EP0185915A2 - Pompe d'injection de carburant pour moteurs à combustion interne - Google Patents

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

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Publication number
EP0185915A2
EP0185915A2 EP85114588A EP85114588A EP0185915A2 EP 0185915 A2 EP0185915 A2 EP 0185915A2 EP 85114588 A EP85114588 A EP 85114588A EP 85114588 A EP85114588 A EP 85114588A EP 0185915 A2 EP0185915 A2 EP 0185915A2
Authority
EP
European Patent Office
Prior art keywords
pump
control
pump piston
delivery
piston
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.)
Withdrawn
Application number
EP85114588A
Other languages
German (de)
English (en)
Other versions
EP0185915A3 (fr
Inventor
Josef Güntert
Walter Häfele
Helmut Dr. Dipl.-Ing. Tschöke
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 EP0185915A2 publication Critical patent/EP0185915A2/fr
Publication of EP0185915A3 publication Critical patent/EP0185915A3/fr
Withdrawn legal-status Critical Current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
    • F02M59/24—Varying fuel delivery in quantity or timing with constant-length-stroke pistons having variable effective portion of stroke
    • F02M59/26—Varying fuel delivery in quantity or timing with constant-length-stroke pistons having variable effective portion of stroke caused by movements of pistons relative to their cylinders
    • 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
    • F02M59/361—Valves being actuated mechanically

