EP2207955A1 - 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

Info

Publication number
EP2207955A1
EP2207955A1 EP08848181A EP08848181A EP2207955A1 EP 2207955 A1 EP2207955 A1 EP 2207955A1 EP 08848181 A EP08848181 A EP 08848181A EP 08848181 A EP08848181 A EP 08848181A EP 2207955 A1 EP2207955 A1 EP 2207955A1
Authority
EP
European Patent Office
Prior art keywords
valve
fuel
valve member
pressure
region
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP08848181A
Other languages
German (de)
French (fr)
Other versions
EP2207955B1 (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
Original Assignee
Robert Bosch GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP2207955A1 publication Critical patent/EP2207955A1/en
Application granted granted Critical
Publication of EP2207955B1 publication Critical patent/EP2207955B1/en
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

Links

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 overflow valve for a
  • Fuel injection device and a fuel injection device with fuel overflow valve according to the preamble of claim 1 and of claim 9.
  • Fuel injection device is known from DE 100 57 244 Al. 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. Through the valve member is the connection of an inlet of the lifting movement of the
  • 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. This creates pressure fluctuations in the drive area. Especially with a
  • High pressure pump with only one pump piston cause relatively high pressure fluctuations.
  • 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.
  • 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.
  • 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 training according to claim 7 or 8 allows without changes to the valve housing a two-stage design of the
  • FIG. 1 shows a fuel injection device in a simplified schematic representation
  • Figure 2 shows 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
  • Figure 3 the
  • FIG. 1 shows a fuel injection device for an internal combustion engine.
  • the fuel injection device has a feed pump 10, which draws fuel from a fuel tank 12 and the suction side of a
  • High pressure pump 14 promotes. 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 defines with its side facing away from the drive shaft 20 a pump working chamber 30.
  • the pump working chamber 30 has a connection with the inlet valve 32 opening into the pump working chamber 30
  • 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.
  • 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 may also be omitted, the high pressure pump 14 is then connected to the injectors 120 via hydraulic lines.
  • the pump piston 26 moves into the interior space 19 and sucks fuel from the feed from the feed pump 10 into the pump working space 30 via the open inlet valve 32.
  • 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 over the open
  • Kraftstoffüberströmventil 36 the funded by the pump 10, but not sucked by the high-pressure pump 14 amount of fuel 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.
  • valve housing 38 is slidably guided in a longitudinal bore 41 a piston-shaped valve member 42 slidably.
  • 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.
  • 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 area in the Kraftstoffüberströmventil 36.
  • the valve member 42 covers the openings 43, the inlet, so the low pressure region is separated from the discharge area and when the valve member 42, the openings 43 at least partially releases, so 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 can by means of an annular
  • Fastener 45 may be fixed to the valve housing 38, wherein the fastener 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 the 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 54 may be like that
  • Support member 50 may be cup-shaped, with its open end facing the valve member 42 and the valve spring 48 projects into the insert 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 member 50 can perform a maximum stroke towards the valve member 42, which is limited by abutment of the support member 50 at an annular shoulder 56 formed at the transition from the longitudinal bore 46 to the smaller longitudinal bore 41 in diameter.
  • In the bottom 52 of the support member 50 there is at least one large-section opening 58.
  • 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.
  • Relief area is connected.
  • 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.
  • valve member 42 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 is shown in Figure 2. 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.
  • valve member 42 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 shown in Figure 3.
  • the low-pressure region is separated from the relief region.
  • valve member 42 is displaced against the force of the valve spring 48 in the longitudinal bore 41 so that the openings 43 are controlled by the valve member 42 and the low-pressure region is connected to the discharge area, so that from the low-pressure fuel into the discharge area can flow out.
  • 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.
  • 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 of the valve member 42 and the support member 50 is also achieved, whereby the load of the valve spring 48 is reduced, since the opening stroke by the building up in the longitudinal bore 46
  • FIG. 5 shows the fuel overflow valve 36 according to a second exemplary embodiment, in which the latter opens in two stages and controls two connections of the low-pressure region.
  • valve member 142 is 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
  • the 142 is provided on this 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 dominated by the low pressure area
  • 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 area is thus separated from the relief 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 design of the Kraftstoffüberströmventils 36 is advantageous in a fuel injection device in which only a portion of the funded by the pump 10 fuel quantity 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 not sufficient to open the fuel spill valve 36, the entire amount of fuel delivered by the feed pump 10 will exceed the
  • Fuel metering 16 of the high-pressure pump 14 is supplied to the promotion.
  • 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 flowing fuel quantity is supplied to the interior 19 via a line 13 according to FIG.
  • the second stage also opens in the case of the fuel overflow valve 36 in that the valve member 142 releases the openings 43 and releases fuel from the low-pressure region via the

