dem ein Ventilglied hubbeweglich angeordnet ist. Durch das Ventilglied wird bei seiner Hubbewegung die Verbindung eines Zulaufs vom Niederdruckbereich her mit einem Ablauf zu einem Entlastungsbereich gesteuert Das Ventilglied ist durch eine Ventilfeder in Richtung einer Schließstellung beaufschlagt, in der die Verbindung des Zulaufs mit dem Ablauf unterbrochen ist, und durch den im Zulauf herrschenden Druck in Öffnungsrichtung beaufschlagt. Die Verbindung des Zulaufs mündet am Mantel des Ventilglieds in das Ventilgehäuse und das Ventilglied bildet mit der Verbind des Zulaufs ein Schieberventil. Wenn der Druck im Niederdruckbereich den durch die Ventilfeder bestimmten Öffnungsdruck überschreitet, so öffnet das Kraftstoffüberströmventil und Kraftstoff kann vom Zulauf aus dem Niederdruckbereich über den Ablauf in einen Entlastungsbereich, beispielsweise einen Rücklauf zum Kraftstoffvorratsbehälter abströmen. Die Kraftstoffeinspritzeinrichtung weist eine Hochdruckpumpe auf, durch die Kraftstoff unter Hochdruck zumindest mittelbar, beispielsweise über einen Speicher, zu wenigstens einem Injektor gefördert wird. Durch eine Förderpumpe wird Kraftstoff zur Hochdruckpumpe gefördert. Die Hochdruckpumpe weist wenigstens einen durch einen in einem Antriebsbereich angeordneten Antrieb in einer Hubbewegung angetriebenen Pumpenkolben auf. Der Niederdruckbereich der Kraftstoffeinspritzeinrichtung erstreckt sich zwischen der Förderpumpe und der Hochdruckpumpe und in diesem herrscht ein durch die Förderpumpe erzeugter Niederdruck. Der Niederdruckbereich ist mit dem Antriebsbereich der Hochdruckpumpe verbunden. Aufgrund der Hubbewegung des wenigstens einen Pumpenkolbens ändert sich das Volumen des Antriebsbereichs, da bei dem auswärts gerichteten Hub des Pumpenkolbens das Volumen des Antriebsbereichs vergrößert und beim einwärts gerichteten Hub des Pumpenkolbens das Volumen des Antriebsbereichs verkleinert wird. Hierdurch entstehen Druckschwankungen im Antriebsbereich. Insbesondere bei einer Hochdruckpumpe mit nur einem Pumpenkolben entstehen relativ starke Druckschwankungen. Hierdurch werden auch Druckschwankungen im gesamten Niederdruckbereich erzeugt, die die Funktion der Kraftstoffeinspritzeinrichtung beeinträchtigen können. Zum Ausgleich dieser Druckschwankungen muss das Ventiglied des Kraftstoffüberströmventils einen großen Hub ausführen können, was entsprechend auch einen großen Hub der Ventilfeder erfordert. Dies führt wiederum dazu, dass ein großer Einbauraum für die Ventilfeder erforderlich ist und diese stark belastet wird und daher brechen kann.Such a fuel spill valve and such a fuel injector is characterized by the DE 100 57 244 A1 known. This fuel spill valve serves to limit the pressure in a low-pressure region of the fuel injection device. The fuel overflow valve has a valve housing in which a valve member is arranged to be liftable. The valve member is controlled in its stroke movement, the connection of an inlet from the low pressure area with a drain to a discharge area The valve member is acted upon by a valve spring in the direction of a closed position in which the connection of the inlet is interrupted with the flow, and by the in the inlet prevailing pressure in the opening direction acted upon. The connection of the inlet opens on the jacket of the valve member into the valve housing and the valve member forms with the connection of the inlet a slide valve. When the pressure in the low-pressure region exceeds the opening pressure determined by the valve spring, the fuel overflow valve opens and fuel can flow out of the low-pressure region via the outlet into a discharge region, for example a return to the fuel reservoir. The fuel injection device has a high-pressure pump through which fuel is conveyed under high pressure at least indirectly, for example via a reservoir, to at least one injector. A feed pump delivers fuel to the high-pressure pump. The high pressure pump has at least one in a drive region arranged drive in a lifting movement driven pump piston. The low-pressure region of the fuel injection device extends between the feed pump and the high-pressure pump and in this there is a low pressure generated by the feed pump. The low-pressure region is connected to the drive region of the high-pressure pump. Due to the lifting movement of the at least one pump piston, the volume of the drive range changes, since the outward stroke of the pump piston increases the volume of the drive portion and the inward stroke of the pump piston decreases the volume of the drive portion. This creates pressure fluctuations in the drive area. In particular, in a high-pressure pump with only one pump piston arise relatively strong pressure fluctuations. As a result, pressure fluctuations throughout the low pressure range are generated, which may affect the function of the fuel injection device. To compensate for these pressure fluctuations, the valve member of the fuel spill valve must be able to perform a large stroke, which also requires a large stroke of the valve spring. This in turn means that a large installation space for the valve spring is required and this is heavily loaded and therefore can break.

Durch die US 2004/0000341 A1 ist ein Ventil bekannt, das in zwei Richtungen durchströmt werden kann und bei dem es keine geschlossene Stellung gibt. Bei diesem Ventil ist ein zylindrisches Teil vorgesehen, das in einer ersten Kammer verschiebbar angeordnet ist und das eine durchgehende Öffnung aufweist. Bei diesem Ventil ist außerdem ein Ventilglied vorgesehen, das in einer zweiten Kammer angeordnet ist und das eine durchgehende Öffnung aufweist. Das Ventilglied wird durch eine Ventilfeder zu einem Anschlag am Übergang der beiden Kammern hin beaufschlagt. Das zylindrische Teil kann am Ventilglied zur Anlage kommen und zylindrisches Teil und Ventilglied sind zusammen gegen die Ventilfeder bewegbar. Die Ventilfeder führt dabei denselben Hub aus wie das Ventilglied. Auch wenn das zylindrische Teil am Ventilglied anliegt erfolgt eine Durchströmung des Ventils durch die Öffnungen, so dass dies keine Schließstellung des zylindrischen Teils oder des Ventilglieds ist. Dieses Ventil ist somit nicht als Überströmventil geeignet, da dieses keine Schließstellung aufweist.By the US 2004/0000341 A1 a valve is known, which can be flowed through in two directions and in which there is no closed position. In this valve, a cylindrical part is provided which is slidably disposed in a first chamber and having a through opening. In this valve, a valve member is also provided, which is arranged in a second chamber and having a through opening. The valve member is acted upon by a valve spring to a stop at the junction of the two chambers out. The cylindrical part can come to rest on the valve member and cylindrical member and valve member are movable together against the valve spring. The valve spring performs the same stroke as the valve member. Even if the cylindrical part bears against the valve member, the valve flows through the openings, so that this is not a closed position of the cylindrical part or of the valve member. This valve is thus not suitable as an overflow valve, since this has no closed position.

