EP2510235B1 - Pump arrangement - Google Patents

Pump arrangement Download PDF

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Publication number
EP2510235B1
EP2510235B1 EP10767994.6A EP10767994A EP2510235B1 EP 2510235 B1 EP2510235 B1 EP 2510235B1 EP 10767994 A EP10767994 A EP 10767994A EP 2510235 B1 EP2510235 B1 EP 2510235B1
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EP
European Patent Office
Prior art keywords
pump
gearwheel
shaft
pressure pump
pump shaft
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Not-in-force
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EP10767994.6A
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German (de)
French (fr)
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EP2510235A1 (en
Inventor
Arnold Gente
Matthias Greiner
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication of EP2510235A1 publication Critical patent/EP2510235A1/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
    • F04B23/00—Pumping installations or systems
    • F04B23/04—Combinations of two or more pumps
    • F04B23/08—Combinations of two or more pumps the pumps being of different types
    • F04B23/10—Combinations of two or more pumps the pumps being of different types at least one pump being of the reciprocating positive-displacement type
    • F04B23/103—Combinations of two or more pumps the pumps being of different types at least one pump being of the reciprocating positive-displacement type being a radial piston pump
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M39/00—Arrangements of fuel-injection apparatus with respect to engines; Pump drives adapted to such arrangements
    • F02M39/005—Arrangements of fuel feed-pumps with respect to fuel injection apparatus
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C11/00—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations
    • F04C11/005—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations of dissimilar working principle
    • F04C11/006—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations of dissimilar working principle having complementary function
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/0057—Driving elements, brakes, couplings, transmission specially adapted for machines or pumps
    • F04C15/0061—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions
    • F04C15/0073—Couplings between rotors and input or output shafts acting by interengaging or mating parts, i.e. positive coupling of rotor and shaft
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/10—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2210/00—Fluid
    • F04C2210/10—Fluid working
    • F04C2210/1044—Fuel

