EP0603447B1 - Brennstoffeinspritzpumpe für Hubkolbenbrennkraftmaschinen - Google Patents

Brennstoffeinspritzpumpe für Hubkolbenbrennkraftmaschinen Download PDF

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Publication number
EP0603447B1
EP0603447B1 EP92811011A EP92811011A EP0603447B1 EP 0603447 B1 EP0603447 B1 EP 0603447B1 EP 92811011 A EP92811011 A EP 92811011A EP 92811011 A EP92811011 A EP 92811011A EP 0603447 B1 EP0603447 B1 EP 0603447B1
Authority
EP
European Patent Office
Prior art keywords
piston
delivery
slider
slide
control edge
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
EP92811011A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0603447A1 (de
Inventor
Klaus Heim
Ulrich Staiger
Patrick Genier
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.)
Winterthur Gas and Diesel AG
Original Assignee
Winterthur Gas and Diesel AG
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
Priority to EP92811011A priority Critical patent/EP0603447B1/de
Application filed by Winterthur Gas and Diesel AG filed Critical Winterthur Gas and Diesel AG
Priority to DE59208200T priority patent/DE59208200D1/de
Priority to DK92811011.3T priority patent/DK0603447T3/da
Priority to FI935642A priority patent/FI105231B/fi
Priority to KR1019930027722A priority patent/KR100322805B1/ko
Priority to CN93112760A priority patent/CN1033101C/zh
Priority to JP5322837A priority patent/JPH06235361A/ja
Publication of EP0603447A1 publication Critical patent/EP0603447A1/de
Application granted granted Critical
Publication of EP0603447B1 publication Critical patent/EP0603447B1/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
    • 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
    • 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 relates to a fuel injection pump for reciprocating piston internal combustion engines with the features of the preamble of claim 1.
  • a pump of this type is known from US Pat. No. Re 32,965.
  • the first control edge for influencing the start of delivery is also arranged obliquely to the direction of movement of the piston. This means that each time the delivery rate is adjusted, the start of injection is inevitably changed by turning the slide around its axis, ie the delivery rate cannot be adjusted without simultaneously influencing the start of delivery. An optimal adaptation of the fuel injection to the needs of the internal combustion engine at different operating points is therefore not possible in a simple manner.
  • the first control edge is above the second control edge and both control edges limit a window-like opening in the slide.
  • Each control edge is assigned a transverse channel in the form of a hole.
  • the object of the invention is to improve the injection pump mentioned at the outset such that adjusting the delivery rate has no influence on the start of delivery, which in turn is adjustable independently of the delivery rate adjustment, and that the overall length of the pump is reduced in the direction of the piston.
  • the start of delivery remains unaffected when the delivery rate is adjusted by rotating the slide or the piston.
  • the start of delivery is adjusted by axially adjusting the slide, which is independent of the delivery rate.
  • This makes it possible in a simple manner to optimally adapt the fuel injection to the respective needs of the reciprocating piston internal combustion engine at different operating points, ie between 0 and 100% load.
  • the second control edge between the first control edge and the Conveying space is located, the cross channel is covered during the conveying phase by the slide wall located between the control edges, which is seen only once in the axial direction of the slide.
  • the slide is therefore measured shorter than the known slide. This also affects the size of the injection pump, which is smaller and more compact than the known one.
  • the fuel injection pump has a housing 1 which, with its upper part in FIG. 1, forms a pump cylinder 2 in which a piston 3 is guided so that it can move up and down.
  • a delivery chamber 4 to which a pressure line 5 connects upwards in FIG. 1, which leads to a schematically illustrated injection nozzle 6, which is inserted in a cylinder cover, not shown, of a diesel-type reciprocating internal combustion engine and with its lower end in the combustion chamber of the working cylinder of this machine protrudes.
  • the piston 3 extends downwards in FIG Suction chamber 7 and then through the lower part of the housing 1.
  • the lower end of the piston 3, not shown, is supported in a known manner via a roller on a drive cam of a camshaft.
  • a source (not shown) for diesel fuel is connected to the suction chamber 7 via at least one channel 8 (arrow A).
  • a sleeve-like slide 9, which can slide on the piston 3, is arranged on the piston 3 within the suction space 7.
  • the slide 1 On its lower end face in FIG. 1, the slide 1 has a first control edge 10 which extends at right angles to the direction of movement of the piston 3 (double arrow B).
  • a second control edge 11 At the upper end of the slide 9 in FIG. 1, a second control edge 11 is provided, which extends obliquely to the direction of movement of the piston 3.
  • the control edges 10 and 11 cooperate with a transverse channel 12 in the form of an elongated hole which begins in the center of the piston 3 and extends radially outwards into the circumferential surface of the piston 3.
  • the transverse channel 12 communicates with an axial channel 13 in the center of the piston 3.
  • the channel 13 extends from the end face 3 'of the piston 3 which contacts the delivery chamber 4 and thus connects the suction chamber 3 to the delivery chamber 4 via the transverse channel 12.
