EP0178505B1 - Pompe d'injection d'essence pour moteurs à combustion - Google Patents

Pompe d'injection d'essence pour moteurs à combustion Download PDF

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Publication number
EP0178505B1
EP0178505B1 EP85112161A EP85112161A EP0178505B1 EP 0178505 B1 EP0178505 B1 EP 0178505B1 EP 85112161 A EP85112161 A EP 85112161A EP 85112161 A EP85112161 A EP 85112161A EP 0178505 B1 EP0178505 B1 EP 0178505B1
Authority
EP
European Patent Office
Prior art keywords
control
control rod
driving members
fuel injection
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.)
Expired
Application number
EP85112161A
Other languages
German (de)
English (en)
Other versions
EP0178505A1 (fr
Inventor
Josef Güntert
Walter Häfele
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 AT85112161T priority Critical patent/ATE40186T1/de
Publication of EP0178505A1 publication Critical patent/EP0178505A1/fr
Application granted granted Critical
Publication of EP0178505B1 publication Critical patent/EP0178505B1/fr
Expired 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
    • F02M59/28—Mechanisms therefor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D17/00—Controlling engines by cutting out individual cylinders; Rendering engines inoperative or idling
    • F02D17/02—Cutting-out
    • 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

Definitions

  • the invention is based on a fuel injection pump according to the preamble of claim 1.
  • the entrainment members are designed as clamps, which are adjustably clamped by tightening the free legs by means of a screw on the round control rod and have a pin which engages on the control slide in an annular groove provided for this purpose.
  • the individual entrainment members can be adjusted relative to one another with regard to their rotational position and thus the control slide with respect to their stroke position, but they cannot be actuated independently of one another. It is therefore also not possible to achieve the partial shutdown of the engine cylinders when the engine is idling (cylinder deactivation).
  • Such a cylinder deactivation is known per se in a fuel injection pump of another type (GB-A-2038934), in which the fuel delivery can be switched off from part of the pump work spaces to the internal combustion engine.
  • a fuel injection pump of another type GB-A-2038934
  • these measures can improve fuel consumption, exhaust gas and noise emissions, especially when the engine is idling and under partial load. In addition, less fuel gets into the engine lubricating oil while avoiding excessive thinning.
  • such a cylinder deactivation is also used in motor vehicles if only auxiliary units are to be driven by the engine of the vehicle for loading and unloading of silo or tank vehicles, for example.
  • these known in-line injection pumps in which the pump pistons of individual units of the pump can be rotated to shut off the delivery to zero delivery, this has not been known in the case of pumps controlled by a linear slide valve.
  • the aim of the invention is now to enable cylinder deactivation in a simple and space-saving manner even in the case of slide valve-controlled fuel injection pumps.
  • the first, two groups of entrainment members and the feature group consisting of two independently operable and arranged control rods comprising control rod from the characterizing part of claim 1 is known per se for fuel injection pumps of another type from GB-A-2038934 cited at the beginning.
  • the two control rods are arranged coaxially with one another, the second control rod being tubular, having radial openings with play in the direction of rotation for the entrainment members carried by the first control rod, and this first control rod guiding the rotary movement. Since the openings only have to be so large that the relative adjustment of the two control rods is possible, the stability of the rods is not impaired, so that even relatively high actuating forces can be transmitted without twisting the rods.
  • the two control rods are penetrated transversely to the longitudinal axis of the control rods by a driving pin that has play in the direction of rotation relative to one or the other control rod, the play being dimensioned such that when the second control rod is rotated in the direction constant opening of the relief bores (switching off the engine), the first control rod with the drive links carried by it is also turned into this opening position.
  • Such a driving pin penetrating both control rods can advantageously save an additional axial fixation of the two control rods against one another, and relatively narrow tolerances can be used, since no additional fastening means, for example the driving pin on the control rod, are required.
  • the combination of all the features specified in claim 1 allows the driving links, for. B. for their equality, independently of each other without affecting the overall function.
  • a particularly advantageous embodiment in terms of manufacture and assembly is that, according to claim 5, the entrainment members are designed as a rotating part having a threaded section and fastened to the respective control rod.
  • eccentrically offset pins can be arranged at one end of the driving members for engagement on the control slide, the driving members being secured against twisting by nuts running on the threaded section.
  • a plurality of cylinder liners 2 are embedded in series, in the pump cylinder 2a of which pump pistons 3 are guided and driven via a camshaft 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 control slide 7 is actuated via a driving element 8, which is connected either to a first control rod 9 or to a second control rod 11 arranged in a tubular manner around it, so that a rotary movement of one of the control rods causes a corresponding displacement of the respective control slide 7.
  • a pump working chamber 12 is delimited by the pump piston 3 and the pump cylinder 2a, from which the pump piston 3 can deliver fuel to the internal combustion engine during its pressure stroke via a pressure valve 13 and a pressure line 14.
  • a relief bore 15 running in the pump piston 3 branches off from this pump work chamber 12 and is connected to an oblique groove 16 arranged on the lateral surface of the pump piston 3.
  • a control bore 17 is present in the control slide 7.