Definitions

  • the invention relates to a pump arrangement, in particular a pump arrangement with a high pressure pump and an external gear pump. Specifically, the invention relates to the field of fuel injection systems of air compressing, self-igniting internal combustion engines.
  • the known pump arrangement has a pump housing for a radial piston pump, a housing part for a gear pump and a closure plate.
  • a cross-plate clutch is provided which drives a drive shaft of the radial piston pump with a shaft of the gear pump drives.
  • a sliding element and a fluid machine are known.
  • a lubricant element is provided on the coupling.
  • an electric oil pump is known.
  • wear of the coupling is reduced by lubrication.
  • From the US 5,542,832 is a fluid compressor with an Oldam coupling known.
  • an Oldam ring of the Oldam clutch is made of ceramic material. To prevent excessive wear of the Oldam ring, a contact load is reduced.
  • the pump assembly according to the invention with the features of claim 1 has the advantage that an axial compensation of the coupling between the high-pressure pump shaft and the gear pump shaft or the gear over the life can be ensured.
  • the gear pump is driven by the coupling of the high pressure pump shaft.
  • the high pressure pump shaft serves as a drive shaft.
  • This wear is amplified by poorly lubricating fuels and can therefore lead to failure of the pump assembly.
  • This is the case especially in the design of a conventional clutch made of hard metal, since this is heavily incorporated into the high-pressure pump shaft, so that the required axial mobility of the clutch for clearance compensation is no longer given and thus to break the clutch or a component of the interface between the high pressure pump and the gear pump can come.
  • the coupling allows axial play between the high-pressure pump shaft and the gear pump shaft. Furthermore, it is advantageous that the high-pressure pump shaft has a two-fold, that the two-flat has a first side surface and a second side surface facing away from the first side surface, that the first side surface has a sacrificial layer and that the second side surface has a sacrificial layer.
  • the sacrificial layers in each case a sacrificial surface is formed.
  • a thickness of the respective sacrificial layer is predetermined with respect to an expected life of the pump assembly. Thus, the sacrificial layer is large enough so that over the life of a complete wear of the sacrificial surface does not occur.
  • the two-face of the high pressure pump shaft at least partially engages in a groove of the gear pump shaft.
  • the coupling can also be realized by a differently designed drive stub of the high-pressure pump shaft, which is provided with at least one sacrificial surface.
  • Fig. 1 shows a pump assembly 1 in a schematic, partial, axial sectional view according to an embodiment of the invention.
  • the pump assembly 1 can be used in particular for fuel injection systems of air-compressing, self-igniting internal combustion engines.
  • a preferred use of the pump assembly 1 is for a fuel injection system having a fuel rail which stores diesel fuel under high pressure.
  • the pump assembly 1 is used in this case for conveying fuel to such Fuel rail.
  • the pump assembly 1 according to the invention is also suitable for other applications.
  • the pump arrangement 1 has a high-pressure pump 2 and a gear pump 3.
  • the high-pressure pump 2 has a housing 4.
  • the gear pump 3 has a housing part 5, which is designed for example as a cover 5.
  • the housing part 5 is suitably connected to the housing 4 of the high-pressure pump 2. In this case, there is a separation between a region of the high-pressure pump 2 and a region of the gear pump 3 through a part 6 of the housing 4.
  • the high-pressure pump 2 has a high-pressure pump shaft 7, which is mounted in a suitable manner in the housing 4.
  • the gear pump 3 has a gear pump shaft 8 which is mounted in a bore 9 of the housing part 5.
  • gear pump shaft 8 designed as a drive gear 10 gear 10 is arranged and fixed.
  • gear 10 may be pressed onto the gear pump shaft 8.
  • the gear pump 3 has a further gear 11, which is in operative connection with the gear 10.
  • the two gears 10, 11 mesh in a manner that a pumping action is achieved.
  • the high-pressure pump shaft 7 serves as a drive shaft which, in addition to pump elements of the high-pressure pump 2, also drives the gear pump shaft 8 and thus the gear pump 3.
  • the gear pump 3 serves as a prefeed pump for the high pressure pump. 2
  • the coupling 12 comprises a coupling part 13 and a coupling part 14.
  • the coupling part 14 is formed in this embodiment on the high-pressure pump shaft 7 in the form of a drive stub 14.
  • the coupling part 14 is designed in the form of a double salmon.
  • the coupling part 14 can also be in operative connection with the high-pressure pump shaft 7 in a suitable manner and, in particular, can be connected to the high-pressure pump shaft 7 in a form-fitting or material-locking manner.
  • the coupling part 13 may be configured as part of the gear pump shaft 8.
  • the coupling part 13 may also be designed as a separate coupling piece 13, which is suitably in operative connection with the gear pump shaft 8 and in particular is positively or materially connected to the gear pump shaft 8.
  • the coupling piece 13 may also be arranged directly on the gear 10, so that the gear pump shaft 8 can be omitted and can be replaced by a bearing stub 8. It is advantageous that the gear 10 is mounted on the bearing stub 8 in the bore 9 of the housing part 5 of the gear pump 3 and that the housing part 5 of the gear pump 3 at least indirectly with the housing 4 of the high-pressure pump. 2 connected is.
  • the coupling part 13 has in this embodiment, a groove 15 which is oriented in the mounted state of the coupling part 13 perpendicular to a longitudinal axis 16 of the pump assembly 1.
  • the high-pressure pump shaft 7 and the gear pump shaft 8 are aligned on the longitudinal axis 16 and rotate in operation at least approximately about the longitudinal axis 16.
  • sacrificial layers 17, 18 are provided on the coupling part 14.
  • the sacrificial layer 17 is applied to a first side surface 19 of the coupling part 14.
  • the sacrificial layer 18 is applied to a second side surface 20 of the coupling part 14.
  • the two side surfaces 19, 20 facing away from each other.
  • the sacrificial layers 17, 18 in each case partially cover the side surfaces 19, 20.
  • the sacrificial layer 17 forms a sacrificial surface 21.
  • the sacrificial layer 18 forms a sacrificial surface 22.
  • the coupling 12 therefore has the sacrificial layers 17, 18 with the sacrificial surfaces 21, 22.
  • the coupling 12 allows a certain axial clearance between the high-pressure pump shaft 7 and the gear pump shaft 8. In operation, therefore, there are relative movements between the coupling parts 13, 14 of the clutch 12.
  • the sacrificial layers 17, 18 are adapted to the material of the coupling part 13. Due to the relative movement, wear occurs that at least essentially affects the sacrificial surfaces 21, 22.
  • Fig. 2 shows the high pressure pump shaft 7 of the high pressure pump 2 in Fig. 1 illustrated pump assembly 1 in a partial, schematic representation.
  • a thickness 23 of the sacrificial layer 17 is set so large that over the life of a complete wear of the sacrificial surface 21 does not occur.
  • a thickness 24 of the sacrificial layer 18 is set so large that over the life of a complete wear of the sacrificial surface 22 does not occur.
  • the axial compensation of the clutch 12 is maintained over the life of the gear pump 3.
  • the components of the gear pump 3 can be used here at least substantially unchanged.
  • an extension of the life of the pump assembly 1 with the high-pressure pump 2 and the gear pump 3 is possible without or with little design changes.

Description

Stand der TechnikState of the art

Die Erfindung betrifft eine Pumpenanordnung, insbesondere eine Pumpenanordnung mit einer Hochdruckpumpe und einer Außenzahnradpumpe. Speziell betrifft die Erfindung das Gebiet der Brennstoffeinspritzanlagen von luftverdichtenden, selbstzündenden Brennkraftmaschinen.The invention relates to a pump arrangement, in particular a pump arrangement with a high pressure pump and an external gear pump. Specifically, the invention relates to the field of fuel injection systems of air compressing, self-igniting internal combustion engines.