Definitions

  • the invention relates to a fuel injection pump according to the preamble of the main claim.
  • Such slide-controlled pumps are mainly used for high delivery rates of mostly less high-speed diesel engines, so that inaccuracies in fuel metering are particularly sensitive as uneven running of the engine and in which the damage that occurs, for example, due to incorrect fuel metering, is particularly costly.
  • the quantity control orifice plunges into the inner bore of the control slide after a stroke determined by the position of the control slide, after which the injection can begin by blocking the quantity control channel.
  • the injection is interrupted again by relieving the pressure in the pump work area.
  • the start and end of delivery are determined by the stroke position of the control spool and the injection quantity by turning the control spool.
  • the pump piston can also be turned slightly for a basic setting.
  • the fuel injection pump according to the invention with the characterizing features of the main claim has that compared to the advantage that the earliest start of delivery is determined independently of the axial position of the control slide by the interaction of the delivery start control opening in the pump piston with the stationary pump cylinder. Accordingly, even when the control slide is pushed extremely down, the start of delivery can no longer take place at an early point in time that is critical for the motor and could possibly result in the motor being destroyed.
  • a control opening of a control channel leading to a low pressure space, in particular a suction space is arranged in the pump cylinder surface, which after covering a maximum delivery stroke of the pump piston can be covered with the delivery start control opening in the pump piston.
  • this reduction in the injection quantity can go so far that zero delivery takes place if the delivery start control opening coincides with the discharge opening before the quantity control channel dips into the bore of the control slide.
  • this embodiment of the invention can advantageously achieve that the high-pressure delivery is ended before the role of the roller tappet in the linear drive portion of the cam drive cam on a curved section, which would strengthen the contact surface (more or less wide line) due to the opposing, pressed parts.
  • the Hertzian pressures in the pairing curvature / straight compared to curvature / curvature can increase many times over without risk of engine damage.
  • the pump piston can be rotated for quantity control and the upper boundary edge of the control groove can be stepped and / or inclined, i. H. the upper control edge of the delivery start control opening facing the pump working chamber can be offset, so that advantageously the maximum delivery stroke determined independently of the control slide also changes when the pump piston is rotated with the injection quantity.
  • the maximum delivery rate for full load can be increased to the larger maximum delivery rate for starting by turning the pump piston.
  • the delivery start control opening opens in a controlled position and / or the control channel of the control opening opens into a suction chamber which serves to supply fuel.
  • the pump work space filling is thereby ensured regardless of the respective control cross section between the control slide and the volume control opening of the pump piston, since the bottom of the pump piston is above the delivery start control opening and / or the discharge opening due to the behavior
  • there is only a slight throttling effect at the inflow This applies particularly to high speeds, so that the pump according to the invention can be used at higher speeds than the known pumps.
  • Refilling the pump workspace is not only necessary to meet the maximum funding, but also to avoid cavitation within the pump workspace.
  • FIG. 1 shows a longitudinal section through the upper part of an in-line fuel injection pump as the first exemplary embodiment
  • FIG. 2 rotates a section of the pump piston from FIG. 1 by 90 ° and on an enlarged scale
  • FIG. 3 shows a representation of the second exemplary embodiment corresponding to FIG. 1 .
  • a plurality of cylinder liners 2, of which only one is shown, are embedded in series, in which pump pistons. 3 via a camshaft, which is no longer shown are driven against the force of a spring 5 for their axial movement forming the working stroke.
  • the cylinder liner 2 there is a recess 6 which receives a control slide 7 which is axially displaceable on the pump piston 3.
  • the individual control slide 7, which are arranged on the pump piston 3 arranged in a pump, are displaced together by a control rod 8, for which purpose a clamping ring 9 with head 10 is clamped on the rotatable control rod 8 for each control slide 7, the head 10 in an annular groove 11 of the control slide 7 engages.
  • a pump working space 12 is delimited by the pump piston 3 and the cylinder liner 2.
  • a blind bore 15 runs in the pump piston, which opens into the pump work chamber 12 and is crossed by a first transverse bore 16 near the pump work chamber 12 and opens into a second transverse bore 17 with its end facing away from the pump work chamber 12.
  • the first transverse bore 16 ends in grooves 18 arranged on the piston surface, which are formed by transverse cuts and which each have a control edge 19 running at right angles to the direction of movement.
  • the second transverse bore 17 opens into two oblique grooves 20 and longitudinal grooves 21, only one of which is shown; the second groove is located on the back of the piston.
  • These grooves 20, 21 are through the control slide 7 for quantity control controlled by being pushed into the inner bore 22 of the control slide 7 during the stroke of the pump piston 3, after which the pump working space 12 is blocked in this direction, so that the pressure required for the injection can build up until the oblique groove 20 overlaps with a arranged in the control slide 7 relief bore 23.
  • this pressure stroke which enables a high pressure in the pump working chamber 12, is different.
