WO2005015017A1 - High pressure pump for a fuel injection device of a combustion engine - Google Patents

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

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Publication number
WO2005015017A1
WO2005015017A1 PCT/DE2004/001304 DE2004001304W WO2005015017A1 WO 2005015017 A1 WO2005015017 A1 WO 2005015017A1 DE 2004001304 W DE2004001304 W DE 2004001304W WO 2005015017 A1 WO2005015017 A1 WO 2005015017A1
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WO
WIPO (PCT)
Prior art keywords
pump
pressure
fuel
low
pressure accumulator
Prior art date
Application number
PCT/DE2004/001304
Other languages
German (de)
French (fr)
Inventor
Armin Merz
Andreas Dutt
Gerhard Meier
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 WO2005015017A1 publication Critical patent/WO2005015017A1/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
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/0404—Details or component parts
    • 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
    • F04B25/00—Multi-stage pumps
    • F04B25/005—Multi-stage pumps with two cylinders

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 29 548 AI.
  • This high-pressure pump has a housing in which a drive shaft and at least one pump element are arranged.
  • the at least one pump element has a pump piston driven by the drive shaft via a tappet in a lifting movement.
  • the pump piston delimits a pump working space which is filled with fuel during the suction stroke of the pump piston and from which fuel is displaced during the delivery stroke of the pump piston.
  • the plunger is guided in a bore in the housing. There is a separate one for the high pressure pump
  • Delivery pump required, through which fuel is drawn from a fuel tank and is delivered under increased pressure into the pump work space of the at least one pump element. This requires a great deal of effort and installation space.
  • the high pressure pump according to the invention with the features according to claim 1 has the advantage that for this no separate feed pump is required, since the tappet of the at least one pump element and the reservoir cause fuel suction from a fuel reservoir and the filling of the pump work space of the at least one pump element.
  • the embodiment according to claim 4 enables a need-adjusted variable suction quantity and thus also the delivery quantity of the high-pressure pump.
  • the embodiment according to claim 5 enables lubrication of the drive area of the high-pressure pump in a simple manner.
  • FIG. 1 shows a high-pressure pump in a cross section along line I-I in FIG. 2 and FIG. 2
  • High-pressure pump in a longitudinal section along line II-II in Figure 1.
  • the high-pressure pump delivers fuel under high pressure, for example into a high-pressure accumulator 8, from which fuel is taken for injection at the internal combustion engine.
  • the high-pressure pump has a housing 10 in which a drive shaft 12 is rotatably mounted about an axis 13. In the housing 10 there are at least one, possibly several, for example two pump elements 14 arranged, which are driven by the drive shaft 12.
  • the pump elements 14 can, for example, as shown in FIG. 2, be rotated relative to one another by approximately 90 ° about the axis of rotation 13 of the drive shaft 12.
  • the drive shaft 12 has a cam 16, which can be a single or multiple cam.
  • the pump elements 14 each have a pump piston 20 which is displaceably and sealingly guided in a cylinder bore 22 of the housing 10 or a separate cylinder head 11, which runs at least approximately radially to the axis of rotation 13 of the drive shaft 12.
  • the pump piston 20 of each pump element 14 is supported with its piston foot 21 via a tappet 24 on the cam 16.
  • the tappet 24 is held in contact with the cam 16 by a spring 26, which is supported on the one hand on the housing 10 or on the cylinder head 11 and on the other hand on the tappet 24.
  • a pump working chamber 28 is delimited by the respective pump piston 20, which can be connected to a fuel supply by an inlet valve 30 opening into the pump working chamber 28, in which there is low pressure and which will be described in more detail below.
  • the pump working chamber 28 can also be connected to the high-pressure accumulator 8 by an outlet valve 32 opening towards the high-pressure accumulator 8.
  • the intake valves 30 and the exhaust valves 32 can be arranged in the housing 10 or in the cylinder head 11.
  • the pump pistons 20 move radially inward, they perform a suction stroke, the inlet valve 30 being open, so that fuel flows into the pump working chamber 28 while the outlet valve 32 is closed.
  • the pump pistons 20 move radially outward, they execute a delivery stroke, the inlet valve 30 being closed and the fuel compressed by the pump pistons 20 reaches the high-pressure accumulator 8 under high pressure through the opened outlet valve 32.
  • the plungers 24 are each slidably guided in a bore 40 in the housing 10.
  • the plunger 24 delimits a working space 42 in the bores 40 on the side of the plunger 24 facing away from the drive shaft 12.
  • the working space 42 is delimited on the one hand by the tappet 24 and on the other hand by the cylinder head 11.
  • the cylinder head 11 can each have a cylindrical extension 44 which projects into the working space 42 and in which the cylinder bore 22 is formed, in which the pump piston 20 is guided and the pump working space 28 is limited.
  • the pump piston 20 has a smaller diameter than the plunger 24 and the bore 40.
  • the outer diameter of the shoulder 44 of the cylinder head 11 is also smaller than the diameter of the bore 40, so that an annular space remains between the shoulder 44 and the bore 40.
  • a cylindrical roller 25 which is arranged with its longitudinal axis at least approximately parallel to the axis of rotation 13 of the drive shaft 12, is rotatably arranged, via which the tappet 24 rolls on the cam 16.
  • the drive shaft 12 has a section which is formed eccentrically to its axis of rotation 13 and on which a section corresponding to the number of pump pistons 20 with flats provided ring is rotatably mounted on the
  • the housing 10 and the plunger 24 can be made of light weight and low strength material are manufactured, for example from aluminum, since these are not subjected to high pressure.
  • the cylinder heads 11 are made of material that has high strength, for example steel.
  • the working space 42 has a connection 46 to a fuel reservoir 48, in which a check valve 50 opening towards the working space 42 is arranged.
  • the work space 42 also has a connection 52 with a low-pressure accumulator 54, in which a
  • Low pressure accumulator 54 opening check valve 56 is arranged.
