WO2005124153A1 - High-pressure pump for a fuel injection device of an internal combustion engine - Google Patents

High-pressure pump for a fuel injection device of an internal combustion engine Download PDF

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Publication number
WO2005124153A1
WO2005124153A1 PCT/EP2005/051738 EP2005051738W WO2005124153A1 WO 2005124153 A1 WO2005124153 A1 WO 2005124153A1 EP 2005051738 W EP2005051738 W EP 2005051738W WO 2005124153 A1 WO2005124153 A1 WO 2005124153A1
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WO
WIPO (PCT)
Prior art keywords
pump
valve member
valve
pump piston
suction
Prior art date
Application number
PCT/EP2005/051738
Other languages
German (de)
French (fr)
Inventor
Michael Mennicken
Andreas Kellner
Falko Bredow
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
Priority to JP2007515913A priority Critical patent/JP4589382B2/en
Priority to US11/597,917 priority patent/US20080069712A1/en
Publication of WO2005124153A1 publication Critical patent/WO2005124153A1/en

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/10—Valves; Arrangement of valves
    • F04B53/12—Valves; Arrangement of valves arranged in or on pistons
    • F04B53/125—Reciprocating valves
    • F04B53/129—Poppet valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/10—Valves; Arrangement of valves
    • F04B53/102—Disc valves
    • F04B53/1022—Disc valves having means for guiding the closure member axially