  • a shaft 14 is mounted in the housing 1, which projects with one end into the suction chamber 7 and has an eccentric pin 15 at this end.
  • the pin 15 protrudes into an annular groove 16 of the slide 9, which runs parallel to the first control edge 10.
  • a pin 19 is fastened in the housing 1 and protrudes into an axial groove 19 'in the slide.
  • a rack 17 is mounted in the housing 1, which cooperates with a ring gear 18, the is rotatably arranged on the piston 3, but allows the axial movement of the piston 3.
  • the rack 17 By moving the rack 17 back and forth in the direction perpendicular to the plane of FIG. 1, the ring gear 18 and thus the piston 3 can be adjusted about its axis 20.
  • the injection pump described functions as follows: In the position shown in FIG. 1, the suction chamber 7 is connected to the delivery chamber 4 via the transverse channel 12 and the axial channel 13 and the latter is filled with fuel.
  • the piston 3 is moved upward from the aforementioned cam, not shown.
  • the delivery phase of the piston 3 begins, since the mouth of the transverse channel 12 is completely covered by the slide 9.
  • the fuel is displaced via the pressure line 5 to the injection nozzle 6, which opens when the injection pressure is reached and allows the fuel to enter the combustion chamber.
  • the delivery phase of the piston 3 ends when the upper boundary 12 ′′ of the transverse channel 12 passes the second control edge 11 of the slide 9.
  • the start of conveyance can now be changed by moving the slide 9 slightly up or down when the shaft 14 of the pin 15 rotates, so that the relative position of the transverse channel 12 to the control edges 10 and 11 is changed.
  • An adjustment of the slide 9 in the downward direction results in an earlier start of delivery and thus the start of injection and vice versa an adjustment upward means a later start of delivery.
  • the delivery rate can also be adjusted with the injection pump by rotating the toothed ring 18 and thus the piston 3 by means of the toothed rack 17, so that the transverse channel 12 in FIG right or left.
  • a shift to the right causes a reduction in the delivery rate because the transverse channel 12 passes the axial distance between the control edges 10 and 11 more quickly, ie the start and end of delivery are closer to each other.
  • the delivery rate is increased because the piston 3 takes a longer time until the cross channel has passed the axial distance between the control edges 10 and 11; Funding start and funding end are further apart.
  • the housing 21 in turn contains a delivery chamber 24 and guides the piston 23 with its cylinder 22.
  • a slide 29 which carries at its lower end a ring gear 48 which has a toothed rack, not shown is engaged. With the help of the ring gear 48, the slide 29 can be adjusted about the axis 40 of the piston 23.
  • the control edges of the slide 29 are designated 30 and 31.
  • a ring 49 is provided which surrounds the piston 23 and which bears with its upper end face in FIG. 2 on the lower end face of the slide 29 and is provided with an inclined sliding surface 50 at its lower end in FIG. 2 .
  • the sliding surface 50 extends approximately over half the circumference of the ring 49 and is supported on a pin-shaped stop 51 which is fastened in the housing 21.
  • the ring 49 also carries a ring gear 52 which meshes with a rack, not shown.
  • FIG. 2 further shows, the slide 29 and the ring 49 are pressed downward against the stop 51 by a coil spring 53.
  • the spring is supported on the one hand at the lower end of the cylinder 22 and on the other hand at the upper end of the slide 29.
  • two transverse channels 62 and 63 are provided in the exemplary embodiment according to FIG. 2, which are axially spaced from one another and which also extend across the entire piston 23.
  • the slide 29 has a symmetrical structure in that two first control edges 30 and two second control edges 31 are present.
  • the control edges 30 each form the upper boundary of a window-like recess, which could also be open at the bottom.
  • the symmetrical arrangement of the control edges in pairs together with the continuous transverse channels 62 and 63 results in a uniform pressurization on the slide 29.
  • the injection pump according to FIGS. 2 and 3 functions as follows: In the position of the piston 23 shown in FIG. 2, the delivery chamber 24 is connected to the suction chamber 27 via the axial channel 33 and the transverse channels 62 and 63, so that the delivery chamber 24 is filled with fuel under suction chamber pressure.
  • the delivery phase begins when the lower boundary of the lower transverse channel 62 has passed the first control edge 30 (FIG. 4 a).
  • the conveying phase lasts until the upper limit of the upper transverse channel 63 has passed the second control edge 31 (FIG. 4b), because there is now a connection again between the conveying chamber 24 and the suction chamber 27.
  • the start of delivery can be adjusted, since the inclined surface 50 sliding on the stop 51 adjusts the ring 49 and thus the slide 29 in the axial direction.
  • the delivery rate can also be adjusted by changing the position of the second control edge 31 relative to the transverse channels 62 and 63 by rotating the slide 29 with the aid of the ring gear 48. 4c shows the position of the slide 29 relative to the piston 23 when the injection pump is to deliver the maximum amount of fuel.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)
EP92811011A 1992-12-21 1992-12-21 Brennstoffeinspritzpumpe für Hubkolbenbrennkraftmaschinen Expired - Lifetime EP0603447B1 (de)