  • the low-pressure accumulator 54 is preferably integrated in the housing 10 of the high-pressure pump and can be designed, for example, as a diaphragm accumulator or as a bladder accumulator or have a spring-loaded piston or can be designed as a combination of these types.
  • the pressure prevailing in the low-pressure accumulator 54 is set by a pressure control valve 58.
  • the pressure control valve 58 can be a spring-loaded valve which, when a predetermined pressure in the low-pressure accumulator 54 is exceeded, releases a connection 60 of the low-pressure accumulator 54 with a relief region, for example a return into the fuel reservoir 48.
  • the pressure control valve 58 can also be an electrically operated valve that is controlled by an electronic control device 62.
  • the pressure in the low-pressure accumulator 54 can be set variably, for example depending on the operating parameters of the internal combustion engine.
  • the pressure control valve 58 can be integrated into the housing 10 of the high-pressure pump or can be attached to it.
  • the pump work spaces 28 of the pump elements 14 are connected to the low-pressure accumulator 54, which is the
  • Fuel supply for this forms In the connection of the Pump workrooms 28 with the low-pressure accumulator 54 are preferably arranged a fuel metering device 64, through which a variable flow cross-section can be set.
  • the fuel metering device 64 has a proportional valve, by means of which the
  • Flow cross section can be changed continuously, and an actuator, for example in the form of an electromagnet.
  • the fuel metering device 64 is controlled by the electronic control device 62.
  • the fuel metering device 64 can be integrated into the housing 10 of the high-pressure pump or can be attached to it.
  • the low-pressure accumulator 54 has a connection 66 to the drive area of the high-pressure pump, in which the drive shaft 12 is arranged.
  • the drive shaft 12 is mounted radially and axially in a cavity of the housing 10 via several, for example two bearing points 12a, 12b.
  • the bearing points 12a, 12b can be designed, for example, as plain bearings.
  • a throttle point 68 is arranged in the connection 66 in order to limit the amount of fuel that flows out of the low-pressure accumulator 54 into the drive area.
  • the function of the high pressure pump is explained below.
  • the drive shaft 12 is driven mechanically by the internal combustion engine, for example.
  • the rotation of the drive shaft 12 is converted via the cam 16 into a lifting movement of the tappets 24 and the pump pistons 20.
  • the plunger 24 draws fuel from the fuel reservoir 48 into the enlarging working spaces 42 via the connections 46 with the check valves 50 open.
  • Low pressure accumulator 54 displaced.
  • the check valves 50 to the fuel tank 48 are closed.
  • a pressure between approximately 2 and 10 bar is generated by the fuel delivered by the tappets 24. Too much fuel delivered by the tappets 24 is diverted by the pressure control valve 58 into the return 60 to the fuel tank 48.
  • the spring 26 is supported by the pressure prevailing in the working space 42 and the tappet 24 with its roller 25 is pressed against the cam 16. The spring 26 can therefore optionally be made smaller, which makes it light and requires less space.
  • Flow cross section is set so large that by the pump piston 20 is only sucked in such a large amount of fuel and is displaced under high pressure into the high-pressure accumulator 8, which is required in order to maintain a predetermined pressure in the high-pressure accumulator 8. If a large amount of fuel has to be delivered in order to maintain the predetermined pressure in the high-pressure accumulator 8, the fuel metering device 64 is controlled by the control device 62 in such a way that it releases a large flow cross section. If only a small amount of fuel needs to be delivered in order to maintain the predetermined pressure in the high-pressure accumulator 8, the fuel metering device 64 is controlled by the control device 62 in such a way that it only releases a small flow cross-section or, if appropriate, that
  • the flow cross-section is completely closed, so that no fuel is conveyed into the high-pressure accumulator 8 by the high-pressure pump.
  • the pressure level in the low-pressure accumulator 54 can be variably set by means of an electrically controlled pressure control valve 58. For example, provision can be made for a higher pressure level in the low-pressure accumulator 54 to be set with increasing speed of the internal combustion engine and thus the high-pressure pump, in order to ensure adequate filling of the pump work spaces 28 despite the shorter time available for filling the pump work spaces 28.

Abstract

The high pressure pump comprises a housing (10), inside of which a drive shaft (12) and at least one pump element (14) are placed. The at least one pump element (14) has a pump piston (20), which is driven in a reciprocating motion by the drive shaft (12) via a tappet (24) and which delimits a pump working space (28). This pump working space is filled with fuel during the suction stroke of the pump piston (20), and fuel is discharged from the space during a delivery stroke of the pump piston (20). The tappet (24) is tightly guided in a displaceable manner inside a bore (40) in the housing (10) and delimits a working space (42) inside the bore (40). Fuel is suctioned into this working space by the tappet (24) during the suction stroke of the pump piston (20), and fuel is discharged from the working space into a low pressure accumulator (54) during the delivery stroke of the pump piston (20). An elevated pressure is maintained inside the low pressure accumulator (54) and, from the low pressure accumulator, the pump working space (28) is filled with fuel during the suction stroke of the pump piston (20). This renders a separate delivery pump for the high pressure pump unnecessary.

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 29 548 AI bekannt. Diese Hochdruckpumpe weist ein Gehäuse auf, in dem eine Antriebswelle und wenigstens ein Pumpenelement angeordnet sind. Das wenigstens einen Pumpenelement weist einen durch die Antriebswelle über einen Stößel in einer Hubbewegung angetriebenen Pumpenkolben auf. Der Pumpenkolben begrenzt einen Pumpenarbeitsraum, der beim Saughub des Pumpenkolbens mit Kraftstoff befüllt wird und aus dem beim Förderhub des Pumpenkolbens Kraftstoff verdrängt wird. Der Stößel ist in einer Bohrung des Gehäuses verschiebbar geführt. Für die Hochdruckpumpe ist eine separateSuch a high pressure pump is known from DE 198 29 548 AI. This high-pressure pump has a housing in which a drive shaft and at least one pump element are arranged. The at least one pump element has a pump piston driven by the drive shaft via a tappet in a lifting movement. The pump piston delimits a pump working space which is filled with fuel during the suction stroke of the pump piston and from which fuel is displaced during the delivery stroke of the pump piston. The plunger is guided in a bore in the housing. There is a separate one for the high pressure pump
Förderpumpe erforderlich, durch die Kraftstoff aus einem Kraftstoffvorratsbehälter angesaugt wird und unter erhöhtem Druck in den Pumpenarbeitsraum des wenigstens einen Pumpenelements gefördert wird. Dies erfordert einen großen Aufwand und Bauraum.Delivery pump required, through which fuel is drawn from a fuel tank and is delivered under increased pressure into the pump work space of the at least one pump element. This requires a great deal of effort and installation space.