  • the recess 6 is connected to a suction chamber 24 in the housing, which is filled with fuel under low pressure.
  • This suction chamber 24 is thus also connected to the grooves 18, 19 and 20, as long as these are not covered by the control slide 7 or the cylinder liner 2.
  • the pump piston 3 can be rotated in a known manner by a speed controller, not shown, via a control rod 25, for which this engages with a driving element 26 on a flattened portion 27 of the pump piston.
  • the first exemplary embodiment shown in FIGS. 1 and 2 works as follows: During the suction stroke of the pump piston 3 and in the region of the bottom dead center of its stroke movement, the suction chamber 24 flows out through the openings serving to control the quantity, namely the oblique groove 20 and the longitudinal groove 21 and Bores 17 and 15 of fuel in the pump work chamber 12. In addition, fuel also flows via the grooves 18, the transverse bore 16 and the end section of the blind bore 15 from the suction chamber 24 into the pump work chamber 12.
  • the inflow cross-section via the grooves 20 and 21 depends on the position of the control slide 7, it also being possible for these two grooves 20, 21 to be through the control slide 7 are fully covered when the control slide assumes a position which is shifted downwards relative to the position shown.
  • the control grooves 18 are immersed in the cylinder liner 2 after the advance stroke has always been the same, so that the connection via the transverse bore 16 is blocked. Only from this preliminary stroke can pressure build up in the pump work chamber 12, provided that the oblique groove 20 and longitudinal groove 21 are also covered by the control slide 7.
  • the start of delivery after sufficient pressure build-up in the pump work chamber 12 can therefore take place at the earliest after the advance stroke determined by the position of the grooves 18 has been completed, but is additionally determined by the stroke of the pump piston 3, which is necessary so that the grooves 20 and 21 are also covered.
  • the injection end is then, as already described, determined by opening the oblique groove 20 through the relief bore 23.
  • this end of delivery is at different times - in each case for a specific position of the control slide 7 - so that the injection quantity depends on the rotational position of the pump piston 3, ie the injection quantity is changed by rotating the pump piston 3.
  • the start of delivery or start of spraying is determined for normal engine operation by the axial position of the spool 7, that is the further the control slide 7 is at the bottom, the earlier the delivery begins, the higher it is at the top, the later the injection begins.
  • this start of delivery which can be determined by the control slide 7, but can be changed, the start of delivery determined by the grooves 18 after the advance stroke has been completed is always constant, so that, depending on the axial position of the control slide 7, the actual start of delivery is determined either by the control slide or by the grooves 18. In any case, the earliest possible start of delivery is determined by the grooves 18.
  • control slide 7 If the control slide 7 is pushed down into an extreme position for the early start of delivery, the longitudinal grooves 21 dip into the control slide 7 from a certain position before the transverse grooves 18 are blocked by the pump cylinder, whereby the latter determine the start of delivery, which is as early as possible and is constant.
  • the further the control slide 7 is pushed downward the shorter the remaining stroke of the pump piston 3 between the immersion of the transverse grooves 18 in the cylinder liner, which determines the start of delivery, and the overlapping of the oblique grooves 20 with the relief bore 23, which is a corresponding reduction in the Injection volume results.
  • the further the control slide 7 is shifted downwards in the early direction the smaller the injection quantity becomes down to the zero delivery quantity, which would result in the engine being switched off. This can be particularly advantageous if the control slide 7 would slide down due to its own weight due to failure of the control gear 8, so that the injection was interrupted if the control device failed.
  • annular groove 118 is arranged on the pump piston 103 for the purpose of generating the stroke, said annular groove 118 having a stepped control edge 119 at the top.
  • a radial bore 28 serving as a control channel is provided in the cylinder liner 102, which opens into the pump working chamber 112 at the bottom dead center position UT of the pump piston 103 and on the other hand leads to the suction chamber 24.
  • the radial bore 28 serves as an additional filling possibility for the pump work chamber 112.
  • it serves as a discharge opening, in that during the pressure stroke of the pump piston 103 after covering a maximum possible pressure stroke, the annular groove 118 which previously controlled the start of delivery comes into overlap with the radial bore 28, thereby over this control channel, the pump work chamber 112 is relieved of pressure towards the suction chamber 24. With the start of conveyance control opening 118, the latest possible end of conveyance is thus also controlled.
  • the stepped design of the control edge 119 causes a different maximum amount depending on the rotational position of the pump piston 103, for example for full load and for start.
  • the corresponding rotational position of the pump piston 103 opens the radial bore 28 serving as the end-of-delivery control opening somewhat later than at full load, in which a smaller injection quantity than when starting is required.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)
EP85114588A 1984-12-24 1985-11-16 Pompe d'injection de carburant pour moteurs à combustion interne Withdrawn EP0185915A3 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3447375 1984-12-24
DE3447375A DE3447375A1 (de) 1984-12-24 1984-12-24 Kraftstoffeinspritzpumpe fuer brennkraftmaschinen