Definitions

  • the invention relates to a high-pressure pump for a fuel injection device of an internal combustion engine according to the preamble of claim 1.
  • Such a high pressure pump is known from DE 198 48 035 AI.
  • This high-pressure pump has at least one pump element, with a pump piston which is driven in a lifting movement and which is displaceably guided in a cylinder bore and delimits a pump working space in the latter.
  • the pump workspace can be filled with fuel via a suction valve.
  • the suction valve has a valve member which opens into the pump work space and which interacts with a valve seat.
  • the pump piston In its end region facing the suction valve, the pump piston has a blind bore into which the valve member of the suction valve is immersed and in which a closing spring acting on the valve member is arranged, which is supported on the one hand on the pump piston and on the other hand on the valve member.
  • the valve member has a shaft surrounded by the closing spring, with which the valve member is displaceably guided in the closing spring.
  • the outside diameter of the closing spring is only slightly smaller than the diameter of the blind hole in the pump piston, so that the closing spring is guided in the blind hole of the pump piston.
  • the high pressure pump according to the invention with the features according to claim 1 has the advantage that the valve member of the suction valve is precisely guided in the pump piston, whereby the function of the suction valve and thus the high pressure pump is improved.
  • the embodiment according to claim 3 enables a large guide length of the valve member in the blind bore with a space-saving arrangement of the closing spring.
  • the embodiment according to claim 4 enables the spring chamber to be filled and emptied during the movement of the valve member, the opening and / or closing movement of the at least one opening in the valve member being able to be influenced in a targeted manner.
  • the design according to claim 5 enables a very precise guidance of the valve member with respect to the valve seat, since the cylinder bore for the pump piston and the valve seat on one
  • Manufacturing device can be manufactured and can therefore be aligned very precisely to each other.
  • FIG. 1 shows a high-pressure pump for a fuel injection device of an internal combustion engine in a longitudinal section
  • FIG. 2 shows a section of the high-pressure pump designated by II in FIG Suction valve in the open state
  • Figure 3 shows the detail II with the suction valve in the closed state.
  • the high-pressure pump has a pump housing 10 in which a drive shaft 12 which can be driven in rotation by the internal combustion engine is rotatably mounted, for example via two bearing points spaced apart from one another in the axial direction.
  • the drive shaft 12 has at least one section eccentric to its axis of rotation 13 or a cam 16, wherein the cam 16 can also be designed as a multiple cam.
  • the high-pressure pump has at least one or more pump elements 18 arranged in the pump housing 10, each with a pump piston 20, which is driven by the eccentric section or the cam 16 of the drive shaft 12 in a stroke movement in at least approximately radial direction to the axis of rotation 13 of the drive shaft 12.
  • the pump piston 20 is guided in a tightly displaceable manner in a cylinder bore 22 formed in the pump housing 10 and bounded with its end facing away from the drive shaft 12
  • the pump work space 24 has a connection to a via a fuel feed channel 26 running in the pump housing 10
  • Fuel supply for example a feed pump 14.
  • Pump working chamber 24 has a suction valve 28 opening into pump working chamber 24.
  • the pump work chamber 24 also has a connection via a fuel drain channel 30 running in the pump housing 10 an outlet, which is connected to a high-pressure accumulator 110, for example.
  • One or preferably a plurality of injectors 120 which are arranged on the cylinders of the internal combustion engine, are connected to the high-pressure accumulator 110 and are used to inject fuel into the cylinders of the internal combustion engine.
  • An outlet valve 32 opening out of the pump work chamber 24 is arranged at the mouth of the fuel drain channel 30 into the pump work chamber 24.
  • a support element in the form of a tappet 34 can be arranged between the pump piston 20 and the eccentric section or cam 16 of the drive shaft 12, via which the pump piston 20 is supported at least indirectly on the cam 16.
  • the pump piston 20 is coupled to the tappet 34 in a manner not shown in the direction of its longitudinal axis 21.
  • the tappet 34 can be supported directly on the eccentric section or cam 16.
  • the plunger 34 is slidably mounted in a bore 36 in the pump housing 10 and takes on the implementation of the
  • the suction valve 28 is described in more detail below with reference to FIGS. 2 and 3.
  • the cylinder bore 22 of the pump housing 10 is adjoined by an at least approximately coaxial bore 40 in the pump housing 10 toward the outside of the pump housing 10 facing away from the drive shaft 12, which bore 40 has a smaller diameter than the cylinder bore 22.
  • an annular shoulder is formed, on which a valve seat 42 is formed, the for example, is at least approximately frustoconical.
  • the bore 40 opens into the fuel inlet anal 26.
  • the suction valve 28 has a valve member 44 which is arranged in the pump work chamber 24 and which is connected to the valve seat 42 for controlling the connection of the
  • the valve member 44 is piston-shaped and cup-shaped, the closed end of the valve member 44 facing the valve seat 42.
  • the valve member 44 has, for example, an at least approximately frustoconical sealing surface 45 with which it cooperates with the valve seat 42.
  • the pump piston 20 has in its end region facing the valve seat 42 an at least approximately coaxial to its longitudinal axis 21 blind bore 46, into which the valve member 44 of the suction valve 28 dips with its open end.
  • the valve member 44 is guided over a large part of its longitudinal extent in the blind bore 46 in the pump piston 20 with little radial play.
  • a spring chamber 48 is delimited in the blind bore 46 by the pump piston 20 and the valve member 44, in which a closing spring 50 of the suction valve 28, which is supported on the one hand at the bottom of the blind bore 46 on the pump piston 20 and on the other hand on the valve member 44, is arranged.
  • the closing spring 50 is designed as a helical compression spring and projects into the valve member 44 and is supported in this on an annular shoulder formed by a reduction in the internal cross section of the valve member 44. The valve member 44 is pressed toward the valve seat 42 by the closing spring 50.
  • At least one opening 52 is provided in the valve member 44, through which the spring chamber 48 is connected to the pump working chamber 24.
  • the at least one opening 52 enables the filling and emptying of the Spring chamber 48 during a movement of valve member 44 relative to pump piston 20, the dimensioning of at least one opening 52 being able to influence the volume flow when filling and emptying spring chamber 48.
  • the suction valve 28 is shown in the open state during the suction stroke of the pump piston 20.
  • fuel flows from the fuel inlet channel 26 into the pump work chamber 24.
  • the suction stroke of the pump piston 20 it moves away from the valve seat 42 of the suction valve 28 together with the closing spring 50 supported thereon, so that the pretension of the closing spring 50 is reduced.
  • the suction valve 28 therefore opens even at a small pressure difference between the fuel inlet channel 26 and the pump work chamber 24.
  • valve member 44 is guided in the blind bore 46 with high accuracy coaxially to the valve seat 42, since the cylinder bore 22, in which the pump piston 20 is guided, and the valve seat 42 in same pump housing 10 are formed. As a result, the valve member 44 securely comes into contact with the valve seat 42 when it closes and thus closes reliably.
  • the outlet valve 38 is closed.
  • fuel is compressed by the pump piston 20 in the pump work chamber 24, so that the suction valve 28 closes as a result of the increased pressure in the pump work chamber 24 while fuel is under high pressure is conveyed through the fuel outlet channel 30 to the high-pressure accumulator 110 with the outlet valve 32 open.
  • the suction valve 28 is shown in the closed state during the delivery stroke of the pump piston 20.
  • valve seat 42 is formed on a different part of the pump housing 10 than the cylinder bore 22 in which the pump piston 20 is guided.
  • the part of the pump housing 10 on which the valve seat 42 is formed is aligned very precisely with respect to the part of the pump housing 10 in which the cylinder bore 22 is formed in order to achieve the required coaxial alignment of the valve seat 42 with respect to FIG To reach cylinder bore 22.

Abstract

The invention relates to a high-pressure pump comprising at least one pump element (18), and a pump piston (20) which is driven in a reciprocating motion, is displaceably guided in a cylinder borehole (22) of a pump housing element (10), and defines a pump working chamber (24) in the cylinder borehole (22). Said pump working chamber can be filled with fuel by means of a suction valve (28) during the suction stroke of the pump piston (20). The suction valve (28) comprises a valve member (44) which opens in the pump working chamber (24) and co-operates with a valve seat (42). The pump piston (20) comprises a blind borehole (46) in the end region thereof facing the suction valve (28), into which the valve member (44) of the suction valve (28) is inserted, and in which a closing spring (50) acting on the valve member (44) is arranged, said closing spring being supported on the pump piston (20) on one end and on the valve member (44) on the other end. The valve member (44) is guided in the blind borehole (46) of the pump piston (20) in a displaceable manner.