Vorteile der ErfindungAdvantages of the invention
Die erfindungsgemäße Hochdruckpumpe mit den Merkmalen gemäß Anspruch 1 hat demgegenüber den Vorteil, dass für diese keine separate Förderpumpe erforderlich ist, da durch den Stößel des wenigstens einen Pumpenelements und den Speicher eine Kraftstof nsaugung aus einem Kraftstoffvorratsbehälter und die Befüllung des Pumpenarbeitsraums des wenigstens einen Pumpenelements erfolgt.The high pressure pump according to the invention with the features according to claim 1 has the advantage that for this no separate feed pump is required, since the tappet of the at least one pump element and the reservoir cause fuel suction from a fuel reservoir and the filling of the pump work space of the at least one pump element.
In den abhängigen Ansprüchen sind vorteilhafte Ausgestaltungen und Weiterbildungen der erfindungsgemäßen Hochdruckpumpe angegeben. Die Ausbildung gemäß Anspruch 4 ermöglicht eine bedarfsangepasste variable Ansaugmenge und damit auch Fördermenge der Hochdruckpumpe. Die Ausbildung gemäß Anspruch 5 ermöglicht auf einfache Weise eine Schmierung des Antriebsbereichs der Hochdruckpumpe.Advantageous refinements and developments of the high-pressure pump according to the invention are specified in the dependent claims. The embodiment according to claim 4 enables a need-adjusted variable suction quantity and thus also the delivery quantity of the high-pressure pump. The embodiment according to claim 5 enables lubrication of the drive area of the high-pressure pump in a simple manner.
Zeichnungdrawing
Ein Ausführungsbeispiel der Erfindung ist in der Zeichnung dargestellt und in der nachfolgenden Beschreibung näher erläutert. Es zeigen Figur 1 eine Hochdruckpumpe in einem Querschnitt entlang Linie I-I in Figur 2 und Figur 2 dieAn embodiment of the invention is shown in the drawing and explained in more detail in the following description. FIG. 1 shows a high-pressure pump in a cross section along line I-I in FIG. 2 and FIG
Hochdruckpumpe in einem Längsschnitt entlang Linie II-II in Figur 1.High-pressure pump in a longitudinal section along line II-II in Figure 1.
Beschreibung des AusführungsbeispielsDescription of the embodiment
In den Figuren 1 und 2 ist eine Hochdruckpumpe für eine Kraftstoffeinspritzeinrichtung einer Brennkraftmaschine beispielsweise eines Kraftfahrzeugs dargestellt, die als Radialkolbenpumpe ausgebildet ist. Durch die Hochdruckpumpe wird dabei Kraftstoff unter Hochdruck gefördert, beispielsweise in einen Hochdruckspeicher 8, aus dem Kraftstoff zur Einspritzung an der Brennkraftmaschine entnommen wird. Die Hochdruckpumpe weist ein Gehäuse 10 auf, in dem eine Antriebswelle 12 um eine Achse 13 drehbar gelagert ist. Im Gehäuse 10 sind wenigstens ein, gegebenenfalls mehrere, beispielsweise zwei Pumpenelemente 14 angeordnet, die durch die Antriebswelle 12 angetrieben werden. Die Pumpenelemente 14 können beispielsweise wie in Figur 2 dargestellt um etwa 90° um die Drehachse 13 der Antriebswelle 12 zueinander verdreht angeordnet sein. Die Antriebswelle 12 weist einen Nocken 16 auf, der ein Einfachoder Mehrfachnocken sein kann. Die Pumpenelemente 14 weisen jeweils einen Pumpenkolben 20 auf, der in einer zumindest annähernd radial zur Drehachse 13 der Antriebswelle 12 verlaufenden Zylinderbohrung 22 des Gehäuses 10 oder eines separaten Zylinderkopfes 11 verschiebbar dicht geführt ist. Der Pumpenkolben 20 jedes Pumpenelements 14 stützt sich mit seinem Kolbenfuß 21 über einen Stößel 24 am Nocken 16 ab. Der Stößel 24 wird dabei durch eine Feder 26, die sich einerseits am Gehäuse 10 oder am Zylinderkopf 11 und andererseits am Stößel 24 abstützt, in Anlage am Nocken 16 gehalten.1 and 2 show a high-pressure pump for a fuel injection device of an internal combustion engine, for example a motor vehicle, which is designed as a radial piston pump. The high-pressure pump delivers fuel under high pressure, for example into a high-pressure accumulator 8, from which fuel is taken for injection at the internal combustion engine. The high-pressure pump has a housing 10 in which a drive shaft 12 is rotatably mounted about an axis 13. In the housing 10 there are at least one, possibly several, for example two pump elements 14 arranged, which are driven by the drive shaft 12. The pump elements 14 can, for example, as shown in FIG. 2, be rotated relative to one another by approximately 90 ° about the axis of rotation 13 of the drive shaft 12. The drive shaft 12 has a cam 16, which can be a single or multiple cam. The pump elements 14 each have a pump piston 20 which is displaceably and sealingly guided in a cylinder bore 22 of the housing 10 or a separate cylinder head 11, which runs at least approximately radially to the axis of rotation 13 of the drive shaft 12. The pump piston 20 of each pump element 14 is supported with its piston foot 21 via a tappet 24 on the cam 16. The tappet 24 is held in contact with the cam 16 by a spring 26, which is supported on the one hand on the housing 10 or on the cylinder head 11 and on the other hand on the tappet 24.
