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, auto-igniting
• the known pump arrangement comprises a pump housing for a radial piston pump, a housing part for a
• a cross-plate clutch which has a drive shaft of the radial piston pump with a shaft of the
• 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.
• High-pressure pump shaft incorporates, 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.
• 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.
• 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.
• the problem is shifted to a different location of the construction of the pump assembly when reducing the abrasive wear.
• High pressure pump shaft and the gear pump shaft allows. 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.
• the sacrificial layer is large enough so that over the life of a complete wear of the sacrificial surface does not occur.
• the two-plane of the high-pressure pump shaft engages at least partially 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 in a schematic, excise, axial
• FIG. 2 shows a high-pressure pump shaft of a high-pressure pump of the pump arrangement shown in FIG. 1 in an excerpted representation.
• FIG. 1 shows a pump arrangement 1 in a schematic, partial, axial sectional representation according to an exemplary embodiment of the invention.
• Pump arrangement 1 can in particular for fuel injection systems of
• a preferred use of the pump assembly 1 is for a fuel injection system with a
• Fuel rail that stores diesel fuel under high pressure.
• 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 on the gear 10 is arranged and fixed.
• Gear pump shaft 8 be pressed.
• the gear pump 3 has another gear
• the high-pressure pump shaft 7 serves as a drive shaft, in addition to pump elements of
• 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 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 with the
• High pressure pump shaft 7 are suitably operatively connected and
• the coupling part 13 may be configured as part of the gear pump shaft 8. However, the coupling part 13 may also be configured 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.
• Gear pump shaft 8 are aligned on the longitudinal axis 16 and rotate in operation at least approximately about the longitudinal axis sixteenth
• sacrificial layers 17, 18 are provided on the coupling part 14.
• the sacrificial layer 17 is on a first side surface 19 of the
• the sacrificial layer 18 is applied to a second side surface 20 of the coupling part 14.
• 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 has the sacrificial layers 17, 18 with the sacrificial surfaces 21, 22.
• the coupling 12 allows a certain axial play between 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 of the pump arrangement 1 illustrated in FIG. 1 in an excerptional, 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. 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.

Landscapes

• Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• General Engineering & Computer Science (AREA)
• Chemical & Material Sciences (AREA)
• Combustion & Propulsion (AREA)
• Details And Applications Of Rotary Liquid Pumps (AREA)
• Rotary Pumps (AREA)
• Fuel-Injection Apparatus (AREA)

Priority Applications (3)

Applications Claiming Priority (2)

Publications (1)

Family

ID=43086287

Family Applications (1)

Country Status (5)

Cited By (1)

Citations (4)

Family Cites Families (2)

• 2009
  • 2009-12-07 DE DE102009047576A patent/DE102009047576A1/de not_active Withdrawn
• 2010
  • 2010-10-07 CN CN201080063197.3A patent/CN102753826B/zh not_active Expired - Fee Related
  • 2010-10-07 WO PCT/EP2010/064972 patent/WO2011069708A1/de active Application Filing
  • 2010-10-07 IN IN5042DEN2012 patent/IN2012DN05042A/en unknown
  • 2010-10-07 EP EP10767994.6A patent/EP2510235B1/de not_active Not-in-force

Patent Citations (4)

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