Abstract

The invention relates to a fuel overflow valve for a fuel injection system, particularly for limiting the pressure in a low-pressure region of the fuel injection system. The fuel overflow valve has a valve housing (38), in which a valve member (42) is disposed in a stroke-moving manner, the stroke movement of said valve member controlling a connection (43) of an inlet to the valve housing (38) to a release region. The valve member (42) is loaded by a valve spring (48) in the direction of a locking position in which the connection (43) of the inlet to the release region is interrupted, and is loaded by the pressure present in the inlet in the opening direction. The valve member (42) may carry out a further stroke in the locking direction beyond the locking position thereof, wherein the valve spring (48) does not act upon the valve member (42). Due to the increased stroke of the valve member (42), an improved balance of pressure and volume fluctuations is enabled in the low pressure region and the stroke of the valve spring (48), and thus the stress thereof, may be kept low.

Description

Beschreibung description
Titeltitle
Kraftstoffüberströmventil für eine Kraftstoffeinspritzeinrichtung undFuel overflow valve for a fuel injection device and
Kraftstoffeinspritzeinrichtung mit KraftstoffüberströmventilFuel injection device with fuel overflow valve
Stand der TechnikState of the art
Die Erfindung geht aus von einem Kraftstoffüberströmventil für eineThe invention is based on a fuel overflow valve for a
Kraftstoffeinspritzeinrichtung und einer Kraftstoffeinspritzeinrichtung mit Kraftstoffüberströmventil nach der Gattung des Anspruchs 1 bzw. des Anspruchs 9.Fuel injection device and a fuel injection device with fuel overflow valve according to the preamble of claim 1 and of claim 9.
Ein solches Kraftstoffüberströmventil und eine solcheSuch a fuel spill valve and such
Kraftstoffeinspritzeinrichtung ist durch die DE 100 57 244 Al 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 vomFuel injection device is known from DE 100 57 244 Al. 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. Through the valve member is the connection of an inlet of the lifting movement of the
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. Wenn der Druck im Niederdruckbereich den durch die Ventilfeder bestimmtenLow pressure range ago controlled 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 acted upon by the pressure prevailing in the inlet in the opening direction. When the pressure in the low pressure area determined by the valve spring
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 einerOpening pressure exceeds, so opens the fuel spill valve and fuel can flow from the inlet from the low pressure region via the drain in a discharge area, such as a return to the fuel tank. 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. Especially with a
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.High pressure pump with only one pump piston cause relatively high 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.
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. EntsprechendeThe 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. Appropriate
Vorteile ergeben sich für die Kraftstoffeinspritzeinrichtung gemäß Anspruch 9 deren Funktion durch die verringerten Druckschwankungen im Niederdruckbereich verbessert ist. 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 desAdvantages arise for the fuel injection device according to claim 9 whose function is improved by the reduced pressure fluctuations in the low pressure range. 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 training according to claim 7 or 8 allows without changes to the valve housing a two-stage design of the
Kraftstoffüberströmventils.Kraftstoffüberströmventils.
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 dasTwo embodiments of the invention are illustrated in the drawing and explained in more detail in the following description. 1 shows a fuel injection device in a simplified schematic representation, Figure 2 shows 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, Figure 3 the
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.Fuel overflow in the closed state with the valve member in a second position, Figure 4, the fuel spill valve in the open state, Figure 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 einerFIG. 1 shows a fuel injection device for an internal combustion engine. The fuel injection device has a feed pump 10, which draws fuel from a fuel tank 12 and the suction side of a
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.High pressure pump 14 promotes. 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 derThe 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
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 demHigh 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 defines with its side facing away from the drive shaft 20 a pump working chamber 30. The pump working chamber 30 has a connection with the inlet valve 32 opening into the pump working chamber 30
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. 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 geöffneteFuel supply from the feed pump 10 forth. 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 may also be omitted, the high pressure pump 14 is then connected to the injectors 120 via hydraulic lines. During its suction stroke, the pump piston 26 moves into the interior space 19 and sucks fuel from the feed from the feed pump 10 into the pump working space 30 via the open inlet valve 32. 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. 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 over the open