Description

Hochdruckpumpe für eine Kraftstoffeinspritzeinrichtung einer BrennkraftmaschineHigh pressure pump for a fuel injector of an internal combustion engine
Stand der TechnikState of the art
Die Erfindung geht aus von einer Hochdruckpumpe für eine Kraftstoffeinspritzeinrichtung einer Brennkraftmaschine nach der Gattung des Anspruchs 1.The invention relates to a high-pressure pump for a fuel injection device of an internal combustion engine according to the preamble of claim 1.
Eine solche Hochdruckpumpe ist durch die DE 198 48 035 AI bekannt. Diese Hochdruckpumpe weist wenigstens ein Pumpenelement auf, mit einem in einer Hubbewegung angetriebenen Pumpenkolben, der in einer Zylinderbohrung verschiebbar geführt ist und in dieser einen Pumpenarbeitsraum begrenzt. Der Pumpenarbeitsraum ist über ein Saugventil mit Kraftstoff befüUbar. Das Saugventil weist ein in den Pumpenarbeitsraum öffnendes Ventilglied auf, das mit einem Ventilsitz zusammenwirkt. Der Pumpenkolben weist in seinem dem Saugventil zugewandten Endbereich eine Sackbohrung auf, in die das Ventilglied des Saugventils eintaucht und in der eine auf das Ventilglied wirkende Schließfeder angeordnet ist, die sich einerseits am Pumpenkolben und andererseits am Ventilglied abstützt. Das Ventilglied weist einen von der Schließfeder umgebenen Schaft auf, mit dem das Ventilglied in der Schließfeder verschiebbar geführt ist. Der Außendurchmesser der Schließfeder ist nur wenig kleiner als der Durchmesser der Sackbohrung im Pumpenkolben, so dass die Schließfeder in der Sackbohrung des Pumpenkolbens geführt ist. Bei dieser Ausführung ergibt sich somit nur eine ungenaue Führung des Ventilglieds, was für die Funktion des Saugventils nachteilig ist. Dies kann wiederum die Befüllung des Pumpenarbeitsraums beeinträchtigen und damit insgesamt die Funktion der Hochdruckpumpe .Such a high pressure pump is known from DE 198 48 035 AI. This high-pressure pump has at least one pump element, with a pump piston which is driven in a lifting movement and which is displaceably guided in a cylinder bore and delimits a pump working space in the latter. The pump workspace can be filled with fuel via a suction valve. The suction valve has a valve member which opens into the pump work space and which interacts with a valve seat. In its end region facing the suction valve, the pump piston has a blind bore into which the valve member of the suction valve is immersed and in which a closing spring acting on the valve member is arranged, which is supported on the one hand on the pump piston and on the other hand on the valve member. The valve member has a shaft surrounded by the closing spring, with which the valve member is displaceably guided in the closing spring. The outside diameter of the closing spring is only slightly smaller than the diameter of the blind hole in the pump piston, so that the closing spring is guided in the blind hole of the pump piston. In this embodiment, there is therefore only an imprecise guidance of the valve member, which is disadvantageous for the function of the suction valve. This can in turn fill the Impair the pump workspace and thus the overall function of the high pressure pump.
Vorteile der ErfindungAdvantages of the invention
Die erfindungsgemäße Hochdruckpumpe mit den Merkmalen gemäß Anspruch 1 hat demgegenüber den Vorteil, dass das Ventilglied des Saugventils präzise im Pumpenkolben geführt ist, wodurch die Funktion des Saugventils und damit der Hochdruckpumpe verbessert ist.The high pressure pump according to the invention with the features according to claim 1 has the advantage that the valve member of the suction valve is precisely guided in the pump piston, whereby the function of the suction valve and thus the high pressure pump is improved.
In den abhängigen Ansprüchen sind vorteilhafte Ausgestaltungen und Weiterbildungen der erfindungsgemäßen Hochdruckpumpe angegeben. Die Ausführung gemäß Anspruch 3 ermöglicht eine große Führungslänge des Ventilglieds in der Sackbohrung bei zugleich platzsparender Anordnung der Schließfeder. Die Ausbildung gemäß Anspruch 4 ermöglicht eine Befüllung und Entleerung des Federraums bei der Bewegung des Ventilglieds, wobei durch geeignete Dimensionierung der wenigstens einen Öffnung im Ventilglied dessen Öffnungs- und/oder Schließbewegung gezielt beeinflusst werden kann. Die Ausbildung gemäß Anspruch 5 ermöglicht eine sehr genaue Führung des Ventilglieds in Bezug auf den Ventilsitz, da die Zylinderbohrung für den Pumpenkolben und der Ventilsitz auf einerAdvantageous refinements and developments of the high-pressure pump according to the invention are specified in the dependent claims. The embodiment according to claim 3 enables a large guide length of the valve member in the blind bore with a space-saving arrangement of the closing spring. The embodiment according to claim 4 enables the spring chamber to be filled and emptied during the movement of the valve member, the opening and / or closing movement of the at least one opening in the valve member being able to be influenced in a targeted manner. The design according to claim 5 enables a very precise guidance of the valve member with respect to the valve seat, since the cylinder bore for the pump piston and the valve seat on one