Aus der DE 197 36 160 A1 ist eine Pumpenanordnung zur Kraftstoffhochdruckversorgung bei Einspritzsystemen von Brennkraftmaschinen bekannt. Die bekannte Pumpenanordnung weist ein Pumpengehäuse für eine Radialkolbenpumpe, ein Gehäuseteil für eine Zahnradpumpe sowie eine Abschlussplatte auf. Dabei ist eine Kreuzscheibenkupplung vorgesehen, die eine Antriebswelle der Radialkolbenpumpe mit einer Welle der Zahnradpumpe antriebsverbindet.From the DE 197 36 160 A1 a pump arrangement for high-pressure fuel supply in injection systems of internal combustion engines is known. The known pump arrangement has a pump housing for a radial piston pump, a housing part for a gear pump and a closure plate. In this case, a cross-plate clutch is provided which drives a drive shaft of the radial piston pump with a shaft of the gear pump drives.

Die aus der DE 197 36 160 A1 bekannte Pumpenanordnung hat den Nachteil, dass ein abrasiver Verschleiß in der Kupplung auftritt. Auch bei einer denkbaren Verbesserung der Reibpartner, insbesondere des Antriebswellenmaterials oder des Kupplungsmaterials, kommt es an anderen Stellen, insbesondere an der Zahnradlagerung der Zahnradpumpe, zu hohen Belastungen.The from the DE 197 36 160 A1 known pump assembly has the disadvantage that an abrasive wear occurs in the coupling. Even with a conceivable improvement of the friction partners, in particular the drive shaft material or the coupling material, it comes in other places, especially on the gear storage of the gear pump, to high loads.

Aus der EP 1 803 939 A1 sind ein Gleitelement und eine Fluidmaschine bekannt. Hierbei ist ein Gleitmittelelement an der Kupplung vorgesehen. Aus der US 200610140805 A1 ist eine elektrische Ölpumpe bekannt. Hierbei wird ein Verschleiß der Kupplung durch eine Schmierung verringert. Aus der US 5,542,832 ist ein Fluidkompressor mit einer Oldam-Kupplung bekannt. Hierbei ist ein Oldam-Ring der Oldam-Kupplung aus keramischem Material hergestellt. Um einen übermäßigen Verschleiß des Oldam-Ringes zu verhindern, wird eine Kontaktbelastung verringert.From the EP 1 803 939 A1 For example, a sliding element and a fluid machine are known. Here, a lubricant element is provided on the coupling. From the US 200610140805 A1 is known an electric oil pump. In this case, wear of the coupling is reduced by lubrication. From the US 5,542,832 is a fluid compressor with an Oldam coupling known. Here, an Oldam ring of the Oldam clutch is made of ceramic material. To prevent excessive wear of the Oldam ring, a contact load is reduced.

Offenbarung der ErfindungDisclosure of the invention

Die erfindungsgemäße Pumpenanordnung mit den Merkmalen des Anspruchs 1 hat den Vorteil, dass ein Axialausgleich der Kupplung zwischen der Hochdruckpumpenwelle und der Zahnradpumpenwelle beziehungsweise dem Zahnrad über die Lebensdauer gewährleistet werden kann.The pump assembly according to the invention with the features of claim 1 has the advantage that an axial compensation of the coupling between the high-pressure pump shaft and the gear pump shaft or the gear over the life can be ensured.

Durch die in den Unteransprüchen aufgeführten Maßnahmen sind vorteilhafte Weiterbildungen der im Anspruch 1 angegebenen Pumpenanordnung möglich.The measures listed in the dependent claims advantageous developments of the pump arrangement specified in claim 1 are possible.