Durch den jeweiligen Pumpenkolben 20 wird ein Pumpenarbeitsraum 28 begrenzt, der durch ein in den Pumpenarbeitsraum 28 öffnendes Einlassventil 30 mit einer KraftstoffZuführung verbindbar ist, in der Niederdruck herrscht und die nachfolgend noch näher beschrieben wird. Der Pumpenarbeitsraum 28 ist außerdem durch ein zum Hochdruckspeicher 8 hin öffnendes Auslassventil 32 mit dem Hochdruckspeicher 8 verbindbar. Die Einlassventile 30 und die Auslassventile 32 können im Gehäuse 10 oder im Zylinderkopf 11 angeordnet sein. Bei der Rotation der Antriebswelle 12 werden die Pumpenkolben 20 über den Nocken 16 der Antriebswelle 12 und die Stößel 24 in einer Hubbewegung angetrieben. Wenn die Pumpenkolben 20 sich radial nach innen bewegen, so führen diese einen Saughub aus, wobei das Einlassventil 30 geöffnet ist, so dass Kraftstoff in den Pumpenarbeitsraum 28 einströmt, während das Auslassventil 32 geschlossen ist. Wenn die Pumpenkolben 20 sich radial nach außen bewegen, so führen diese einen Förderhub aus, wobei das Einlassventil 30 geschlossen ist und der von den Pumpenkolben 20 verdichtete Kraftstoff durch das geöffnete Auslassventil 32 unter hohem Druck in den Hochdruckspeicher 8 gelangt.A pump working chamber 28 is delimited by the respective pump piston 20, which can be connected to a fuel supply by an inlet valve 30 opening into the pump working chamber 28, in which there is low pressure and which will be described in more detail below. The pump working chamber 28 can also be connected to the high-pressure accumulator 8 by an outlet valve 32 opening towards the high-pressure accumulator 8. The intake valves 30 and the exhaust valves 32 can be arranged in the housing 10 or in the cylinder head 11. When the drive shaft 12 rotates, the pump pistons 20 are driven in one stroke movement via the cams 16 of the drive shaft 12 and the tappets 24. When the pump pistons 20 move radially inward, they perform a suction stroke, the inlet valve 30 being open, so that fuel flows into the pump working chamber 28 while the outlet valve 32 is closed. When the pump pistons 20 move radially outward, they execute a delivery stroke, the inlet valve 30 being closed and the fuel compressed by the pump pistons 20 reaches the high-pressure accumulator 8 under high pressure through the opened outlet valve 32.
Die Stößel 24 sind jeweils in einer Bohrung 40 des Gehäuses 10 verschiebbar dicht geführt. Durch die Stößel 24 wird in den Bohrungen 40 auf der der Antriebswelle 12 abgewandten Seite der Stößel 24 jeweils ein Arbeitsraum 42 begrenzt. Der Arbeitsraum 42 wird beim dargestellten Ausführungsbeispiel jeweils einerseits durch den Stößel 24 und andererseits durch den Zylinderkopf 11 begrenzt. Der Zylinderkopf 11 kann jeweils einen zylindrischen Ansatz 44 aufweisen, der in den Arbeitsraum 42 ragt und in dem die Zylinderbohrung 22 ausgebildet ist, in der der Pumpenkolben 20 geführt ist und der Pumpenarbeitsraum 28 begrenzt ist. Der Pumpenkolben 20 weist gegenüber dem Stößel 24 und der Bohrung 40 einen kleineren Durchmesser auf. Der Aussendurchmesser des Ansatzes 44 des Zylinderkopfs 11 ist ebenfalls kleiner als der Durchmesser der Bohrung 40, so dass zwischen dem Ansatz 44 und der Bohrung 40 ein Ringraum verbleibt. Im Stößel 24 ist eine mit ihrer Längsachse zumindest annähernd parallel zur Drehachse 13 der Antriebswelle 12 angeordnete zylindrische Rolle 25 drehbar angeordnet, über die der Stößel 24 am Nocken 16 abrollt. Anstelle des hier beschriebenen Antriebs der Pumpenkolben 20 über den Nocken 16, die Stößel 24 sowie die Rollen 25 kann auch vorgesehen sein, dass die Antriebswelle 12 einen exzentrisch zu ihrer Drehachse 13 ausgebildeten Abschnitt aufweist, auf dem ein entsprechend der Anzahl der Pumpenkolben 20 mit Abflachungen versehener Ring drehbar gelagert ist, an dem dieThe plungers 24 are each slidably guided in a bore 40 in the housing 10. The plunger 24 delimits a working space 42 in the bores 40 on the side of the plunger 24 facing away from the drive shaft 12. In the illustrated embodiment, the working space 42 is delimited on the one hand by the tappet 24 and on the other hand by the cylinder head 11. The cylinder head 11 can each have a cylindrical extension 44 which projects into the working space 42 and in which the cylinder bore 22 is formed, in which the pump piston 20 is guided and the pump working space 28 is limited. The pump piston 20 has a smaller diameter than the plunger 24 and the bore 40. The outer diameter of the shoulder 44 of the cylinder head 11 is also smaller than the diameter of the bore 40, so that an annular space remains between the shoulder 44 and the bore 40. In the tappet 24, a cylindrical roller 25, which is arranged with its longitudinal axis at least approximately parallel to the axis of rotation 13 of the drive shaft 12, is rotatably arranged, via which the tappet 24 rolls on the cam 16. Instead of the drive of the pump pistons 20 described here via the cams 16, the tappets 24 and the rollers 25, it can also be provided that the drive shaft 12 has a section which is formed eccentrically to its axis of rotation 13 and on which a section corresponding to the number of pump pistons 20 with flats provided ring is rotatably mounted on the
Pumpenkolben 20 direkt oder über Stößel anliegen. Der Ring dreht sich dabei nicht mit der Antriebswelle 12 mit und über den extentrischen Abschnitt der Antriebswelle 12 wird deren Drehbewegung in eine Hubbewegung der Pumpenkolben 20 umgewandelt. Das Gehäuse 10 und die Stößel 24 können aus Material mit geringem Gewicht und geringer Festigkeit gefertigt werden, beispielsweise aus Aluminium, da diese nicht von Hochdruck beaufschlagt sind. Die Zylinderköpfe 11 sind aus Material gefertigt, das eine hohe Festigkeit aufweist, beispielsweise aus Stahl.Apply pump piston 20 directly or via tappet. The ring does not rotate with the drive shaft 12 and, via the eccentric section of the drive shaft 12, its rotational movement is converted into a stroke movement of the pump pistons 20. The housing 10 and the plunger 24 can be made of light weight and low strength material are manufactured, for example from aluminum, since these are not subjected to high pressure. The cylinder heads 11 are made of material that has high strength, for example steel.
