EP0377830A1 - Pompe distributrice d'injection de combustible pour moteurs à combustion interne - Google Patents

Pompe distributrice d'injection de combustible pour moteurs à combustion interne Download PDF

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Publication number
EP0377830A1
EP0377830A1 EP19890122725 EP89122725A EP0377830A1 EP 0377830 A1 EP0377830 A1 EP 0377830A1 EP 19890122725 EP19890122725 EP 19890122725 EP 89122725 A EP89122725 A EP 89122725A EP 0377830 A1 EP0377830 A1 EP 0377830A1
Authority
EP
European Patent Office
Prior art keywords
distributor
piston
suction
longitudinal
pump
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.)
Granted
Application number
EP19890122725
Other languages
German (de)
English (en)
Other versions
EP0377830B1 (fr
Inventor
André Brunel
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 EP0377830A1 publication Critical patent/EP0377830A1/fr
Application granted granted Critical
Publication of EP0377830B1 publication Critical patent/EP0377830B1/fr
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
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/20—Varying fuel delivery in quantity or timing
    • F02M59/36—Varying fuel delivery in quantity or timing by variably-timed valves controlling fuel passages to pumping elements or overflow passages
    • F02M59/366—Valves being actuated electrically
    • 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
    • F02M41/02—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor being spaced from pumping elements
    • F02M41/06—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor being spaced from pumping elements the distributor rotating
    • 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
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/02—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively
    • F02M63/0205—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively for cutting-out pumps or injectors in case of abnormal operation of the engine or the injection apparatus, e.g. over-speed, break-down of fuel pumps or injectors ; for cutting-out pumps for stopping the engine