Speziell bei Hochdruckpumpen für Common-Rail-Anwendungen ist es vorteilhaft, dass die Zahnradpumpe über die Kupplung von der Hochdruckpumpenwelle angetrieben wird. Die Hochdruckpumpenwelle dient hierbei als Antriebswelle. Bei der Übertragung des Antriebsmoments von der Hochdruckpumpenwelle auf die Zahnradpumpenwelle entsteht durch Relativbewegungen von der Kupplung zur Antriebswelle ein abrasiver Verschleiß. Dieser Verschleiß wird durch schlecht schmierende Brennstoffe verstärkt und kann daher zum Ausfall der Pumpenanordnung führen. Dies ist speziell bei der Ausgestaltung einer herkömmlichen Kupplung aus Hartmetall der Fall, da sich diese stark in die Hochdruckpumpenwelle einarbeitet, so dass die erforderliche axiale Beweglichkeit der Kupplung zum Spielausgleich nicht mehr gegeben ist und es somit zum Bruch der Kupplung oder eines Bauteils der Schnittstelle zwischen der Hochdruckpumpe und der Zahnradpumpe kommen kann. Speziell bei hohen Drehzahlen und schlecht schmierenden Brennstoffen ist solch ein abrasiver Verschleiß so groß, dass eine herkömmliche Kupplung zu stark in die Antriebswelle einläuft und die Gefahr eines Bruches der Kupplung besteht. Durch Verbesserung der Reibpartner, insbesondere des Antriebswellenmaterials oder des Kupplungsmaterials und der damit erfolgenden Verminderung des abrasiven Verschleißes wird die Belastung einer Zahnradlagerung der Zahnradpumpe zu groß, so dass sich beispielsweise ein Lagerpin des Primärzahnrades der Zahnradpumpe zu stark verbiegt. Hierbei kann es zum Einlaufen der Zahnräder in ein Gehäuseteil der Zahnradpumpe kommen. Somit wird bei Verringerung des abrasiven Verschleißes die Problematik an eine andere Stelle der Konstruktion der Pumpenanordnung verschoben.Especially in high pressure pumps for common rail applications, it is advantageous that the gear pump is driven by the coupling of the high pressure pump shaft. The high pressure pump shaft serves as a drive shaft. In the transmission of the drive torque from the high pressure pump shaft to the gear pump shaft is formed by relative movements of the clutch to the drive shaft abrasive wear. This wear is amplified by poorly lubricating fuels and can therefore lead to failure of the pump assembly. This is the case especially in the design of a conventional clutch made of hard metal, since this is heavily incorporated into the high-pressure pump shaft, so that the required axial mobility of the clutch for clearance compensation is no longer given and thus to break the clutch or a component of the interface between the high pressure pump and the gear pump can come. Especially at high speeds and poorly lubricating fuels such abrasive wear is so great that a conventional clutch runs too much into the drive shaft and there is a risk of breakage of the clutch. By improving the friction partners, in particular the drive shaft material or the coupling material and thus reducing the abrasive wear, the load of a gear bearing of the gear pump is too large, so that, for example, a Lagerpin the primary gear of the gear pump bends too much. This can lead to the running of the gears in a housing part of the gear pump. Thus, the problem is shifted to a different location of the construction of the pump assembly when reducing the abrasive wear.

Durch die Opferfläche der Kupplung wird weiterhin ein abrasiver Verschleiß ermöglicht. Somit wird zum einen ein Einlaufen der Hochdruckpumpenwelle in die Kupplung verhindert und zum anderen eine erhöhte Belastung an anderen Stellen der Pumpenanordnung, insbesondere an der Zahnradlagerung, verhindert.Due to the sacrificial surface of the coupling, an abrasive wear is still possible. Thus, on the one hand prevents the high-pressure pump shaft from entering the coupling and, on the other hand, prevents increased stress at other points of the pump arrangement, in particular at the gear bearing.

Vorteilhaft ist es deshalb, dass die Kupplung ein axiales Spiel zwischen der Hochdruckpumpenwelle und der Zahnradpumpenwelle ermöglicht. Ferner ist es vorteilhaft, dass die Hochdruckpumpenwelle einen Zweiflach aufweist, dass der Zweiflach eine erste Seitenfläche und eine von der ersten Seitenfläche abgewandte zweite Seitenfläche aufweist, dass die erste Seitenfläche eine Opferschicht aufweist und dass die zweite Seitenfläche eine Opferschicht aufweist. Durch die Opferschichten ist hierbei jeweils eine Opferfläche gebildet. Eine Stärke der jeweiligen Opferschicht ist in Bezug auf eine erwartete Lebensdauer der Pumpenanordnung vorgegeben. Somit ist die Opferschicht groß genug, so dass über die Lebensdauer ein vollständiger Verschleiß der Opferfläche nicht vorkommt. Ein Axialausgleich der Kupplung bleibt somit über die Lebensdauer der Pumpenanordnung, insbesondere der Zahnradpumpe, erhalten, da die Kupplung sich am Zweiflach nicht festfressen kann. Hierbei kann die Opferfläche bei einer weitgehenden Beibehaltung der Konstruktion der Pumpenanordnung realisiert werden. Speziell sind die erforderlichen Änderungen an den Bauteilen der Pumpenanordnung gering und auf den Bereich der Kupplung begrenzt. Somit kann mit geringem konstruktiven Aufwand die Lebensdauer der Pumpenanordnung verlängert werden.It is therefore advantageous that the coupling allows axial play between the high-pressure pump shaft and the gear pump shaft. Furthermore, it is advantageous that the high-pressure pump shaft has a two-fold, that the two-flat has a first side surface and a second side surface facing away from the first side surface, that the first side surface has a sacrificial layer and that the second side surface has a sacrificial layer. Through the sacrificial layers in each case a sacrificial surface is formed. A thickness of the respective sacrificial layer is predetermined with respect to an expected life of the pump assembly. Thus, the sacrificial layer is large enough so that over the life of a complete wear of the sacrificial surface does not occur. An axial compensation of the coupling thus remains over the life of the pump assembly, especially the gear pump, because the coupling can not seize on the two-fold. In this case, the sacrificial surface can be realized while largely maintaining the construction of the pump arrangement. Specifically, the required changes to the components of the pump assembly are small and limited to the range of the coupling. Thus, the life of the pump assembly can be extended with little design effort.