Fertigungseinrichtung hergestellt werden können und daher sehr genau zueinander ausgerichtet werden können.Manufacturing device can be manufactured and can therefore be aligned very precisely to each other.
Zeichnungdrawing
Ein Ausführungsbeispiel der Erfindung ist in der Zeichnung dargestellt und in der nachfolgenden Beschreibung näher erläutert. Es zeigen Figur 1 eine Hochdruckpumpe für eine Kraftstoffeinspritzeinrichtung einer Brennkraftmaschine in einem Längsschnitt, Figur 2 einen in Figur 1 mit II bezeichneten Ausschnitt der Hochdruckpumpe mit einem Saugventil in geöffnetem Zustand und Figur 3 den Ausschnitt II mit dem Saugventil in geschlossenem Zustand.An embodiment of the invention is shown in the drawing and explained in more detail in the following description. 1 shows a high-pressure pump for a fuel injection device of an internal combustion engine in a longitudinal section, FIG. 2 shows a section of the high-pressure pump designated by II in FIG Suction valve in the open state and Figure 3 shows the detail II with the suction valve in the closed state.
Beschreibung des AusführungsbeispielsDescription of the embodiment
In den Figuren 1 bis 3 ist eine Hochdruckpumpe für eine Kraftstoffeinspritzeinrichtung einer Brennkraftmaschine dargestellt. Die Hochdruckpumpe weist ein Pumpengehäuse 10 auf, in dem eine durch die Brennkraftmaschine rotierend antreibbare Antriebswelle 12 drehbar gelagert ist, beispielsweise über zwei in axialer Richtung zueinander beabstandete Lagerstellen. In einem zwischen den beiden Lagerstellen liegenden Bereich weist die Antriebswelle 12 wenigstens einen zu ihrer Drehachse 13 exzentrischen Abschnitt oder einen Nocken 16 auf, wobei der Nocken 16 auch als Mehrfachnocken ausgebildet sein kann. Die Hochdruckpumpe weist wenigstens ein oder mehrere im Pumpengehäuse 10 angeordnete Pumpenelemente 18 mit jeweils einem Pumpenkolben 20 auf, der durch den exzentrischen Abschnitt oder den Nocken 16 der Antriebswelle 12 in einer Hubbewegung in zumindest annähernd radialer Richtung zur Drehachse 13 der Antriebswelle 12 angetrieben wird.1 to 3 show a high-pressure pump for a fuel injection device of an internal combustion engine. The high-pressure pump has a pump housing 10 in which a drive shaft 12 which can be driven in rotation by the internal combustion engine is rotatably mounted, for example via two bearing points spaced apart from one another in the axial direction. In an area lying between the two bearing points, the drive shaft 12 has at least one section eccentric to its axis of rotation 13 or a cam 16, wherein the cam 16 can also be designed as a multiple cam. The high-pressure pump has at least one or more pump elements 18 arranged in the pump housing 10, each with a pump piston 20, which is driven by the eccentric section or the cam 16 of the drive shaft 12 in a stroke movement in at least approximately radial direction to the axis of rotation 13 of the drive shaft 12.
Der Pumpenkolben 20 ist in einer im Pumpengehäuse 10 ausgebildeten Zylinderbohrung 22 dicht verschiebbar geführt und begrenzt mit seiner der Antriebswelle 12 abgewandtenThe pump piston 20 is guided in a tightly displaceable manner in a cylinder bore 22 formed in the pump housing 10 and bounded with its end facing away from the drive shaft 12
Stirnseite in der Zylinderbohrung 22 einenFront in the cylinder bore 22 a
Pumpenarbeitsraum 24. Der Pumpenarbeitsraum 24 weist über einen im Pumpengehäuse 10 verlaufenden Kraftstoffzulaufkanal 26 eine Verbindung mit einemPump work space 24. The pump work space 24 has a connection to a via a fuel feed channel 26 running in the pump housing 10
Kraftstoffzulauf, beispielsweise einer Förderpumpe 14 auf.Fuel supply, for example a feed pump 14.
An der Mündung des Kraftstoffzulaufkanals 26 in denAt the mouth of the fuel inlet channel 26 in the