  • the oblique groove 16 interacts for the control of the relief bore 15 on the one hand with the control edge 18 formed by the lower end of the inner bore of the control slide 7 and on the other hand with the control bore 17 such that as long as the oblique groove 16 at least through the control bore 17 or the lower control edge 18 is partially open, fuel can flow out of the pump work chamber 12 via the relief bore 15 without pressure.
  • the pump piston 3 is rotated in a known manner by a speed controller by means of a third control rod 19, for which purpose this control rod 19 engages via a bushing 20 at a correspondingly flattened point 21 of the piston.
  • the first control rod 9 is of solid construction and is flattened in the area 22 opposite the control slides 7 such that the remaining cylinder segments 23 on the inner wall 24 of the tubular second control rod 11 for a relative rotational movement of the control rods to one another are led.
  • a first group of first driving links 26 is attached to the first control rod 9 (FIGS. 3 and 4), and a second group of second driving links 27 are mounted on the second control rod 11 (FIGS. 4 and 4).
  • the first and second driving members 26, 27 are bolt-shaped, each with a threaded section 28 at one end and an eccentrically offset to the longitudinal axis pin 29 with head 31, of which the latter engages in an annular groove 32 arranged on the control slide 7.
  • a nut 33 runs to fix the driving member on the control rod.
  • a slot 34 is provided on the end face of the driving member 26 facing away from the head 31 for the engagement of a turning tool (screwdriver), so that the individual heads 31 and the control slide 7 can be adjusted relative to one another by rotating the driving members 26 due to the eccentric arrangement of the pins 29 . The adjusted position can then be fixed by tightening the nuts 33.
  • a turning tool screwdriver
  • the first driving member 26 has a collar 35 as a counter-bearing to the nut 33, which is supported on a twist 36, which is located on one of the two flattened sides 37 of the first control rod 9.
  • the second control rod 11 there are radial openings 38 for the first driver links 26 in order to enable their relative pivoting in relation to the second driver links 27 or a relative rotation of the first control rod 9 in relation to the second control rod 11.
  • a sleeve 39 is provided for the power transmission, whereby on the one hand the opening 38 on this side is made only as large as is absolutely necessary and on the other hand the key 33 can be attacked by a key tool outside the second control rod 11.
  • the second driving member 27 has a conical collar 41 which bears against the inside of the tubular control rod 11 for tightening the driving member 27.
  • a recess 42 is provided for receiving a washer 43, via which the force is transmitted from the nut 33 to the control rod.
  • a collar 44 is provided which is guided in a bore 45 of the second control rod 11.
  • corresponding recesses 46 are provided in the first control rod 9 for the passage of the second driver links 27.
  • part of the control slide 7 can be axially related to the other part are displaced, whereby a part of the pump units of the fuel injection pump arranged in series can be switched off for the injection without influencing the injection function of the other part, as will be described in detail below.
  • the first control rod 9 with the first driver links 26 for “cylinder deactivation” can be rotated with respect to the second control rod 11 with the second driver links 27.
  • a pin 47 which is guided in a transverse bore 48 of the first control rods 9 and slides with its ends in circumferential grooves 49 of the second control rod 11, serves as a driving coupling between the two control rods 9 and 11.
  • These circumferential grooves 49 enable the first control rod 9 to rotate the associated control slide 7 in a position for cylinder deactivation, but if the second control rod 11 is rotated into such a position and the first control rod 9 is in the normal working position, the latter is for the shutdown of all cylinders is rotated.
  • a torsion spring 51 (FIG. 5) engaging with one end on the first control rod 9 and the other end on the second control rod 11, the first control rod 9 is held in a position in normal operation with respect to the second control rod 11 in which all Driving links 26, 27 or all control spools 7 assume the same working position.
  • a knurled head 52 of the first control rod this can then be adjusted in the manner described relative to the second control rod 11 into the switch-off position against the force of the spring 51.
  • a toothing 53 is provided at the end thereof, into which, as on the knurled head 52, corresponding adjustment means such as toothed rings or levers engage.
  • the second control rod 11 is in a position for normal operation with the second driving element 27.
  • this lower section of the oblique groove 16 dips into the control slide 7, so that the pressure required for the injection can then build up in the pump work chamber 12.
  • the injection is interrupted since the fuel can now flow out of the pump work chamber 12 via the relief bore 15 and the control bore 17 largely relieved of pressure.
  • the twist of the two control rods is used primarily to adjust the start of injection. If the control slide 7 is pushed up into the dashed position, the control bore 17 also moves upward accordingly.
  • the correspondingly articulated number of control slides 7 is shifted downward into the position shown in broken lines.
  • the oblique groove 16 overlaps with the control bore 17, and after the start of the stroke of the pump piston 3 upwards, the oblique groove 16 emerges from the control slide 7 before it is separated from the control bore 17, so that a connection is always made exists between the pump working space 12 and the recess 6. Accordingly, no injection pressure can build up and no injection can take place.
  • This cylinder deactivation is also carried out from a normal operating position of all control slides 7 when the second control rod 11 is rotated clockwise, takes the first control rod 9 and its group of articulated control slides with it via the pin 47, so that all control slides 7 are in a position for cylinder deactivation and thus Engine shutdown.
  • control slide controls the injection quantity by rotating or axially displacing it, and at least some of the control slides are displaceable in the cylinder deactivation position.