Definitions

  • the invention relates to a distributor fuel injection pump for internal combustion engines according to the preamble of the main claim.
  • the stroke of the distributor piston must be relatively large, which has a disadvantageous effect on the entire construction and, above all, on the parking speed, since due to the relatively large stroke, a corresponding amount of fuel is also required for this control Displacement of the distributor piston is required.
  • an enlarged cross section of the control valve passage would be necessary, which in turn would necessitate an increase in the actuating forces, for example of a magnet.
  • the distributor fuel injection pump according to the invention with the characterizing features of the main claim has the advantage that only a slight displacement of the distributor piston is required to switch off the engine, which is determined by the steepness of the inclined control surface, at the same time opening an outflow cross section which corresponds to the suction cross section.
  • the suction cross-section must always be so large that it ensures sufficient filling of the pump work area even at maximum speeds. This cross section is all the more sufficient for the pressure relief during the pressure stroke of the pump piston.
  • Another advantage of the invention is that the two end positions of the distributor piston can be better determined.
  • the guide recess is L-shaped with a longitudinal groove serving as an introduction and opening into the end face of the distributor piston, to which the guide section with the oblique control surface adjoins in the circumferential direction.
  • the guide recess in the guide section has a sack-shaped extension into which the driving finger is hooked for normal operation of the fuel injection pump.
  • the suction channels arranged in the distributor cylinder are designed in a slot-like manner, so that in the position of the distributor piston for turning off the Motors there is an optimal cross-sectional coverage between suction openings and suction distributor grooves.
  • the distributor piston for engine shutdown is displaced against a return spring, the return spring being arranged in a bushing for limiting the stroke and reducing friction.
  • FIG. 1 shows a distributor fuel injection pump in longitudinal section
  • FIG. 2 shows a detail from FIG. 1 on an enlarged scale for the operating position of the distributor piston
  • FIG. 3 shows a development on an enlarged scale of the guide recess
  • FIG. 4 shows a schematic representation of the longitudinal suction grooves and the 2
  • FIGS. 5 to 7 representations corresponding to the representations shown in FIGS. 2 to 4 for the stop position of the distributor piston.
  • FIG. 1 The illustration of a distributor fuel injection pump chosen in FIG. 1 is basically a longitudinal section through the distributor injection pump, although the cuts are arranged in different planes in order to make it easier to overlook the function of the pump. In addition, some parts are only partially shown for clarity.
  • a drive shaft 2 is mounted in a housing 1 and is driven at a speed synchronous with the engine speed.
  • a feed pump 3 is driven by the drive shaft 2, which is shown rotated by 90 ° here and is mounted in the pump housing 1.
  • the drive shaft 2 drives a cup-shaped driving part 4, which in turn drives a cam ring 5, which is mounted in the housing 1 for its rotation.
  • the pump housing 1 is closed by a housing head 6, in which a distribution cylinder 7 is arranged.
  • a distribution cylinder 7 In the distribution cylinder 7, radial pistons 8 are supported in radial bores, only one of which is shown and which is anchored to a roller shoe 9 of a drive roller 11.
  • a piston spring 12 engages the roller shoe 9 and presses the roller 11 against the cam track of the cam ring 5, thereby to ensure a reciprocating movement of the radial piston 8 determined by the cams.
  • a distributor piston 14 is axially displaceably and rotatably mounted.
  • a driving finger 15 is arranged on the driving part 4, which engages in a guide recess 16 in the outer surface of the distributor piston 14.
  • annular groove 17 is also provided, which delimits a pump working space 19 with the guide bore 13 and the corresponding end face of the radial piston 8 and the cylinder bore 18 receiving the radial piston 8.
  • an existing bore 21 in the distributor piston 14 leads to a distributor groove 22 which, during one revolution of the distributor piston 14, successively overlaps with pressure lines 23, the number of which corresponds to the number of cylinders of the internal combustion engine which are supplied with fuel.
  • Each pressure line 23 leads to an injection nozzle 24, of which only one is shown.
  • the distributor groove 22 is in register with one of the pressure lines 23, so that the To allow promotion to one of the fuel injectors 24.
  • the pump working space 19 is connected to a suction space 27, which is filled with fuel under a certain pressure, via longitudinal suction grooves 25 arranged in the lateral surface of the distributor piston 14 and with suction channels 26 which cooperate with these.
  • the number of longitudinal suction grooves 25 and suction channels 26 corresponds to the number of pressure lines 23, so that a considerable suction cross section is available during the suction stroke of the pump piston 8.
  • the injection quantity is controlled via a solenoid valve 28, which controls a relief channel 29 of the pump work chamber 19, which ends 31 in the suction chamber 27.
  • a solenoid valve 28 which controls a relief channel 29 of the pump work chamber 19, which ends 31 in the suction chamber 27.
  • a return spring 34 acts on the distributor piston 14 in the direction of the operating position, while the other end faces into a control chamber 35, via which the fuel delivered by the feed pump 3 under a certain pressure is delivered into the suction chamber 27.
  • a conveying channel 36 which opens into the control chamber 35, and a conveying line 37 extending therefrom, which then ends in the relief channel 29, which opens at 31 into the suction chamber 27.