Der Arbeitsraum 42 weist eine Verbindung 46 mit einem Kraftstoffvorratsbehälter 48 auf, in der ein zum Arbeitsraum 42 hin öffnendes Rückschlagventil 50 angeordnet ist. Der Arbeitsraum 42 weist ausserdem eine Verbindung 52 mit einem Niederdruckspeicher 54 auf, in der ein zumThe working space 42 has a connection 46 to a fuel reservoir 48, in which a check valve 50 opening towards the working space 42 is arranged. The work space 42 also has a connection 52 with a low-pressure accumulator 54, in which a
Niederdruckspeicher 54 hin öffnendes Rückschlagventil 56 angeordnet ist. Der Niederdruckspeicher 54 ist vorzugsweise in das Gehäuse 10 der Hochdruckpumpe integriert und kann beispielsweise als Membranspeicher oder als Blasenspeicher ausgebildet sein oder einen federbelasteten Kolben aufweisen oder als eine Kombination aus diesen Bauarten ausgebildet sein. Der im Niederdruckspeicher 54 herrschende Druck wird durch ein Drucksteuerventil 58 eingestellt. Das Drucksteuerventil 58 kann ein federbelastetes Ventil sein, das bei Überschreiten eines vorgegebenen Drucks im Niederdruckspeicher 54 eine Verbindung 60 des Niederdruckspeichers 54 mit einem Entlastungsbereich, beispielsweise einem Rücklauf in den Kraftstoffvorratsbehälter 48 freigibt. Alternativ kann das Drucksteuerventil 58 auch ein elektrisch betätigtes Ventil sein, das von einer elektronischen Steuereinrichtung 62 angesteuert wird. Hierbei kann der Druck im Niederdruckspeicher 54 variabel eingestellt werden, beispielsweise in Abhängigkeit von Betriebsparametern der Brennkraftmaschine. Das Drucksteuerventil 58 kann in das Gehäuse 10 der Hochdruckpumpe integriert oder an dieses angebaut sein.Low pressure accumulator 54 opening check valve 56 is arranged. The low-pressure accumulator 54 is preferably integrated in the housing 10 of the high-pressure pump and can be designed, for example, as a diaphragm accumulator or as a bladder accumulator or have a spring-loaded piston or can be designed as a combination of these types. The pressure prevailing in the low-pressure accumulator 54 is set by a pressure control valve 58. The pressure control valve 58 can be a spring-loaded valve which, when a predetermined pressure in the low-pressure accumulator 54 is exceeded, releases a connection 60 of the low-pressure accumulator 54 with a relief region, for example a return into the fuel reservoir 48. Alternatively, the pressure control valve 58 can also be an electrically operated valve that is controlled by an electronic control device 62. Here, the pressure in the low-pressure accumulator 54 can be set variably, for example depending on the operating parameters of the internal combustion engine. The pressure control valve 58 can be integrated into the housing 10 of the high-pressure pump or can be attached to it.
Die Pumpenarbeitsräume 28 der Pumpenelemente 14 sind mit dem Niederdruckspeicher 54 verbunden, der dieThe pump work spaces 28 of the pump elements 14 are connected to the low-pressure accumulator 54, which is the
KraftstoffZuführung für diese bildet. In der Verbindung der Pumpenarbeitsräume 28 mit dem Niederdruckspeicher 54 ist vorzugsweise eine KraftstoffZumesseinrichtung 64 angeordnet, durch die ein variabler Durchflussquerschnitt eingestellt werden kann. Die KraftstoffZumesseinrichtung 64 weist ein Proportionalventil auf, mittels dem derFuel supply for this forms. In the connection of the Pump workrooms 28 with the low-pressure accumulator 54 are preferably arranged a fuel metering device 64, through which a variable flow cross-section can be set. The fuel metering device 64 has a proportional valve, by means of which the
Durchflussquerschnitt kontinuierlich verändert werden kann, und einen Aktor, beispielsweise in Form eines Elektromagneten. Die KraftstoffZumesseinrichtung 64 wird durch die elektronische Steuereinrichtung 62 angesteuert. Die KraftstoffZumesseinrichtung 64 kann in das Gehäuse 10 der Hochdruckpumpe integriert oder an dieses angebaut sein.Flow cross section can be changed continuously, and an actuator, for example in the form of an electromagnet. The fuel metering device 64 is controlled by the electronic control device 62. The fuel metering device 64 can be integrated into the housing 10 of the high-pressure pump or can be attached to it.
