EP0261156B1 - Pompe a injection de carburant pour moteurs a combustion interne - Google Patents

Pompe a injection de carburant pour moteurs a combustion interne Download PDF

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Publication number
EP0261156B1
EP0261156B1 EP87901398A EP87901398A EP0261156B1 EP 0261156 B1 EP0261156 B1 EP 0261156B1 EP 87901398 A EP87901398 A EP 87901398A EP 87901398 A EP87901398 A EP 87901398A EP 0261156 B1 EP0261156 B1 EP 0261156B1
Authority
EP
European Patent Office
Prior art keywords
pump
working chamber
oblique groove
control
pump 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.)
Expired - Lifetime
Application number
EP87901398A
Other languages
German (de)
English (en)
Other versions
EP0261156A1 (fr
Inventor
Josef Güntert
Walter Häfele
Johann Warga
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
Priority to AT87901398T priority Critical patent/ATE58574T1/de
Publication of EP0261156A1 publication Critical patent/EP0261156A1/fr
Application granted granted Critical
Publication of EP0261156B1 publication Critical patent/EP0261156B1/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
    • F02M59/24—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
    • F02M59/265—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 characterised by the arrangement or form of spill port of spill contour on the piston
    • 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

Definitions

  • the invention is based on a fuel injection pump according to the preamble of claim 1.
  • a known injection pump of this type (DE-A-34 28 174)
  • the control recess in the pump piston in addition to an oblique groove for controlling the delivery end during the pressure stroke of the pump piston, also has one with the latter connected longitudinal groove, the end edge of which away from the pump work space controls the start of delivery.
  • the longitudinal groove at a certain relative rotational position of the pump piston and the control slide serves to completely cancel the injection delivery in order to achieve a safe and quick shutdown of the internal combustion engine.
  • control recess in the pump piston jacket designed in this way, considerable functional advantages are achieved compared to previously known fuel injection pumps, but it has the disadvantage that, due to the large area of the control recess, which is acted upon by the injection pressure during the pressure stroke of the pump piston, the pressure prevailing there is also at the pressure with the latter Surface covering part of the inside of the spool acts, so that with a relatively thin-walled spool for reasons of space, a deformation of the spool occurs with an increase in friction during the pump piston stroke and that the durability of the spool is greatly reduced by the load changes occurring with each piston stroke.
  • the fuel injection pump according to the invention with the characterizing features of claim 1 has the advantage that the durability and service life of the spool is very high due to the relatively small pressurized area of the control recess in the pump piston.
  • a preferred, relatively slow pressure increase is achieved by the shape of the countersink, the control edge of which forms an arc when immersed in the slider.
  • a rapid pressure drop is achieved when unnecessary, since unnecessary deflections of the control quantity between the channel in the pump piston and the control bore in the control slide are largely avoided.
  • FIG. 1 shows a part of a fuel injection pump in cross section
  • FIG. 2 shows a pump piston of the fuel injection pump according to FIG. 1 on an enlarged scale
  • FIG. 3 shows the pump piston according to FIG. 2 in cross section in plane 111-111 of FIG. 2
  • FIG. 4 shows a development of the lateral surface of the Pump piston in the control area according to Figure 2
  • Figure 5 is a partial view of a pump piston corresponding to Figure 2, but for the second embodiment
  • Figure 6 shows an embodiment of the pump piston shown in Figure 2 for the third embodiment.
  • cylinder liners 2 are inserted in a row in a housing 1 of a fuel injection pump, in which pump pistons 3 are driven for their axial movement by a camshaft (not shown).
  • a recess 4 is provided, which receives a control slide 5 axially displaceable on the pump piston 3.
  • the control slide 5 can be axially adjusted by a housing-mounted lever 6 to change the start of delivery, for which this lever engages with a ball head 7 in a groove 8 of the control slide 5.
  • the drive-side end of the pump piston 3 with a flattened portion 10 engages axially displaceably in a rotatable sleeve 9.
  • This sleeve 9 has in its upper section a toothed ring 9a into which a toothed rack 11 serving as a control rod engages .
  • any other device can also serve as a twisting means.
  • two oblique grooves 15 are machined axially symmetrically as control recesses, which extend at a certain angle to the longitudinal axis of the pump piston 3 and which have a flat base 16 and two parallel, oblique control edges 17, 18.
  • a cylindrical countersink 21 is arranged in each end region 19 of the two oblique grooves 15, which is remote from the working end face 20 of the pump piston 3.
  • the Countersinks 21 have a diameter that is equal to or greater than the width of the inclined grooves 15.