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.Kraftstoffüberströmventil 36, the funded by the pump 10, but not sucked by the high-pressure pump 14 amount of fuel 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 AbschnittThe fuel spill valve 36 according to a first embodiment will be explained in more detail below with reference to Figures 2 to 4. 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 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 des39 of the valve housing 38 is slidably guided in a longitudinal bore 41 a piston-shaped valve member 42 slidably. 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
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 ringförmigenValve member 42. The open end of the longitudinal bore 41 thus forms an inlet from the low pressure area in the Kraftstoffüberströmventil 36. When the valve member 42 covers the openings 43, the inlet, so the low pressure region is separated from the discharge area and when the valve member 42, the openings 43 at least partially releases, so 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 can by means of an annular
Befestigungselements 45 am Ventilgehäuse 38 fixiert sein, wobei das Befestigungselement beispielsweise durch eine Bördelung mit dem Ventilgehäuse 38 verbunden sein kann.Fastener 45 may be fixed to the valve housing 38, wherein the fastener 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 dasIn 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 the 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 54 may be like that
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.Support member 50 may be cup-shaped, with its open end facing the valve member 42 and the valve spring 48 projects into the insert 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 demThe 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 member 50 can perform a maximum stroke towards the valve member 42, which is limited by abutment of the support member 50 at an annular shoulder 56 formed at the transition from the longitudinal bore 46 to the smaller longitudinal bore 41 in diameter. In the bottom 52 of the support member 50 there is at least one large-section opening 58. 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, so this does not cover the opening 62, so that the longitudinal bore 46 with the
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, drosselndenRelief area is connected. 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
Durchflussquerschnitt mit dem Entlastungsbereich verbunden ist bzw. von diesem getrennt ist.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 demThe 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
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.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.The function of the fuel overflow valve 36 will be explained in more detail below.
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 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 is shown in Figure 2. 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 shown in Figure 3.
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 desIf 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 area, the opening pressure of the
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 geöffnetenAchieved fuel relief 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 controlled by the valve member 42 and the low-pressure region is connected to the discharge area, so that from the low-pressure fuel into the discharge area can flow out. In this open
Stellung ist das Ventilglied 42 in Figur 4 dargestellt.Position is the valve member 42 shown in Figure 4.
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 desIf 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
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.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 the insert 54 to the plant. 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 aufbauendenBy 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 of the valve member 42 and the support member 50 is also achieved, whereby the load of the valve spring 48 is reduced, since the opening stroke by the building up in the longitudinal bore 46
Kraftstoff druck gedämpft wird.Fuel pressure is damped.
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, dasFIG. 5 shows the fuel overflow valve 36 according to a second exemplary embodiment, in which the latter opens in two stages and controls two connections of the low-pressure region. The valve housing 38, the
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 VentilgliedsSupport 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 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 herrschenden142 is provided on this 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 dominated by the low pressure area
Druck beaufschlagt.Pressure applied.
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 area is thus separated from the relief 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 Kraftstoff menge 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 dieA use of the two-stage design of the Kraftstoffüberströmventils 36 is advantageous in a fuel injection device in which only a portion of the funded by the pump 10 fuel quantity 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 not sufficient to open the fuel spill valve 36, the entire amount of fuel delivered by the feed pump 10 will exceed the
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 denFuel metering 16 of the high-pressure pump 14 is supplied to the promotion. 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 flowing fuel quantity is supplied to the interior 19 via a line 13 according to FIG. As a result, first 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, the second stage also opens in the case of the fuel overflow valve 36 in that the valve member 142 releases the openings 43 and releases fuel from the low-pressure region via the
Rücklauf 11 in den Kraftstoffvorratsbehälter 12 abströmen kann. Return 11 can flow into the fuel tank 12.