Der Niederdruckspeicher 54 weist eine Verbindung 66 mit dem Antriebsbereich der Hochdruckpumpe auf, in dem die Antriebswelle 12 angeordnet ist. Die Antriebswelle 12 ist in einem Hohlraum des Gehäuses 10 über mehrere, beispielsweise zwei Lagerstellen 12a, 12b radial und axial gelagert. Die Lagerstellen 12a, 12b können beispielsweise als Gleitlager ausgebildet sein. Über die Verbindung 66 wird den Lagerstellen 12a, 12b der Antriebswelle 12 sowie dem Nocken 16 und den Rollen 25 Kraftstoff zu deren Schmierung und Kühlung zugeführt. In der Verbindung 66 ist eine Drosselstelle 68 angeordnet, um die Kraftstoffmenge, die aus dem Niederdruckspeicher 54 in den Antriebsbereich abfließt, zu begrenzen.The low-pressure accumulator 54 has a connection 66 to the drive area of the high-pressure pump, in which the drive shaft 12 is arranged. The drive shaft 12 is mounted radially and axially in a cavity of the housing 10 via several, for example two bearing points 12a, 12b. The bearing points 12a, 12b can be designed, for example, as plain bearings. Via the connection 66, the bearings 12a, 12b of the drive shaft 12 as well as the cam 16 and the rollers 25 are supplied with fuel for their lubrication and cooling. A throttle point 68 is arranged in the connection 66 in order to limit the amount of fuel that flows out of the low-pressure accumulator 54 into the drive area.
Nachfolgend wird die Funktion der Hochdruckpumpe erläutert. Die Antriebswelle 12 wird beispielsweise mechanisch durch die Brennkraftmaschine angetrieben. Die Rotation der Antriebswelle 12 wird über den Nocken 16 in eine Hubbewegung der Stößel 24 und der Pumpenkolben 20 umgewandelt. Beim Saughub der Pumpenkolben 20 wird durch die Stößel 24 Kraftstoff über die Verbindungen 46 bei geöffneten Rückschlagventilen 50 aus dem Kraftstoffvorratsbehälter 48 in die sich vergrößernden Arbeitsräume 42 angesaugt. DieThe function of the high pressure pump is explained below. The drive shaft 12 is driven mechanically by the internal combustion engine, for example. The rotation of the drive shaft 12 is converted via the cam 16 into a lifting movement of the tappets 24 and the pump pistons 20. During the suction stroke of the pump pistons 20, the plunger 24 draws fuel from the fuel reservoir 48 into the enlarging working spaces 42 via the connections 46 with the check valves 50 open. The
Rückschlagventile 56 zum Niederdruckspeicher 54 sind dabei geschlossen. Die Stößel 24 sind dabei selbstansaugend, das bedeutet, dass zwischen dem Kraftstoffvorratsbehälter 48 und den Arbeitsräumen 42 keine weitere Förderpumpe erforderlich ist. Beim Förderhub der Pumpenkolben 20 wird durch die Stößel 24 über die Verbindungen 52 Kraftstoff aus den sich verkleinernden Arbeitsräumen 42 bei geöffneten Rückschlagventilen 56 in denCheck valves 56 to the low pressure accumulator 54 are included closed. The plungers 24 are self-priming, which means that no further feed pump is required between the fuel tank 48 and the working spaces 42. During the delivery stroke of the pump pistons 20, the plunger 24, via the connections 52, transfers fuel from the shrinking working spaces 42 when the check valves 56 are open
Niederdruckspeicher 54 verdrängt. Die Rückschlagventile 50 zum Kraftstoffvorratsbehälter 48 sind dabei geschlossen. Im Niederdruckspeicher 54 wird durch den durch die Stößel 24 geförderten Kraftstoff beispielsweise ein Druck zwischen etwa 2 und 10 bar erzeugt. Von den Stößeln 24 zu viel geförderter Kraftstoff wird durch das Drucksteuerventil 58 in den Rücklauf 60 zum Kraftstoffvorratsbehälter 48 abgesteuert. Durch den im Arbeitsraum 42 herrschenden Druck wird die Feder 26 unterstützt und der Stößel 24 mit seiner Rolle 25 gegen den Nocken 16 gedrückt. Die Feder 26 kann daher gegebenenfalls kleiner dimensioniert werden, wodurch diese leichte wird und einen kleineren Bauraum erfordert.Low pressure accumulator 54 displaced. The check valves 50 to the fuel tank 48 are closed. In the low-pressure accumulator 54, for example, a pressure between approximately 2 and 10 bar is generated by the fuel delivered by the tappets 24. Too much fuel delivered by the tappets 24 is diverted by the pressure control valve 58 into the return 60 to the fuel tank 48. The spring 26 is supported by the pressure prevailing in the working space 42 and the tappet 24 with its roller 25 is pressed against the cam 16. The spring 26 can therefore optionally be made smaller, which makes it light and requires less space.