Pumpenarbeitsraum 24 ist ein in den Pumpenarbeitsraum 24 öffnendes Saugventil 28 angeordnet. Der Pumpenarbeitsraum 24 weist ausserdem über einen im Pumpengehäuse 10 verlaufenden Kraftstoffablaufkanal 30 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. An der Mündung des Kraftstoffablaufkanals 30 in den Pumpenarbeitsraum 24 ist ein aus dem Pumpenarbeitsraum 24 öffnendes Auslassventil 32 angeordnet .Pump working chamber 24 has a suction valve 28 opening into pump working chamber 24. The pump work chamber 24 also has a connection via a fuel drain channel 30 running in the pump housing 10 an outlet, which is connected to a high-pressure accumulator 110, for example. One or preferably a plurality of injectors 120, which are arranged on the cylinders of the internal combustion engine, are connected to the high-pressure accumulator 110 and are used to inject fuel into the cylinders of the internal combustion engine. An outlet valve 32 opening out of the pump work chamber 24 is arranged at the mouth of the fuel drain channel 30 into the pump work chamber 24.
Zwischen dem Pumpenkolben 20 und dem exzentrischen Abschnitt oder Nocken 16 der Antriebswelle 12 kann ein Stützelement in Form eines Stößels 34 angeordnet sein, über den sich der Pumpenkolben 20 zumindest mittelbar am Nocken 16 abstützt. Der Pumpenkolben 20 ist dabei mit dem Stößel 34 in nicht näher dargestellter Weise in Richtung seiner Längsachse 21 gekoppelt. Der Stößel 34 kann sich direkt am exzentrischen Abschnitt oder Nocken 16 abstützen. Der Stößel 34 ist im Pumpengehäuse 10 in einer Bohrung 36 verschiebbar gelagert und nimmt bei der Umsetzung derA support element in the form of a tappet 34 can be arranged between the pump piston 20 and the eccentric section or cam 16 of the drive shaft 12, via which the pump piston 20 is supported at least indirectly on the cam 16. The pump piston 20 is coupled to the tappet 34 in a manner not shown in the direction of its longitudinal axis 21. The tappet 34 can be supported directly on the eccentric section or cam 16. The plunger 34 is slidably mounted in a bore 36 in the pump housing 10 and takes on the implementation of the
Drehbewegung der Antriebswelle 12 in die Hubbewegung des Pumpenkolbens 20 auftretende Querkräfte auf, so dass diese nicht auf den Pumpenkolben 20 wirken. Am Stößel 34 greift eine vorgespannte Rückstellfeder 38 an, durch die der Stößel 34 und der mit diesem verbundene Pumpenkolben 20 zum Nocken 16 hin gedrückt werden.Rotary movement of the drive shaft 12 in the stroke movement of the pump piston 20 occurring transverse forces so that they do not act on the pump piston 20. A preloaded return spring 38 acts on the plunger 34, by means of which the plunger 34 and the pump piston 20 connected to it are pressed toward the cam 16.
Nachfolgend wird anhand der Figuren 2 und 3 das Saugventil 28 näher beschrieben. An die Zylinderbohrung 22 des Pumpengehäuses 10 schließt sich zu der der Antriebswelle 12 abgewandten Außenseite des Pumpengehäuses 10 hin eine zumindest annähernd zur Zylinderbohrung 22 koaxiale Bohrung 40 im Pumpengehäuse 10 an, die einen kleineren Durchmesser aufweist als die Zylinderbohrung 22. Am Übergang von der Zylinderbohrung 22 zur Bohrung 40 ist eine Ringschulter gebildet, an der ein Ventilsitz 42 ausgebildet ist, der beispielsweise zumindest annähernd kegelstumpfförmig ist. Die Bohrung 40 mündet in den Kraftstoffzulauf anal 26. Das Saugventil 28 weist ein Ventilglied 44 auf, das im Pumpenarbeitsraum 24 angeordnet ist und das mit dem Ventilsitz 42 zur Steuerung der Verbindung desThe suction valve 28 is described in more detail below with reference to FIGS. 2 and 3. The cylinder bore 22 of the pump housing 10 is adjoined by an at least approximately coaxial bore 40 in the pump housing 10 toward the outside of the pump housing 10 facing away from the drive shaft 12, which bore 40 has a smaller diameter than the cylinder bore 22. At the transition from the cylinder bore 22 to the bore 40, an annular shoulder is formed, on which a valve seat 42 is formed, the for example, is at least approximately frustoconical. The bore 40 opens into the fuel inlet anal 26. The suction valve 28 has a valve member 44 which is arranged in the pump work chamber 24 and which is connected to the valve seat 42 for controlling the connection of the
Pumpenarbei sraums 24 mit dem Kraftstoffzulaufkanal 26 zusammenwirkt. Das Ventilglied 44 ist kolbenförmig und topfförmig ausgebildet, wobei das geschlossene Ende des Ventilglieds 44 dem Ventilsitz 42 zugewandt ist. Das Ventilglied 44 weist eine beispielsweise zumindest annähernd kegelstumpfförmige Dichtfläche 45 auf, mit der es mit dem Ventilsitz 42 zusammenwirkt.Pumpenarbei sraums 24 cooperates with the fuel inlet channel 26. The valve member 44 is piston-shaped and cup-shaped, the closed end of the valve member 44 facing the valve seat 42. The valve member 44 has, for example, an at least approximately frustoconical sealing surface 45 with which it cooperates with the valve seat 42.