  • the area of the recesses 21 partially overlaps, for example, a quarter to a third, with the end region 19 of the inclined grooves 15. Their depth is so great that its outer circumference cuts the bottom 16 of the oblique grooves 15.
  • the central axis of the countersinks 21 runs radially to the pump piston 3 and is arranged approximately at the level of an imaginary corner point 22 which is the most distant from the working end face 20 of the pump piston 3.
  • the countersinks 21 must be arranged in such a way that their drive-side boundaries formed by an arc 30 and not the corner points 22a determine the start of delivery. (The end region 19 is no longer visible and is therefore indicated by dash-dotted lines).
  • a transverse bore 24 radially penetrates the pump piston 3, into which a blind bore 25, which starts from the working end face 20 and runs axially in the pump piston 3, opens.
  • the transverse bore 24 and the blind bore 25 form a channel between the oblique grooves 15 and the pump working space 26, which is delimited by the end face 20 of the pump piston 3.
  • control slide 5 Arranged in the control slide 5 are two coaxial, opposite radial control bores 28 which cooperate with the control edge 17 of the oblique grooves 15 close to the working end face 20 of the pump piston 3 for determining the injection quantity, in particular for controlling the delivery end during the delivery stroke.
  • These diverter bores 28 have a noticeably larger diameter than known diverter bores, which ensures a rapid outflow of fuel from the pump work chamber 26 and prevents a renewed activation with corresponding subsequent delivery taking place after the end of delivery.
  • the start of delivery is controlled by the complete immersion of the counterbores 21 in the control slide 5 from an end edge 29 of the same and can be adjusted by axially displacing the control slide 5 on the pump piston 3.
  • This configuration of the oblique grooves 15 has the effect that, in the stop-rotary position of the pump piston 3, in which the countersinks 33 near the pump working chamber 26 come into congruence with the control bores 28 of the control slide 5 when the pump piston 3 is lifted, even with a slight slope of the oblique grooves 15 a zero delivery is effected since the counterbores 33 reach the control bores 28 before the counterbores 21, which are distant from the pump working chamber, dip into the ring slide 5, so that no pressure build-up takes place during the pump piston stroke.
  • the additional countersinks 33 near the pump work chamber 26 simulate practically steeper inclined grooves.
  • the third exemplary embodiment shown in FIG. 6 only differs in the control edge design from the previously described exemplary embodiments.
  • the pump piston 3 shown in a partial view in FIG. 6, like the pump piston described in FIG. 2, has relatively steep oblique grooves 15 and in the end region 19 distant from the pump work chamber 26, the cylindrical countersink 21.
  • the pump penarbeitsraum 26 distant end portion 19 of the oblique groove 15 there is a limiting groove 35 which extends at right angles to the axis of the pump piston 3 over a short section of the lateral surface and opens laterally into the oblique groove 15.
  • This limiting groove 35 is adjacent to the countersink 21, in the illustrated installation position of the pump piston just above this countersink 21 and forms with its boundary facing the pump working chamber 26 a horizontal control edge 36 into which the oblique control edge 17 merges and through which the effective length thereof is limited.
  • This measure to limit the effective length of the control edge 17 is particularly necessary if, due to the large useful stroke required between zero delivery and maximum full load delivery rate, the oblique groove 15 has to be introduced into the pump piston jacket surface at a relatively steep angle. Because of the change in the start of delivery possible by the control slide 5, there is a risk that if the delivery is inadvertently set to a larger delivery volume than the maximum full load, the pump delivery will take place near top dead center and thus on the small radius of the cam located there, which inevitably leads to cam damage . Such exceeding of the intended operating control range can occur if the full load stop is set incorrectly or if the controller malfunctions. Such cam damage is avoided, however, by the horizontal control edge 36, which serves to limit the useful stroke and is formed by the limiting groove 35.
  • the limiting grooves 35 described can of course be provided in the configuration of the control recesses shown there.
  • the width and depth of the limiting groove can be significantly smaller than the corresponding dimensions of the oblique groove 15, which ensure a quick injection end Overflow fuel must discharge quickly. So it is sufficient if e.g. at a width of the oblique groove 15 of three millimeters and a depth of 1.6 millimeters, the width and depth of the limiting groove 35 are only half as large.
  • the third exemplary embodiment also helps to achieve the object according to the invention by guaranteeing the required durability of the control slide 12 by means of the smallest possible area of the control recess.
  • the pump piston 3 is set such that it can be rotated relative to the control slide 5 in order to adjust the delivery rate.
  • the control slide can be set up not only axially but also rotatably in a manner known per se. Then the pump piston does not need to be turned.