  • a control valve 38 designed as a solenoid valve is arranged, which, as soon as it is closed, causes a backlog that causes the amount of fuel delivered by the delivery pump 3, so that a back pressure can build up in the control chamber 35 above the end face of the distributor piston 14.
  • the distributor piston 14 is displaced counter to the force of the return spring 34, so that a short-circuit connection of the pump working chamber is already produced during the pressure stroke of the radial piston 8 via the longitudinal suction grooves 25 and the suction channels 26 due to the relative rotation of the distributor piston 14 to the driving part 4 19 to the suction chamber 27 arises.
  • this relative rotation of the distributor piston 14 means that the distributor groove 22 is no longer in overlap with the pressure line 23 during the pressure stroke of the radial piston 8.
  • a pressure valve 41 is provided between the suction chamber 27 and the suction side of the feed pump 3.
  • the distributor fuel injection pump described works as follows. As soon as the drive shaft 2 is rotated when the engine is started, the radial piston or pistons 8 begin the reciprocating pump movement. By the rotating cam ring 5, the inner cam track of this cam ring 5 is pulled over the rollers 11 of the radial piston 8, the piston springs 12 ensuring a positive contact between the rollers 11 and the cam track, so that each radial piston 8 is driven by the piston spring 12 performs a suction stroke and a pressure stroke driven by the cams. During the suction stroke of the radial piston 8, fuel is conveyed from the suction chamber 27 into the pump working chamber 19 via the longitudinal suction grooves 25 and suction channels 26.
  • the distributor piston 14 When the distributor piston 14 is turned further, the longitudinal suction grooves 25 are separated from the suction channels 26 and the distributor groove 22 is brought into alignment with one of the pressure lines 23, so that in the meantime pressure stroke of the radial piston 8 causes fuel from the pump work chamber 19 via the bore 21 and the Distributor groove 22 is conveyed into the pressure lines 23 to the nozzles 24.
  • the amount of fuel to be injected is limited in that the solenoid valve 28 opens in time after energizing the electromagnet 32, so that the remaining fuel delivered during this pressure stroke flows back into the suction chamber 27 via the relief part 29. After the end of the pressure stroke and before the start of the suction stroke of the radial piston 8, the solenoid valve 28 is closed again, so that the injection cycle can begin again.
  • the control valve 38 When the engine is started up, the control valve 38 is opened by energizing the magnet 39, so that the distributor slide 14 remains in its initial position. To switch off the engine, for example via the ignition key, the magnet 39 is de-energized and the control valve 38 is closed, so that the distribution piston 14 is displaced against the force of the return spring 34 by the feed pump pressure which is set in the control chamber 35 and thus during the pressure Strokes of the radial piston 8, the longitudinal suction grooves 25 overlap with the suction channels 26.
  • the injection pump is regulated to achieve the desired characteristic curves by means of an electronic control unit, via which the magnet 32 of the solenoid valve 28 is controlled. Additional individual operating parameters can in part be taken from the fuel injection pump (not shown), but can also be taken from the internal combustion engine or the environment via corresponding sensors and processed in the electronic control unit.
  • Fig. 2 are shown on an enlarged scale and partially schematized (solenoid valves, feed pump) across the parts important for the invention.
  • an overpressure line 42 branches off from the delivery line 37 upstream of the control valve 38 and opens directly into the suction chamber 27.
  • a check valve 43 is arranged in this overpressure line 42, by means of which the pressure in the control chamber 35 required for the adjustment of the distributor piston 14 can be limited.
  • the return spring 34 is encapsulated by a bushing 44, in order thereby to avoid tilting of the spring or unnecessary friction with the wall of the blind bore 45 receiving the spring 34, since this causes the displacement movement of the distributor piston 14 and thus could affect the switching off of the engine.
  • the driving finger 15 is arranged on a bolt 46 which is fastened in a corresponding radial bore in the driving part 4.
  • annular groove 47 which communicates with the distributor groove 22 and which cooperates with the inlet of the relief channel 29, is provided in the distributor piston 14.
  • the driving finger 15 slides in the longitudinal guide groove 48 before it reaches the oblique control surface 51 in the guide section 49 in a bayonet-like manner.
  • the driving finger 15 slides along the oblique control surface 51 out of the bag-shaped one Extension 52 out, due to the inclination of the control surface 51, a corresponding relative rotation of the distributor piston 14 with respect to the driving part 4 takes place.
  • FIG. 4 the assignment of the longitudinal suction grooves 25 arranged in the lateral surface of the distributor piston 14 to the mouths of the suction channels 26 facing them is shown purely schematically. As can clearly be seen, the suction channels 26 are also designed as slots in order to obtain the greatest possible overlap with the longitudinal suction grooves 25.
  • the relative rotation b has the effect that, as shown in FIG. 7, the longitudinal suction grooves 25 are in register with the slots of the suction channels 26.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)
EP89122725A 1989-01-07 1989-12-09 Pompe distributrice d'injection de combustible pour moteurs à combustion interne Expired - Lifetime EP0377830B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3900318 1989-01-07
DE3900318A DE3900318A1 (de) 1989-01-07 1989-01-07 Verteilerkraftstoffeinspritzpumpe fuer brennkraftmaschinen