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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)
  • High-Pressure Fuel Injection Pump Control (AREA)

Claims (6)

1. Pompe d'injection de carburant pour moteurs à combustion interne avec une ligne de pistons de pompe (3), disposés en ligne, guidés dans des cylindres de pompe (2a), délimitant avec ceux-ci une enceinte de travail de pompe (12) et entraînés pour effectuer une course de travail de va-et-vient, avec pour chacun un tiroir de commande (7) mobile au moins axialement sur chaque piston de pompe (3), pour commander au moins un alésage de décharge (15) se développant dans le piston de pompe (3) et avec des éléments d'entraînement (8) disposés tournants sur une tige de réglage (9, 11) pour déplacer les tiroirs de commande (7) et venant en prise sur les tiroirs de commande (7), caractérisé en ce que deux groupes d'éléments d'entraînement (8) sont prévus, un premier groupe d'éléments d'entraînement (26) étant mobile à volonté, en une position de commande constante des alésages de décharge (15) de quelques enceintes de travail de pompe (12), indépendamment d'un deuxième groupe d'éléments d'entraînement (27) commandant simultanément une marche normal, et en ce que la tige de réglage se compose de deux tiges de réglage actionnables indépendamment et disposées l'une à l'intérieur de l'autre, une première tige de réglage (9) portant le premier groupe d'éléments d'entraînement (26) et une deuxième tige de réglage (11), portant le deuxième groupe d'éléments d'entraînement (27), en ce que les deux tiges de réglage (9, 11) sont disposées coaxialement l'une par rapport à l'autre, la deuxième tige de réglage (11) étant à cette occasion réalisée selon une forme tubulaire, avec des communications (38) radiales, avec un jeu dans le sens de la rotation, pour les éléments d'entraînement (26) portés par la première tige de réglage (9) et guidant cette première tige de réglage (9) dans son mouvement de rotation, et en ce que les deux tiges de rotation (9, 11) sont traversées transversalement par rapport à l'axe longitudinal des tiges de réglage (9, 11), par une goupille d'entraînement (47) présentant un jeu dans le sens de rotation, par rapport à l'une ou l'autre des tiges de réglage, le jeu étant à cette occasion dimensionné de telle sorte que, lors de la rotation de la deuxième tige de réglage (11) dans le sens d'une commande constante des alésages de décharge (15), la première tige de réglage (9) soit également entraînée dans cette position de commande, avec les éléments d'entraînement (26) qu'elle porte.
2. Pompe d'injection de carburant selon la revendication 1, caractérisé en ce que les éléments d'entraînement (27) portés par la deuxième tige de réglage (11) traversant le tube de cette tige de réglage, ainsi que les évidements (46) prévus dans la première tige de réglage (9) guidée, en présentant un jeu.
3. Pompe d'injection de carburant selon la revendication 1 ou 2, caractérisée en ce que la première tige de réglage (9) est aplatie et est guidée sur la paroi intérieure (24) de la tige de réglage (11) de forme tubulaire, par les segments de cylindres (23) prévus sur les côtés étroits.
4. Pompe d'injection de carburant selon l'une des revendications précédentes 1 à 3, caractérisée en ce qu'au moins l'une des tiges de réglage (9, 11) est en prise sur un élément (51) élastique en torsion, rappelant les tiges de réglage dans une position identique, par rapport aux éléments d'entraînement (8).
5. Pompe d'injection de carburant selon l'une des revendications précédentes, caractérisée en ce que les éléments d'entraînement (8, 26, 27) sont réalisés sous forme de parties tournantes, présentant une section filetée (28), fixées sur chaque tige de réglage (9, 11).
6. Pompe d'injection de carburant selon la revendication 5, caractérisée en ce que des tourillons (29) sont disposés de manière décalée à une extrémité des éléments d'entraînement (8, 26, 28) venant en prise sur le tiroir de commande (7) et en ce que les éléments d'entraînement (8, 26, 27) sont susceptibles d'être assurés contre une rotation, au moyen d'écrous (33) se déplaçant sur la section filetée (28).
EP85112161A 1984-10-01 1985-09-25 Pompe d'injection d'essence pour moteurs à combustion Expired EP0178505B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT85112161T ATE40186T1 (de) 1984-10-01 1985-09-25 Kraftstoffeinspritzpumpe fuer brennkraftmaschinen.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3435987 1984-10-01
DE19843435987 DE3435987A1 (de) 1984-10-01 1984-10-01 Kraftstoffeinspritzpumpe fuer brennkraftmaschinen