Der Pumpenkolben 20 weist in seinem dem Ventilsitz 42 zugewandten Endbereich eine zumindest annähernd koaxial zu seiner Längsachse 21 verlaufende Sackbohrung 46 auf, in die das Ventilglied 44 des Saugventils 28 mit seinem offenen Ende eintaucht. Das Ventilglied 44 ist dabei über einen großen Teil seiner Längserstreckung in der Sackbohrung 46 im Pumpenkolben 20 mit geringem radialem Spiel verschiebbar geführt. Durch den Pumpenkolben 20 und das Ventilglied 44 ist in der Sackbohrung 46 ein Federraum 48 begrenzt, in dem eine sich einerseits am Grund der Sackbohrung 46 am Pumpenkolben 20 und andererseits am Ventilglied 44 abstützende Schließfeder 50 des Saugventils 28 angeordnet ist. Die Schließfeder 50 ist als Schraubendruckfeder ausgeführt und ragt in das Ventilglied 44 hinein und stützt sich in diesem an einer durch eine Verringerung des Innenquerschnitts des Ventilglieds 44 gebildeten Ringschulter ab. Durch die Schließfeder 50 wird das Ventilglied 44 zum Ventilsitz 42 hin gedrückt.The pump piston 20 has in its end region facing the valve seat 42 an at least approximately coaxial to its longitudinal axis 21 blind bore 46, into which the valve member 44 of the suction valve 28 dips with its open end. The valve member 44 is guided over a large part of its longitudinal extent in the blind bore 46 in the pump piston 20 with little radial play. A spring chamber 48 is delimited in the blind bore 46 by the pump piston 20 and the valve member 44, in which a closing spring 50 of the suction valve 28, which is supported on the one hand at the bottom of the blind bore 46 on the pump piston 20 and on the other hand on the valve member 44, is arranged. The closing spring 50 is designed as a helical compression spring and projects into the valve member 44 and is supported in this on an annular shoulder formed by a reduction in the internal cross section of the valve member 44. The valve member 44 is pressed toward the valve seat 42 by the closing spring 50.
Im Ventilglied 44 ist wenigstens eine Öffnung 52 vorgesehen, durch die der Federraum 48 mit dem Pumpenarbeitsraum 24 verbunden ist. Die wenigstens eine Öffnung 52 ermöglicht eine Befüllung und Entleerung des Federraums 48 bei einer Bewegung des Ventilglieds 44 relativ zum Pumpenkolben 20, wobei durch die Dimensionierung der wenigstens einen Öffnung 52 der Volumenstrom bei der Befüllung und Entleerung des Federraums 48 beeinflusst werden kann.At least one opening 52 is provided in the valve member 44, through which the spring chamber 48 is connected to the pump working chamber 24. The at least one opening 52 enables the filling and emptying of the Spring chamber 48 during a movement of valve member 44 relative to pump piston 20, the dimensioning of at least one opening 52 being able to influence the volume flow when filling and emptying spring chamber 48.
Beim Saughub des Pumpenkolbens 20, bei dem sich dieser zusammen mit dem Stößel 34 bewirkt durch die Rückstellfeder 38 radial nach innen bewegt, herrscht im Pumpenarbeitsraum 24 ein geringer Druck, so dass das Saugventil 28 öffnet, indem dessen Ventilglied 44 mit seiner Dichtfläche 45 vom Ventilsitz 42 abhebt, da durch den im Kraftstoffzulauf 26 herrschenden Druck eine größere Kraft in Öffnungsrichtung erzeugt wird als die Summe der Kraft der Schließfeder 50 und der durch den im Pumpenarbeitsraum 24 herrschendenDuring the suction stroke of the pump piston 20, during which it moves together with the tappet 34, caused by the return spring 38 to move radially inward, there is a low pressure in the pump working chamber 24, so that the suction valve 28 opens by the valve member 44 with its sealing surface 45 from the valve seat 42 lifts off, since a greater force is generated in the opening direction by the pressure prevailing in the fuel inlet 26 than the sum of the force of the closing spring 50 and by the force prevailing in the pump working chamber 24
