EP2850318B1 - High pressure pump - Google Patents

High pressure pump Download PDF

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Publication number
EP2850318B1
EP2850318B1 EP13714617.1A EP13714617A EP2850318B1 EP 2850318 B1 EP2850318 B1 EP 2850318B1 EP 13714617 A EP13714617 A EP 13714617A EP 2850318 B1 EP2850318 B1 EP 2850318B1
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EP
European Patent Office
Prior art keywords
drive shaft
pressure pump
cavity
fuel
roller
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Not-in-force
Application number
EP13714617.1A
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German (de)
French (fr)
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EP2850318A1 (en
Inventor
Sascha Ambrock
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication of EP2850318A1 publication Critical patent/EP2850318A1/en
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Publication of EP2850318B1 publication Critical patent/EP2850318B1/en
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    • 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
    • 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
    • F04B1/0439—Supporting or guiding means for the pistons

Definitions

  • the present invention relates to a high-pressure pump according to the preamble of claim 1 and a high-pressure injection system according to the preamble of claim 10.
  • a high-pressure pump continuously ensures the maintenance of the pressure in the high-pressure accumulator of the common-rail injection system.
  • the high-pressure pump can be driven, for example, by a camshaft of the internal combustion engine by means of a drive shaft.
  • Vor detailpumpen, z. B. a gear or rotary vane pump used, which are connected upstream of the high-pressure pump.
  • the prefeed pump delivers the fuel from a fuel tank through a fuel line to the high pressure pump.
  • piston pumps are used as high-pressure pumps.
  • a drive shaft is mounted. Radially to pistons are arranged in a cylinder.
  • a roller with a roller rolling surface On the drive shaft with at least one cam is a roller with a roller rolling surface, which is mounted in a roller shoe.
  • the roller shoe is connected to the piston, so that the piston is forced to oscillate translational motion.
  • a spring applies to the roller shoe a radially directed to the drive shaft force, so that the roller is in constant contact with the drive shaft.
  • the roller stands with the roller rolling surface on a shaft rolling surface as the surface of the drive shaft with the at least one cam in contact with the drive shaft.
  • the roller is mounted by means of a sliding bearing in the roller shoe.
  • the drive shaft with the at least one cam is generally made of steel, on the one hand to have sufficient rigidity and on the other hand to withstand the mechanical loads due to the roller, which rolls on the drive roller can withstand.
  • the drive shaft has a large mass and when the high-pressure pump is used in a motor vehicle, a large mass of the high-pressure pump also leads to a greater fuel consumption of the motor vehicle in a disadvantageous manner.
  • the DE 10 2006 045 933 A1 shows a high-pressure pump for high-pressure fuel delivery according to the preamble of claim 1.
  • the high-pressure pump has a drive shaft with cams. Cylindrical rollers are supported by roller shoes and rest on the cams. The roller shoes are mounted by means of a plunger assembly in a bore of a part of the housing. The pump elements are attached to the plunger assembly. A coil spring presses the plunger assembly onto the cams.
  • a high-pressure pump according to the invention is defined in claim 1.
  • the drive shaft has a cavity, which is machined, for example as an axial bore machined into the drive shaft.
  • the mass of the drive shaft can be reduced in an advantageous manner, thereby reducing the fuel consumption of the motor vehicle when the high-pressure pump is used in a motor vehicle.
  • as at least one cavity of the at least one drive shaft is also considered a space which is at least partially filled by a stiffening member and / or a sealing plug.
  • the cavity is closed with at least one sealing plug in the region of an axial end of the at least one drive shaft.
  • the cavity is closed in a fluid-tight manner with the at least one sealing plug so that no fuel can flow into the at least one cavity.
  • the high-pressure pump has a lubricant space through which fuel flows and within this lubrication space, the roller and the drive shaft is arranged. If the fuel flows into the cavity, additional mass would thereby be arranged in the drive shaft due to the fuel.
  • the sealing plug is arranged at an axial end of the drive shaft, so that thereby the cavity is not filled with fuel, but for example, filled with air, so that thereby the drive shaft has a lower mass.
  • At least one stiffening part is arranged in the cavity.
  • the drive shaft In a large formation of the cavity, ie, that in a section perpendicular to a longitudinal axis of the drive shaft, the cavity occupies a large proportion, the drive shaft may not have sufficient rigidity.
  • a stiffening member is disposed within the cavity, so that characterized the drive shaft has sufficient rigidity. This is necessary because a compressive force is applied to the drive shaft perpendicular to the longitudinal axis of the roller.
  • the at least one stiffening member and / or the sealing plug has a lower density, preferably at least 10%, 30% or 50% lower density, than the drive shaft.
  • the stiffening member and / or the sealing plug have a lower density than the drive shaft, thereby reducing mass on the drive shaft.
  • the drive shaft is at least partially made of metal and the at least one stiffening part and / or the sealing plug is at least partially made of titanium and / or carbon.
  • the drive shaft is generally made of steel, since on the outside of the drive shaft, the roller rolls off and thereby a considerable mechanical stress on the outside of a shaft rolling surface of the drive shaft is present. This generally requires steel.
  • the stiffening member and / or the sealing plug have titanium with a low density and thus mass to keep one hand, the mass of the drive shaft with stiffening and / or sealing plug low, and on the other hand, titanium and / or carbon also ensures sufficient rigidity.
  • the at least one stiffening part and / or the closure plug force and / or cohesive, z. B. by means of a press fit, connected to the drive shaft.
  • the at least one stiffening part and / or the at least one sealing plug can also be connected to the at least one drive shaft by means of a screw connection.
  • the volume of the cavity of the drive shaft is at least 10%, 30%, 50% or 70% of the total volume of the drive shaft.
  • the volume of the cavity the drive shaft has a substantial portion of the total volume of the drive shaft, thereby substantially reducing the mass of the drive shaft by means of the cavity.
  • the volume of the cavity of the drive shaft to at least 10%, 30%, 50%, 70%, 90% or 98% filled with the at least one stiffening part. If the volume of the cavity is filled to a substantial extent by the stiffening part and the stiffening part is also sufficiently connected to the drive shaft, the rigidity of the drive shaft can be increased to a significant extent with the stiffening part.
  • a contact surface between the roller and the drive shaft is lubricated by means of fuel.
  • the at least one roller is mounted in at least one roller shoe by means of at least one sliding bearing or a plain bearing.
  • the at least one roller in a section perpendicular to a longitudinal axis as the axis of rotation, surrounds the plain bearing to more than 50% of the at least one roller.
  • the plain bearing by means of fuel, for.
  • fuel for.
  • an eccentric shaft is considered as a drive shaft with at least one cam.
  • Inventive high-pressure injection system for an internal combustion engine in particular for a motor vehicle, comprising a high pressure pump, a high pressure rail, preferably a prefeed pump for conveying a fuel from a fuel tank to the high pressure pump, wherein the high pressure pump is designed as a high pressure pump described in this patent application.
