EP0386448B1 - Dispositif de réglage du début d'injection pour moteur à combustion interne - Google Patents

Dispositif de réglage du début d'injection pour moteur à combustion interne Download PDF

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Publication number
EP0386448B1
EP0386448B1 EP90101873A EP90101873A EP0386448B1 EP 0386448 B1 EP0386448 B1 EP 0386448B1 EP 90101873 A EP90101873 A EP 90101873A EP 90101873 A EP90101873 A EP 90101873A EP 0386448 B1 EP0386448 B1 EP 0386448B1
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EP
European Patent Office
Prior art keywords
adjuster
injection timing
setting
intermediate elements
pistons
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
EP90101873A
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German (de)
English (en)
Other versions
EP0386448A1 (fr
Inventor
Gerhard Dipl.-Ing. Geyer
Johann Mendle
Hermann-Josef Dipl.-Ing. Dillmann (Fh)
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
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Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP0386448A1 publication Critical patent/EP0386448A1/fr
Application granted granted Critical
Publication of EP0386448B1 publication Critical patent/EP0386448B1/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
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D1/00—Controlling fuel-injection pumps, e.g. of high pressure injection type
    • F02D1/16—Adjustment of injection timing
    • F02D1/18—Adjustment of injection timing with non-mechanical means for transmitting control impulse; with amplification of control impulse
    • F02D1/183—Adjustment of injection timing with non-mechanical means for transmitting control impulse; with amplification of control impulse hydraulic