Beim Saughub der Pumpenkolben 20 wird durch diese bei geöffneten Einlassventilen 30 und geschlossenen Auslassventilen 32 Kraftstoff aus dem Niederdruckspeicher 54 in die Pumpenarbeitsräume 28 angesaugt. Der Durchflussquerschnitt zwischen dem Niederdruckspeicher 54 und den Pumpenarbeitsräumen 28 wird dabei durch die KraftstoffZumesseinrichtung 64 eingestellt. Beim Förderhub der Pumpenkolben 20 wird durch diese bei geöffneten Auslassventilen 32 und geschlossenen Einlassventilen 30 Kraftstoff aus den Pumpenarbeitsräumen 28 in den Hochdruckspeicher 8 verdrängt. Der Druck im Hochdruckspeicher 8 wird durch einen Drucksensor erfasst, der mit der Steuereinrichtung 62 verbunden ist. Durch die Steuereinrichtung 62 wird die KraftstoffZumesseinrichtung 64 derart angesteuert, dass durch diese derDuring the suction stroke of the pump pistons 20, fuel is sucked from the low-pressure accumulator 54 into the pump work spaces 28 through these with the inlet valves 30 and the outlet valves 32 closed. The flow cross-section between the low-pressure accumulator 54 and the pump work spaces 28 is set by the fuel metering device 64. During the delivery stroke of the pump pistons 20, fuel is displaced from the pump work spaces 28 into the high-pressure accumulator 8 by these with the outlet valves 32 and the inlet valves 30 closed. The pressure in the high-pressure accumulator 8 is detected by a pressure sensor which is connected to the control device 62. The fuel metering device 64 is controlled by the control device 62 in such a way that the fuel metering device 64
Durchflussquerschnitt so groß eingestellt wird, dass durch die Pumpenkolben 20 nur eine so große Kraftstoffmenge angesaugt und unter Hochdruck in den Hochdruckspeicher 8 verdrängt wird, die erforderlich ist, um im Hochdruckspeicher 8 einen vorgegebenen Druck aufrechtzuerhalten. Wenn zur Aufrechterhaltung des vorgegebenen Drucks im Hochdruckspeicher 8 eine große Kraftstoffmenge gefördert werden muss, so wird die KraftstoffZumesseinrichtung 64 durch die Steuereinrichtung 62 derart angesteuert, dass diese einen großen Durchflussquerschnitt freigibt. Wenn zur Aufrechterhaltung des vorgegebenen Drucks im Hochdruckspeicher 8 nur eine geringe Kraftstoffmenge gefördert werden muss, so wird die KraftstoffZumesseinrichtung 64 durch die Steuereinrichtung 62 derart angesteuert, dass diese nur einen kleinen Durchflussquerschnitt freigibt oder gegebenenfalls denFlow cross section is set so large that by the pump piston 20 is only sucked in such a large amount of fuel and is displaced under high pressure into the high-pressure accumulator 8, which is required in order to maintain a predetermined pressure in the high-pressure accumulator 8. If a large amount of fuel has to be delivered in order to maintain the predetermined pressure in the high-pressure accumulator 8, the fuel metering device 64 is controlled by the control device 62 in such a way that it releases a large flow cross section. If only a small amount of fuel needs to be delivered in order to maintain the predetermined pressure in the high-pressure accumulator 8, the fuel metering device 64 is controlled by the control device 62 in such a way that it only releases a small flow cross-section or, if appropriate, that
Durchflussquerschnitt vollständig verschließt, so dass durch die Hochdruckpumpe kein Kraftstoff in den Hochdruckspeicher 8 gefördert wird.The flow cross-section is completely closed, so that no fuel is conveyed into the high-pressure accumulator 8 by the high-pressure pump.
Bei der Förderung von Kraftstoff durch die Stößel 24 aus dem Kraftstoffvorratsbehälter 48 auftretende Druckstöße werden durch das Volumen des Niederdruckspeichers 54 weitgehend ausgeglichen, so dass die Befüllung der Pumpenarbeitsräume 28 aus dem Niederdruckspeicher 54 mit nahezu konstantem Druck erfolgen kann. Das Druckniveau im Niederdruckspeicher 54 kann mittels eines elektrisch angesteuerten Drucksteuerventils 58 variabel eingestellt werden. Es kann beispielsweise vorgesehen sein, dass mit zunehmender Drehzahl der Brennkraftmaschine und damit der Hochdruckpumpe ein höheres Druckniveau im Niederdruckspeicher 54 eingestellt werden, um trotz der dann zur Verfügung stehenden kürzeren Zeit zur Befüllung der Pumpenarbeitsräume 28 eine ausreichende Befüllung der Pumpenarbeitsräume 28 sicherzustellen. Pressure surges that occur during the delivery of fuel by the tappets 24 from the fuel reservoir 48 are largely compensated for by the volume of the low-pressure accumulator 54, so that the pump working spaces 28 can be filled from the low-pressure accumulator 54 with an almost constant pressure. The pressure level in the low-pressure accumulator 54 can be variably set by means of an electrically controlled pressure control valve 58. For example, provision can be made for a higher pressure level in the low-pressure accumulator 54 to be set with increasing speed of the internal combustion engine and thus the high-pressure pump, in order to ensure adequate filling of the pump work spaces 28 despite the shorter time available for filling the pump work spaces 28.

Claims

Ansprüche Expectations
1. Hochdruckpumpe für eine Kraftstoffeinspritzeinrichtung einer Brennkraftmaschine, mit einem Gehäuse (10) , in dem eine Antriebswelle (12) und wenigstens ein Pumpenelement (14) angeordnet sind, wobei das wenigstens eine Pumpenelement (14) einen durch die Antriebswelle (12) über einen Stößel (24) in einer Hubbewegung angetriebenen Pumpenkolben (20) aufweist, der einen Pumpenarbeitsraum (28) begrenzt, der beim Saughub des Pumpenkolbens (20) mit Kraftstoff befüllt wird und aus dem beim Förderhub des Pumpenkolbens (20) Kraftstoff verdrängt wird, wobei der Stößel (24) in einer Bohrung (40) im Gehäuse (10) verschiebbar geführt ist, dadurch gekennzeichnet, dass der Stößel (24) in der Bohrung (40) des 'Gehäuses (10) dicht geführt ist, dass der Stößel (24) in der Bohrung (40) einen Arbeitsraum (42) begrenzt, in den beim Saughub des Pumpenkolbens (20) durch den Stößel (24) Kraftstoff angesaugt wird und aus dem beim Förderhub des Pumpenkolbens (20) Kraftstoff in einen Niederdruckspeicher (54) verdrängt wird, in dem ein erhöhter Druck aufrechterhalten wird und aus dem beim Saughub des Pumpenkolbens (20) der Pumpenarbeitsraum (28) mit Kraftstoff befüllt wird.1. High-pressure pump for a fuel injection device of an internal combustion engine, with a housing (10) in which a drive shaft (12) and at least one pump element (14) are arranged, the at least one pump element (14) one through the drive shaft (12) via a The plunger (24) has a pump piston (20) driven in one stroke movement, which delimits a pump working chamber (28) which is filled with fuel during the suction stroke of the pump piston (20) and from which fuel is displaced during the delivery stroke of the pump piston (20), the Tappet (24) is slidably guided in a bore (40) in the housing (10), characterized in that the tappet (24) is tightly guided in the bore (40) of the ' housing (10) such that the tappet (24) in the bore (40) delimits a working space (42) into which fuel is sucked in by the tappet (24) during the suction stroke of the pump piston (20) and from which fuel flows into a depression during the delivery stroke of the pump piston (20) r pressure reservoir (54) is displaced, in which an increased pressure is maintained and from which the pump working chamber (28) is filled with fuel during the suction stroke of the pump piston (20).