  • the high-pressure injection system has a metering unit which controls or regulates the quantity of fuel delivered per unit time by the prefeed pump to the high-pressure pump.
  • the producible by the high-pressure pump pressure in the high-pressure rail is, for example, in the range of 1000 to 3000 bar z. B. for diesel engines or between 40 bar and 400 bar z. B. for gasoline engines.
  • Fig. 1 a cross section of a high pressure pump 1 for a high pressure injection system 36 is shown.
  • the high-pressure pump 1 serves to fuel, z. As gasoline or diesel, to promote an internal combustion engine 39 under high pressure.
  • the pressure which can be generated by the high-pressure pump 1 is, for example, in a range between 1000 and 3000 bar.
  • the high-pressure pump 1 has a drive shaft 2 with two cams 3, which performs a rotational movement about a rotation axis 26.
  • the axis of rotation 26, which also represents a longitudinal axis 26 of the drive shaft 2 lies in the plane of the drawing Fig. 1 and is perpendicular to the plane of Fig. 2 .
  • a piston 5 is mounted in a cylinder 6 as a piston guide 7, which is formed by a housing 8.
  • a working chamber 29 is bounded by the cylinder 6, the housing 8 and the piston 5.
  • Into the working space 29 opens an inlet channel 22 with an inlet valve 19 and an outlet channel 24 with an outlet valve 20. Through the inlet channel 22, the fuel flows into the working space 29 and through the outlet channel 24, the fuel flows out of the working space 29 under high pressure.
  • the volume of the working chamber 29 is changed due to an oscillating stroke movement of the piston 5.
  • the piston 5 is indirectly supported on the drive shaft 2 from.
  • a roller shoe 9 is attached to a roller 10.
  • the roller 10 can perform a rotational movement, the axis of rotation 25 in the plane according to Fig. 1 lies and perpendicular to the plane of Fig. 2 stands.
  • the drive shaft 2 with the at least one cam 3 has a shaft rolling surface 4 and the roller 10 has a roller rolling surface 11.
  • the roller-running surface 11 of the roller 10 rolls on a contact surface 12 on the shaft rolling surface 4 of the drive shaft 2 with the two cams 3 from.
  • the roller shoe 9 is mounted in a roller shoe bearing formed by the housing 8 as a sliding bearing.
  • a spring 27 or spiral spring 27 as an elastic element 28 which is clamped between the housing 8 and the roller shoe 9 is, brings on the roller shoe 9 a compressive force, so that the roller rolling surface 11 of the roller 10 is in constant contact with the shaft rolling surface 4 of the drive shaft 2.
  • the roller shoe 9 and the piston 5 thus carry out together an oscillating stroke movement.
  • a drive shaft 2 is shown in a longitudinal section.
  • the drive shaft 2 made of steel two cavities 17 are incorporated as an axial bore 38. Because of these two cavities 17 thus has the drive shaft 2 a significantly reduced mass and on the other hand, the rigidity of the drive shaft 2 made of steel is still sufficiently large, since the holes 38 in cross section still leave a sufficiently large proportion of the drive shaft 2 made of steel.
  • Two axial ends 40 of the drive shaft 2 are arranged outside of a not shown lubrication chamber of the high-pressure pump 1, so that thereby no fuel located within the lubricant space can flow into the two bores 38.
  • a first embodiment of the drive shaft 2 is shown.
  • the drive shaft 2 has an axial bore 38 as a cavity 17 and at an in Fig. 5 On the left axial end 40 shown, the cavity 17 is closed fluid-tight by a closure plug 16 made of titanium or carbon.
  • the closure plug 16 has the effect that no fuel can flow into the cavity 17 from a lubricant space of the high-pressure pump 1. As a result, 16 air is disposed within the cavity 17 apart from the sealing plug and the drive shaft 2 thereby has a low mass.
  • a second embodiment of the drive shaft 2 is shown.
  • the drive shaft 2 made of steel has an axial bore 38 as a cavity 17 and this cavity 17 is substantially filled with a stiffening member 15 made of titanium.
  • the axial bore 38 is machined, z. B. by means of drilling, incorporated and then the closure plug 16 inserted into this bore 38 and thereby positively connected by means of a press fit with the drive shaft 2 made of steel. Due to the size of the bore 38, the drive shaft 2 without the stiffening part 5 made of titanium does not have sufficient rigidity. By means of the stiffening member 15 made of titanium, the rigidity of the drive shaft. 2 be increased significantly.
  • titanium advantageously has on the one hand a low mass and on the other hand also a sufficiently high rigidity in order to increase the rigidity of the drive shaft 2.
  • the drive shaft 2 in particular on the shaft rolling surface 4 for supporting the roller 10, made of steel, so that thereby the drive shaft 2 can withstand the mechanical stresses due to the rolling of the roller 10 on the shaft rolling surface 4 in the long term.
  • a third embodiment of the drive shaft 2 is shown.
  • the stiffening member 15 is formed as a sleeve with a stiffening member cavity 14 and at an axial end 40 of the drive shaft 2 shown in Figure left this stiffening member cavity 14 of the stiffening member 15 is closed by a sealing plug 16. As a result, no fuel can flow from the lubricant space of the high-pressure pump 1, which is not shown, into the stiffening part cavity 14.
  • the stiffening part 15 made of titanium has a lower rigidity than the stiffening part 15 in FIG Fig. 6 on, since the stiffening part 15 in Fig.
  • stiffening member 15 is formed as a sleeve with a stiffening member cavity 14.
  • the stiffening part 15 in Fig. 7 can thereby provide only a smaller increase in the rigidity of the drive shaft 2 available as in Fig. 6 shown stiffening part 15. This is sufficient because in the in Fig. 7 illustrated third embodiment of the drive shaft 2, the drive shaft 2 either requires less rigidity and / or due to the formation of the bore 38 with a smaller diameter, the drive shaft 2 itself has sufficient rigidity and this only slightly with the stiffening member 15 as a sleeve as shown in FIG Fig. 7 must be increased to meet the requirements for the rigidity of the drive shaft 2.
  • FIG. 3 is a highly schematic representation of the high-pressure injection system 36 for a motor vehicle (not shown) imaged with a high-pressure rail 30 or a fuel rail 31.
  • the fuel is injected by means of valves (not shown) in the combustion chamber of the engine 39.
  • a prefeed pump 35 delivers fuel from a fuel tank 32 through a fuel pipe 33 to the high-pressure pump 1 according to the above embodiment.
  • the high-pressure pump 1 and the prefeed pump 35 are driven by the drive shaft 2.
  • the drive shaft 2 is coupled to a crankshaft of the engine 39.
  • the high pressure rail 30 serves - as already described - to inject the fuel into the combustion chamber of the internal combustion engine 39.
  • the funded by the feed pump 35 fuel is passed through the fuel line 33 to the high-pressure pump 1.
  • the fuel not required by the high-pressure pump 1 is thereby returned to the fuel tank 32 through a fuel return line 34.
  • a metering unit 37 controls and / or regulates the quantity of fuel supplied to the high-pressure pump 1, so that the fuel return line 34 can be dispensed with in a further embodiment (not shown).
  • the drive shaft 2 made of steel has a bore 38 as a cavity 17, so that thereby the drive shaft 2 has a reduced mass.
  • a stiffening member 15, z To increase the rigidity of the drive shaft 2 can within the cavity 17, a stiffening member 15, z.
  • Example of titanium to thereby increase the one hand, the rigidity of the drive shaft 2, at a low mass of the drive shaft 2 due to the low density of the stiffening member 15, and on the other hand on the shaft rolling surface 4, a sufficient mechanical wear resistance for rolling the To get roller 10.