Durch die EP 0 392 187 A1 ist eine Förderpumpe bekannt, die ein federbelastetes Saugventil und ein federbelastetes Druckventil aufweist. Durch Ventilfedern wird das jeweilige Ventilglied des Saugventils bzw. des Druckventils in einer Schließrichtung zu einem Ventilsitz hin beaufschlagt. Die Ventilsitze sind jeweils in einem Ventilsitzträger ausgebildet. Eine Bewegung des Ventilglieds über dessen durch die Anlage am Ventilsitz bestimmte Schließstellung hinaus in Schließrichtung ist nicht möglich. Bei der Förderpumpe gemäß diesem Dokument ist außerdem vorgesehen, dass deren Förderrichtung umgekehrt werden kann, indem das normalerweise als Saugventil wirkende Ventil als Druckventil wirkt und das normalerweise als Druckventil wirkende Ventil als Saugventil wirkt. Hierzu werden die Ventilfedern durch eine Verschiebung der Ventilsitzträger unwirksam gemacht und stattdessen werden andere Ventilfedern in Anlage an die Ventilglieder gebracht. Durch die anderen Ventilfedern wird das jeweilige Ventilglied des Saugventils bzw. des Druckventils in einer Schließrichtung zu einem anderen Ventilsitz hin beaufschlagt. Die Ventilfedern führen stets denselben Hub aus wie die Ventilglieder.By the EP 0 392 187 A1 a feed pump is known which comprises a spring-loaded suction valve and a spring-loaded pressure valve. By valve springs, the respective valve member of the suction valve or the pressure valve is acted upon in a closing direction to a valve seat. The valve seats are each formed in a valve seat carrier. A movement of the valve member beyond its closed position determined by the system at the valve seat in the closing direction is not possible. In the feed pump according to this document is also provided that the conveying direction can be reversed by the normally acting as a suction valve acts as a pressure valve and the normally acting as a pressure valve valve acts as a suction valve. For this purpose, the valve springs are rendered ineffective by a displacement of the valve seat carrier and instead other valve springs are brought into abutment against the valve members. By the other valve springs, the respective valve member of the suction valve and the pressure valve is acted upon in a closing direction to another valve seat. The valve springs always execute the same stroke as the valve members.

Durch die EP 1338 787 A1 ist ebenfalls ein Überströmventil bekannt, das als Sitzventil ausgebildet ist, bei dem das Ventilglied in seiner Schließstellung durch die Ventilfeder beaufschlagt an einem Ventilsitz zur Anlage kommt und sich in Schließrichtung über den Ventilsitz hinaus nicht weiter bewegen kann. Die Ventilfeder führt denselben Hub aus wie das Ventilglied.By the EP 1338 787 A1 An overflow valve is also known, which is designed as a seat valve, in which the valve member in its closed position acted upon by the valve spring comes into contact with a valve seat and can not move further in the closing direction beyond the valve seat. The valve spring performs the same stroke as the valve member.

Offenbarung der ErfindungDisclosure of the invention Vorteile der ErfindungAdvantages of the invention

Das erfindungsgemäße Kraftstoffüberströmventil mit den Merkmalen gemäß Anspruch 1 hat demgegenüber den Vorteil, dass das Ventilglied unabhängig von der Ventilfeder einen größeren Hub ausführen kann, wodurch ein besserer Ausgleich der Druckschwankungen ermöglicht ist. Die Ventilfeder braucht nur einen begrenzten Hub auszuführen, um das Ventilglied in seine Schließstellung zu bewegen, wodurch der Bauraum des Kraftstoffüberströmventils und die Belastung der Ventilfeder gering gehalten werden können. Entsprechende Vorteile ergeben sich für die Kraftstoffeinspritzeinrichtung gemäß Anspruch 9 deren Funktion durch die verringerten Druckschwankungen im Niederdruckbereich verbessert ist.The fuel spill valve according to the invention with the features according to claim 1 has the advantage that the valve member can perform a larger stroke independently of the valve spring, whereby a better balance of the pressure fluctuations is possible. The valve spring needs to perform only a limited stroke to move the valve member in its closed position, whereby the space of the Kraftstoffüberströmventils and the load of the valve spring can be kept low. Corresponding advantages arise for the fuel injection device according to claim 9 whose function is improved by the reduced pressure fluctuations in the low-pressure region.

In den abhängigen Ansprüchen sind vorteilhafte Ausgestaltungen und Weiterbildungen des erfindungsgemäßen Kraftstoffüberströmventils angegeben. Die Ausbildung gemäß Anspruch 2 ermöglicht auf einfache Weise den gegenüber dem Ventilfederhub vergrößerten Hub des Ventilglieds. Durch die Ausbildung gemäß Anspruch 3 wird eine Dämpfung der Hubbewegung des Stützelements und damit des Ventilglieds und der Ventilfeder erreicht, wodurch die Belastung der Ventilfeder reduziert wird. Die Ausbildung gemäß Anspruch 5 ermöglicht ebenfalls eine Dämpfung der Hubbewegung des Stützelements und damit des Ventilglieds und der Ventilfeder. Die Ausbildung gemäß Anspruch 7 oder 8 ermöglicht ohne Änderungen am Ventilgehäuse eine zweistufige Ausführung des Kraftstoffüberströmventils.In the dependent claims advantageous refinements and developments of the fuel spill valve according to the invention are given. The embodiment according to claim 2 allows in a simple manner compared to the valve spring stroke enlarged stroke of the valve member. Due to the construction according to claim 3 damping of the lifting movement of the support member and thus the valve member and the valve spring is achieved, whereby the load on the valve spring is reduced. The embodiment of claim 5 also allows damping of the lifting movement of the support member and thus the valve member and the valve spring. The embodiment of claim 7 or 8 allows without changes to the valve housing a two-stage design of the fuel spill valve.

Zeichnungdrawing

Zwei Ausführungsbeispiele der Erfindung sind in der Zeichnung dargestellt und in der nachfolgenden Beschreibung näher erläutert. Es zeigen Figur 1 eine Kraftstoffeinspritzeinrichtung in einer vereinfachten schematischen Darstellung, Figur 2 ein Kraftstoffüberströmventil der Kraftstoffeinspritzeinrichtung gemäß einem ersten Ausführungsbeispiel in geschlossenem Zustand in einem Längsschnitt mit einem Ventilglied in einer ersten Stellung, Figur 3 das Kraftstoffüberströmventil in geschlossenem Zustand mit dem Ventilglied in einer zweiten Stellung, Figur 4 das Kraftstoffüberströmventil in geöffnetem Zustand, Figur 5 das Kraftstoffüberströmventil gemäß einem zweiten Ausführungsbeispiel in geschlossenem Zustand.Two embodiments of the invention are illustrated in the drawing and explained in more detail in the following description. Show it FIG. 1 a fuel injection device in a simplified schematic representation, FIG. 2 a fuel overflow valve of the fuel injection device according to a first embodiment in the closed state in a longitudinal section with a valve member in a first position, FIG. 3 the fuel spill valve in the closed state with the valve member in a second position, FIG. 4 the fuel spill valve in the open state, FIG. 5 the fuel spill valve according to a second embodiment in the closed state.