Publications (2)

Publication Number Publication Date
EP0377830A1 true EP0377830A1 (fr) 1990-07-18
EP0377830B1 EP0377830B1 (fr) 1992-09-16

Family

ID=6371685

Family Applications (1)

Application Number Title Priority Date Filing Date
EP89122725A Expired - Lifetime EP0377830B1 (fr) 1989-01-07 1989-12-09 Pompe distributrice d'injection de combustible pour moteurs à combustion interne

Country Status (4)

Country Link
US (1) US5020493A (fr)
EP (1) EP0377830B1 (fr)
JP (1) JPH02227550A (fr)
DE (2) DE3900318A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5878710A (en) * 1998-07-20 1999-03-09 Caterpillar Inc. Fuel injection shutdown system

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2771066A (en) * 1953-01-30 1956-11-20 Bosch Arma Corp Fuel injection pump
FR2356014A1 (fr) * 1976-06-26 1978-01-20 Lucas Industries Ltd Perfectionnements aux pompes d'injection de combustible liquide
GB2122695A (en) * 1982-06-29 1984-01-18 Bosch Gmbh Robert Fuel injection pump
DE3719807A1 (de) * 1987-06-13 1988-12-22 Bosch Gmbh Robert Verteilerkraftstoffeinspritzpumpe der radialkolbenbauart

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1387296A (fr) * 1963-12-19 1965-01-29 Sigma Perfectionnements apportés aux pompes d'injection de combustible à distributeur rotatif
US4377139A (en) * 1979-09-18 1983-03-22 Lucas Industries Limited Pumping systems
DE3035605A1 (de) * 1980-09-20 1982-05-06 Robert Bosch Gmbh, 7000 Stuttgart Abstellvorrichtung fuer kraftstoffeinspritzpumpen
US4426983A (en) * 1980-10-04 1984-01-24 Lucas Industries Limited Liquid fuel pumping apparatus
US4393826A (en) * 1980-12-23 1983-07-19 Lucas Industries Limited Liquid fuel injection pumping apparatus
US4441474A (en) * 1980-12-31 1984-04-10 Lucas Industries Limited Fuel injection pumping apparatus
DE3124500A1 (de) * 1981-06-23 1983-01-13 Robert Bosch Gmbh, 7000 Stuttgart Kraftstoffeinspritzpumpe
ES8702583A1 (es) * 1986-02-24 1987-01-16 Cav Condiesel Sa Perfeccionamientos en las bombas rotativas de inyeccion.
GB8613409D0 (en) * 1986-06-03 1986-07-09 Lucas Ind Plc Fuel injection pumps
DE3719831A1 (de) * 1987-06-13 1988-12-22 Bosch Gmbh Robert Kraftstoffeinspritzpumpe
GB8724795D0 (en) * 1987-10-22 1987-11-25 Lucas Ind Plc Fuel injection pump

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2771066A (en) * 1953-01-30 1956-11-20 Bosch Arma Corp Fuel injection pump
FR2356014A1 (fr) * 1976-06-26 1978-01-20 Lucas Industries Ltd Perfectionnements aux pompes d'injection de combustible liquide
GB2122695A (en) * 1982-06-29 1984-01-18 Bosch Gmbh Robert Fuel injection pump
DE3719807A1 (de) * 1987-06-13 1988-12-22 Bosch Gmbh Robert Verteilerkraftstoffeinspritzpumpe der radialkolbenbauart

Also Published As

Publication number Publication date
DE3900318A1 (de) 1990-07-12
DE58902298D1 (de) 1992-10-22
US5020493A (en) 1991-06-04
EP0377830B1 (fr) 1992-09-16
JPH02227550A (ja) 1990-09-10

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