Publications (2)

Publication Number Publication Date
EP0185915A2 true EP0185915A2 (fr) 1986-07-02
EP0185915A3 EP0185915A3 (fr) 1988-01-07

Family

ID=6253879

Family Applications (1)

Application Number Title Priority Date Filing Date
EP85114588A Withdrawn EP0185915A3 (fr) 1984-12-24 1985-11-16 Pompe d'injection de carburant pour moteurs à combustion interne

Country Status (4)

Country Link
US (1) US4705005A (fr)
EP (1) EP0185915A3 (fr)
JP (1) JPS61157754A (fr)
DE (1) DE3447375A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0185914A2 (fr) * 1984-12-24 1986-07-02 Robert Bosch Gmbh Pompe d'injection de carburant pour moteurs à combustion interne
FR2606090A1 (fr) * 1986-10-31 1988-05-06 Bosch Gmbh Robert Pompe d'injection de carburant pour moteur a combustion interne

Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6295173U (fr) * 1985-12-05 1987-06-17
DE3633899A1 (de) * 1986-10-04 1988-04-07 Bosch Gmbh Robert Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
EP0301222B1 (fr) * 1987-07-25 1992-05-06 Robert Bosch Gmbh Pompe d'injection de combustible pour moteurs à combustion interne
DE3813320A1 (de) * 1988-04-08 1989-10-19 Voest Alpine Automotive Pumpenduese fuer dieselmotoren
DE3811845A1 (de) * 1988-04-08 1989-10-19 Voest Alpine Automotive Pumpeduese fuer dieselmotoren
US5080564A (en) * 1989-02-08 1992-01-14 Diesel Kiki Co., Ltd. Prestroke control device for fuel injection pumps
DE3926166A1 (de) * 1989-08-08 1991-02-14 Bosch Gmbh Robert Kraftstoffeinspritzpumpe fuer dieselbrennkraftmaschinen
DE4137073A1 (de) * 1991-11-12 1993-05-13 Bosch Gmbh Robert Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
JPH10231763A (ja) * 1997-02-18 1998-09-02 Zexel Corp 燃料噴射ポンプ

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2147390A (en) * 1934-04-17 1939-02-14 Provencale De Const Aeronautiq Fuel feed pump
US3667437A (en) * 1970-08-19 1972-06-06 Allis Chalmers Mfg Co Multiple plunger fuel injection pump
US4211520A (en) * 1978-01-20 1980-07-08 Caterpillar Tractor Co. Timing control for sleeve metering fuel system
US4351293A (en) * 1979-06-04 1982-09-28 Hewitt John T Diesel vehicle speed control system
EP0185914A2 (fr) * 1984-12-24 1986-07-02 Robert Bosch Gmbh Pompe d'injection de carburant pour moteurs à combustion interne

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2746443A (en) * 1953-02-20 1956-05-22 Texas Co Fuel injection pump
US3312209A (en) * 1964-11-12 1967-04-04 Bosch Arma Corp Fuel delivery system
DE3018791A1 (de) * 1980-05-16 1981-11-26 Robert Bosch Gmbh, 7000 Stuttgart Kraftstoffeinspritzpumpe fuer brennkraftmaschinen

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2147390A (en) * 1934-04-17 1939-02-14 Provencale De Const Aeronautiq Fuel feed pump
US3667437A (en) * 1970-08-19 1972-06-06 Allis Chalmers Mfg Co Multiple plunger fuel injection pump
US4211520A (en) * 1978-01-20 1980-07-08 Caterpillar Tractor Co. Timing control for sleeve metering fuel system
US4351293A (en) * 1979-06-04 1982-09-28 Hewitt John T Diesel vehicle speed control system
EP0185914A2 (fr) * 1984-12-24 1986-07-02 Robert Bosch Gmbh Pompe d'injection de carburant pour moteurs à combustion interne

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0185914A2 (fr) * 1984-12-24 1986-07-02 Robert Bosch Gmbh Pompe d'injection de carburant pour moteurs à combustion interne
EP0185914A3 (en) * 1984-12-24 1988-01-07 Robert Bosch Gmbh Fuel injection pump for internal combustion engines
FR2606090A1 (fr) * 1986-10-31 1988-05-06 Bosch Gmbh Robert Pompe d'injection de carburant pour moteur a combustion interne
DE3724409A1 (de) * 1986-10-31 1988-05-19 Bosch Gmbh Robert Kraftstoffeinspritzpumpe fuer brennkraftmaschinen

Also Published As

Publication number Publication date
US4705005A (en) 1987-11-10
EP0185915A3 (fr) 1988-01-07
DE3447375A1 (de) 1986-07-03
JPS61157754A (ja) 1986-07-17

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Inventor name: GUENTERT, JOSEF

Inventor name: HAEFELE, WALTER

Inventor name: TSCHOEKE, HELMUT, DR. DIPL.-ING.