Beschreibung der AusführungsbeispieleDescription of the embodiments

In Figur 1 ist eine Kraftstoffeinspritzeinrichtung für eine Brennkraftmaschine dargestellt. Die Kraftstoffeinspritzeinrichtung weist eine Förderpumpe 10 auf, die Kraftstoff aus einem Kraftstoffvorratsbehälter 12 ansaugt und zur Saugseite einer Hochdruckpumpe 14 fördert. Von der Förderpumpe 10 wird der Kraftstoff auf einen Förderdruck von beispielsweise etwa 4 bis 6 bar verdichtet. Die Förderpumpe 10 kann elektrisch oder mechanisch angetrieben sein. Zwischen der Förderpumpe 10 und der Saugseite der Hochdruckpumpe 14 kann eine Kraftstoffzumesseinrichtung 16 angeordnet sein, durch die die von der Hochdruckpumpe 14 angesaugte und unter Hochdruck geförderte Kraftstoffmenge variabel eingestellt werden kann. Die Kraftstoffzumesseinrichtung 16 kann ein Proportionalventil sein, das unterschiedlich große Durchflussquerschnitte einstellen kann, oder ein getaktetes Ventil und wird mechanisch oder elektrisch durch eine elektronische Steuereinrichtung 17 angesteuert.In FIG. 1 a fuel injection device for an internal combustion engine is shown. The fuel injection device has a feed pump 10, which draws fuel from a fuel reservoir 12 and conveys it to the suction side of a high-pressure pump 14. From the feed pump 10, the fuel is compressed to a delivery pressure of, for example, about 4 to 6 bar. The feed pump 10 may be driven electrically or mechanically. Between the feed pump 10 and the suction side of the high-pressure pump 14, a fuel metering device 16 may be arranged, through which the of the High pressure pump 14 sucked and funded under high pressure fuel quantity can be variably adjusted. The fuel metering device 16 may be a proportional valve that can set different flow cross sections, or a clocked valve and is controlled mechanically or electrically by an electronic control device 17.

Die Hochdruckpumpe 14 weist ein Gehäuse 18 auf, in dem in einem Innenraum 19 eine rotierend angetriebene Antriebswelle 20 angeordnet ist. Der Innenraum 19 des Gehäuses 18 mit der Antriebswelle 20 bildet einen Antriebsbereich der Hochdruckpumpe 14. Die Antriebswelle 20 weist wenigstens einen Nocken 22 oder Exzenter auf, wobei der Nocken 22 auch als Mehrfachnocken ausgebildet sein kann. Die Hochdruckpumpe weist wenigstens ein oder mehrere Pumpenelemente 24 mit jeweils einem Pumpenkolben 26 auf, der durch den Nocken 22 der Antriebswelle 20 mittelbar in einer Hubbewegung in zumindest annähernd radialer Richtung zur Drehachse der Antriebswelle 20 angetrieben wird. Der Pumpenkolben 26 ist in einer Zylinderbohrung 28 dicht geführt und begrenzt mit seiner der Antriebswelle 20 abgewandten Seite einen Pumpenarbeitsraum 30. Der Pumpenarbeitsraum 30 weist über ein in den Pumpenarbeitsraum 30 öffnendes Einlassventil 32 eine Verbindung mit dem Kraftstoffzulauf von der Förderpumpe 10 her auf. Der Pumpenarbeitsraum 30 weist ausserdem über ein aus dem Pumpenarbeitsraum 30 öffnendes Auslassventil 34 eine Verbindung mit einem Auslass auf, der beispielsweise mit einem Hochdruckspeicher 110 verbunden ist. Mit dem Hochdruckspeicher 110 sind ein oder vorzugsweise mehrere an den Zylindern der Brennkraftmaschine angeordnete Injektoren 120 verbunden, durch die Kraftstoff in die Zylinder der Brennkraftmaschine eingespritzt wird. Der Hochdruckspeicher 110 kann auch entfallen, wobei die Hochdruckpumpe 14 dann mit den Injektoren 120 über hydraulische Leitungen verbunden ist Bei seinem Saughub bewegt sich der Pumpenkolben 26 in den Innenraum 19 hinein und saugt dabei über das geöffnete Einlassventil 32 Kraftstoff aus dem Zulauf von der Förderpumpe 10 her in den Pumpenarbeitsraum 30 an. Bei seinem Förderhub bewegt sich der Pumpenkolben 26 aus dem Innenraum 19 heraus und fördert Kraftstoff unter Hochdruck aus dem Pumpenarbeitsraum 30 über das geöffnete Auslassventil 34 in den Hochdruckspeicher 110 bzw. zu den Injektoren 120.The high-pressure pump 14 has a housing 18 in which a rotationally driven drive shaft 20 is arranged in an interior 19. The interior 19 of the housing 18 with the drive shaft 20 forms a drive region of the high pressure pump 14. The drive shaft 20 has at least one cam 22 or eccentric, wherein the cam 22 may be formed as a multiple cam. The high-pressure pump has at least one or more pump elements 24, each having a pump piston 26, which is indirectly driven by the cam 22 of the drive shaft 20 in a lifting movement in at least approximately radial direction to the axis of rotation of the drive shaft 20. The pump piston 26 is tightly guided in a cylinder bore 28 and bounded with its side facing away from the drive shaft 20 a pump working space 30. The pump working chamber 30 has via an opening into the pump working chamber 30 inlet valve 32 a connection with the fuel inlet from the feed pump 10 ago. The pump working chamber 30 also has, via an outlet valve 34 opening out of the pump working chamber 30, a connection to an outlet, which is connected, for example, to a high-pressure accumulator 110. One or preferably a plurality of injectors 120 arranged on the cylinders of the internal combustion engine are connected to the high-pressure accumulator 110, through which fuel is injected into the cylinders of the internal combustion engine. The high-pressure accumulator 110 can also be dispensed with, with the high-pressure pump 14 then being connected to the injectors 120 via hydraulic lines. During its intake stroke, the pump piston 26 moves into the interior 19 and sucks in fuel from the feed pump 10 via the open inlet valve 32 forth in the pump work chamber 30 at. During its delivery stroke, the pump piston 26 moves out of the interior 19 and delivers fuel under high pressure from the pump working chamber 30 via the open outlet valve 34 into the high-pressure accumulator 110 or to the injectors 120.