Publications (2)

Publication Number Publication Date
EP0178505A1 EP0178505A1 (fr) 1986-04-23
EP0178505B1 true EP0178505B1 (fr) 1989-01-18

Family

ID=6246821

Family Applications (1)

Application Number Title Priority Date Filing Date
EP85112161A Expired EP0178505B1 (fr) 1984-10-01 1985-09-25 Pompe d'injection d'essence pour moteurs à combustion

Country Status (5)

Country Link
US (1) US4706626A (fr)
EP (1) EP0178505B1 (fr)
JP (1) JPH0681938B2 (fr)
AT (1) ATE40186T1 (fr)
DE (2) DE3435987A1 (fr)

Families Citing this family (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4830587A (en) * 1986-03-22 1989-05-16 Robert Bosch Gmbh Fuel injection pump for internal combustion engines
DE3707646A1 (de) * 1986-03-24 1987-10-08 Bosch Gmbh Robert Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
DE3633899A1 (de) * 1986-10-04 1988-04-07 Bosch Gmbh Robert Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
DE3724409A1 (de) * 1986-10-31 1988-05-19 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
DE3736091A1 (de) * 1987-10-24 1989-05-03 Bosch Gmbh Robert Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
US5080564A (en) * 1989-02-08 1992-01-14 Diesel Kiki Co., Ltd. Prestroke control device for fuel injection pumps
DE4041656A1 (de) * 1990-12-22 1992-07-02 Bosch Gmbh Robert Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
DE4100093A1 (de) * 1991-01-04 1992-07-09 Bosch Gmbh Robert Kraftstoffeinspritzpumpe fuer brennkraftmaschinen mit last- und/oder drehzahlabhaengigem einspritzverlauf
US5592797A (en) * 1992-07-20 1997-01-14 Mid-America Building Products Corporation Decorative molding strip system
US7762238B2 (en) * 1999-04-16 2010-07-27 Caterpillar Inc. Sleeve metered unit pump and fuel injection system using the same

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2146578A1 (de) * 1970-09-18 1972-03-30 Caterpillar Tractor Co., Peoria, 111. (V.StA.) Treibstoffeinspritzpumpe mit durch Hebel einstellbarer Dosierbuchse

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1967101A (en) * 1928-08-31 1934-07-17 Bosch Robert Fuel feed mechanism
DE821288C (de) * 1950-03-23 1951-11-15 Kloeckner Humboldt Deutz Ag Einspritzpumpe
US3385221A (en) * 1967-03-07 1968-05-28 Caterpillar Tractor Co Multi-plunger engine fuel oil pump
FR1585785A (fr) * 1968-10-10 1970-01-30
US4071010A (en) * 1976-07-19 1978-01-31 Caterpillar Tractor Co. Engine start-up system and method
DE2821161C2 (de) * 1978-05-13 1983-08-04 Mtu Motoren- Und Turbinen-Union Friedrichshafen Gmbh, 7990 Friedrichshafen Geteilte Regelstange für eine Kraftstoffeinspritzpumpe
DE7836111U1 (de) * 1978-12-06 1980-05-14 Robert Bosch Gmbh, 7000 Stuttgart Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
JPS56118551A (en) * 1980-02-22 1981-09-17 Hino Motors Ltd Fuel injection pump for engine
JPS58114875U (ja) * 1982-01-29 1983-08-05 三菱自動車工業株式会社 列型噴射ポンプ装置

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2146578A1 (de) * 1970-09-18 1972-03-30 Caterpillar Tractor Co., Peoria, 111. (V.StA.) Treibstoffeinspritzpumpe mit durch Hebel einstellbarer Dosierbuchse

Also Published As

Publication number Publication date
JPS61182458A (ja) 1986-08-15
US4706626A (en) 1987-11-17
ATE40186T1 (de) 1989-02-15
DE3435987A1 (de) 1986-04-10
EP0178505A1 (fr) 1986-04-23
DE3567701D1 (en) 1989-02-23
JPH0681938B2 (ja) 1994-10-19

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