Druck erzeugten Kraft. In Figur 2 ist das Saugventil 28 in geöffnetem Zustand während des Saughubs des Pumpenkolbens 20 dargestellt. Aus dem Kraftstoffzulaufkanal 26 strömt bei geöffnetem Saugventil 28 Kraftstoff in den Pumpenarbeitsraum 24. Beim Saughub des Pumpenkolbens 20 bewegt sich dieser zusammen mit der sich an diesem abstützenden Schließfeder 50 vom Ventilsitz 42 des Saugventils 28 weg, so dass die Vorspannung der Schließfeder 50 verringert wird. Das Saugventil 28 öffnet daher bereits bei einer geringen Druckdifferenz zwischen dem Kraftstoffzulaufkanal 26 und dem Pumpenarbeitsraum 24. Durch geeignete Dimensionierung der wenigstens einen Öffnung 52 im Ventilglied 44 kann erreicht werden, dass sich der Federraum 48 nur langsam mit Kraftstoff befüllen kann, wodurch das Ventilglied 44 beim Saughub desPressure generated force. In Figure 2, the suction valve 28 is shown in the open state during the suction stroke of the pump piston 20. When the suction valve 28 is open, fuel flows from the fuel inlet channel 26 into the pump work chamber 24. During the suction stroke of the pump piston 20, it moves away from the valve seat 42 of the suction valve 28 together with the closing spring 50 supported thereon, so that the pretension of the closing spring 50 is reduced. The suction valve 28 therefore opens even at a small pressure difference between the fuel inlet channel 26 and the pump work chamber 24. By suitable dimensioning of the at least one opening 52 in the valve member 44, it can be achieved that the spring chamber 48 can only fill with fuel slowly, as a result of which the valve member 44 during the suction stroke of the
Pumpenkolbens 20 mit dem Pumpenkolben 20 mitbewegt wird, wodurch ein schnelles und weites Öffnen des Saugventils 28 erreicht wird. Das Ventilglied 44 ist in der Sackbohrung 46 mit hoher Genauigkeit koaxial zum Ventilsitz 42 verschiebbar geführt, da die Zylinderbohrung 22, in der der Pumpenkolben 20 geführt ist, und der Ventilsitz 42 im selben Pumpengehäuse 10 ausgebildet sind. Hierdurch kommt das Ventilglied 44 beim Schließen mit seiner Dichtfläche 45 sicher am Ventilsitz 42 zur Anlage und schließt somit zuverlässig.Pump piston 20 is moved with the pump piston 20, whereby a quick and wide opening of the suction valve 28 is achieved. The valve member 44 is guided in the blind bore 46 with high accuracy coaxially to the valve seat 42, since the cylinder bore 22, in which the pump piston 20 is guided, and the valve seat 42 in same pump housing 10 are formed. As a result, the valve member 44 securely comes into contact with the valve seat 42 when it closes and thus closes reliably.
Bei geringem Druck im Pumpenarbeitsraum 30 während dessen Befüllung ist das Auslassventil 38 geschlossen. Beim Förderhub des Pumpenkolbens 20, bei dem sich dieser zusammen mit dem Stößel 34 radial nach aussen bewegt, wird durch den Pumpenkolben 20 Kraftstoff im Pumpenarbeitsraum 24 verdichtet, so dass das Saugventil 28 infolge des erhöhten Drucks im Pumpenarbeitsraum 24 schließt, während unter Hochdruck stehender Kraftstoff durch den Kraftstoffablaufkanal 30 bei geöffnetem Auslassventil 32 zum Hochdruckspeicher 110 gefördert wird. In Figur 3 ist das Saugventil 28 in geschlossenem Zustand während des Förderhubs des Pumpenkolbens 20 dargestellt.If the pressure in the pump work chamber 30 is low, the outlet valve 38 is closed. During the delivery stroke of the pump piston 20, during which it moves radially outwards together with the tappet 34, fuel is compressed by the pump piston 20 in the pump work chamber 24, so that the suction valve 28 closes as a result of the increased pressure in the pump work chamber 24 while fuel is under high pressure is conveyed through the fuel outlet channel 30 to the high-pressure accumulator 110 with the outlet valve 32 open. In Figure 3, the suction valve 28 is shown in the closed state during the delivery stroke of the pump piston 20.
Alternativ zur vorstehend erläuterten Ausführung kann auch vorgesehen sein, dass der Ventilsitz 42 an einem anderen Teil des Pumpengehäuses 10 ausgebildet ist als die Zylinderbohrung 22, in der der Pumpenkolben 20 geführt ist. Hierbei muss jedoch sichergestellt werden, dass der Teil des Pumpengehäuses 10, an dem der Ventilsitz 42 ausgebildet ist, sehr genau bezüglich des Teils des Pumpengehäuses 10 ausgerichtet wird, in dem die Zylinderbohrung 22 ausgebildet ist, um die erforderliche koaxiale Ausrichtung des Ventilsitzes 42 bezüglich der Zylinderbohrung 22 zu erreichen. As an alternative to the embodiment explained above, it can also be provided that the valve seat 42 is formed on a different part of the pump housing 10 than the cylinder bore 22 in which the pump piston 20 is guided. Here, however, it must be ensured that the part of the pump housing 10 on which the valve seat 42 is formed is aligned very precisely with respect to the part of the pump housing 10 in which the cylinder bore 22 is formed in order to achieve the required coaxial alignment of the valve seat 42 with respect to FIG To reach cylinder bore 22.