Der Bereich zwischen der Förderpumpe 10 und der Kraftstoffzumesseinrichtung 16 bildet einen Niederdruckbereich, in dem der von der Förderpumpe 10 erzeugte Druck herrscht. Durch die Förderpumpe 10 wird dabei ständig dieselbe Kraftstoffmenge gefördert, jedoch wird durch die Hochdruckpumpe 14 abhängig von der Einstellung der Kraftstoffzumesseinrichtung 16 eine variable Kraftstoffmenge angesaugt. Aus diesem Grund ist ein Kraftstoffüberströmventil 36 vorgesehen, durch das der Druck im Niederdruckbereich begrenzt wird. Das Kraftstoffüberströmventil 36 öffnet, wenn der Druck im Niederdruckbereich dessen Öffnungsdruck überschreitet und über das geöffnete Kraftstoffüberströmventil 36 wird die von der Förderpumpe 10 geförderte, jedoch von der Hochdruckpumpe 14 nicht angesaugte Kraftstoffmenge in einen Entlastungsbereich abgesteuert, der beispielsweise ein Rücklauf 11 zum Kraftstoffvorratsbehälter 12 ist.The region between the feed pump 10 and the fuel metering device 16 forms a low-pressure region in which the pressure generated by the feed pump 10 prevails. By the feed pump 10 while constantly the same amount of fuel delivered, but is sucked by the high-pressure pump 14, depending on the setting of the fuel metering 16, a variable amount of fuel. For this reason, a fuel overflow valve 36 is provided, by which the pressure in the low-pressure region is limited. The fuel spill valve 36 opens when the pressure in the low pressure region exceeds its opening pressure and via the open Kraftstoffüberströmventil 36 funded by the feed pump 10, but not sucked by the high pressure pump 14 fuel quantity is diverted into a discharge area, which is for example a return 11 to the fuel tank 12.

Das Kraftstoffüberströmventil 36 gemäß einem ersten Ausführungsbeispiel wird anhand der Figuren 2 bis 4 nachfolgend näher erläutert. Das Kraftstoffüberströmventil 36 weist ein rohrförmiges Ventilgehäuse 38 auf, das einen rohrförmigen Abschnitt 39 mit geringerem Durchmesser und einen rohrförmigen Abschnitt 40 mit größerem Durchmesser umfasst. In dem Abschnitt 39 des Ventilgehäuses 38 ist in einer Längsbohrung 41 ein kolbenförmiges Ventilglied 42 verschiebbar dicht geführt. Im Abschnitt 39 des Ventilgehäuses 38 ist wenigstens eine Öffnung 43 vorgesehen, die die Längsbohrung 41 mit dem Außenmantel des Abschnitts 39 verbindet. Die Öffnung 43 ist vorzugsweise als Bohrung ausgebildet, wobei beispielsweise zwei einander diametral gegenüberliegende Bohrungen 43 vorgesehen sind. Über die Öffnungen 43 ist die Längsbohrung 41 mit einem Entlastungsbereich, beispielsweise einem Rücklauf in den Kraftstoffvorratsbehälter 12 verbindbar. Der im Niederdruckbereich herrschende Druck wirkt über deren offenes Ende auch in der Längsbohrung 41 des Ventilgehäuses 38 und damit auf die Stirnseite des Ventilglieds 42. Das offene Ende der Längsbohrung 41 bildet somit einen Zulauf vom Niederdruckbereich in das Kraftstoffüberströmventil 36. Wenn das Ventilglied 42 die Öffnungen 43 überdeckt, so ist der Zulauf, also der Niederdruckbereich vom Entlastungsbereich getrennt und wenn das Ventilglied 42 die Öffnungen 43 zumindest teilweise freigibt, so ist der Zulauf, also der Niederdruckbereich, mit dem Entlastungsbereich verbunden. Das Ventilglied 42 bildet somit mit den Öffnungen 43 ein Schieberventil. Am offenen Ende der Längsbohrung 41 kann am Ventilgehäuse 38 ein Filtersieb 44 angeordnet sein, durch das verhindert wird, dass aus dem Niederdruckbereich Schmutzpartikel in die Längsbohrung 41 eintreten können. Das Filtersieb 44 kann mittels eines ringförmigen Befestigungselements 45 am Ventilgehäuse 38 fixiert sein, wobei das Befestigungselement beispielsweise durch eine Bördelung mit dem Ventilgehäuse 38 verbunden sein kann.The fuel spill valve 36 according to a first embodiment will be described with reference to FIGS FIGS. 2 to 4 explained in more detail below. The fuel spill valve 36 includes a tubular valve housing 38 that includes a smaller diameter tubular portion 39 and a larger diameter tubular portion 40. In the section 39 of the valve housing 38, a piston-shaped valve member 42 is slidably guided in a longitudinal bore 41. In section 39 of the valve housing 38 at least one opening 43 is provided, which connects the longitudinal bore 41 with the outer jacket of the portion 39. The opening 43 is preferably formed as a bore, wherein, for example, two diametrically opposite holes 43 are provided. Via the openings 43, the longitudinal bore 41 with a discharge area, for example, a return to the fuel tank 12 connectable. The pressure prevailing in the low-pressure region acts via its open end also in the longitudinal bore 41 of the valve housing 38 and thus on the end face of the valve member 42. The open end of the longitudinal bore 41 thus forms an inlet from the low-pressure region into the fuel spill valve 36. When the valve member 42, the openings Covered 43, so the inlet, so the low pressure area is separated from the discharge area and when the valve member 42, the openings 43 at least partially releases, so is the inlet, so the low pressure area, with connected to the discharge area. The valve member 42 thus forms with the openings 43 a slide valve. At the open end of the longitudinal bore 41, a filter screen 44 can be arranged on the valve housing 38, by which it is prevented that dirt particles can enter the longitudinal bore 41 from the low-pressure region. The filter screen 44 may be fixed by means of an annular fastening element 45 on the valve housing 38, wherein the fastening element may be connected, for example by a flange with the valve housing 38.