In vorteilhafter Weise greift der Zweiflach der Hochdruckpumpenwelle zumindest teilweise in eine Nut der Zahnradpumpenwelle ein. Die Kupplung kann allerdings auch durch einen anders ausgestalteten Antriebsstummel der Hochdruckpumpenwelle, die mit zumindest einer Opferfläche versehen ist, realisiert werden.Advantageously, the two-face of the high pressure pump shaft at least partially engages in a groove of the gear pump shaft. However, the coupling can also be realized by a differently designed drive stub of the high-pressure pump shaft, which is provided with at least one sacrificial surface.

Somit wird auch bei hochdrehenden Hochdruckpumpen und bei schlecht schmierenden Brennstoffen, die beispielsweise zur Schmierung im Bereich der Kupplung dienen, ein axiales Spiel im Bereich der Kupplung über die Lebensdauer der Pumpenanordnung gewährleistet.Thus, even with high-speed high-pressure pumps and poorly lubricating fuels, which serve for example for lubrication in the clutch, axial play in the clutch ensures over the life of the pump assembly.

Kurze Beschreibung der ZeichnungenBrief description of the drawings

Bevorzugte Ausführungsbeispiele der Erfindung sind in der nachfolgenden Beschreibung anhand der beigefügten Zeichnungen, in denen sich entsprechende Elemente mit übereinstimmenden Bezugszeichen versehen sind, näher erläutert. Es zeigt:

  • Fig. 1 eine Pumpenanordnung in einer schematischen, auszugsweisen, axialen Schnittdarstellung entsprechend einem Ausführungsbeispiel der Erfindung und
  • Fig. 2 eine Hochdruckpumpenwelle einer Hochdruckpumpe der in Fig. 1 dargestellten Pumpenanordnung in einer auszugsweisen Darstellung.
Preferred embodiments of the invention are explained in more detail in the following description with reference to the accompanying drawings, in which corresponding elements are provided with corresponding reference numerals. It shows:
  • Fig. 1 a pump assembly in a schematic, partial, axial sectional view according to an embodiment of the invention and
  • Fig. 2 a high pressure pump shaft of a high pressure pump of Fig. 1 illustrated pump assembly in an excerpted representation.

Ausführungsformen der ErfindungEmbodiments of the invention

Fig. 1 zeigt eine Pumpenanordnung 1 in einer schematischen, auszugsweise, axialen Schnittdarstellung entsprechend einem Ausführungsbeispiel der Erfindung. Die Pumpenanordnung 1 kann insbesondere für Brennstoffeinspritzanlagen von luftverdichtenden, selbstzündenden Brennkraftmaschinen dienen. Ein bevorzugter Einsatz der Pumpenanordnung 1 besteht für eine Brennstoffeinspritzanlage mit einer Brennstoffverteilerleiste, die Dieselbrennstoff unter hohem Druck speichert. Die Pumpenanordnung 1 dient in diesem Fall zum Fördern von Brennstoff zu solch einer Brennstoffverteilerleiste. Die erfindungsgemäße Pumpenanordnung 1 eignet sich jedoch auch für andere Anwendungsfälle. Fig. 1 shows a pump assembly 1 in a schematic, partial, axial sectional view according to an embodiment of the invention. The pump assembly 1 can be used in particular for fuel injection systems of air-compressing, self-igniting internal combustion engines. A preferred use of the pump assembly 1 is for a fuel injection system having a fuel rail which stores diesel fuel under high pressure. The pump assembly 1 is used in this case for conveying fuel to such Fuel rail. However, the pump assembly 1 according to the invention is also suitable for other applications.

Die Pumpenanordnung 1 weist eine Hochdruckpumpe 2 und eine Zahnradpumpe 3 auf. Die Hochdruckpumpe 2 weist ein Gehäuse 4 auf. Die Zahnradpumpe 3 weist ein Gehäuseteil 5 auf, das beispielsweise als Deckel 5 ausgestaltet ist. Das Gehäuseteil 5 ist auf geeignete Weise mit dem Gehäuse 4 der Hochdruckpumpe 2 verbunden. Hierbei besteht durch ein Teil 6 des Gehäuses 4 eine Trennung zwischen einem Bereich der Hochdruckpumpe 2 und einem Bereich der Zahnradpumpe 3.The pump arrangement 1 has a high-pressure pump 2 and a gear pump 3. The high-pressure pump 2 has a housing 4. The gear pump 3 has a housing part 5, which is designed for example as a cover 5. The housing part 5 is suitably connected to the housing 4 of the high-pressure pump 2. In this case, there is a separation between a region of the high-pressure pump 2 and a region of the gear pump 3 through a part 6 of the housing 4.