Claims

Ansprüche claims
1. Kraftstoffüberströmventil für eine Kraftstoffeinspritzeinrichtung, insbesondere zur Druckbegrenzung in einem Niederdruckbereich der Kraftstoffeinspritzeinrichtung, mit einem Ventilgehäuse (38), mit einem im Ventilgehäuse (38) hubbeweglich angeordneten Ventilglied (42;142), durch das durch seine Hubbewegung eine Verbindung (43) eines Zulaufs zum1. A fuel overflow valve for a fuel injection device, in particular for limiting the pressure in a low-pressure region of the fuel injection device, with a valve housing (38), with a valve member (38) hubbeweglich arranged valve member (42, 142), through which by its lifting movement a connection (43) of a Inflow to
Ventilgehäuse (38) mit einem Entlastungsbereich gesteuert wird, wobei das Ventilglied (42;142) durch eine Ventilfeder (48) in Richtung einer Schließstellung beaufschlagt ist, in der die Verbindung (43) des Zulaufs mit dem Entlastungsbereich unterbrochen ist, und durch den im Zulauf herrschenden Druck in Öffnungsrichtung beaufschlagt ist, dadurch gekennzeichnet, dass dasValve housing (38) is controlled with a discharge region, wherein the valve member (42; 142) is acted upon by a valve spring (48) in the direction of a closed position in which the connection (43) of the inlet is interrupted with the discharge area, and by the Supply prevailing pressure is applied in the opening direction, characterized in that the
Ventilglied (42;142) in Schließrichtung über dessen Schließstellung hinaus einen weiteren Hub ausführen kann, bei dem die Ventilfeder (48) nicht auf das Ventilglied (42;142) wirkt.Valve member (42, 142) in the closing direction beyond its closed position can perform a further stroke, in which the valve spring (48) does not act on the valve member (42, 142).
2. Kraftstoffüberströmventil nach Anspruch 1, dadurch gekennzeichnet, dass die2. fuel spill valve according to claim 1, characterized in that the
Ventilfeder (48) über ein Stützelement (50) auf das Ventilglied (42;142) wirkt, das nicht mit dem Ventilglied (42;142) verbunden ist, und dass das Stützelement (50) in Schließrichtung im Bereich der Schließstellung des Ventilglieds (42;142) an einem Anschlag (56) im Ventilgehäuse (38) zur Anlage kommt.Valve spring (48) via a support member (50) acts on the valve member (42; 142), which is not connected to the valve member (42; 142), and that the support element (50) in the closing direction in the closed position of the valve member (42 142) abuts against a stop (56) in the valve housing (38).
3. Kraftstoffüberströmventil nach Anspruch 2, dadurch gekennzeichnet, dass das Stützelement (50) im Ventilgehäuse (38) verschiebbar geführt ist und im Ventilgehäuse (38) einen Raum (46) begrenzt, in dem die Ventilfeder (48) angeordnet ist, dass dieser Raum (46) eine Verbindung (62) zu einem Entlastungsbereich aufweist und dass diese Verbindung (62) durch das3. fuel spill valve according to claim 2, characterized in that the support element (50) in the valve housing (38) is displaceably guided and in the valve housing (38) defines a space (46) in which the valve spring (48) is arranged, that this space (46) has a connection (62) to a discharge region, and that said connection (62) through the
Stützelement (50) abhängig von dessen Hub gesteuert wird.Support member (50) is controlled depending on its stroke.
4. Kraftstoffüberströmventil nach Anspruch 3, dadurch gekennzeichnet, dass die Verbindung (62) des Raums (46) mit dem Entlastungsbereich bei am Anschlag (56) anliegendem Stützelement (50) geöffnet ist und bei Bewegung des Stützelements (50) in Richtung zur Öffnungsstellung des Ventilglieds (42;142) durch das Stützelement (50) geschlossen wird.4. fuel spill valve according to claim 3, characterized in that the connection (62) of the space (46) with the discharge area at the abutment (56) fitting support member (50) is opened and during movement of the Support member (50) towards the open position of the valve member (42, 142) by the support member (50) is closed.