Priority Applications (7)

Application Number Priority Date Filing Date Title
DE59208200T DE59208200D1 (de) 1992-12-21 1992-12-21 Brennstoffeinspritzpumpe für Hubkolbenbrennkraftmaschinen
DK92811011.3T DK0603447T3 (da) 1992-12-21 1992-12-21 Brændstofindsprøjtningspumpe til stempelforbrændingsmotorer
EP92811011A EP0603447B1 (de) 1992-12-21 1992-12-21 Brennstoffeinspritzpumpe für Hubkolbenbrennkraftmaschinen
KR1019930027722A KR100322805B1 (ko) 1992-12-21 1993-12-15 왕복연소기관의연료분사펌프
FI935642A FI105231B (fi) 1992-12-21 1993-12-15 Iskumäntäpolttomoottorikoneiden polttonesteen suihkutuspumppu
CN93112760A CN1033101C (zh) 1992-12-21 1993-12-20 一种用于往复式内燃机的燃油喷射泵
JP5322837A JPH06235361A (ja) 1992-12-21 1993-12-21 レシプロ式内然機関における燃料噴射ポンプ

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP92811011A EP0603447B1 (de) 1992-12-21 1992-12-21 Brennstoffeinspritzpumpe für Hubkolbenbrennkraftmaschinen

Publications (2)

Publication Number Publication Date
EP0603447A1 EP0603447A1 (de) 1994-06-29
EP0603447B1 true EP0603447B1 (de) 1997-03-12

Family

ID=8212053

Family Applications (1)

Application Number Title Priority Date Filing Date
EP92811011A Expired - Lifetime EP0603447B1 (de) 1992-12-21 1992-12-21 Brennstoffeinspritzpumpe für Hubkolbenbrennkraftmaschinen

Country Status (7)

Country Link
EP (1) EP0603447B1 (ko)
JP (1) JPH06235361A (ko)
KR (1) KR100322805B1 (ko)
CN (1) CN1033101C (ko)
DE (1) DE59208200D1 (ko)
DK (1) DK0603447T3 (ko)
FI (1) FI105231B (ko)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102012214247A1 (de) * 2012-08-10 2014-02-13 Robert Bosch Gmbh Schieberventil mit einem Gehäuse und einem Ventilschieber mit mindestens einer schieberseitigen Steuerkante

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4211520A (en) * 1978-01-20 1980-07-08 Caterpillar Tractor Co. Timing control for sleeve metering fuel system
USRE32965E (en) * 1984-07-31 1989-06-27 Robert Bosch Gmbh Fuel injection pump for internal combustion engines
DE3736091A1 (de) * 1987-10-24 1989-05-03 Bosch Gmbh Robert Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
US4861243A (en) * 1988-04-08 1989-08-29 Ford Motor Company Diesel fuel injection pump with variable injection timing

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
US-E-RE32965 (ROBERT BOSCH GMBH) *

Also Published As

Publication number Publication date
DE59208200D1 (de) 1997-04-17
KR100322805B1 (ko) 2002-06-20
DK0603447T3 (da) 1997-04-01
EP0603447A1 (de) 1994-06-29
CN1092503A (zh) 1994-09-21
FI935642A (fi) 1994-06-22
FI935642A0 (fi) 1993-12-15
JPH06235361A (ja) 1994-08-23
FI105231B (fi) 2000-06-30
CN1033101C (zh) 1996-10-23
KR940015257A (ko) 1994-07-20

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