Description

Die vorliegende Erfindung betrifft eine Hochdruckpumpe gemäß dem Oberbegriff des Anspruches 1 und ein Hochdruckeinspritzsystem gemäß dem Oberbegriff des Anspruches 10.The present invention relates to a high-pressure pump according to the preamble of claim 1 and a high-pressure injection system according to the preamble of claim 10.

Stand der TechnikState of the art

In Hochdruckeinspritzsystemen für Verbrennungsmotoren, insbesondere in Common-Rail-Einspritzsystemen von Diesel- oder Benzinmotoren, sorgt eine Hochdruckpumpe dauernd für die Aufrechterhaltung des Druckes in dem Hochdruckspeicher des Common-Rail-Einspritzsystems. Die Hochdruckpumpe kann beispielsweise durch eine Nockenwelle des Verbrennungsmotors mittels einer Antriebswelle angetrieben werden. Für die Förderung des Kraftstoffs zur Hochdruckpumpe werden Vorförderpumpen, z. B. eine Zahnrad- oder Drehschieberpumpe, verwendet, die der Hochdruckpumpe vorgeschaltet sind. Die Vorförderpumpe fördert den Kraftstoff von einem Kraftstofftank durch eine Kraftstoffleitung zu der Hochdruckpumpe.In high-pressure injection systems for internal combustion engines, in particular in common-rail injection systems of diesel or gasoline engines, a high-pressure pump continuously ensures the maintenance of the pressure in the high-pressure accumulator of the common-rail injection system. The high-pressure pump can be driven, for example, by a camshaft of the internal combustion engine by means of a drive shaft. For the promotion of the fuel to the high-pressure pump Vorförderpumpen, z. B. a gear or rotary vane pump used, which are connected upstream of the high-pressure pump. The prefeed pump delivers the fuel from a fuel tank through a fuel line to the high pressure pump.

Als Hochdruckpumpen werden unter anderem Kolbenpumpen eingesetzt. In einem Gehäuse ist eine Antriebswelle gelagert. Radial dazu sind Kolben in einem Zylinder angeordnet. Auf der Antriebswelle mit wenigstens einem Nocken liegt eine Laufrolle mit einer Rollen-Rollfläche auf, die in einem Rollenschuh gelagert ist. Der Rollenschuh ist mit dem Kolben verbunden, so dass der Kolben zu einer oszillierenden Translationsbewegung gezwungen ist. Eine Feder bringt auf den Rollenschuh eine radial zu der Antriebswelle gerichtet Kraft auf, so dass die Laufrolle in ständigen Kontakt zu der Antriebswelle steht. Die Laufrolle steht mit der Rollen-Rollfläche an einer Wellen-Rollfläche als Oberfläche der Antriebswelle mit dem wenigstens einen Nocken in Kontakt mit der Antriebswelle. Die Laufrolle ist mittels eines Gleitlagers in dem Rollenschuh gelagert.Amongst others, piston pumps are used as high-pressure pumps. In a housing, a drive shaft is mounted. Radially to pistons are arranged in a cylinder. On the drive shaft with at least one cam is a roller with a roller rolling surface, which is mounted in a roller shoe. The roller shoe is connected to the piston, so that the piston is forced to oscillate translational motion. A spring applies to the roller shoe a radially directed to the drive shaft force, so that the roller is in constant contact with the drive shaft. The roller stands with the roller rolling surface on a shaft rolling surface as the surface of the drive shaft with the at least one cam in contact with the drive shaft. The roller is mounted by means of a sliding bearing in the roller shoe.

Die Antriebswelle mit dem wenigstens einen Nocken besteht im Allgemeinen aus Stahl, um einerseits eine ausreichende Steifigkeit aufzuweisen und andererseits den mechanischen Belastungen aufgrund der Laufrolle, welche sich auf der Antriebsrolle abrollt, standhalten zu können. Dadurch weist die Antriebswelle eine große Masse auf und bei einem Einsatz der Hochdruckpumpe in einem Kraftfahrzeug führt eine große Masse der Hochdruckpumpe auch zu einem größeren Kraftstoffverbrauch des Kraftfahrzeuges in nachteiliger Weise.The drive shaft with the at least one cam is generally made of steel, on the one hand to have sufficient rigidity and on the other hand to withstand the mechanical loads due to the roller, which rolls on the drive roller can withstand. As a result, the drive shaft has a large mass and when the high-pressure pump is used in a motor vehicle, a large mass of the high-pressure pump also leads to a greater fuel consumption of the motor vehicle in a disadvantageous manner.

Die DE 10 2006 045 933 A1 zeigt eine Hochdruckpumpe zur Kraftstoffhochdruckförderung gemäß dem Oberbegriff des Anspruchs 1.The DE 10 2006 045 933 A1 shows a high-pressure pump for high-pressure fuel delivery according to the preamble of claim 1.

Die Hochdruckpumpe weist eine Antriebswelle mit Nocken auf. Zylindrische Rollen sind von Rollenschuhen gelagert und liegen auf den Nocken auf. Die Rollenschuhe sind mittels einer Stößelbaugruppe in einer Bohrung eines Teils des Gehäuses gelagert. Die Pumpenelemente sind an der Stößelbaugruppe befestigt. Eine Schraubenfeder drückt die Stößelbaugruppe auf die Nocken.The high-pressure pump has a drive shaft with cams. Cylindrical rollers are supported by roller shoes and rest on the cams. The roller shoes are mounted by means of a plunger assembly in a bore of a part of the housing. The pump elements are attached to the plunger assembly. A coil spring presses the plunger assembly onto the cams.

Aus der DE 103 56 262 A1 ist eine Radialkolbenpumpe zur Kraftstoffhochdruckerzeugung bei Kraftstoffeinspritzsystemen von Brennkraftmaschinen bekannt. In einem Pumpengehäuse ist eine Antriebswelle gelagert. Kolben stützen sich an der Antriebswelle ab, so dass durch Drehen der Antriebswelle die Kolben hin und her bewegt werden. Zwischen den Kolben und der Antriebswelle sind Stößel angeordnet.From the DE 103 56 262 A1 is a radial piston pump for fuel high pressure generation in fuel injection systems of internal combustion engines known. In a pump housing, a drive shaft is mounted. Pistons are supported on the drive shaft, so that by rotating the drive shaft, the pistons are moved back and forth. Between the piston and the drive shaft tappets are arranged.

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

Eine erfindungsgemäße Hochdruckpumpe ist in Anspruch 1 definiert. Die Antriebswelle weist einen Hohlraum auf, der beispielsweise als axiale Bohrung spanabhebend in die die Antriebswelle eingearbeitet ist. Dadurch kann in vorteilhafter Weise die Masse der Antriebswelle reduziert werden und dadurch bei einem Einsatz der Hochdruckpumpe in einem Kraftfahrzeug der Kraftstoffverbrauch des Kraftfahrzeuges verkleinert werden. Dabei wird als wenigstens ein Hohlraum der wenigstens einen Antriebswelle auch ein Raum angesehen, welcher von einem Versteifungsteil und/oder einem Verschlussstopfen wenigstens teilweise ausgefüllt ist.A high-pressure pump according to the invention is defined in claim 1. The drive shaft has a cavity, which is machined, for example as an axial bore machined into the drive shaft. As a result, the mass of the drive shaft can be reduced in an advantageous manner, thereby reducing the fuel consumption of the motor vehicle when the high-pressure pump is used in a motor vehicle. In this case, as at least one cavity of the at least one drive shaft is also considered a space which is at least partially filled by a stiffening member and / or a sealing plug.