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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)

Abstract

Une pompe à injection de carburant pour moteurs à combustion interne est équipée d'un piston (3) de pompe à mouvement de va-et-vient, ainsi que d'un distributeur (5) pouvant glisser sur celui-ci et muni d'un perçage de commande (28) qui coopère avec une rainure oblique (15) disposée sur le piston (3) de la pompe et reliée au moyen d'un passage (24, 25) avec la chambre de travail (6) de la pompe. Pour commander l'amorçage du pompage, la rainure oblique (15) est reliée à une dépression cylindrique (21) dans sa partie extrême (22), située à une certaine distance de la chambre de travail de la pompe. De plus, dans le cas de rainures obliques (15) relativement peu profondes, la chambre de travail de la pompe peut être reliée, dans la région de l'extrémité (23) de la rainure de commande (15), à une deuxième dépression de manière à permettre un refoulement nul.

Claims (7)

1. Pompe d'injection de carburant pour moteurs à combustion interne comprenant au moins un piston de pompe (3) animé d'un mouvement alternatif, qui délimite à une extrémité par une face frontale de travail (20) une chambre de travail de la pompe et est reliée à son autre extrémité à un entraînement, qui a sur sa surface latérale un évidement de commande relié par un canal (24, 25) à la chambre de travail de la pompe (26), qui présente une rainure oblique (15) s'étendant suivant un angle déterminé par rapport à la direction périphérique du piston de pompe (3) sur la surface latérale de celui-ci, pourvu d'un tiroir de commande (5) mobile axialement sur le piston de pompe (3), lequel commande au moyen d'un bord frontal (29) lors de la plongée de l'évidement de commande dans le tiroir de commande (5) le début de l'alimentation et commande au moyen d'un alésage de commande (28) radial, conjointement avec l'arête de commande (17) de la rainure oblique (15) située sur le côté de la chambre de travail de la pompe la fin de l'alimentation, le piston de pompe (3) et le tiroir de commande (5) pouvant tourner l'un par rapport à l'autre pour modifier la quantité refoulée, caractérisée en ce que l'évidement de commande présente la rainure oblique (15) et un chanfrein cylindrique (21) se raccordant à la zone d'extrémité éloignée (19) de la chambre de travail de la pompe (26) et couvrant en partie cette zone d'extrémité (19), dont une délimitation du côté entraînement formant une courbe (30) se trouve à une plus grande distance de la face frontale de travail (20) en regard de la chambre de travail de la pompe (26) qu'un point (22) fictif très éloigné de la chambre de travail (26) sur la zone d'extrémité (19) de la rainure oblique (15), en ce que le point (22) fictif constitue le point d'intersection du prolongement du bord côté entraînement de la rainure oblique (15) et du prolongement du bord voisin de la rainure oblique (15), en ce que le chanfrein élargit la zone d'extrémité (19) de la rainure oblique (15) éloignée de la chambre de travail de la pompe (26) et en ce que le canal (24, 25) débouche dans la zone médiane de la rainure oblique (15).
2. Pompe d'injection de carburant selon la revendication 1, caractérisée en ce que le diamètre du chanfrein (21) est supérieur à la largeur de la rainure oblique (15).
3. Pompe d'injection de carburant selon la revendication 1 ou 2, caractérisée en ce que le milieu du chanfrein (21) se trouve approximativement à la même hauteur que le point (22) fictif de la zone d'extrémité (19) de la rainure oblique (15) qui est très éloigné de la chambre de travail de la pompe (26).
4. Pompe d'injection de carburant selon l'une des revendications 1 à 3, caractérisée en ce que l'axe du chanfrein (21) s'étend radialement par rapport au piston (3).
5. Pompe d'injection de carburant selon l'une des revendications 1 à 4, caractérisée en ce que se raccorde à la zone d'extrémité (23) de la rainure oblique (15) proche de la chambre de travail de la pompe (26) un deuxième chanfrein (33) recouvrant en partie cette zone d'extrémité.
6. Pompe d'injection de carburant selon la revendication 5, caractérisée en ce que le deuxième chanfrein (33) s'étend en forme de courbe de la rainure oblique (15) à la chambre de travail de la pompe (26).
7. Pompe d'injection de carburant selon l'une des revendications qui précédent, caractérisée en ce que se trouve dans la zone d'extrémité (19) éloignée de la chambre de travail de la pompe (26) de la rainure oblique (15), voisine du chanfrein cylindrique (21) se trouvant là, une rainure de limitation (35) s'étendant dans la direction périphérique du piston de pompe (3) sur un court segment de sa surface latérale et débouchant latéralement dans la rainure oblique (15), qui limite avec une arête de commande (36) s'étendant suivant la direction périphérique du piston (3), la longueur utile de l'arête de commande (17) proche de la chambre de travail de la pompe (26).
EP87901398A 1986-03-22 1987-03-20 Pompe a injection de carburant pour moteurs a combustion interne Expired - Lifetime EP0261156B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT87901398T ATE58574T1 (de) 1986-03-22 1987-03-20 Kraftstoffeinspritzpumpe fuer brennkraftmaschinen.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3609759 1986-03-22
DE3609759 1986-03-22

