EP0469142A1 - Dispositif d'injection de carburant pour moteurs a combustion interne a injection. - Google Patents

Dispositif d'injection de carburant pour moteurs a combustion interne a injection.

Info

Publication number
EP0469142A1
EP0469142A1 EP91905879A EP91905879A EP0469142A1 EP 0469142 A1 EP0469142 A1 EP 0469142A1 EP 91905879 A EP91905879 A EP 91905879A EP 91905879 A EP91905879 A EP 91905879A EP 0469142 A1 EP0469142 A1 EP 0469142A1
Authority
EP
European Patent Office
Prior art keywords
control edge
injection
piston
delivery
recess
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
EP91905879A
Other languages
German (de)
English (en)
Other versions
EP0469142B1 (fr
Inventor
Gerhard Weiss
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 AG
Original Assignee
Automotive Diesel 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 Automotive Diesel GmbH filed Critical Automotive Diesel GmbH
Publication of EP0469142A1 publication Critical patent/EP0469142A1/fr
Application granted granted Critical
Publication of EP0469142B1 publication Critical patent/EP0469142B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

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
    • F02M45/00—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship
    • F02M45/02—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts
    • F02M45/04—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts with a small initial part, e.g. initial part for partial load and initial and main part for full load
    • F02M45/06—Pumps peculiar thereto
    • F02M45/066—Having specially arranged spill port and 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
    • F02M45/00—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship
    • F02M45/02—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts
    • F02M45/04—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts with a small initial part, e.g. initial part for partial load and initial and main part for full load
    • F02M45/06—Pumps peculiar thereto
    • 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