Insbesondere ist der Hohlraum mit wenigstens einem Verschlussstopfen im Bereich eines axialen Endes der wenigstens einen Antriebswelle verschlossen. Der Hohlraum ist mit dem wenigstens einem Verschlussstopfen fluiddicht verschlossen, so dass dadurch kein Kraftstoff in den wenigstens einen Hohlraum einströmen kann. Die Hochdruckpumpe weist einen Schmierraum auf durch welchen Kraftstoff strömt und innerhalb dieses Schmierraumes ist die Laufrolle und die Antriebswelle angeordnet. Bei einem Einströmen des Kraftstoffes in den Hohlraum würde dadurch zusätzliche Masse aufgrund des Kraftstoffes in der Antriebswelle angeordnet sein. Um dies zu vermeiden, wird der Verschlussstopfen an einem axialen Ende der Antriebswelle angeordnet, so dass dadurch der Hohlraum nicht mit Kraftstoff gefüllt, sondern beispielsweise mit Luft gefüllt ist, so dass dadurch die Antriebswelle eine geringere Masse aufweist. Erfindungsgemäß ist in dem Hohlraum wenigstens ein Versteifungsteil angeordnet. Bei einer großen Ausbildung des Hohlraumes, d. h. dass in einem Schnitt senkrecht zu einer Längsachse der Antriebswelle der Hohlraum einen großen Anteil einnimmt, kann die Antriebswelle eine nicht mehr ausreichende Steifigkeit aufweisen. Um die Steifigkeit der Antriebswelle zu erhöhen, wird deshalb innerhalb des Hohlraumes ein Versteifungsteil angeordnet, so dass dadurch die Antriebswelle eine ausreichende Steifigkeit aufweist. Diese ist erforderlich, da auf die Antriebswelle senkrecht zu der Längsachse von der Laufrolle eine Druckkraft aufgebracht wird.In particular, the cavity is closed with at least one sealing plug in the region of an axial end of the at least one drive shaft. The cavity is closed in a fluid-tight manner with the at least one sealing plug so that no fuel can flow into the at least one cavity. The high-pressure pump has a lubricant space through which fuel flows and within this lubrication space, the roller and the drive shaft is arranged. If the fuel flows into the cavity, additional mass would thereby be arranged in the drive shaft due to the fuel. To avoid this, the sealing plug is arranged at an axial end of the drive shaft, so that thereby the cavity is not filled with fuel, but for example, filled with air, so that thereby the drive shaft has a lower mass. According to the invention, at least one stiffening part is arranged in the cavity. In a large formation of the cavity, ie, that in a section perpendicular to a longitudinal axis of the drive shaft, the cavity occupies a large proportion, the drive shaft may not have sufficient rigidity. In order to increase the rigidity of the drive shaft, therefore, a stiffening member is disposed within the cavity, so that characterized the drive shaft has sufficient rigidity. This is necessary because a compressive force is applied to the drive shaft perpendicular to the longitudinal axis of the roller.

In einer ergänzenden Ausführungsform weist das wenigstens eine Versteifungsteil und/oder der Verschlussstopfen eine geringere Dichte, vorzugsweise um wenigstens 10%, 30% oder 50% geringere Dichte, auf als die Antriebswelle. Das Versteifungsteil und/oder der Verschlussstopfen weisen eine geringere Dichte auf als die Antriebswelle, um dadurch Masse an der Antriebswelle zu reduzieren.In a supplementary embodiment, the at least one stiffening member and / or the sealing plug has a lower density, preferably at least 10%, 30% or 50% lower density, than the drive shaft. The stiffening member and / or the sealing plug have a lower density than the drive shaft, thereby reducing mass on the drive shaft.

Vorzugsweise besteht die Antriebswelle wenigstens teilweise aus Metall und das wenigstens eine Versteifungsteil und/oder der Verschlussstopfen besteht wenigstens teilweise aus Titan und/oder Karbon. Die Antriebswelle ist im Allgemeinen aus Stahl hergestellt, da außenseitig an der Antriebswelle sich die Laufrolle abrollt und dadurch eine erhebliche mechanische Beanspruchung außenseitig an einer Wellen-Rollfläche der Antriebswelle vorhanden ist. Hierzu ist im Allgemeinen Stahl erforderlich. Das Versteifungsteil und/oder der Verschlussstopfen weisen mit Titan eine geringe Dichte und damit Masse auf, um einerseits die Masse der Antriebswelle mit Versteifungsteil und/oder Verschlussstopfen gering zu halten, und andererseits gewährleistet Titan und/oder Karbon auch eine ausreichende Steifigkeit.Preferably, the drive shaft is at least partially made of metal and the at least one stiffening part and / or the sealing plug is at least partially made of titanium and / or carbon. The drive shaft is generally made of steel, since on the outside of the drive shaft, the roller rolls off and thereby a considerable mechanical stress on the outside of a shaft rolling surface of the drive shaft is present. This generally requires steel. The stiffening member and / or the sealing plug have titanium with a low density and thus mass to keep one hand, the mass of the drive shaft with stiffening and / or sealing plug low, and on the other hand, titanium and / or carbon also ensures sufficient rigidity.

In einer Variante ist das wenigstens eine Versteifungsteil und/oder der Verschlussstopfen kraft- und/oder stoffschlüssig, z. B. mittels eines Presssitzes, mit der Antriebswelle verbunden. Abweichend hiervon kann das wenigstens eine Versteifungsteil und/oder der wenigstens eine Verschlussstopfen auch mittels einer Schraubverbindung mit der wenigstens einen Antriebswelle verbunden sein.In a variant, the at least one stiffening part and / or the closure plug force and / or cohesive, z. B. by means of a press fit, connected to the drive shaft. Notwithstanding this, the at least one stiffening part and / or the at least one sealing plug can also be connected to the at least one drive shaft by means of a screw connection.

Zweckmäßig beträgt das Volumen des Hohlraumes der Antriebswelle wenigstens 10%, 30%, 50% oder 70% des Gesamtvolumens der Antriebswelle. Das Volumen des Hohlraumes der Antriebswelle weist einen wesentlichen Anteil am Gesamtvolumen der Antriebswelle auf, so dass dadurch in einem wesentlichen Umfang die Masse der Antriebswelle mit Hilfe des Hohlraumes reduziert werden kann.Suitably, the volume of the cavity of the drive shaft is at least 10%, 30%, 50% or 70% of the total volume of the drive shaft. The volume of the cavity the drive shaft has a substantial portion of the total volume of the drive shaft, thereby substantially reducing the mass of the drive shaft by means of the cavity.