2. Hochdruckpumpe nach Anspruch 1, dadurch gekennzeichnet, dass zwischen dem Arbeitsraum (42) und einem Kraftstoffvorratsbehälter (48) ein zum Arbeitsraum (42) hin öffnendes Rückschlagventil (50) und zwischen dem Arbeitsraum (42) und dem Niederdruckspeicher (54) ein zum Niederdruckspeicher (54) hin öffnendes Rückschlagventil (56) angeordnet ist. 2. High-pressure pump according to claim 1, characterized in that between the work space (42) and a fuel reservoir (48) to the work space (42) opening check valve (50) and between the work space (42) and the low pressure accumulator (54) to Low pressure accumulator (54) opening check valve (56) is arranged.
3. Hochdruckpumpe nach Anspruch 1 oder 2, dadurch gekennzeichnet, dass der Druck im Niederdruckspeicher (54) mittels eines Drucksteuerventils (58) eingestellt wird.3. High-pressure pump according to claim 1 or 2, characterized in that the pressure in the low-pressure accumulator (54) is set by means of a pressure control valve (58).
4. Hochdruckpumpe nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, dass zwischen dem Niederdruckspeicher (54) und dem Pumpenarbeitsraum (28) eine4. High-pressure pump according to one of claims 1 to 3, characterized in that between the low-pressure accumulator (54) and the pump work space (28)
KraftstoffZumesseinrichtung (64) angeordnet ist, durch die ein veränderlicher Durchflussquerschnitt einstellbar ist, so dass die durch den Pumpenkolben (20) in den Pumpenarbeitsraum (28) angesaugte Kraftstoffmenge veränderlich ist.Fuel metering device (64) is arranged, by means of which a variable flow cross section can be set, so that the amount of fuel sucked into the pump working chamber (28) by the pump piston (20) can be changed.
5. Hochdruckpumpe nach einem der vorstehenden Ansprüche, dadurch gekennzeichnet, dass der Niederdruckspeicher (54) mit einem Antriebsbereich der Hochdruckpumpe, in dem die Antriebswelle (12) angeordnet ist, verbunden ist.5. High-pressure pump according to one of the preceding claims, characterized in that the low-pressure accumulator (54) is connected to a drive region of the high-pressure pump, in which the drive shaft (12) is arranged.
6. Hochdruckpumpe nach Anspruch 5, dadurch gekennzeichnet, dass in der Verbindung ( ) des Niederdruckspeichers (54) mit dem Antriebsbereich eine Drosselstelle ( ) zur Begrenzung des KraftstoffZulaufs in den Antriebsbereich angeordnet ist.6. High-pressure pump according to claim 5, characterized in that in the connection () of the low-pressure accumulator (54) to the drive area, a throttle point () for limiting the fuel supply to the drive area is arranged.
7. Hochdruckpumpe nach einem der vorstehenden Ansprüche, dadurch gekennzeichnet, dass der Niederdruckspeicher (54) in das Gehäuse (10) der Hochdruckpumpe integriert ist. 7. High-pressure pump according to one of the preceding claims, characterized in that the low-pressure accumulator (54) is integrated in the housing (10) of the high-pressure pump.
PCT/DE2004/001304 2003-08-04 2004-06-22 High pressure pump for a fuel injection device of a combustion engine WO2005015017A1 (en)

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2012139799A1 (en) * 2011-04-14 2012-10-18 Robert Bosch Gmbh High pressure fuel pump for a fuel injection system of an internal combustion engine

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102006023470A1 (en) 2006-05-18 2007-11-22 Siemens Ag Common-rail-injection system for e.g. diesel engine, has return line for returning fuel from injector to high pressure fuel pump under return pressure, where pressure control valve adjusts return pressure
DE102008042649B4 (en) * 2008-10-07 2017-07-27 Robert Bosch Gmbh Plug-in pump with integrated low-pressure pump
DE102009003094A1 (en) * 2009-05-14 2010-11-18 Robert Bosch Gmbh High-pressure fuel pump
DE102011076016A1 (en) * 2011-05-18 2012-07-19 Continental Automotive Gmbh High pressure pump for promotion of fluid, has one-piece formed housing portion with housing recess, and drive shaft with longitudinal axis

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4149831A (en) * 1977-12-12 1979-04-17 Stanadyne, Inc. Double-acting differential piston supply pump
US5573381A (en) * 1995-06-20 1996-11-12 Navistar International Transportation Corp. Internally regulated self priming fuel pump assembly
DE19627757A1 (en) * 1996-07-10 1998-01-15 Bosch Gmbh Robert Fuel pump
DE19829548A1 (en) * 1998-07-02 2000-01-13 Bosch Gmbh Robert Radial piston pump
EP1184568A2 (en) * 2000-08-31 2002-03-06 Delphi Technologies, Inc. Fuel pump
DE10153189A1 (en) * 2001-10-27 2003-05-15 Bosch Gmbh Robert Fuel pump, fuel system, method for operating a fuel system and internal combustion engine

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4149831A (en) * 1977-12-12 1979-04-17 Stanadyne, Inc. Double-acting differential piston supply pump
US5573381A (en) * 1995-06-20 1996-11-12 Navistar International Transportation Corp. Internally regulated self priming fuel pump assembly
DE19627757A1 (en) * 1996-07-10 1998-01-15 Bosch Gmbh Robert Fuel pump
DE19829548A1 (en) * 1998-07-02 2000-01-13 Bosch Gmbh Robert Radial piston pump
EP1184568A2 (en) * 2000-08-31 2002-03-06 Delphi Technologies, Inc. Fuel pump
DE10153189A1 (en) * 2001-10-27 2003-05-15 Bosch Gmbh Robert Fuel pump, fuel system, method for operating a fuel system and internal combustion engine

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2012139799A1 (en) * 2011-04-14 2012-10-18 Robert Bosch Gmbh High pressure fuel pump for a fuel injection system of an internal combustion engine

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