EP0678161B1 - Verteilerkraftstoffeinspritzpumpe für brennkraftmaschinen - Google Patents

Verteilerkraftstoffeinspritzpumpe für brennkraftmaschinen Download PDF

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Publication number
EP0678161B1
EP0678161B1 EP95900049A EP95900049A EP0678161B1 EP 0678161 B1 EP0678161 B1 EP 0678161B1 EP 95900049 A EP95900049 A EP 95900049A EP 95900049 A EP95900049 A EP 95900049A EP 0678161 B1 EP0678161 B1 EP 0678161B1
Authority
EP
European Patent Office
Prior art keywords
pump
cylinder bore
pistons
cylinder
stop
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.)
Expired - Lifetime
Application number
EP95900049A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0678161A1 (de
Inventor
Wolfgang Fehlmann
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 EP0678161A1 publication Critical patent/EP0678161A1/de
Application granted granted Critical
Publication of EP0678161B1 publication Critical patent/EP0678161B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • 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
    • F02M41/00—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor
    • F02M41/08—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined
    • F02M41/14—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined rotary distributor supporting pump pistons
    • 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
    • F02M41/00—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor
    • F02M41/08—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined
    • F02M41/14—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined rotary distributor supporting pump pistons
    • F02M41/1405—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined rotary distributor supporting pump pistons pistons being disposed radially with respect to rotation axis