5. Kraftstoffüberströmventil nach einem der Ansprüche 2 bis 4, dadurch gekennzeichnet, dass das Stützelement (50) topfförmig ausgebildet ist, dass die5. fuel spill valve according to one of claims 2 to 4, characterized in that the support element (50) is cup-shaped, that the
Ventilfeder (48) in das Stützelement (50) hineinragt und an dessen Boden (52) anliegt und dass das Stützelement (50) mit seinem Boden (52) am Ventilglied (42;142) zur Anlage kommt.Valve spring (48) protrudes into the support element (50) and abuts against the bottom (52) and that the support element (50) with its bottom (52) on the valve member (42, 142) comes into contact.
6. Kraftstoffüberströmventil nach Anspruch 5, dadurch gekennzeichnet, dass das6. fuel spill valve according to claim 5, characterized in that the
Stützelement (50) in einem Bereich seines Bodens (52), in dem dieses am Ventilglied (42;142) zur Anlage kommt, wenigstens eine erste Öffnung (58) mit großem Querschnitt aufweist und in einem Bereich seines Bodens (52) außerhalb der Anlage am Ventilglied (42;142) wenigstens eine zweite Öffnung (60) mit kleinem Querschnitt aufweist.Support member (50) in a region of its bottom (52) in which this comes to rest on the valve member (42; 142), at least one first opening (58) having a large cross-section and in a region of its bottom (52) outside the plant has at least one second opening (60) with a small cross section on the valve member (42; 142).
7. Kraftstoffüberströmventil nach einem der vorstehenden Ansprüche, dadurch gekennzeichnet, dass durch das Ventilglied (142) außerdem eine gedrosselte Verbindung (180) des Zulaufs mit einem Ablauf (62) gesteuert wird, wobei beim Hub des Ventilglieds (142) in Öffnungsrichtung durch dieses bei geringem7. fuel spill valve according to one of the preceding claims, characterized in that by the valve member (142) also a throttled connection (180) of the inlet with a drain (62) is controlled, wherein the stroke of the valve member (142) in the opening direction by this at low
Öffnungshub zunächst die gedrosselte Verbindung (180) des Zulaufs mit dem Ablauf (62) geöffnet wird und bei größerem Öffnungshub die Verbindung (43) des Zulaufs mit dem Entlastungsbereich geöffnet wird.Opening stroke initially the throttled connection (180) of the inlet with the outlet (62) is opened and the connection (43) of the inlet is opened with the discharge area at a larger opening stroke.
8. Kraftstoffüberströmventil nach Anspruch 7, dadurch gekennzeichnet, dass das8. fuel spill valve according to claim 7, characterized in that the
Ventilglied (142) kolbenförmig ausgebildet ist, in einer Längsbohrung (41) des Ventilgehäuses (38) dicht geführt ist und eine zu dessen der Ventilfeder (48) abgewandtem Ende hin offene Sackbohrung (176) aufweist, die ständig mit dem Zulauf verbunden ist, dass die Verbindung (43) zum Entlastungsbereich von der Längsbohrung (41) am Mantel des Ventilglieds (142) abführt und dieseValve member (142) is piston-shaped, in a longitudinal bore (41) of the valve housing (38) is tightly guided and facing away from the valve spring (48) facing end blind bore (176) which is permanently connected to the inlet, that the connection (43) discharges to the discharge area of the longitudinal bore (41) on the jacket of the valve member (142) and this