Definitions

  • the invention relates to a fuel injection device for injection internal combustion engines, in which a
  • pump piston and a pump piston bushing or a control sleeve can be rotated relative to one another and the delivery end is determined by at least one oblique control edge of one part, which overlaps an overflow bore of the other part, and the start of delivery by a ⁇ _5 other control edge of this one part, which overflows the overflow bore of the other part, is determined, an escape piston guided in an escape cylinder connected to the high-pressure chamber being provided to achieve a pre-injection and main injection, and the volume released by the escape piston being the injection pause between pre-injection and main injection.
  • the curve according to which the oblique control edge runs is continuous.
  • the control angle over which the rotatable part has to be rotated in the phase from the beginning of the control of the fuel in the alternating cylinder to the reaching of the full swallowing volume of the alternating cylinder, which corresponds to the interval between the pre-injection and the main injection, is relatively large .
  • This also represents a considerable disadvantage.
  • a reduction in the control angle could indeed be achieved by a steeper arrangement of the oblique control edge, but this would again reduce the control sensitivity.
  • the object of the invention is to shorten the required control angle.
  • the invention essentially consists in that the oblique control edge in the region of zero conveyance has a recess which springs back in the direction of the rotary positions corresponding to an increase in the conveyance, and that the distance at which the oblique control edge enters the recessed recess passes from the control edge controlling the start of delivery is larger than the diameter of the overflow bore. Through this recess, the rotary position "zero delivery” is shifted towards the rotary positions corresponding to an increase in the delivery. The angle of rotation between the rotational position corresponding to zero delivery at maximum speed and the rotational position corresponding to idling is reduced.
  • control angle is also reduced in the phase between the beginning of the overflow of the fuel into the evasive cylinder until the full swallowing volume thereof is reached. It is even possible to reduce this control angle to zero at a predetermined speed. In this way, a substantial reduction in the overall control angle is achieved in the entire control range.
  • the delivery is ended. This applies to both idle and load operation. Because the distance from the point at which the oblique control edge merges into the recessed recess from the control edge controlling the start of delivery is greater than the diameter of the overflow bore, a useful stroke results in all rotary positions between the completion of the overflow bore and the opening thereof. which also ensures the delivery rate required when idling. If this distance were equal to or less than the diameter of the overflow bore, the delivery volume would be swallowed by the compensating cylinder and no main injection would develop.
  • the inclined control edge can spring back in the form of a step to form this recess.
  • a step can be easily incorporated into the oblique control edge.
  • the region of the control edge forming the step runs in the direction of the axis of the pump piston. In the case of zero delivery, the step enables the outflow into the overflow bore just before delivery. When moving to delivery, the step edge covers the overflow hole, taking into account the required sealing gap. After the start of the conveyance, after a stroke determined by the rotational position, the oblique region of the control edge overrides the oblique region of the control edge, whereby the conveyance ends becomes.
  • the step runs in the direction of the axis of the pump piston, the required sealing gap is kept the same during the stroke of the pump piston, and therefore a more precise use of the delivery or the idling delivery is made possible. Apart from this, the fact that the step extends in the direction of the axis of the pump piston also makes it easier to incorporate it during manufacture.
  • the recess or step of the oblique control edge extends so far that the required sealing gap width is ensured between the edge delimiting the recess or the step and the control bore when idling.
  • the fact that the step runs in the direction of the axis of the pump piston has a favorable effect, since the sealing gap remains the same at the various stroke positions of the piston in the area of this step. It can therefore be reduced to a minimum by this recess or step of the control angle between the "zero delivery" position and the idling position, without the required sealing gap being impaired.
  • Fig.l shows a side view of the piston.
  • 2 shows a development of the piston jacket with the oblique control edge.
  • 3 shows a diagram in which the injection quantity is plotted in the ordinate and the control angle in the abscissa
  • FIG. 4 shows a modified embodiment.
  • 5 shows another exemplary embodiment.
  • the piston 7 has an oblique control edge 1, which the overflow bore 2 grinds over.
  • the oblique control edge runs along a steady curve, as is indicated in dashed lines in the area la.
  • the control edge 1-la runs along a steady curve
  • the relative position of the overflow bore with zero delivery is in the ordinate a.
  • the relative position of the overflow bore 2 when idling is in the ordinate b.
  • the position 2 'of the overflow bore 2 shows the start of delivery and the position 2''shows the end of delivery.
  • the control angle 3 between the position "zero delivery" and the idle position b is therefore relatively large in the known designs.
  • the control edge runs on a discontinuous curve.
  • the lower control edge 1 has a step 4 which runs in the direction of the piston axis.
  • the lower control edge now runs along line 1-4.
  • the position "zero funding” is shifted by a value 5 in the direction of ordinate b and is now in ordinate c.
  • the control angle is therefore reduced by the area 5.
  • the required sealing gap between the overflow bore 2 in the idle position ordinate b and the control edge region forming the step 4 is shown by 6. It can thus be seen that the entire control angle is shortened by the region 5. In this way it is possible to find the right length with a control angle of about 60 °.
  • the upper edge 8 of the piston 7 represents the upper control edge, which at the start of the conveyance overlaps the overflow bore 2 in the pump piston bushing 9.
  • the distance of the point 28 at which the oblique control edge 1 changes into the recessed step 4 from the upper control edge 8 controlling the start of conveyance is larger than the diameter of the overflow bore. This results in a useful stroke from the piston position at which the upper control edge 8 closes the overflow bore 2 (start of delivery) to the piston position at which the oblique control edge 1 releases the overflow bore 2 (discharge end).
  • Level 4 shortens the control angle. This shortens the phase indicated by curve 12. At a certain constant speed selected for the diagram according to FIG. 3, this phase of curve 12 is even shortened to zero. In this case, the pilot injection follows curve 15 until the full pilot injection is reached at point 13. After the injection pause determined by the swallowing volume of the evasive cylinder, the main injection is formed according to curve 14. The absolute values to be read off the ordinate in mm 3 indicate the total injection quantity. This applies to an assumed speed n ... At other speeds, the pilot injection and main injection can be designed, for example, according to n 2 . If the values 5 (FIG. 2) are smaller, the shortening of the phase indicated by curve 12 may be less and the pre-injection may be designed according to curve 16, for example. In any case, the control angle is reduced in the phase indicated by curve 12 without the pitch angle of the oblique control edge 1 being reduced.
  • FIG. 17 A modified embodiment is shown in FIG.
  • the piston 17 has oblique slots 18, the lower control edge 19 ends the promotion.
  • These oblique slots 18 are connected by an axial bore 20 and a transverse bore 21 to the working space of the pump piston 17 and the control is carried out by a control sleeve 22 which has the overflow bore 23.
  • a recess 24 extending in the axial direction of the piston is attached to the oblique slots 18, as a result of which a step 25 of the control edge 19 is formed, which has the same function as the step 4 according to FIG.
  • the start of delivery takes place when the transverse bore 26 is blended through the edge 27 of the control sleeve 22.
  • the oblique control edge 29 and the step 30, into which the oblique control edge 29 merges at point 31, are provided in a bush 32 surrounding the piston.
  • the overflow bore 33 is provided in the piston 34 and is connected to the working space 36 by a central bore 35 in the piston 34.
  • the promotion begins when the upper control edge 37 of the sleeve 32 overrides the overflow bore 33 and ends when the oblique control edge 29 of the sleeve 32 clears the overflow bore 33 of the piston 34.
  • the distance between the point 31 at which the oblique control edge 29 transitions into step 30 ' from the control edge 37 controlling the start of conveyance is greater than the diameter of the overflow bore 33.
  • 38 is an evasive piston which is in an evasive cylinder 39 is led. With 40 the evasive stroke of the evasive piston 38 is designated.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)