In einer weiteren Ausgestaltung ist das Volumen des Hohlraumes der Antriebswelle zu wenigstens 10%, 30%, 50%, 70%, 90% oder 98% mit dem wenigstens einen Versteifungsteil ausgefüllt. Ist das Volumen des Hohlraumes in einem wesentlichen Umfang von dem Versteifungsteil ausgefüllt und ist das Versteifungsteil auch ausreichend mit der Antriebswelle verbunden, kann dadurch mit dem Versteifungsteil die Steifigkeit der Antriebswelle in einem signifikanten Umfang erhöht werden.In a further embodiment, the volume of the cavity of the drive shaft to at least 10%, 30%, 50%, 70%, 90% or 98% filled with the at least one stiffening part. If the volume of the cavity is filled to a substantial extent by the stiffening part and the stiffening part is also sufficiently connected to the drive shaft, the rigidity of the drive shaft can be increased to a significant extent with the stiffening part.

Insbesondere ist eine Kontaktfläche zwischen der Laufrolle und der Antriebswelle mittels Kraftstoff geschmiert.In particular, a contact surface between the roller and the drive shaft is lubricated by means of fuel.

Zweckmäßig ist die wenigstens eine Laufrolle mittels wenigstens einen Gleitlagers bzw. einer Gleitlagerung in wenigstens einem Rollenschuh gelagert.Suitably, the at least one roller is mounted in at least one roller shoe by means of at least one sliding bearing or a plain bearing.

In einer weiteren Ausführungsform umgreift in einem Schnitt senkrecht zu einer Längsachse als Rotationsachse die wenigstens eine Laufrolle das Gleitlager zu mehr als 50 % die wenigstens einen Laufrolle.In a further embodiment, in a section perpendicular to a longitudinal axis as the axis of rotation, the at least one roller surrounds the plain bearing to more than 50% of the at least one roller.

Insbesondere ist das Gleitlager mittels Kraftstoff, z. B. Benzin oder Diesel, geschmiert.In particular, the plain bearing by means of fuel, for. As gasoline or diesel lubricated.

In einer weiteren Variante wird eine Exzenterwelle als eine Antriebswelle mit wenigstens einem Nocken betrachtet.In a further variant, an eccentric shaft is considered as a drive shaft with at least one cam.

Erfindungsgemäßes Hochdruckeinspritzsystem für einen Verbrennungsmotor, insbesondere für ein Kraftfahrzeug, umfassend eine Hochdruckpumpe, ein Hochdruck-Rail, vorzugsweise eine Vorförderpumpe zum Fördern eines Kraftstoffes von einem Kraftstofftank zu der Hochdruckpumpe, wobei die Hochdruckpumpe als eine in dieser Schutzrechtsanmeldung beschriebene Hochdruckpumpe ausgebildet ist.Inventive high-pressure injection system for an internal combustion engine, in particular for a motor vehicle, comprising a high pressure pump, a high pressure rail, preferably a prefeed pump for conveying a fuel from a fuel tank to the high pressure pump, wherein the high pressure pump is designed as a high pressure pump described in this patent application.

In einer weiteren Variante weist das Hochdruckeinspritzsystem eine Zumesseinheit auf, welche die von der Vorförderpumpe zu der Hochdruckpumpe geförderte Menge an Kraftstoff pro Zeiteinheit steuert oder regelt.In a further variant, the high-pressure injection system has a metering unit which controls or regulates the quantity of fuel delivered per unit time by the prefeed pump to the high-pressure pump.

Der von der Hochdruckpumpe erzeugbare Druck in dem Hochdruck-Rail liegt beispielsweise im Bereich von 1000 bis 3000 bar z. B. für Dieselmotoren oder zwischen 40 bar und 400 bar z. B. für Benzinmotoren.The producible by the high-pressure pump pressure in the high-pressure rail is, for example, in the range of 1000 to 3000 bar z. B. for diesel engines or between 40 bar and 400 bar z. B. for gasoline engines.

Kurze Beschreibung der ZeichnungenBrief description of the drawings

Im Nachfolgenden werden Ausführungsbeispiele der Erfindung unter Bezugnahme auf die beigefügten Zeichnungen näher beschrieben. Es zeigt:

Fig. 1
einen Querschnitt einer Hochdruckpumpe in einem ersten Ausführungsbeispiel
Fig. 2
einen Schnitt A-A gemäß Fig. 1 einer Laufrolle mit Rollenschuh und einer Antriebswelle,
Fig. 3
eine stark schematisierte Ansicht eines Hochdruckeinspritzsystems,
Fig. 4
einen Längsschnitt einer Antriebswelle,
Fig. 5
einen Längsschnitt der Antriebswelle in einem ersten Ausführungsbeispiel,
Fig. 6
einen Längsschnitt der Antriebswelle in einem zweiten Ausführungsbeispiel und
Fig. 7
einen Längsschnitt der Antriebswelle in einem dritten Ausführungsbeispiel.
Hereinafter, embodiments of the invention will be described in more detail with reference to the accompanying drawings. It shows:
Fig. 1
a cross section of a high-pressure pump in a first embodiment
Fig. 2
a section AA according to Fig. 1 a roller with roller shoe and a drive shaft,
Fig. 3
a highly schematic view of a high-pressure injection system,
Fig. 4
a longitudinal section of a drive shaft,
Fig. 5
a longitudinal section of the drive shaft in a first embodiment,
Fig. 6
a longitudinal section of the drive shaft in a second embodiment and
Fig. 7
a longitudinal section of the drive shaft in a third embodiment.

Ausführungsformen der ErfindungEmbodiments of the invention

In Fig. 1 ist ein Querschnitt einer Hochdruckpumpe 1 für ein Hochdruckeinspritzsystem 36 dargestellt. Die Hochdruckpumpe 1 dient dazu, Kraftstoff, z. B. Benzin oder Diesel, zu einem Verbrennungsmotor 39 unter Hochdruck zu fördern. Der von der Hochdruckpumpe 1 erzeugbare Druck liegt beispielsweise in einem Bereich zwischen 1000 und 3000 bar.In Fig. 1 a cross section of a high pressure pump 1 for a high pressure injection system 36 is shown. The high-pressure pump 1 serves to fuel, z. As gasoline or diesel, to promote an internal combustion engine 39 under high pressure. The pressure which can be generated by the high-pressure pump 1 is, for example, in a range between 1000 and 3000 bar.