Claims

Ansprüche Expectations
1. Hochdruckpumpe für eine Kraftstoffeinspritzeinrichtung einer Brennkraftmaschine, mit wenigstens einem Pumpenelement (18), das einen in einer Hubbewegung angetriebenen, in einer Zylinderbohrung (22) eines Pumpengehäuseteils (10) verschiebbar geführten Pumpenkolben (20) aufweist, der in der Zylinderbohrung (22) einen Pumpenarbeitsraum (24) begrenzt, der über ein Saugventil (28) beim Saughub des Pumpenkolbens (20) mit Kraftstoff befüUbar ist, wobei das Saugventil (28) ein in den Pumpenarbeitsraum (24) öffnendes, mit einem Ventilsitz (42) zusammenwirkendes Ventilglied (44) aufweist, wobei der Pumpenkolben (20) in seinem dem Saugventil (28) zugewandten Endbereich eine Sackbohrung (46) aufweist, in die das1. High-pressure pump for a fuel injection device of an internal combustion engine, with at least one pump element (18) which has a pump piston (20) which is driven in a lifting movement and is displaceably guided in a cylinder bore (22) of a pump housing part (10) and which is in the cylinder bore (22) delimits a pump work space (24) which can be supplied with fuel via a suction valve (28) during the suction stroke of the pump piston (20), the suction valve (28) opening into the pump work space (24) and interacting with a valve seat (42) valve member ( 44), the pump piston (20) having in its end region facing the suction valve (28) a blind bore (46) into which the
Ventilglied (44) des Saugventils (28) eintaucht und in der eine auf das Ventilglied (44) wirkende Schließfeder (50) angeordnet ist, die sich einerseits am Pumpenkolben (20) und andererseits am Ventilglied (44) abstützt, dadurch gekennzeichnet, dass das Ventilglied (44) in derImmersed valve member (44) of the suction valve (28) and in which a closing spring (50) acting on the valve member (44) is arranged, which is supported on the one hand on the pump piston (20) and on the other hand on the valve member (44), characterized in that Valve member (44) in the
Sackbohrung (46) des Pumpenkolbens (20) verschiebbar geführt ist.Blind bore (46) of the pump piston (20) is slidably guided.
2. Hochdruckpumpe nach Anspruch 1, dadurch gekennzeichnet, dass die Schließfeder (50) in der Sackbohrung (46) in einem durch den Pumpenkolben (20) und das Ventilglied (44) begrenzten Federraum (48) angeordnet ist.2. High-pressure pump according to claim 1, characterized in that the closing spring (50) is arranged in the blind bore (46) in a spring chamber (48) delimited by the pump piston (20) and the valve member (44).
3. Hochdruckpumpe nach Anspruch 2, dadurch gekennzeichnet, dass das Ventilglied (44) topfförmig ausgebildet ist und mit seinem offenen Ende in die Sackbohrung (46) im Pumpenkolben (20) ragt, dass die Schließfeder (50) in das Ventilglied (44) hineinragt und dass das Ventilglied (44) mit seinem aus der Sackbohrung (46) ragenden geschlossenen Ende (45) mit dem Ventilsitz (42) zusammenwirkt.3. High-pressure pump according to claim 2, characterized in that the valve member (44) is cup-shaped and with its open end in the blind bore (46) in Pump piston (20) protrudes that the closing spring (50) projects into the valve member (44) and that the valve member (44) cooperates with the valve seat (42) with its closed end (45) protruding from the blind bore (46).
4. Hochdruckpumpe nach Anspruch 3, dadurch gekennzeichnet, dass das Ventilglied (44) wenigstens eine Öffnung (52) aufweist, durch die der Federraum (48) mit dem Pumpenarbeitsraum (24) verbunden ist.4. High-pressure pump according to claim 3, characterized in that the valve member (44) has at least one opening (52) through which the spring chamber (48) is connected to the pump working chamber (24).
5. Hochdruckpumpe nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, dass der Ventilsitz (42) im selben Pumpengehäuseteil (10) ausgebildet ist wie die Zylinderbohrung (22), in der der Pumpenkolben (20) geführt ist. 5. High-pressure pump according to one of claims 1 to 4, characterized in that the valve seat (42) is formed in the same pump housing part (10) as the cylinder bore (22) in which the pump piston (20) is guided.
PCT/EP2005/051738 2004-06-16 2005-04-20 High-pressure pump for a fuel injection device of an internal combustion engine WO2005124153A1 (en)

Priority Applications (2)

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JP2007515913A JP4589382B2 (en) 2004-06-16 2005-04-20 High pressure pump for fuel injection device of internal combustion engine
US11/597,917 US20080069712A1 (en) 2004-06-16 2005-04-20 High-Pressure Pump for a Fuel Injection System of an Internal Combustion Engine

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DE102004028999A DE102004028999A1 (en) 2004-06-16 2004-06-16 High-pressure pump for a fuel injection device of an internal combustion engine
DE102004028999.9 2004-06-16

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JP (1) JP4589382B2 (en)
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US20080069712A1 (en) 2008-03-20
JP2008502838A (en) 2008-01-31
DE102004028999A1 (en) 2006-01-05
JP4589382B2 (en) 2010-12-01

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