In einer Längsbohrung 46 des Abschnitts 40 des Ventilgehäuses 38, die zumindest annähernd koaxial zur Längsbohrung 41 verläuft jedoch einen größeren Durchmesser aufweist als diese, ist eine Ventilfeder 48 angeordnet, die über ein Stützelement 50 auf das Ventilglied 42 wirkt. Das Stützelement 50 ist topfförmig ausgebildet, wobei dessen Boden 52 zum Ventilglied 42 weist und dessen offene Seite dem Ventilglied 42 abgewandt ist. Das Stützelement 50 ist in der Längsbohrung 46 verschiebbar geführt und in dieses ragt von dessen offener Seite her die als Schraubendruckfeder ausgebildete Ventilfeder 48 hinein, die am Boden 52 anliegt. Das dem Ventilglied 42 abgewandte Ende der Längsbohrung 46 des Ventilgehäuses 38 ist mittels eines Einsatzteils 54 verschlossen, das auch als Abstützung für die Ventilfeder 48 dient. Das Einsatzteil 54 kann wie das Stützelement 50 topfförmig ausgebildet sein, wobei dessen offenes Ende zum Ventilglied 42 weist und die Ventilfeder 48 in das Einsatzteil 54 hineinragt und sich an dessen Boden abstützt. Das Einsatzteil 54 ist in der Längsbohrung 46 fixiert, beispielsweise in diese eingepresst. Das Stützelement 50 und/oder das Einsatzteil 54 können als Blechformteil ausgebildet sein.In a longitudinal bore 46 of the portion 40 of the valve housing 38 which is at least approximately coaxial with the longitudinal bore 41 but has a larger diameter than this, a valve spring 48 is arranged, which acts via a support member 50 on the valve member 42. The support member 50 is cup-shaped, with its bottom 52 facing the valve member 42 and the open side facing away from the valve member 42. The support member 50 is slidably guided in the longitudinal bore 46 and projects into this from the open side thereof designed as a helical compression spring valve spring 48, which rests against the bottom 52. The valve member 42 remote from the end of the longitudinal bore 46 of the valve housing 38 is closed by means of an insert member 54, which also serves as a support for the valve spring 48. The insert member 54 may be like the support member 50 cup-shaped, with its open end facing the valve member 42 and the valve spring 48 protrudes into the insert member 54 and is supported on the bottom thereof. The insert 54 is fixed in the longitudinal bore 46, for example, pressed into this. The support member 50 and / or the insert 54 may be formed as a sheet metal part.

Das Stützelement 50 ist nicht mit dem Ventilglied 42 verbunden sondern kommt nur durch die Wirkung der Ventilfeder 48 am Ventilglied 42 mit seinem Boden 52 zur Anlage. Das Stützelement 50 kann zum Ventilglied 42 hin einen maximalen Hub ausführen, der durch Anlage des Stützelements 50 an einer am Übergang von der Längsbohrung 46 zu der im Durchmesser kleineren Längsbohrung 41 gebildeten Ringschulter 56 begrenzt ist Im Boden 52 des Stützelements 50 ist wenigstens eine Öffnung 58 mit großem Querschnitt vorhanden. Im Randbereich des Bodens 52 nahe dessen Übergang zur Mantelfläche des Stützelements 50 ist wenigstens eine Öffnung 60 mit kleinem Querschnitt vorgesehen. Die Längsbohrung 46 ist über wenigstens eine am Außenmantel des Abschnitts 40 des Ventilgehäuses 38 mündende Öffnung 62 mit einem Entlastungsbereich verbindbar, der beispielsweise ein Rücklauf zum Kraftstoffvorratsbehälter 12 sein kann. Wenn sich das Stützelement 50 in Anlage an der Ringschulter 56 befindet, so überdeckt dieses die Öffnung 62 nicht, so dass die Längsbohrung 46 mit dem Entlastungsbereich verbunden ist. Wenn sich das Stützelement 50 ausgehend von seiner Anlage an der Ringschulter 56 in die Längsbohrung 46 hineinbewegt, so wird durch dieses zunehmend die Öffnung 62 überdeckt und somit der Querschnitt verringert und gegebenenfalls ganz verschlossen, so dass die Längsbohrung 46 nur noch über einen kleinen, drosselnden Durchflussquerschnitt mit dem Entlastungsbereich verbunden ist bzw. von diesem getrennt ist.The support member 50 is not connected to the valve member 42 but comes only by the action of the valve spring 48 on the valve member 42 with its bottom 52 to the plant. The support element 50 can perform a maximum stroke towards the valve member 42 which is limited by abutment of the support element 50 at an annular shoulder 56 formed at the transition from the longitudinal bore 46 to the smaller longitudinal bore 41. In the bottom 52 of the support element 50 there is at least one opening 58 available with large cross section. In the edge region of the bottom 52 near its transition to the lateral surface of the support member 50 at least one opening 60 is provided with a small cross-section. The Longitudinal bore 46 can be connected via at least one opening 62 opening onto the outer jacket of section 40 of valve housing 38 to a relief region, which can be, for example, a return to fuel tank 12. When the support member 50 is in abutment with the annular shoulder 56, it does not cover the opening 62, so that the longitudinal bore 46 is connected to the relief region. When the support member 50 moves from its abutment against the annular shoulder 56 into the longitudinal bore 46, it progressively covers the opening 62 and thus reduces the cross-section and possibly completely closed so that the longitudinal bore 46 only has a small throttling action Flow cross-section is connected to the discharge area or is separated from this.

Das Kraftstoffüberströmventil 36 mit dem Ventilgehäuse 38, dem Ventilglied 42, der Ventilfeder 48, dem Stützelement 50 und dem Einsatzteil 54 sowie dem Filtersieb 44 bildet eine vormontierte Baugruppe, die in ein Aufnahmegehäuse 70 eingefügt ist. Das Aufnahmegehäuse 70 kann ein separates Gehäuse sein oder ein Teil des Gehäuses 18 der Hochdruckpumpe 14.The fuel spill valve 36 with the valve housing 38, the valve member 42, the valve spring 48, the support member 50 and the insert member 54 and the filter screen 44 forms a preassembled module which is inserted into a receiving housing 70. The receiving housing 70 may be a separate housing or a part of the housing 18 of the high-pressure pump 14.

Nachfolgend wird die Funktion des Kraftstoffüberströmventils 36 näher erläutert. Die Länge des Ventilglieds 42 und die Position der Ringschulter 56 im Ventilgehäuse 38 zur Begrenzung des Hubs des Stützelements 50 sind so aufeinander abgestimmt, dass das Ventilglied 42 bei an der Ringschulter 56 anliegendem Stützelement 50 die Öffnungen 43 gerade überdeckt und somit die Verbindung des Niederdruckbereichs mit dem Entlastungsbereich trennt. In dieser Stellung ist das Ventilglied 42 in Figur 2 dargestellt. Ausgehend von dieser Stellung kann sich das Ventilglied 42 noch weiter in Richtung zum offenen Ende der Längsbohrung 41 bewegen, wobei sich das Ventilglied 42 nicht mehr in Anlage am Stützelement 50 befindet und die Ventilfeder 48 somit nicht mehr auf das Ventilglied 42 wirkt. Das Ventilglied 42 ist somit frei in der Längsbohrung 41 beweglich entsprechend der Differenz des auf dessen eine Stirnseite wirkenden Drucks im Niederdruckbereich und des auf dessen andere Stirnseite wirkenden Drucks in der Zylinderbohrung 46. Durch die Ventilfeder 48 kann das Ventilglied 42 in seine Schließstellung bewegt werden und unabhängig von der Ventilfeder 48 kann das Ventilglied 42 über seine Schließstellung hinaus noch einen weiteren Hub ausführen, der beispielsweise durch das Filtersieb 44 oder das Befestigungselement 45 begrenzt sein kann, um zu verhindern, dass sich das Ventilglied 42 aus der Längsbohrung 41 heraus bewegt. In dieser Endstellung ist das Ventilglied 42 in Figur 3 dargestellt.The function of the fuel overflow valve 36 will be explained in more detail below. The length of the valve member 42 and the position of the annular shoulder 56 in the valve housing 38 to limit the stroke of the support member 50 are coordinated so that the valve member 42 at the voltage applied to the annular shoulder 56 support member 50, the openings 43 just covers and thus the connection of the low pressure area separates the discharge area. In this position, the valve member 42 in FIG. 2 shown. Starting from this position, the valve member 42 can move even further towards the open end of the longitudinal bore 41, wherein the valve member 42 is no longer in contact with the support member 50 and the valve spring 48 thus no longer acts on the valve member 42. The valve member 42 is thus free to move in the longitudinal bore 41 according to the difference of acting on one end face pressure in the low pressure region and acting on the other end face pressure in the cylinder bore 46. By the valve spring 48, the valve member 42 can be moved to its closed position and Independently of the valve spring 48, the valve member 42 beyond its closed position still another run further stroke, which may be limited, for example by the filter screen 44 or the fastener 45, to prevent the valve member 42 moves out of the longitudinal bore 41 out. In this end position, the valve member 42 is in FIG. 3 shown.