Die Hochdruckpumpe 1 weist eine Antriebswelle 2 mit zwei Nocken 3 auf, die um eine Rotationsachse 26 eine Rotationsbewegung ausführt. Die Rotationsachse 26, welche auch eine Längsachse 26 der Antriebswelle 2 darstellt, liegt in der Zeichenebene von Fig. 1 und steht senkrecht auf der Zeichenebene von Fig. 2. Ein Kolben 5 ist in einem Zylinder 6 als Kolbenführung 7 gelagert, der von einem Gehäuse 8 gebildet ist. Ein Arbeitsraum 29 wird von dem Zylinder 6, dem Gehäuse 8 und dem Kolben 5 begrenzt. In den Arbeitsraum 29 mündet ein Einlasskanal 22 mit einem Einlassventil 19 und ein Auslasskanal 24 mit einem Auslassventil 20. Durch den Einlasskanal 22 strömt der Kraftstoff in den Arbeitsraum 29 ein und durch den Auslasskanal 24 strömt der Kraftstoff unter Hochdruck aus den Arbeitsraum 29 wieder aus. Das Einlassventil 19, z. B. ein Rückschlagventil, ist dahingehend ausgebildet, dass nur Kraftstoff in den Arbeitsraum 29 einströmen kann und das Auslassventil 20, z. B. ein Rückschlagventil, ist dahingehend ausgebildet, dass nur Kraftstoff aus dem Arbeitsraum 29 ausströmen kann. Das Volumen des Arbeitsraumes 29 wird aufgrund einer oszillierenden Hubbewegung des Kolbens 5 verändert. Der Kolben 5 stützt sich mittelbar auf der Antriebswelle 2 ab. Am Ende des Kolbens 5 bzw. Pumpenkolbens 5 ist ein Rollenschuh 9 mit einer Laufrolle 10 befestigt. Die Laufrolle 10 kann dabei eine Rotationsbewegung ausführen, deren Rotationsachse 25 in der Zeichenebene gemäß Fig. 1 liegt und senkrecht auf der Zeichenebene von Fig. 2 steht. Die Antriebswelle 2 mit dem wenigstens einen Nocken 3 weist eine Wellen-Rollfläche 4 und die Laufrolle 10 eine Rollen-Rollfläche 11 auf.The high-pressure pump 1 has a drive shaft 2 with two cams 3, which performs a rotational movement about a rotation axis 26. The axis of rotation 26, which also represents a longitudinal axis 26 of the drive shaft 2, lies in the plane of the drawing Fig. 1 and is perpendicular to the plane of Fig. 2 , A piston 5 is mounted in a cylinder 6 as a piston guide 7, which is formed by a housing 8. A working chamber 29 is bounded by the cylinder 6, the housing 8 and the piston 5. Into the working space 29 opens an inlet channel 22 with an inlet valve 19 and an outlet channel 24 with an outlet valve 20. Through the inlet channel 22, the fuel flows into the working space 29 and through the outlet channel 24, the fuel flows out of the working space 29 under high pressure. The inlet valve 19, z. As a check valve, is designed to the effect that only fuel can flow into the working space 29 and the exhaust valve 20, z. B. a check valve is designed to the effect that only fuel can flow out of the working space 29. The volume of the working chamber 29 is changed due to an oscillating stroke movement of the piston 5. The piston 5 is indirectly supported on the drive shaft 2 from. At the end of the piston 5 or pump piston 5, a roller shoe 9 is attached to a roller 10. The roller 10 can perform a rotational movement, the axis of rotation 25 in the plane according to Fig. 1 lies and perpendicular to the plane of Fig. 2 stands. The drive shaft 2 with the at least one cam 3 has a shaft rolling surface 4 and the roller 10 has a roller rolling surface 11.

Die Rollen-Lauffläche 11 der Laufrolle 10 rollt sich an einer Kontaktfläche 12 auf der Wellen-Rollfläche 4 der Antriebswelle 2 mit den beiden Nocken 3 ab. Der Rollenschuh 9 ist in einer von dem Gehäuse 8 gebildeten Rollenschuhlagerung als Gleitlager gelagert. Eine Feder 27 bzw. Spiralfeder 27 als elastisches Element 28, die zwischen dem Gehäuse 8 und dem Rollenschuh 9 eingespannt ist, bringt auf den Rollenschuh 9 eine Druckkraft auf, so dass die Rollen-Rollfläche 11 der Laufrolle 10 in ständigen Kontakt mit der Wellen-Rollfläche 4 der Antriebswelle 2 steht. Der Rollenschuh 9 und der Kolben 5 führen damit gemeinsam eine oszillierende Hubbewegung aus.The roller-running surface 11 of the roller 10 rolls on a contact surface 12 on the shaft rolling surface 4 of the drive shaft 2 with the two cams 3 from. The roller shoe 9 is mounted in a roller shoe bearing formed by the housing 8 as a sliding bearing. A spring 27 or spiral spring 27 as an elastic element 28, which is clamped between the housing 8 and the roller shoe 9 is, brings on the roller shoe 9 a compressive force, so that the roller rolling surface 11 of the roller 10 is in constant contact with the shaft rolling surface 4 of the drive shaft 2. The roller shoe 9 and the piston 5 thus carry out together an oscillating stroke movement.

In Fig. 4 ist ein Beispiel einer Antriebswelle 2 in einem Längsschnitt dargestellt. In die Antriebswelle 2 aus Stahl sind zwei Hohlräume 17 als axiale Bohrung 38 eingearbeitet. Aufgrund dieser beiden Hohlräume 17 weist somit die Antriebswelle 2 eine deutlich reduzierte Masse auf und andererseits ist die Steifigkeit der Antriebswelle 2 aus Stahl noch ausreichend groß, da die Bohrungen 38 im Querschnitt noch einen ausreichend großen Anteil der Antriebswelle 2 aus Stahl belassen. Zwei axiale Enden 40 der Antriebswelle 2 sind dabei außerhalb eines nicht dargestellten Schmierraumes der Hochdruckpumpe 1 angeordnet, so dass dadurch kein innerhalb des Schmierraumes sich befindlicher Kraftstoff in die beiden Bohrungen 38 einströmen kann.In Fig. 4 an example of a drive shaft 2 is shown in a longitudinal section. In the drive shaft 2 made of steel, two cavities 17 are incorporated as an axial bore 38. Because of these two cavities 17 thus has the drive shaft 2 a significantly reduced mass and on the other hand, the rigidity of the drive shaft 2 made of steel is still sufficiently large, since the holes 38 in cross section still leave a sufficiently large proportion of the drive shaft 2 made of steel. Two axial ends 40 of the drive shaft 2 are arranged outside of a not shown lubrication chamber of the high-pressure pump 1, so that thereby no fuel located within the lubricant space can flow into the two bores 38.

In Fig. 5 ist ein erstes Ausführungsbeispiel der Antriebswelle 2 dargestellt. Die Antriebswelle 2 weist eine axiale Bohrung 38 als Hohlraum 17 auf und an einem in Fig. 5 links dargestellten axialen Ende 40 ist der Hohlraum 17 fluiddicht von einem Verschlussstopfen 16 aus Titan oder Karbon verschlossen. Der Verschlussstopfen 16 bewirkt, dass in den Hohlraum 17 kein Kraftstoff aus einem Schmierraum der Hochdruckpumpe 1 einströmen kann. Dadurch ist innerhalb des Hohlraumes 17 abgesehen von dem Verschlussstopfen 16 Luft angeordnet und die Antriebswelle 2 weist dadurch eine geringe Masse auf.In Fig. 5 a first embodiment of the drive shaft 2 is shown. The drive shaft 2 has an axial bore 38 as a cavity 17 and at an in Fig. 5 On the left axial end 40 shown, the cavity 17 is closed fluid-tight by a closure plug 16 made of titanium or carbon. The closure plug 16 has the effect that no fuel can flow into the cavity 17 from a lubricant space of the high-pressure pump 1. As a result, 16 air is disposed within the cavity 17 apart from the sealing plug and the drive shaft 2 thereby has a low mass.