Definitions

  • the invention is based on a distributor fuel injection pump for internal combustion engines according to the preamble of claim 1.
  • a drive shaft drives a rotor guided in a housing in which two pump piston pairs, each guided in a cylinder bore, are arranged in a radial plane to the drive shaft are.
  • the arranged in a common radial plane of the rotor cylinder bores intersect at right angles, so that the individual pump pistons with their radially inward-facing end faces a common pump working space in the overlapping area of the Limit cylinder bores.
  • the pump pistons run with their ends protruding from the cylinder bores by means of a roller tappet on a stationary cam track of a cam ring guided in the housing, so that they are set in a reciprocating stroke movement when the rotor rotates, whereby they move during the radially outward suction stroke movement open the connection of the cylinder bore with a filling line starting from a low-pressure chamber, which is then closed in the subsequent delivery stroke by the pump pistons.
  • the fuel compressed in the common pump work space during the delivery stroke then passes via a high-pressure channel in the rotor to a distributor bore radially leading away from it, which overlaps with the individual high-pressure delivery lines to the injection points during the rotary movement of the rotor.
  • the pump piston pairs in the two cylinder bores are designed so that a longer pair of pistons guided in a first cylinder bore protrudes into the second cylinder bore with its end facing the pump working space and the shorter piston pair guided there does not reach the first cylinder bore even in its maximum stroke position.
  • the known distributor fuel injection pump has the disadvantage that the cam stroke that is the same for all pump pistons must be less than half the diameter of the cylinder bores of the same size. This is necessary to ensure that the long pistons are still immersed in the second cylinder bore, even in their maximum suction stroke position, in order to move the shorter pistons independently between the long pistons when the internal combustion engine is switched off and the pump work chamber is depressurized Avoid safely, as this would otherwise lead to mechanical destruction of the distributor injection pump during operation.
  • the distributor fuel injection pump according to the invention with the features of claim 1 has the advantage that a stop at the end protruding from the cylinder bore of the shorter pump pistons, their unwanted sliding into the cylinder bore between the long pump pistons can be safely avoided.
  • This increase in the delivery stroke can advantageously be converted into an increase in the injection pressure or a larger delivery amount.
  • the stop on the short pump piston is advantageously arranged in such a way that it allows them to be immersed in the cylinder bore leading them until their end face facing the pump work space has approached to a small extent the second cylinder bore, so that large delivery heights are reached to let.
  • the stop on the short pump piston can be easily by a collar or in an annular groove Carry out a circlip on the shaft of the short pistons, which then simply interact with the end wall of the cylinder bore.
  • FIG. 1 shows a longitudinal section through the part of the distributor fuel injection pump that is essential to the invention
  • FIG. 2 shows a first embodiment of the pump piston lock by means of a collar in a section from FIG. 1
  • FIG. 3 shows a second embodiment of the pump piston lock by means of a lock ring in an analogous manner to FIG. 2 shown representation.
  • a piston-shaped rotor part 1 is mounted rotatably about its axis in a cylinder bore 2 of a cylindrical guide part 5 which is fixedly connected to the pump housing 3.
  • the rotor part 1 has at its one end a part 7 with a larger diameter, which is connected in a rotationally fixed manner to a drive shaft 9 which is driven synchronously with the engine speed and in which two through bores 11 intersecting at right angles in a common radial of the axis of the rotor part 1 extending plane are arranged.
  • a delivery channel 13 leads off in the axis of the rotor part 1, which contains a check valve 15 and whose end merges into a radially extending distributor bore 17.
  • the guide part 5 has injection lines 19 which start from the cylinder bore 2 to the individual injection points of the internal combustion engine.
  • the injection lines 19 are distributed according to the number of injection points to be supplied and at a corresponding distance from one another on the circumference of the guide part 5.
  • a supply bore 21 in the rotor part 1 which leads radially away from the delivery channel 13 and which can be connected to a fuel supply line 23 in the guide part 5, which in turn leads to a fuel delivery line (not shown), preferably having a feed pump and having a feed pump a fuel reservoir forming a low pressure space is connected.
  • the radial through-bores 11 in the diameter-enlarged part 7 of the rotor part 1 are designed as cylinder bores, in which, as can also be seen in FIGS. 2 and 3, two pump pistons lying opposite one another and working against one another are arranged.
  • a first cylinder bore 25 receives a first pair of pump pistons 27 with an axial extension, the pump pistons 27 of which are so long that they protrude into the region of a second cylinder bore 29 that intersects the first during the delivery stroke movement.
  • this second cylinder bore 29 is a second shorter pump piston pair 31 guided, the pump pistons 31 are dimensioned such that they do not protrude into the region of the first cylinder bore 25 even in the maximum delivery stroke position.
  • the pump pistons 27, 31 delimit a common pump working space 33, in the cylinder bores 25, 29, which can be connected to the injection lines 19 and the fuel supply line 23 via the delivery channel 13.
  • the pump pistons 27, 31 each abut a roller tappet 35, the roller 37 of which runs on a cam track 39 of a cam ring 41 located in the radial plane and guided in the pump housing 3.
  • the pump pistons 27, 31 are held in contact with the roller tappets 35 by the centrifugal force when the distributor fuel injection pump is in operation.
  • the pump pistons 27, 31 can move independently in the cylinder bores 25, 29.
  • the short pump pistons 31 In order to avoid with certainty that a short pump piston 31 slips between the long pump pistons 27 into the region of the first cylinder bore 25, the short pump pistons 31 have a stop at their ends projecting radially from the second cylinder bore 29, which stops with the respective axial end wall 49 of the cylinder bore 29 cooperates.
  • this stop is designed as a collar 43 formed by enlarging the cross section.
  • the axial end stop on the short pump piston 31 is formed by a securing ring 45 which protrudes from the cylinder bore 29 in an annular groove 47 End of the short pump piston 31 is guided and also cooperates with the axial end wall 49 of the cylinder bore 29.
  • the distributor fuel injection pump according to the invention works in the following manner.
  • the pump pistons 27, 31 are in indefinite positions, depending on the position of the rotor part 1, when the pump work chamber 33 is depressurized, which can also be the respective maximum stroke positions.
  • the rotor part 1 With the start of operation of the distributor fuel injection pump, the rotor part 1 is set into a rotating movement by the drive shaft 9, as a result of which the pump pistons 27, 31 are brought into contact with the roller tappet 35 by centrifugal force, which in turn run on the cam track 39 and so on set the pump pistons 27, 31 in a reciprocating motion in the cylinder bores 25, 29.
  • the fuel compressed in the pump work chamber 33 during the delivery stroke of the pump pistons 27, 31 is guided via the delivery channel 13 and the check valve 15 to the distributor bore 17, from where it is supplied to the respective injection points when the individual injection lines 19 are passed over.
  • the feed line 23 from the low-pressure chamber is at the time of the high-pressure delivery closed, this closing can take place via a solenoid valve arranged in the feed line 23 or the immersion of the suction bore 21 from the overlap with the feed bore 23.
  • the end of the high-pressure delivery is regulated by reopening the connection between the supply line 21 and the fuel supply line 23.
  • the high-pressure residual fuel initially flows back into the low-pressure chamber before the pump pistons 27, 31 are refilled during the suction stroke of the pump work chamber 33, the check valve 15 ensuring a constant stand pressure in the distributor bore 17 and the injection lines 19.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)
EP95900049A 1993-11-10 1994-10-28 Verteilerkraftstoffeinspritzpumpe für brennkraftmaschinen Expired - Lifetime EP0678161B1 (de)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE4338344 1993-11-10
DE4338344A DE4338344A1 (de) 1993-11-10 1993-11-10 Verteilerkraftstoffeinspritzpumpe für Brennkraftmaschinen
PCT/DE1994/001267 WO1995013469A1 (de) 1993-11-10 1994-10-28 Verteilerkraftstoffeinspritzpumpe für brennkraftmaschinen