Wenn der im Niederdruckbereich herrschende Druck nicht ausreicht um das Ventilglied 42 gegen die Kraft der Ventilfeder 48 so weit in der Längsbohrung 41 zu verschieben, dass die Öffnungen 43 durch das Ventilglied 42 aufgesteuert werden, so ist der Niederdruckbereich vom Entlastungsbereich getrennt. Wenn der im Niederdruckbereich herrschende Druck den Öffnungsdruck des Kraftstoffüberströmventils 36 erreicht, so wird das Ventilglied 42 gegen die Kraft der Ventilfeder 48 in der Längsbohrung 41 verschoben, so dass durch das Ventilglied 42 die Öffnungen 43 aufgesteuert werden und der Niederdruckbereich mit dem Entlastungsbereich verbunden ist, so dass aus dem Niederdruckbereich Kraftstoff in den Entlastungsbereich abströmen kann. In dieser geöffneten Stellung ist das Ventilglied 42 in Figur 4 dargestellt.If the pressure prevailing in the low-pressure region is insufficient to displace the valve member 42 against the force of the valve spring 48 in the longitudinal bore 41 in such a way that the openings 43 are opened by the valve member 42, then the low-pressure region is separated from the relief region. When the pressure prevailing in the low-pressure region reaches the opening pressure of the fuel overflow valve 36, the valve member 42 is displaced against the force of the valve spring 48 in the longitudinal bore 41 so that the openings 43 are opened by the valve member 42 and the low-pressure region is connected to the relief region, so that from the low pressure area fuel can flow into the discharge area. In this open position, the valve member 42 is in FIG. 4 shown.

Wenn durch das Ventilglied 42 die Öffnungen 43 überdeckt sind, also der Niederdruckbereich vom Entlastungsbereich getrennt ist, so kann das Ventilglied 42 dennoch einen weiteren Hub zum offenen Ende der Längsbohrung 41 hin ausführen und somit Druck- und Volumenschwankungen im Niederdruckbereich zumindest teilweise ausgleichen. Der Hub, den das Stützelement 50 und die Ventilfeder 48 ausführen, ist gegenüber dem möglichen Hub des Ventilglieds 42 kleiner. Dies führt zu geringeren Belastungen der Ventilfeder 48, die entsprechend schwächer dimensioniert werden kann. Der maximale Hub des Stützelements 50 und des Ventilglieds 42 und damit der maximale Federweg der Ventilfeder 48 ist dadurch begrenzt, dass das Stützelement 50 am Einsatzteil 54 zur Anlage kommt. Hierbei ist die Ventilfeder 48 vorzugsweise noch nicht auf Block zusammengedrückt.If the openings 43 are covered by the valve member 42, ie the low-pressure region is separated from the relief region, the valve member 42 can nevertheless carry out a further stroke towards the open end of the longitudinal bore 41 and thus at least partially compensate for pressure and volume fluctuations in the low-pressure region. The stroke that the support element 50 and the valve spring 48 perform is smaller than the possible stroke of the valve member 42. This leads to lower loads on the valve spring 48, which can be dimensioned correspondingly weaker. The maximum stroke of the support member 50 and the valve member 42 and thus the maximum travel of the valve spring 48 is limited by the fact that the support member 50 comes to rest on the insert 54. Here, the valve spring 48 is preferably not yet compressed to block.

Durch die wenigstens eine Öffnung 58 im Boden 52 des Stützelements 50 ist sichergestellt, dass sich das Ventilglied 42 leicht vom Stützelement 50 lösen bzw. wieder an diesem zur Anlage kommen kann. Durch die wenigstens eine Öffnung 60 im Stützelement 50 ist ein Druckausgleich zwischen den beiden Seiten des Stützelements 50 sichergestellt, so dass dieses sich in der kraftstoffgefüllten Längsbohrung 46 bewegen kann. Durch die hubabhängige Steuerung der Öffnung 62 durch das Stützelement 50 ist außerdem eine Dämpfung der Öffnungshubbewegung des Ventilglieds 42 und des Stützelements 50 erreicht, wodurch die Belastung der Ventilfeder 48 verringert wird, da die Öffnungshubbewegung durch den sich in der Längsbohrung 46 aufbauenden Kraftstoffdruck gedämpft wird.By the at least one opening 58 in the bottom 52 of the support member 50 it is ensured that the valve member 42 can be easily detached from the support member 50 and again come to rest on this. By the at least one opening 60 in the support member 50, a pressure equalization between the two sides of the support member 50 is ensured so that it is in the fuel-filled Can move longitudinal bore 46. By the stroke-dependent control of the opening 62 by the support member 50, a damping of the Öffnungshubbewegung the valve member 42 and the support member 50 is also achieved, whereby the load on the valve spring 48 is reduced, since the opening stroke is damped by the building up in the longitudinal bore 46 fuel pressure.