Die Hochdruckpumpe 2 weist eine Hochdruckpumpenwelle 7 auf, die auf geeignete Weise in dem Gehäuse 4 gelagert ist. Außerdem weist die Zahnradpumpe 3 eine Zahnradpumpenwelle 8 auf, die in einer Bohrung 9 des Gehäuseteils 5 gelagert ist. Hierbei ist auf der Zahnradpumpenwelle 8 ein als Antriebszahnrad 10 ausgestaltetes Zahnrad 10 angeordnet und befestigt. Beispielsweise kann das Zahnrad 10 auf die Zahnradpumpenwelle 8 aufgepresst sein. Die Zahnradpumpe 3 weist ein weiteres Zahnrad 11 auf, das mit dem Zahnrad 10 in Wirkverbindung steht. Hierbei kämmen die beiden Zahnräder 10, 11 auf eine Weise, dass eine Pumpenwirkung erzielt ist. Hierbei dient die Hochdruckpumpenwelle 7 als Antriebswelle, die neben Pumpenelementen der Hochdruckpumpe 2 auch die Zahnradpumpenwelle 8 und somit die Zahnradpumpe 3 antreibt. Die Zahnradpumpe 3 dient als Vorförderpumpe für die Hochdruckpumpe 2.The high-pressure pump 2 has a high-pressure pump shaft 7, which is mounted in a suitable manner in the housing 4. In addition, the gear pump 3 has a gear pump shaft 8 which is mounted in a bore 9 of the housing part 5. Here, on the gear pump shaft 8 designed as a drive gear 10 gear 10 is arranged and fixed. For example, the gear 10 may be pressed onto the gear pump shaft 8. The gear pump 3 has a further gear 11, which is in operative connection with the gear 10. Here, the two gears 10, 11 mesh in a manner that a pumping action is achieved. Here, the high-pressure pump shaft 7 serves as a drive shaft which, in addition to pump elements of the high-pressure pump 2, also drives the gear pump shaft 8 and thus the gear pump 3. The gear pump 3 serves as a prefeed pump for the high pressure pump. 2

Zwischen der Hochdruckpumpenwelle 7 und der Zahnradpumpenwelle 8 ist eine Kupplung 12 vorgesehen. Die Kupplung 12 umfasst ein Kupplungsteil 13 und ein Kupplungsteil 14. Das Kupplungsteil 14 ist in diesem Ausführungsbeispiel an der Hochdruckpumpenwelle 7 in Form eines Antriebsstummels 14 ausgebildet. Hierbei ist das Kupplungsteil 14 in Form eines Zweiflachs ausgestaltet. Das Kupplungsteil 14 kann allerdings auch mit der Hochdruckpumpenwelle 7 auf geeigneter Weise in Wirkverbindung stehen und insbesondere form- oder stoffschlüssig mit der Hochdruckpumpenwelle 7 verbunden sein. Das Kupplungsteil 13 kann als Teil der Zahnradpumpenwelle 8 ausgestaltet sein. Allerdings kann das Kupplungsteil 13 auch als separates Kupplungsstück 13 ausgestaltet sein, das auf geeignete Weise mit der Zahnradpumpenwelle 8 in Wirkverbindung steht und insbesondere form- oder stoffschlüssig mit der Zahnradpumpenwelle 8 verbunden ist. Das Kupplungsstück 13 kann auch direkt am Zahnrad 10 angeordnet sein, so dass die Zahnradpumpenwelle 8 entfallen kann und durch einen Lagerstummel 8 ersetzt werden kann. Hierbei ist es vorteilhaft, dass das Zahnrad 10 über den Lagerstummel 8 in der Bohrung 9 des Gehäuseteils 5 der Zahnradpumpe 3 gelagert ist und dass das Gehäuseteil 5 der Zahnradpumpe 3 zumindest mittelbar mit dem Gehäuse 4 der Hochdruckpumpe 2 verbunden ist. Das Kupplungsteil 13 weist in diesem Ausführungsbeispiel eine Nut 15 auf, die im montierten Zustand des Kupplungsteils 13 senkrecht zu einer Längsachse 16 der Pumpenanordnung 1 orientiert ist. Die Hochdruckpumpenwelle 7 und die Zahnradpumpenwelle 8 sind an der Längsachse 16 ausgerichtet und rotieren im Betrieb zumindest näherungsweise um die Längsachse 16.Between the high-pressure pump shaft 7 and the gear pump shaft 8, a clutch 12 is provided. The coupling 12 comprises a coupling part 13 and a coupling part 14. The coupling part 14 is formed in this embodiment on the high-pressure pump shaft 7 in the form of a drive stub 14. In this case, the coupling part 14 is designed in the form of a double salmon. However, the coupling part 14 can also be in operative connection with the high-pressure pump shaft 7 in a suitable manner and, in particular, can be connected to the high-pressure pump shaft 7 in a form-fitting or material-locking manner. The coupling part 13 may be configured as part of the gear pump shaft 8. However, the coupling part 13 may also be designed as a separate coupling piece 13, which is suitably in operative connection with the gear pump shaft 8 and in particular is positively or materially connected to the gear pump shaft 8. The coupling piece 13 may also be arranged directly on the gear 10, so that the gear pump shaft 8 can be omitted and can be replaced by a bearing stub 8. It is advantageous that the gear 10 is mounted on the bearing stub 8 in the bore 9 of the housing part 5 of the gear pump 3 and that the housing part 5 of the gear pump 3 at least indirectly with the housing 4 of the high-pressure pump. 2 connected is. The coupling part 13 has in this embodiment, a groove 15 which is oriented in the mounted state of the coupling part 13 perpendicular to a longitudinal axis 16 of the pump assembly 1. The high-pressure pump shaft 7 and the gear pump shaft 8 are aligned on the longitudinal axis 16 and rotate in operation at least approximately about the longitudinal axis 16.