Publications (2)

Publication Number Publication Date
EP0261156A1 EP0261156A1 (fr) 1988-03-30
EP0261156B1 true EP0261156B1 (fr) 1990-11-22

Family

ID=6297056

Family Applications (1)

Application Number Title Priority Date Filing Date
EP87901398A Expired - Lifetime EP0261156B1 (fr) 1986-03-22 1987-03-20 Pompe a injection de carburant pour moteurs a combustion interne

Country Status (6)

Country Link
US (1) US4830587A (fr)
EP (1) EP0261156B1 (fr)
JP (1) JPH086659B2 (fr)
BR (1) BR8706768A (fr)
DE (1) DE3766331D1 (fr)
WO (1) WO1987005665A1 (fr)

Families Citing this family (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3804843A1 (de) * 1988-02-17 1989-08-31 Bosch Gmbh Robert Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
DE3923306A1 (de) * 1989-07-14 1991-01-24 Daimler Benz Ag Schraegkantengesteuerte kraftstoffeinspritzpumpe fuer brennkraftmaschinen
DE3926166A1 (de) * 1989-08-08 1991-02-14 Bosch Gmbh Robert Kraftstoffeinspritzpumpe fuer dieselbrennkraftmaschinen
DE4100093A1 (de) * 1991-01-04 1992-07-09 Bosch Gmbh Robert Kraftstoffeinspritzpumpe fuer brennkraftmaschinen mit last- und/oder drehzahlabhaengigem einspritzverlauf
JP2552893Y2 (ja) * 1991-06-19 1997-10-29 株式会社ゼクセル 燃料噴射ポンプ
DE4132505A1 (de) * 1991-09-30 1993-04-01 Bosch Gmbh Robert Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
DE4132502C2 (de) * 1991-09-30 2001-09-27 Bosch Gmbh Robert Kraftstoffeinspritzpumpe
DE4306872A1 (de) * 1993-03-05 1994-09-08 Bosch Gmbh Robert Kraftstoffeinspritzpumpe für Brennkraftmaschinen
DE19526692A1 (de) * 1995-07-21 1997-01-23 Bosch Gmbh Robert Kraftstoffeinspritzeinrichtung für Brennkraftmaschinen
JP3612585B2 (ja) * 1996-10-31 2005-01-19 株式会社ボッシュオートモーティブシステム 燃料噴射ポンプのプランジャ

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3428174A1 (de) * 1984-07-31 1986-02-13 Robert Bosch Gmbh, 7000 Stuttgart Kraftstoffeinspritzpumpe fuer brennkraftmaschinen

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB604305A (en) * 1944-08-17 1948-07-01 Bendix Aviat Corp Improvements in or relating to reciprocating pumps
US2890657A (en) * 1955-08-12 1959-06-16 Gen Motors Corp Unit injector pump with pilot injection
DD113950A1 (fr) * 1974-03-19 1975-07-05
DE3224127A1 (de) * 1981-08-01 1983-02-24 Robert Bosch Gmbh, 7000 Stuttgart Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
AU563901B2 (en) * 1984-05-08 1987-07-23 Bosch Automotive Systems Corporation Fuel injection pump and method of adjusting the same pump
DE3435987A1 (de) * 1984-10-01 1986-04-10 Robert Bosch Gmbh, 7000 Stuttgart Kraftstoffeinspritzpumpe fuer brennkraftmaschinen

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3428174A1 (de) * 1984-07-31 1986-02-13 Robert Bosch Gmbh, 7000 Stuttgart Kraftstoffeinspritzpumpe fuer brennkraftmaschinen

Also Published As

Publication number Publication date
JPH086659B2 (ja) 1996-01-29
US4830587A (en) 1989-05-16
WO1987005665A1 (fr) 1987-09-24
EP0261156A1 (fr) 1988-03-30
JPS63503076A (ja) 1988-11-10
DE3766331D1 (de) 1991-01-03
BR8706768A (pt) 1988-02-23

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