In Figur 5 ist das Kraftstoffüberströmventil 36 gemäß einem zweiten Ausführungsbeispiel dargestellt, bei dem dieses zweistufig öffnet und zwei Verbindungen des Niederdruckbereichs steuert. Das Ventilgehäuse 38, das Stützelement 50, die Ventilfeder 48, das Einsatzteil 54 sowie das Filtersieb 44 und dessen Befestigungselement 45 sind dabei identisch ausgebildet wie beim ersten Ausführungsbeispiel. Lediglich das Ventilglied 142 ist gegenüber dem ersten Ausführungsbeispiel abweichend ausgebildet, wobei jedoch die äußeren Abmessungen des Ventilglieds 142, also Durchmesser und Länge, identisch wie beim ersten Ausführungsbeispiel sind. Das Ventilglied 142 ist abweichend vom ersten Ausführungsbeispiel hohl ausgebildet und weist eine von dessen der Ventilfeder 48 abgewandtem Ende ausgehende Sackbohrung 176 auf, wobei der am Stützelement 50 zur Anlage kommende Boden 178 des Ventilglieds 142 geschlossen ausgebildet ist. Nahe dem geschlossenen Ende des Ventilglieds 142 ist an diesem wenigstens eine Öffnung 180, beispielsweise in Form einer Bohrung, vorgesehen, durch die die Sackbohrung 176 mit dem Außenmantel des Ventilglieds 142 verbunden ist. Die Öffnung 180 ist dabei vorzugsweise als Drosselbohrung mit definiertem Querschnitt ausgeführt. Das Innere der Sackbohrung 176 ist ständig von dem im Niederdruckbereich herrschenden Druck beaufschlagt.In FIG. 5 the fuel spill valve 36 is shown according to a second embodiment in which it opens in two stages and controls two connections of the low-pressure area. The valve housing 38, the support member 50, the valve spring 48, the insert member 54 and the filter screen 44 and its fastening element 45 are formed identically as in the first embodiment. Only the valve member 142 is deviating from the first embodiment, but the outer dimensions of the valve member 142, ie diameter and length, are identical to the first embodiment. Deviating from the first embodiment, the valve member 142 is hollow and has a blind bore 176 extending from its end facing away from the valve spring 48, wherein the bottom 178 of the valve member 142 coming to rest on the support element 50 is designed to be closed. Near the closed end of the valve member 142 there is provided at least one opening 180, for example in the form of a bore, through which the blind bore 176 is connected to the outer jacket of the valve member 142. The opening 180 is preferably designed as a throttle bore with a defined cross-section. The interior of the blind bore 176 is constantly acted upon by the pressure prevailing in the low-pressure region.

Wenn sich das Ventilglied 142 durch die Ventilfeder 48 bewirkt in seiner Schließstellung befindet, so werden durch dieses die Öffnungen 43 überdeckt und die Mündung der Öffnung 180 befindet sich innerhalb der Längsbohrung 41 und wird durch diese überdeckt Der Niederdruckbereich ist somit von den Entlastungsbereichen getrennt. Wenn der Druck im Niederdruckbereich ausreicht um das Ventilglied 142 gegen die Kraft der Ventilfeder 48 zu bewegen, so tritt zunächst bei geringem Öffnungshub des Ventilglieds 142 die Öffnung 180 aus der Längsbohrung 41 aus, so dass der Niederdruckbereich über die Sackbohrung 176, die Öffnung 180 und die wenigstens eine Öffnung 60 im Stützelement 50 mit der Öffnung 62 verbunden ist und über diese Öffnung 62 Kraftstoff aus dem Niederdruckbereich abströmen kann. Die Öffnungen 43 werden bei diesem geringen Öffnungshub des Ventilglieds 142 durch dieses weiterhin überdeckt und bleiben verschlossen, so dass aus dem Niederdruckbereich kein Kraftstoff über die Öffnungen 43 abströmen kann. Bei weiterem Öffnungshub des Ventilglieds 142 werden durch dieses auch die Öffnungen 43 freigegeben, so dass Kraftstoff aus dem Niederdruckbereich auch über die Öffnungen 43 in den Rücklauf 11 abströmen kann.When the valve member 142 effected by the valve spring 48 is in its closed position, so are the openings 43 covered by this and the mouth of the opening 180 is located within the longitudinal bore 41 and is covered by this The low-pressure region is thus separated from the discharge areas. If the pressure in the low-pressure region is sufficient to move the valve member 142 against the force of the valve spring 48, the opening 180 initially emerges from the longitudinal bore 41 with a slight opening stroke of the valve member 142, so that the low-pressure region via the blind bore 176, the opening 180 and the at least one opening 60 in the support member 50 is connected to the opening 62 and can flow through this opening 62 fuel from the low pressure region. The openings 43 are further covered by this small opening stroke of the valve member 142 through this and remain closed, so that no fuel can flow out of the low pressure region via the openings 43. Upon further opening stroke of the valve member 142, the openings 43 are released by this, so that fuel can flow from the low-pressure region via the openings 43 in the return line 11.

Eine Verwendung der zweistufigen Ausführung des Kraftstoffüberströmventils 36 ist vorteilhaft bei einer Kraftstoffeinspritzeinrichtung, bei der nur ein Teil der von der Förderpumpe 10 geförderten Kraftstoffmenge dem Innenraum 19 der Hochdruckpumpe 14 für die Schmierung und Kühlung von deren Antrieb zugeführt wird. Wenn der im Niederdruckbereich herrschende Druck nicht ausreicht, um das Kraftstoffüberströmventil 36 zu öffnen, so wird die gesamte von der Förderpumpe 10 geförderte Kraftstoffmenge über die Kraftstoffzumesseinrichtung 16 der Hochdruckpumpe 14 zur Förderung zugeführt. Wenn der im Niederdruckbereich herrschende Druck einen ersten Grenzwert erreicht, so öffnet das Kraftstoffüberströmventil 36 in der ersten Stufe und die über die bei Öffnung der ersten Stufe aus der Sackbohrung 176, die Öffnung 180, die wenigstens eine Öffnung 60 im Stützelement 50 und die Öffnung 62 abströmende Kraftstoffmenge wird gemäß Figur 1 über eine Leitung 13 dem Innenraum 19 zugeführt. Hierdurch ist zunächst eine schnelle Kraftstoffförderung durch die Hochdruckpumpe 14 beim Starten der Brennkraftmaschine und anschließend eine ausreichende Schmierung und Kühlung des Antriebsbereichs der Hochdruckpumpe 14 sichergestellt Wenn der im Niederdruckbereich herrschende Druck einen zweiten, höheren Grenzwert erreicht, so öffnet beim Kraftstoffüberströmventil 36 auch die zweite Stufe, indem das Ventilglied 142 die Öffnungen 43 freigibt und Kraftstoff aus dem Niederdruckbereich über den Rücklauf 11 in den Kraftstoffvorratsbehälter 12 abströmen kann.A use of the two-stage embodiment of the Kraftstoffüberströmventils 36 is advantageous in a fuel injection device in which only a portion of the funded by the feed pump 10 amount of fuel is supplied to the interior 19 of the high-pressure pump 14 for the lubrication and cooling of the drive. If the pressure prevailing in the low-pressure region is insufficient to open the fuel spill valve 36, the entire amount of fuel delivered by the feed pump 10 is supplied via the fuel metering device 16 to the high-pressure pump 14 for delivery. When the pressure prevailing in the low-pressure region reaches a first limit value, the fuel overflow valve 36 opens in the first stage and that over the opening of the first stage from the blind bore 176, the opening 180, the at least one opening 60 in the support element 50 and the opening 62 outflowing fuel quantity is according to FIG. 1 fed via a line 13 to the interior 19. As a result, a fast fuel delivery by the high-pressure pump 14 when starting the internal combustion engine and then sufficient lubrication and cooling of the drive range of the high-pressure pump 14 is ensured. When the pressure prevailing in the low-pressure region reaches a second, higher limit value, then the second stage opens at the fuel overflow valve 36, in that the valve member 142 releases the openings 43 and fuel can flow out of the low-pressure region via the return 11 into the fuel tank 12.