In diesem Ausführungsbeispiel sind an dem Kupplungsteil 14 Opferschichten 17, 18 vorgesehen. Hierbei ist die Opferschicht 17 auf eine erste Seitenfläche 19 des Kupplungsteils 14 aufgebracht. Die Opferschicht 18 ist auf eine zweite Seitenfläche 20 des Kupplungsteils 14 aufgebracht. Hierbei sind die beiden Seitenflächen 19, 20 voneinander abgewandt. Die Opferschichten 17, 18 bedecken die Seitenflächen 19, 20 hierbei jeweils teilweise. Die Opferschicht 17 bildet eine Opferfläche 21. Ferner bildet die Opferschicht 18 eine Opferfläche 22. In diesem Ausführungsbeispiel weist die Kupplung 12 daher die Opferschichten 17, 18 mit den Opferflächen 21, 22 auf.In this embodiment, sacrificial layers 17, 18 are provided on the coupling part 14. Here, the sacrificial layer 17 is applied to a first side surface 19 of the coupling part 14. The sacrificial layer 18 is applied to a second side surface 20 of the coupling part 14. Here, the two side surfaces 19, 20 facing away from each other. The sacrificial layers 17, 18 in each case partially cover the side surfaces 19, 20. The sacrificial layer 17 forms a sacrificial surface 21. Furthermore, the sacrificial layer 18 forms a sacrificial surface 22. In this exemplary embodiment, the coupling 12 therefore has the sacrificial layers 17, 18 with the sacrificial surfaces 21, 22.

Die Kupplung 12 ermöglicht ein gewisses axiales Spiel zwischen der Hochdruckpumpenwelle 7 und der Zahnradpumpenwelle 8. Im Betrieb kommt es daher zu Relativbewegungen zwischen den Kupplungsteilen 13, 14 der Kupplung 12. Die Opferschichten 17, 18 sind an den Werkstoff des Kupplungsteils 13 angepasst. Auf Grund der Relativbewegung kommt es zu einem Verschleiß, der zumindest im Wesentlichen die Opferflächen 21, 22 betrifft.The coupling 12 allows a certain axial clearance between the high-pressure pump shaft 7 and the gear pump shaft 8. In operation, therefore, there are relative movements between the coupling parts 13, 14 of the clutch 12. The sacrificial layers 17, 18 are adapted to the material of the coupling part 13. Due to the relative movement, wear occurs that at least essentially affects the sacrificial surfaces 21, 22.

Fig. 2 zeigt die Hochdruckpumpenwelle 7 der Hochdruckpumpe 2 der in Fig. 1 dargestellten Pumpenanordnung 1 in einer auszugsweisen, schematischen Darstellung. Eine Stärke 23 der Opferschicht 17 ist so groß vorgegeben, dass über die Lebensdauer ein vollständiger Verschleiß der Opferfläche 21 nicht vorkommt. Entsprechend ist eine Stärke 24 der Opferschicht 18 so groß vorgegeben, dass über die Lebensdauer ein vollständiger Verschleiß der Opferfläche 22 nicht auftritt. Somit bleibt der Axialausgleich der Kupplung 12 über die Lebensdauer der Zahnradpumpe 3 erhalten. Die Bauteile der Zahnradpumpe 3 können hierbei zumindest im Wesentlichen unverändert zum Einsatz kommen. Somit ist ohne oder nur mit geringen konstruktiven Änderungen eine Verlängerung der Lebensdauer der Pumpenanordnung 1 mit der Hochdruckpumpe 2 und der Zahnradpumpe 3 möglich. Fig. 2 shows the high pressure pump shaft 7 of the high pressure pump 2 in Fig. 1 illustrated pump assembly 1 in a partial, schematic representation. A thickness 23 of the sacrificial layer 17 is set so large that over the life of a complete wear of the sacrificial surface 21 does not occur. Accordingly, a thickness 24 of the sacrificial layer 18 is set so large that over the life of a complete wear of the sacrificial surface 22 does not occur. Thus, the axial compensation of the clutch 12 is maintained over the life of the gear pump 3. The components of the gear pump 3 can be used here at least substantially unchanged. Thus, an extension of the life of the pump assembly 1 with the high-pressure pump 2 and the gear pump 3 is possible without or with little design changes.

Die Erfindung ist nicht auf die beschriebenen Ausführungsbeispiele beschränkt.The invention is not limited to the described embodiments.