In Fig. 6 ist ein zweites Ausführungsbeispiel der Antriebswelle 2 dargestellt. Die Antriebswelle 2 aus Stahl weist eine axiale Bohrung 38 als Hohlraum 17 auf und dieser Hohlraum 17 ist im Wesentlichen mit einem Versteifungsteil 15 aus Titan befüllt. Bei der Herstellung der Antriebswelle 2 aus Stahl wird somit zunächst die axiale Bohrung 38 spanabhebend, z. B. mittels Bohren, eingearbeitet und anschließend der Verschlussstopfen 16 in diese Bohrung 38 eingeführt und dabei kraftschlüssig mittels eines Presssitzes mit der Antriebswelle 2 aus Stahl verbunden. Aufgrund der Größe der Bohrung 38 weist die Antriebswelle 2 ohne dem Versteifungsteil 5 aus Titan keine ausreichende Steifigkeit auf. Mittels des Versteifungsteiles 15 aus Titan kann die Steifigkeit der Antriebswelle 2 wesentlich erhöht werden. Titan weist dabei in vorteilhafter Weise einerseits eine geringe Masse auf und andererseits auch eine ausreichend große Steifigkeit, um die Steifigkeit der Antriebswelle 2 zu erhöhen. Außenseitig besteht somit die Antriebswelle 2, insbesondere an der Wellen-Rollfläche 4 zur Auflage der Laufrolle 10, aus Stahl, so dass dadurch die Antriebswelle 2 den mechanischen Beanspruchungen aufgrund des Abrollens der Laufrolle 10 an der Wellen-Rollfläche 4 auf Dauer standhalten kann.In Fig. 6 a second embodiment of the drive shaft 2 is shown. The drive shaft 2 made of steel has an axial bore 38 as a cavity 17 and this cavity 17 is substantially filled with a stiffening member 15 made of titanium. In the production of the drive shaft 2 made of steel thus first the axial bore 38 is machined, z. B. by means of drilling, incorporated and then the closure plug 16 inserted into this bore 38 and thereby positively connected by means of a press fit with the drive shaft 2 made of steel. Due to the size of the bore 38, the drive shaft 2 without the stiffening part 5 made of titanium does not have sufficient rigidity. By means of the stiffening member 15 made of titanium, the rigidity of the drive shaft. 2 be increased significantly. In this case, titanium advantageously has on the one hand a low mass and on the other hand also a sufficiently high rigidity in order to increase the rigidity of the drive shaft 2. On the outside, therefore, there is the drive shaft 2, in particular on the shaft rolling surface 4 for supporting the roller 10, made of steel, so that thereby the drive shaft 2 can withstand the mechanical stresses due to the rolling of the roller 10 on the shaft rolling surface 4 in the long term.

In Fig. 7 ist ein drittes Ausführungsbeispiel der Antriebswelle 2 dargestellt. Im Nachfolgenden werden im Wesentlichen nur die Unterschiede zu dem zweiten Ausführungsbeispiel gemäß Fig. 6 beschrieben. Das Versteifungsteil 15 ist als eine Hülse mit einem Versteifungsteilhohlraum 14 ausgebildet und an einem in Figur links dargestellten axialen Ende 40 der Antriebswelle 2 ist dieser Versteifungsteilhohlraum 14 des Versteifungsteiles 15 von einem Verschlussstopfen 16 verschlossen. Dadurch kann in den Versteifungsteilhohlraum 14 kein Kraftstoff aus dem nicht dargestellten Schmierraum der Hochdruckpumpe 1 einströmen. Das Versteifungsteil 15 aus Titan weist eine geringere Steifigkeit als das Versteifungsteil 15 in Fig. 6 auf, da das Versteifungsteil 15 in Fig. 6 aus einem Vollmaterial besteht und das in Fig. 7 in dem dritten Ausführungsbeispiel eingesetzte Versteifungsteil 15 als eine Hülse mit einem Versteifungsteilhohlraum 14 ausgebildet ist. Das Versteifungsteil 15 in Fig. 7 kann dadurch nur eine geringere Erhöhung der Steifigkeit der Antriebswelle 2 zur Verfügung stellen als das in Fig. 6 dargestellte Versteifungsteil 15. Dies ist ausreichend, da in den in Fig. 7 dargestellten dritten Ausführungsbeispiel der Antriebswelle 2 die Antriebswelle 2 entweder eine geringere Steifigkeit erfordert und/oder aufgrund der Ausbildung der Bohrung 38 mit einem geringeren Durchmesser die Antriebswelle 2 selbst eine ausreichende Steifigkeit aufweist und diese nur geringfügig mit dem Versteifungsteil 15 als Hülse gemäß der Darstellung in Fig. 7 erhöht werden muss, um den Anforderungen hinsichtlich der Steifigkeit der Antriebswelle 2 zu genügen.In Fig. 7 a third embodiment of the drive shaft 2 is shown. In the following, only the differences from the second embodiment will be essentially according to FIG Fig. 6 described. The stiffening member 15 is formed as a sleeve with a stiffening member cavity 14 and at an axial end 40 of the drive shaft 2 shown in Figure left this stiffening member cavity 14 of the stiffening member 15 is closed by a sealing plug 16. As a result, no fuel can flow from the lubricant space of the high-pressure pump 1, which is not shown, into the stiffening part cavity 14. The stiffening part 15 made of titanium has a lower rigidity than the stiffening part 15 in FIG Fig. 6 on, since the stiffening part 15 in Fig. 6 made of a solid material and that in Fig. 7 In the third embodiment used stiffening member 15 is formed as a sleeve with a stiffening member cavity 14. The stiffening part 15 in Fig. 7 can thereby provide only a smaller increase in the rigidity of the drive shaft 2 available as in Fig. 6 shown stiffening part 15. This is sufficient because in the in Fig. 7 illustrated third embodiment of the drive shaft 2, the drive shaft 2 either requires less rigidity and / or due to the formation of the bore 38 with a smaller diameter, the drive shaft 2 itself has sufficient rigidity and this only slightly with the stiffening member 15 as a sleeve as shown in FIG Fig. 7 must be increased to meet the requirements for the rigidity of the drive shaft 2.