Publications (2)

Publication Number Publication Date
EP0678161A1 EP0678161A1 (de) 1995-10-25
EP0678161B1 true EP0678161B1 (de) 1996-09-04

Family

ID=6502237

Family Applications (1)

Application Number Title Priority Date Filing Date
EP95900049A Expired - Lifetime EP0678161B1 (de) 1993-11-10 1994-10-28 Verteilerkraftstoffeinspritzpumpe für brennkraftmaschinen

Country Status (8)

Country Link
US (1) US5592920A (ja)
EP (1) EP0678161B1 (ja)
JP (1) JPH08505681A (ja)
KR (1) KR100333453B1 (ja)
DE (2) DE4338344A1 (ja)
ES (1) ES2092420T3 (ja)
RU (1) RU2133870C1 (ja)
WO (1) WO1995013469A1 (ja)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7048516B2 (en) * 2003-06-09 2006-05-23 Delphi Technologies, Inc. High pressure fuel pump with multiple radial plungers

Family Cites Families (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3771506A (en) * 1972-06-07 1973-11-13 Stanadyne Inc Fuel injection pump and automatic timing means therefor
US3938911A (en) * 1973-02-28 1976-02-17 Stanadyne, Inc. Fuel injection pump with metering valve controlled cooling
FR2437502A1 (fr) * 1978-09-29 1980-04-25 Cav Roto Diesel Pompe d'injection de combustible
DE3342993A1 (de) * 1982-12-06 1984-06-07 Nissan Motor Co., Ltd., Yokohama, Kanagawa Steuereinrichtung fuer die treibstoffeinspritzmenge bei einem verbrennungsmotor
DE3412834A1 (de) * 1984-04-05 1985-10-24 Robert Bosch Gmbh, 7000 Stuttgart Kraftstoffeinspritzpumpe
GB8410280D0 (en) * 1984-04-19 1984-05-31 Lumber P M P Rotary distributor pump
DE3612942A1 (de) * 1986-04-17 1987-10-22 Bosch Gmbh Robert Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
DE3719831A1 (de) * 1987-06-13 1988-12-22 Bosch Gmbh Robert Kraftstoffeinspritzpumpe
DE3816508A1 (de) * 1988-05-14 1989-11-23 Bosch Gmbh Robert Kraftstoffeinspritzpumpe fuer brennkraftmaschine
GB8902860D0 (en) * 1989-02-09 1989-03-30 Lucas Ind Plc Fuel injection pump
US5215060A (en) * 1991-07-16 1993-06-01 Stanadyne Automotive Corp. Fuel system for rotary distributor fuel injection pump
GB9315342D0 (en) * 1993-07-23 1993-09-08 Lucas Ind Plc Fuel pumping apparatus

Also Published As

Publication number Publication date
KR100333453B1 (ko) 2002-09-17
KR960700405A (ko) 1996-01-20
DE59400598D1 (de) 1996-10-10
DE4338344A1 (de) 1995-05-11
ES2092420T3 (es) 1996-11-16
WO1995013469A1 (de) 1995-05-18
RU2133870C1 (ru) 1999-07-27
JPH08505681A (ja) 1996-06-18
EP0678161A1 (de) 1995-10-25
US5592920A (en) 1997-01-14

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