Claims (10)

  1. Pump arrangement (1), in particular for fuel injection systems of air-compressing, auto-ignition internal combustion engines, having a high-pressure pump (2) which has a high-pressure pump shaft (7), and having a gearwheel pump (3), wherein a coupling (12) is provided between the high-pressure pump shaft (7) and a gearwheel pump shaft (8) of the gearwheel pump (3) or a gearwheel (10) of the gearwheel pump (3),
    characterized
    in that the coupling (12) has at least one sacrificial surface (21, 22), and in that the sacrificial surface (21, 22) is formed on a sacrificial layer (17, 18).
  2. Pump arrangement according to Claim 1,
    characterized
    in that the coupling (12) permits axial play between the high-pressure pump shaft (7) and the gearwheel pump shaft (8) or the gearwheel (10) over a service life.
  3. Pump arrangement according to Claim 1 or 2,
    characterized
    in that the high-pressure pump shaft (7) has a dihedron (14), in that the dihedron (14) has a first side surface (19) and a second side surface (20) facing away from the first side surface (19), in that the first side surface (19) has a sacrificial layer (17), and in that the second side surface (20) has a sacrificial layer (18).
  4. Pump arrangement according to Claim 3,
    characterized
    in that the gearwheel pump shaft (8) or the gearwheel (10) has a groove (15), and in that the dihedron (14) of the high-pressure pump shaft (7) engages at least partially into the groove (15) of the gearwheel pump shaft (8) or of the gearwheel (10).
  5. Pump arrangement according to Claim 3 or 4,
    characterized
    in that the side surface (19, 20) is partially coated with a sacrificial layer (17, 18).
  6. Pump arrangement according to one of Claims 1 to 5,
    characterized
    in that a thickness (23, 24) of the sacrificial layer (17, 18) is predefined with regard to a service life.
  7. Pump arrangement according to one of Claims 1 to 6,
    characterized
    in that the sacrificial surface (21, 22) is provided on a drive stub (13) of the high-pressure pump shaft (7).
  8. Pump arrangement according to one of Claims 1 to 7,
    characterized
    in that a gearwheel (10) is arranged on the gearwheel pump shaft (8), in that the gearwheel pump shaft (8) is mounted in a housing part (5) of the gearwheel pump (3), and in that the housing part (5) of the gearwheel pump (3) is connected at least indirectly to a housing (4) of the high-pressure pump (2).
  9. Pump arrangement according to one of Claims 1 to 7,
    characterized
    in that the gearwheel (10) is mounted in a housing part (5) of the gearwheel pump (3), and in that the housing part (5) of the gearwheel pump (3) is connected at least indirectly to a housing (4) of the high-pressure pump (2).
  10. Pump arrangement according to one of Claims 1 to 9,
    characterized
    in that the high-pressure pump (2) is designed as a high-speed high-pressure pump (2).
EP10767994.6A 2009-12-07 2010-10-07 Pump arrangement Not-in-force EP2510235B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102009047576A DE102009047576A1 (en) 2009-12-07 2009-12-07 pump assembly
PCT/EP2010/064972 WO2011069708A1 (en) 2009-12-07 2010-10-07 Pump arrangement

Publications (2)

Publication Number Publication Date
EP2510235A1 EP2510235A1 (en) 2012-10-17
EP2510235B1 true EP2510235B1 (en) 2013-08-07

Family

ID=43086287

Family Applications (1)

Application Number Title Priority Date Filing Date
EP10767994.6A Not-in-force EP2510235B1 (en) 2009-12-07 2010-10-07 Pump arrangement

Country Status (5)

Country Link
EP (1) EP2510235B1 (en)
CN (1) CN102753826B (en)
DE (1) DE102009047576A1 (en)
IN (1) IN2012DN05042A (en)
WO (1) WO2011069708A1 (en)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2559148B (en) * 2017-01-26 2019-06-05 Delphi Tech Ip Ltd Driveshaft with transfer pump adapter

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH07269478A (en) * 1994-03-31 1995-10-17 Toshiba Corp Fluid compressor
DE19736160A1 (en) 1997-08-20 1999-02-25 Bosch Gmbh Robert High pressure fuel pump for IC engine in common rail systems
KR20070058535A (en) * 2004-09-28 2007-06-08 다이킨 고교 가부시키가이샤 Slide member and fluid machine
JP4289460B2 (en) * 2004-12-28 2009-07-01 株式会社山田製作所 Electric oil pump
CN100458203C (en) * 2007-03-21 2009-02-04 太原市通泽成套设备有限公司 Universal-joint-pin type universal coupling
CN101368600A (en) * 2007-08-15 2009-02-18 胡厚飞 High-torsion universal joint structure

Also Published As

Publication number Publication date
IN2012DN05042A (en) 2015-10-09
EP2510235A1 (en) 2012-10-17
WO2011069708A1 (en) 2011-06-16
CN102753826A (en) 2012-10-24
DE102009047576A1 (en) 2011-06-09
CN102753826B (en) 2015-10-21

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