In Fig. 3 ist in stark schematisierter Darstellung das Hochdruckeinspritzsystem 36 für ein Kraftfahrzeug (nicht dargestellt) abgebildet mit einem Hochdruck-Rail 30 oder einem Kraftstoffverteilerrohr 31. Von dem Hochdruck-Rail 30 wird der Kraftstoff mittels Ventilen (nicht dargestellt) in den Verbrennungsraum des Verbrennungsmotors 39 eingespritzt. Eine Vorförderpumpe 35 fördert Kraftstoff von einem Kraftstofftank 32 durch eine Kraftstoffleitung 33 zu der Hochdruckpumpe 1 gemäß dem obigen Ausführungsbeispiel. Die Hochdruckpumpe 1 und die Vorförderpumpe 35 werden dabei von der Antriebswelle 2 angetrieben. Die Antriebswelle 2 ist mit einer Kurbelwelle des Verbrennungsmotors 39 gekoppelt. Das Hochdruck-Rail 30 dient - wie bereits beschrieben - dazu, den Kraftstoff in den Verbrennungsraum des Verbrennungsmotors 39 einzuspritzen. Der von der Vorförderpumpe 35 geförderte Kraftstoff wird durch die Kraftstoffleitung 33 zu der Hochdruckpumpe 1 geleitet. Der von der Hochdruckpumpe 1 nicht benötigte Kraftstoff wird dabei durch eine Kraftstoffrücklaufleitung 34 wieder in den Kraftstofftank 32 zurückgeleitet. Eine Zumesseinheit 37 steuert und/oder regelt die der Hochdruckpumpe 1 zugeleitete Menge an Kraftstoff, so dass in einer weiteren Ausgestaltung auf die Kraftstoffrücklaufleitung 34 verzichtet werden kann (nicht dargestellt).In Fig. 3 is a highly schematic representation of the high-pressure injection system 36 for a motor vehicle (not shown) imaged with a high-pressure rail 30 or a fuel rail 31. From the high-pressure rail 30, the fuel is injected by means of valves (not shown) in the combustion chamber of the engine 39. A prefeed pump 35 delivers fuel from a fuel tank 32 through a fuel pipe 33 to the high-pressure pump 1 according to the above embodiment. The high-pressure pump 1 and the prefeed pump 35 are driven by the drive shaft 2. The drive shaft 2 is coupled to a crankshaft of the engine 39. The high pressure rail 30 serves - as already described - to inject the fuel into the combustion chamber of the internal combustion engine 39. The funded by the feed pump 35 fuel is passed through the fuel line 33 to the high-pressure pump 1. The fuel not required by the high-pressure pump 1 is thereby returned to the fuel tank 32 through a fuel return line 34. A metering unit 37 controls and / or regulates the quantity of fuel supplied to the high-pressure pump 1, so that the fuel return line 34 can be dispensed with in a further embodiment (not shown).

Die Einzelheiten der verschiedenen Ausführungsbeispiele können miteinander kombiniert werden, sofern nichts Gegenteiliges erwähnt wird.The details of the various embodiments may be combined with each other unless otherwise specified.

Insgesamt betrachtet sind mit der erfindungsgemäßen Hochdruckpumpe 1 und dem erfindungsgemäßen Hochdruckeinspritzsystem 36 wesentliche Vorteile verbunden. Die Antriebswelle 2 aus Stahl weist eine Bohrung 38 als Hohlraum 17 auf, so dass dadurch die Antriebswelle 2 eine reduzierte Masse aufweist. Zur Erhöhung der Steifigkeit der Antriebswelle 2 kann innerhalb des Hohlraumes 17 ein Versteifungsteil 15, z. B. aus Titan, angeordnet sein, um dadurch einerseits die Steifigkeit der Antriebswelle 2 zu erhöhen, bei einer geringen Masse der Antriebswelle 2 aufgrund der geringen Dichte des Versteifungsteiles 15, und andererseits an der Wellen-Rollfläche 4 auch eine ausreichende mechanische Verschleißfestigkeit zum Abrollen der Laufrolle 10 zu erhalten.Overall, significant advantages are associated with the high-pressure pump 1 according to the invention and the high-pressure injection system 36 according to the invention. The drive shaft 2 made of steel has a bore 38 as a cavity 17, so that thereby the drive shaft 2 has a reduced mass. To increase the rigidity of the drive shaft 2 can within the cavity 17, a stiffening member 15, z. Example of titanium, to thereby increase the one hand, the rigidity of the drive shaft 2, at a low mass of the drive shaft 2 due to the low density of the stiffening member 15, and on the other hand on the shaft rolling surface 4, a sufficient mechanical wear resistance for rolling the To get roller 10.

Claims (9)

  1. High-pressure pump (1) for conveying a fluid, in particular fuel, for example diesel, comprising
    - a drive shaft (2) with at least one cam (3),
    - at least one piston (5),
    - at least one cylinder (6) for the mounting of the at least one piston (5),
    - wherein the at least one piston (5) is supported indirectly by means of at least one roller (10) on the drive shaft (2) with the at least one cam (3), such that the at least one piston (5) can perform a translational movement owing to a rotational movement of the drive shaft (2),
    characterized in that
    the drive shaft (2) with the at least one cam (3) is formed as a hollow shaft (2) with a cavity (17) in order to reduce the mass of the drive shaft (2), and at least one stiffening part (15) is arranged in the cavity (17) in order to increase the stiffness of the drive shaft (2).
  2. High-pressure pump according to Claim 1, characterized in that
    the cavity (17) is closed off by means of a closure plug (16) in the region of one axial end (40) of the drive shaft (2).
  3. High-pressure pump according to Claim 1 or 2, characterized in that
    the at least one stiffening part (15) and/or the closure plug (16) has a lower density, preferably a density that is lower by at least 10%, 30% or 50%, than the drive shaft (2).
  4. High-pressure pump according to one or more of the preceding claims,
    characterized in that
    the drive shaft (2) is composed at least partially of metal, and the at least one stiffening part (15) and/or the closure plug (16) is composed at least partially of titanium and/or carbon.
  5. High-pressure pump according to one or more of the preceding claims,
    characterized in that
    the at least one stiffening part (15) and/or the closure plug (16) is connected in non-positively locking and/or cohesive fashion to the drive shaft (2).
  6. High-pressure pump according to one or more of the preceding claims,
    characterized in that
    the volume of the cavity (17) of the drive shaft (2) amounts to at least 10%, 30%, 50% or 70% of the total volume of the drive shaft (2).
  7. High-pressure pump according to one or more of the preceding claims,
    characterized in that
    at least 10%, 30%, 50%, 70%, 90% or 98% of the volume of the cavity (17) of the drive shaft (2) is filled by the at least one stiffening part (15).
  8. High-pressure pump according to one or more of the preceding claims,
    characterized in that
    a contact surface between the roller (10) and the drive shaft (2) is lubricated by means of fuel.
  9. High-pressure injection system (36) for an internal combustion engine (39), comprising
    - a high-pressure pump (1),
    - a high-pressure rail (30),
    - a predelivery pump (35) for delivering a fuel from a fuel tank (32) to the high-pressure pump (1),
    characterized in that
    the high-pressure pump (1) is designed according to one or more of the preceding claims.
EP13714617.1A 2012-05-16 2013-04-02 High pressure pump Not-in-force EP2850318B1 (en)

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DE102012208189A DE102012208189A1 (en) 2012-05-16 2012-05-16 high pressure pump
PCT/EP2013/056859 WO2013170997A1 (en) 2012-05-16 2013-04-02 High-pressure pump

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EP2850318A1 EP2850318A1 (en) 2015-03-25
EP2850318B1 true EP2850318B1 (en) 2017-09-20

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EP (1) EP2850318B1 (en)
CN (1) CN104285061B (en)
DE (1) DE102012208189A1 (en)
IN (1) IN2014DN06883A (en)
WO (1) WO2013170997A1 (en)

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DE102015220870A1 (en) 2015-10-26 2017-04-27 Robert Bosch Gmbh high pressure pump

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Also Published As

Publication number Publication date
WO2013170997A1 (en) 2013-11-21
EP2850318A1 (en) 2015-03-25
IN2014DN06883A (en) 2015-05-22
DE102012208189A1 (en) 2013-11-21
CN104285061B (en) 2018-10-12
CN104285061A (en) 2015-01-14

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