Abstract

Dispositif d'injection de carburant pour moteurs à combustion interne à injection dans lequel un piston plongeur (7) et un manchon de piston (9) ou une douille de commande (22) peuvent tourner l'un par rapport à l'autre, l'extrémité d'alimentation étant définie par au moins une arête de commande inclinée (1) au-dessus de laquelle se trouve un orifice d'écoulement (2) de l'autre partie, cependant qu'il est prévu, afin d'obtenir une pré-injection et une injection principale, un piston de déviation (38) guidé dans un cylindre se trouvant en communication avec l'espace haute pression, le volume libéré par ledit piston déterminant l'intervalle de repos entre la pré-injection et l'injection principale, caractérisé en ce que l'arête de commande inclinée (1) présente, dans la zone d'alimentation nulle, un cran qui revient dans la direction de la position de rotation correspondant à une augmentation de l'alimentation. La distance de l'emplacement (28) où l'arête de commande inclinée (1) passe dans l'évidement revenant en position (4) à partir de l'arête (8) commandant le début de l'alimentation est plus grande que le diamètre de l'orifice d'écoulement (2). Ce cran permet d'accroître la zone d'alimentation nul et de la déplacer dans le sens d'une alimentation accrue. L'angle de réglage requis se trouve ainsi réduit sans pour autant accroître la pente de l'arête de commande inclinée (1).
EP91905879A 1990-02-21 1991-02-20 Dispositif d'injection de carburant pour moteurs a combustion interne a injection Expired - Lifetime EP0469142B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
AT39890 1990-02-21
AT398/90 1990-02-21
PCT/AT1991/000030 WO1991013252A1 (fr) 1990-02-21 1991-02-20 Dispositif d'injection de carburant pour moteurs a combustion interne a injection

Publications (2)

Publication Number Publication Date
EP0469142A1 true EP0469142A1 (fr) 1992-02-05
EP0469142B1 EP0469142B1 (fr) 1995-04-05

Family

ID=3489555

Family Applications (1)

Application Number Title Priority Date Filing Date
EP91905879A Expired - Lifetime EP0469142B1 (fr) 1990-02-21 1991-02-20 Dispositif d'injection de carburant pour moteurs a combustion interne a injection

Country Status (3)

Country Link
US (1) US5144925A (fr)
EP (1) EP0469142B1 (fr)
WO (1) WO1991013252A1 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH08270521A (ja) * 1995-04-03 1996-10-15 Zexel Corp 分配型燃料噴射ポンプ
DE29616780U1 (de) * 1996-09-26 1998-01-29 Bosch Gmbh Robert Stabspule für Zündanlagen
GB0712032D0 (en) * 2007-06-22 2007-08-01 Delphi Tech Inc Fluid pump

Family Cites Families (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2159177A (en) * 1936-05-19 1939-05-23 Ricardo Harry Ralph Fuel injection pump for internal combustion engines
US2258055A (en) * 1938-04-29 1941-10-07 Murphy Diesel Company Fuel pump
US2356627A (en) * 1940-06-27 1944-08-22 George A Rubissow Interruption injection pump
US2398834A (en) * 1940-07-25 1946-04-23 Kammer George Stephen Fuel injection in internalcombustion engines
US2565681A (en) * 1945-11-01 1951-08-28 Caterpillar Tractor Co Fuel injection for internal combustion engines
FR1164392A (fr) * 1956-01-17 1958-10-08 Bosch Gmbh Robert Pompe à injection de combustible pour moteurs
FR2067883A5 (fr) * 1969-11-20 1971-08-20 Peugeot
DE2421668A1 (de) * 1974-05-04 1975-11-13 Daimler Benz Ag Einspritzpumpe fuer eine luftverdichtende einspritzbrennkraftmaschine
DE2730091C2 (de) * 1977-07-02 1986-12-04 Robert Bosch Gmbh, 7000 Stuttgart Schrägkantengesteuerte Kraftstoffeinspritzpumpe für Brennkraftmaschinen
DE2922426A1 (de) * 1979-06-01 1980-12-11 Daimler Benz Ag Kraftstoffeinspritzpumpe mit unterteilter foerderung
FR2487434B1 (fr) * 1980-07-25 1985-11-29 Inst Francais Du Petrole Dispositif de pompage et d'injection pour moteur a combustion interne
JPS57148054A (en) * 1981-03-06 1982-09-13 Kawasaki Heavy Ind Ltd Fuel injection pump
DE3224127A1 (de) * 1981-08-01 1983-02-24 Robert Bosch Gmbh, 7000 Stuttgart Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
DE3330774A1 (de) * 1983-08-26 1985-03-14 Robert Bosch Gmbh, 7000 Stuttgart Kraftstoffeinspritzeinrichtung mit vor- und haupteinspritzung bei brennkraftmaschinen
AU563901B2 (en) * 1984-05-08 1987-07-23 Bosch Automotive Systems Corporation Fuel injection pump and method of adjusting the same pump
DE3428174A1 (de) * 1984-07-31 1986-02-13 Robert Bosch Gmbh, 7000 Stuttgart Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
DE3809700A1 (de) * 1988-03-23 1989-10-12 Hatz Motoren Kraftstoff-einspritzpumpe fuer brennkraftmaschinen mit vor- und haupteinspritzung
JP2597154B2 (ja) * 1988-07-18 1997-04-02 株式会社クボタ ディーゼルエンジンの逃孔式燃料噴射ポンプ

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO9113252A1 *

Also Published As

Publication number Publication date
WO1991013252A1 (fr) 1991-09-05
US5144925A (en) 1992-09-08
EP0469142B1 (fr) 1995-04-05

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