Claims (10)

  1. Fuel overflow valve for a fuel injection device, in particular for pressure limitation in a low-pressure region of the fuel injection device, having a valve housing (38), having a valve element (42; 142) which is arranged in the valve housing (38) so as to be capable of performing a stroke movement and by means of which, by way of the stroke movement thereof, a connection (43) between an inlet to the valve housing (38) and a relief region is controlled, wherein the valve element (42; 142) is loaded by a valve spring (48) in the direction of a closed position in which the connection (43) between the inlet and the relief region is shut off, and the valve element (42; 142) is loaded in the opening direction by the pressure prevailing in the inlet, wherein the connection (43) between the inlet and the relief region in the valve housing (38) opens out at the shell of the valve element (42; 142), wherein a slide valve is formed by the valve element (42; 142) together with the connection (43) between the inlet and the relief region, characterized in that the valve element (42; 142) can, in the valve housing (38), perform a further stroke in the closing direction beyond its closed position, during which further stroke the valve spring (48) does not act on the valve element (42; 142).
  2. Fuel overflow valve according to Claim 1, characterized in that the valve spring (48) acts on the valve element (42; 142) via a support element (50) which is not connected to the valve element (42; 142), and in that the support element (50), in the closing direction and in the region of the closed position of the valve element (42; 142), abuts against a stop (56) in the valve housing (38).
  3. Fuel overflow valve according to Claim 2, characterized in that the support element (50) is guided displaceably in the valve housing (38) and, in the valve housing (38), delimits a chamber (46) in which the valve spring (48) is arranged, in that said chamber (46) has a connection (62) to a relief region, and in that said connection (62) is controlled by the support element (50) in a manner dependent on the stroke thereof.
  4. Fuel overflow valve according to Claim 3, characterized in that the connection (62) between the chamber (46) and the relief region is open when the support element (50) is bearing against the stop (56) and is closed by the support element (50) when the support element (50) moves in the direction of the open position of the valve element (42; 142).
  5. Fuel overflow valve according to one of Claims 2 to 4, characterized in that the support element (50) is of pot-shaped form, in that the valve spring (48) projects into the support element (50) and bears against the base (52) thereof, and in that the support element (50) bears by way of its base (52) against the valve element (42; 142).
  6. Fuel overflow valve according to Claim 5, characterized in that the support element (50) has at least one first opening (58) of large cross section in a region of its base (52) in which it abuts against the valve element (42; 142), and has at least one second opening (60) of small cross section in a region of its base (52) outside the area of abutment against the valve element (42; 142).
  7. Fuel overflow valve according to one of the preceding claims, characterized in that the valve element (142) furthermore controls a throttled connection (180) between the inlet and an outlet (62), wherein, during the stroke of the valve element (142) in the opening direction, said valve element, at small opening strokes, initially opens the throttled connection (180) between the inlet and the outlet (62), and said valve element, at larger opening strokes, opens the connection (43) between the inlet and the relief region.
  8. Fuel overflow valve according to Claim 7, characterized in that the valve element (142) is of piston-like design, is guided sealingly in a longitudinal bore (41) of the valve housing (38) and has a blind bore (176) open towards its end facing away from the valve spring (48), which blind bore is connected permanently to the inlet, in that the connection (43) to the relief region leads away from the longitudinal bore (41) at the shell of the valve element (142), and said connection (43) is controlled by the open face end of the valve element (142), and in that the throttled connection comprises at least one opening (180) which leads away from the blind bore (176) close to the closed base (178), which faces towards the valve spring (48), of the valve element (142), which opening opens out at the shell of the valve element (142), the connection to the outlet (62) being controlled by the overlap of said opening with the longitudinal bore (41).
  9. Fuel injection device for an internal combustion engine, having a high-pressure pump (14) by means of which fuel at high pressure is delivered at least indirectly to at least one injector (120), having a delivery pump (10) through which fuel is delivered to the high-pressure pump (14), wherein the high-pressure pump (14) has at least one pump piston (26) which is driven in a stroke movement by a drive (20, 22) arranged in a drive region (19), wherein a low-pressure region is formed between the delivery pump (10) and the high-pressure pump (14), wherein the drive region (19) of the high-pressure pump (14) is connected to the low-pressure region, and wherein a fuel overflow valve (36) is provided in the low-pressure region, characterized in that the fuel overflow valve (36) is designed according to one of the preceding claims.
  10. Fuel injection device according to Claim 9, characterized in that a fuel metering device (16) is provided between the delivery pump (10) and the high-pressure pump (14), by means of which fuel metering device the fuel flow rate delivered by the high-pressure pump (14) can be variably adjusted, and in that the low-pressure region extends between the delivery pump (10) and the fuel metering device (16).
EP20080848181 2007-11-05 2008-09-18 Fuel overflow valve for a fuel injection system, and fuel injection system having a fuel overflow valve Not-in-force EP2207955B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE200710052665 DE102007052665A1 (en) 2007-11-05 2007-11-05 Fuel overflow valve for a fuel injector and fuel injector with fuel spill valve
PCT/EP2008/062443 WO2009059833A1 (en) 2007-11-05 2008-09-18 Fuel overflow valve for a fuel injection system, and fuel injection system having a fuel overflow valve

Publications (2)

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EP2207955A1 EP2207955A1 (en) 2010-07-21
EP2207955B1 true EP2207955B1 (en) 2014-11-12

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US (1) US8973557B2 (en)
EP (1) EP2207955B1 (en)
JP (1) JP5222368B2 (en)
KR (1) KR101481206B1 (en)
CN (1) CN101849096B (en)
DE (1) DE102007052665A1 (en)
WO (1) WO2009059833A1 (en)

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JP2011503413A (en) 2011-01-27
CN101849096B (en) 2013-06-19
KR101481206B1 (en) 2015-01-09
CN101849096A (en) 2010-09-29
JP5222368B2 (en) 2013-06-26
WO2009059833A1 (en) 2009-05-14
DE102007052665A1 (en) 2009-05-07
US8973557B2 (en) 2015-03-10
EP2207955A1 (en) 2010-07-21
KR20100072338A (en) 2010-06-30

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