Verbindung (43) durch das offene Stirnende des Ventilglieds (142) gesteuert wird, dass die gedrosselte Verbindung wenigstens eine von der Sackbohrung (176) nahe dem der Ventilfeder (48) zugewandten geschlossenen Boden (178) des Ventilglieds (142) abführende und am Mantel des Ventilglieds (142) mündende Öffnung (180) umfasst, durch deren Überdeckung mit der Längsbohrung (41) die Verbindung mit dem Ablauf (62) gesteuert wird.Connection (43) is controlled by the open end of the valve member (142) that the throttled connection at least one of the blind bore (176) near the valve spring (48) facing closed bottom (178) of the valve member (142) and laxative on the jacket the valve member (142) opening Opening (180), by the overlap with the longitudinal bore (41), the connection with the drain (62) is controlled.
9. Kraftstoffeinspritzeinrichtung für eine Brennkraftmaschine mit einer Hochdruckpumpe (14), durch die Kraftstoff unter Hochdruck zumindest mittelbar zu wenigstens einem Injektor (120) gefördert wird, mit einer Förderpumpe (10), durch die Kraftstoff zur Hochdruckpumpe (14) gefördert wird, wobei die Hochdruckpumpe (14) wenigstens einen Pumpenkolben (26) aufweist, der durch einen in einem Antriebsbereich (19) angeordneten Antrieb (20,22) in einer Hubbewegung angetrieben wird, wobei ein Niederdruckbereich zwischen der9. Fuel injection device for an internal combustion engine with a high-pressure pump (14), is conveyed by the fuel under high pressure at least indirectly to at least one injector (120), with a feed pump (10) through which fuel to the high-pressure pump (14) is conveyed, wherein the High-pressure pump (14) at least one pump piston (26) which is driven by a in a drive region (19) arranged drive (20,22) in a lifting movement, wherein a low-pressure region between the
Förderpumpe (10) und der Hochdruckpumpe (14) gebildet ist, wobei der Antriebsbereich (19) der Hochdruckpumpe (14) mit dem Niederdruckbereich verbunden ist und wobei im Niederdruckbereich ein Kraftstoffüberströmventil (36) vorgesehen ist, dadurch gekennzeichnet, dass das Kraftstoffüberströmventil (36) nach einem der vorstehenden Ansprüche ausgebildet ist.Feed pump (10) and the high pressure pump (14) is formed, wherein the drive region (19) of the high pressure pump (14) is connected to the low pressure region and wherein in the low pressure region, a fuel overflow valve (36) is provided, characterized in that the fuel overflow valve (36) is designed according to one of the preceding claims.
10. Kraftstoffeinspritzeinrichtung nach Anspruch 9, dadurch gekennzeichnet, dass zwischen der Förderpumpe (10) und der Hochdruckpumpe (14) eine Kraftstoffzumesseinrichtung (16) vorgesehen ist, durch die die von der Hochdruckpumpe (14) geförderte Kraftstoffmenge variabel einstellbar ist und dass sich der Niederdruckbereich zwischen der Förderpumpe (10) und der Kraftstoffzumesseinrichtung (16) erstreckt. 10. Fuel injection device according to claim 9, characterized in that between the feed pump (10) and the high-pressure pump (14) a fuel metering device (16) is provided, by which by the high-pressure pump (14) funded fuel quantity is variably adjustable and that the low-pressure region between the feed 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)

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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

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

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JP (1) JP5222368B2 (en)
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CN101849096A (en) 2010-09-29
EP2207955B1 (en) 2014-11-12
US20100258092A1 (en) 2010-10-14
JP5222368B2 (en) 2013-06-26
US8973557B2 (en) 2015-03-10
KR20100072338A (en) 2010-06-30
DE102007052665A1 (en) 2009-05-07
WO2009059833A1 (en) 2009-05-14
KR101481206B1 (en) 2015-01-09
CN101849096B (en) 2013-06-19
JP2011503413A (en) 2011-01-27

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