EP2510235B1 - Pumpenanordnung - Google Patents

Pumpenanordnung Download PDF

Info

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
Authority
EP
European Patent Office
Prior art keywords
pump
gearwheel
shaft
pressure pump
pump shaft
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
EP10767994.6A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP2510235A1 (de
Inventor
Arnold Gente
Matthias Greiner
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP2510235A1 publication Critical patent/EP2510235A1/de
Application granted granted Critical
Publication of EP2510235B1 publication Critical patent/EP2510235B1/de
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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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.

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)
EP10767994.6A 2009-12-07 2010-10-07 Pumpenanordnung Not-in-force EP2510235B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102009047576A DE102009047576A1 (de) 2009-12-07 2009-12-07 Pumpenanordnung
PCT/EP2010/064972 WO2011069708A1 (de) 2009-12-07 2010-10-07 Pumpenanordnung

Publications (2)

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

Family

ID=43086287

Family Applications (1)

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

Country Status (5)

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

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 (ja) * 1994-03-31 1995-10-17 Toshiba Corp 流体圧縮機
DE19736160A1 (de) 1997-08-20 1999-02-25 Bosch Gmbh Robert Pumpenanordnung zur Kraftstoffhochdruckversorgung bei Kraftstoffeinspritzsystemen von Brennkraftmaschinen
KR20070058535A (ko) * 2004-09-28 2007-06-08 다이킨 고교 가부시키가이샤 습동부재 및 유체기계
JP4289460B2 (ja) * 2004-12-28 2009-07-01 株式会社山田製作所 電動オイルポンプ
CN100458203C (zh) * 2007-03-21 2009-02-04 太原市通泽成套设备有限公司 十字轴式万向联轴器
CN101368600A (zh) * 2007-08-15 2009-02-18 胡厚飞 高扭力的万向接头结构

Also Published As

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

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