Definitions

  • the invention is based on an injection timing adjuster for internal combustion engines according to the preamble of the main claim.
  • Such an injection timing adjuster is already known from DE-PS 33 39 009.
  • the stroke movement of actuating pistons guided in a piston carrier is converted here via intermediate members and transmission members located thereon and an eccentric adjustment gear into a mutual rotation of two coaxial shafts, namely an input and an output shaft.
  • Two actuating pistons are arranged parallel to each other on one adjuster side in a plane perpendicular to the longitudinal axis of the adjuster.
  • Coupling bolts each of which protrudes into a transverse bore in one of the actuating pistons and are firmly connected to one of the intermediate members, serve as transmission members between the actuating pistons and the intermediate members.
  • the longitudinal axes of the coupling bolts extend perpendicular to the longitudinal axis of the adjuster and perpendicular to the longitudinal axes of the actuating pistons.
  • the piston carrier Due to the eccentric effect of the adjustment gear, the piston carrier is rotated on its guide part when the two shafts are adjusted relative to one another and the forces required to rotate the piston carrier are transmitted to the piston carrier by the coupling bolts projecting into the actuating piston and the actuating piston itself.
  • the actuating pistons are additionally stressed by the lateral forces that occur and can jam and wear in their guides in the piston carrier.
  • Each of the coupling bolts protrudes into a central bore of the associated actuating piston, because z. B. two parallel actuating pistons are not connected to a common coupling bolt, since otherwise the actuating pistons would open with their lower edges for the passage of the coupling bolts necessary slots in the piston carrier.
  • the coupling bolts can therefore only be connected on one side to the intermediate links, and because of the small wall thickness of the intermediate links only short connecting lengths are available. Due to the one-sided mounting of the coupling bolts, there is a risk that they will bend or come loose from the connecting bore or tilt, causing the actuating pistons to jam.
  • the intermediate members move radially outwards or inwards during an adjustment and are guided radially only via the coupling bolts and the actuating pistons. Due to play and consequently tilting of the coupling bolts in the actuating piston, it is possible for the intermediate members to jam during a radial movement.
  • the injection timing adjuster according to the invention with the characterizing features of the main claim has the advantage that the intermediate links are guided over large areas on the piston carrier.
  • the parallel guidance of the intermediate links directly on the piston carrier separates the function of guiding the intermediate links and the introduction of the actuating forces into the intermediate links.
  • the forces required to rotate the piston carrier are transmitted directly to the piston carrier via the large contact surfaces between the intermediate members and the piston carrier.
  • FIG. 1 shows a first embodiment of an injection timing adjuster as a longitudinal section
  • FIG. 2 shows the injection adjuster as a cross section
  • FIG. 3 shows an intermediate link of the injection adjuster in a front view
  • FIG. 4 shows the intermediate link in a top view
  • FIG. 5 shows a second embodiment of the injection adjuster as a cross section.
  • the injection timing adjuster 1 shown in Figure 1 is attached to a fuel injection pump, not shown, for diesel engines, is provided as an open built-in injection timing adjuster for installation in a closed drive housing or in the wheel housing of the internal combustion engine with a gearwheel 2 serving in a known manner as a drive element.
  • the injection timing adjuster can also be designed as a closed sprayer adjuster.
  • the injection adjuster 1 serves, as will be explained in more detail below, in a known manner for changing the mutual rotational position of two coaxial shafts, an input shaft and an output shaft, depending on the operating parameters, the output shaft being either the camshaft of the injection pump or an intermediate shaft coupled to it. By changing the rotational position of both shafts, the time of injection or the start of delivery of the fuel injection pump is changed depending on a predetermined law.
  • a drive gear 2 serves as the drive shaft and a camshaft 3 of the fuel injection pump serves as the output shaft.
  • an adjuster disk 8 provided with two plane-parallel end faces 6 and 7, which is designed as a flange-shaped part of an adjuster hub 10.
  • the adjuster hub 10 is fastened on the camshaft 3 by means of a clamping screw 11 and receives a piston carrier 9 on a guide part 10a.
  • the compensation eccentric 14 are each connected to the drive gear 2 by means of a bolt 16 and serve to compensate for the arc height which the center points of the adjusting eccentrics 13 would reach if they would rotate about the bolts 16 without a compensation eccentric 14.
  • This rotary movement is mutually parallel by two, d. H. Actuated in pairs in the piston carrier 9, and actuated by the pressure of a hydraulic medium, actuating piston 18, which, according to the pressure of the hydraulic medium controlled by a control device, counteracts the force of return springs 19, in oil-tight cylinder bores 20 of the piston carrier 9 arranged parallel to one another and pointing outwards. move away from the adjuster hub 10.
  • the adjusting eccentrics 13 are rotated via intermediate members 22 which engage eccentrically on the adjusting eccentrics 13.
  • the actuating pistons 18 are all guided within a plane 24, indicated by dash-dotted lines in FIG. 1, perpendicular to a longitudinal axis 23 of the adjuster.
  • the piston carrier 9 has two flat boundary surfaces 26 running parallel to the longitudinal axis 23 of the adjuster and parallel to the longitudinal axes 21 of the cylinder bores 20.
  • the boundary surfaces 26 and partition walls 27 arranged between the actuating pistons 18 are provided with outwardly directed slots 29 in the region of the cylinder bores 20.
  • the intermediate members 22 each consist of a central part 30 which is U-shaped perpendicular to the longitudinal axis 23 of the adjuster.
  • Two walls 31 project vertically from the middle part 30, which extend parallel to the boundary surfaces 26 and point towards the piston carrier 9.
  • the piston carrier 9 is in the region of the cylinder bores 20 from the walls 31 and
  • Middle part 30 of the intermediate members 22 includes a U-shape.
  • a flat surface 32 on the central part 30 and two mutually opposite guide surfaces 33 on the walls 31 of the intermediate links 22 form a sliding guide for the intermediate links 22.
  • Two actuating pistons 18, which are arranged parallel to one another on an adjuster side, are connected to one of the intermediate links 22 via a single, common coupling pin 34 connected.
  • a one-piece molded bolt 28 projects, which engages in one of the adjusting eccentrics 13.
  • the coupling bolts 34 are pressed into bores 35a, b in the walls 31 of the intermediate members 22, can pass through the slots 29 in the boundary surfaces 26 and the partition walls 27 through the piston carrier 9 and are received by transverse bores 36 in the actuating piston 18.
  • the coupling bolts 34 extend perpendicular to the longitudinal axis 23 of the adjuster and perpendicular to the longitudinal axes 21 of the cylinder bores 20.
  • the coupling bolts 34 are provided with a somewhat smaller diameter at their front end 34a, with which they are inserted during assembly, than at their rear Late 34b. Accordingly, the bores 35b, through which the coupling bolts 34 are first inserted, are somewhat larger in diameter than the opposite bores 35a. The different diameters prevent the fit of the bore 35 b from being destroyed during the assembly of the coupling bolts 34.
  • the actuating pistons 18 are designed as hollow pistons and the transverse bores 36 for the passage of the coupling bolt 34 are each connected via a bore 38 to the interior of the actuating pistons 18 and thus to the pressurized areas of the cylinder bores 20 below the actuating pistons 18.
  • compression springs 19 acting on brackets 22b on the mutually facing ends 22a of the intermediate members 22 serve as return springs and at the same time have a restoring and stabilizing effect.
  • the compression springs 19 are clamped between spring abutments 39 and 40.
  • the spring abutments 39 are designed as spring plates and are each attached to the ends of a free-floating guide pin 42 that holds the compression springs 19 together.
  • the spring abutments 40 are received by the brackets 22b of the intermediate members 22 which protrude at right angles and are drilled through and are likewise designed as sleeve-shaped spring plates.
  • the hydraulic medium is fed into the cylinder bores 20 under the actuating piston 18 through the bores 44 in the adjuster hub 10.
  • the drive gear 2 assumes a predetermined rotational position with respect to the adjusting hub 10.
  • the intermediate members 22 are supported with their ends 22a against one another under the pretensioning force of the return springs 19, as a result of which the starting position is fixed.
  • An actuating movement of the actuating pistons 18 is transmitted via the coupling bolts 34 to the intermediate members 22 and from there via the molded bolts 28 to the adjusting eccentric 13.
  • the intermediate members 22 move, guided by the piston carrier 9, radially outward or inward and at the same time perform a rotary movement about the longitudinal axis 23 of the adjuster.
  • the piston carrier 9 is carried along by the guide surfaces 33 and makes the rotary movement of the intermediate members 22.
  • the intermediate links 22 are guided radially safely and precisely through the piston carrier 9 via the large guide surfaces 33 and boundary surfaces 26. This prevents jamming of the intermediate members 22 during radial movement on the guide pin 42. Lateral forces exerted by the intermediate members 22 during their rotational movement on the piston carrier 9 and lateral forces resulting from torsional vibrations on the piston carrier 9 are also transmitted via the large guide surfaces 33 and boundary surfaces 26, so that low surface pressures and great durability of the adjuster result.
  • the coupling bolts 34 which are connected to two of the actuating pistons 18 and are pressed into each of the two walls 31 of an intermediate member 22, achieve an exact guidance of the actuating pistons 18 in the cylinder bores 20, since the coupling bolts 34 bend only slightly and therefore the actuating pistons 18 do not tilt and can get stuck. A targeted lubrication of the coupling bolts 34 is achieved with low losses via the bores 38 in the actuating piston 18.
  • the cylinder bores 120 in the piston carrier 109 are covered on the outside by a respective end part 145 serving as a spring yoke.
  • a compression spring serving as a return spring 119 is clamped between each actuating piston 118 and the spring yoke 145.
  • the compression springs are guided in the end recesses 146 in the actuating piston 118 and in counterbores 148 in the spring yoke 145.
  • the spring yoke 145 is connected to the piston carrier 109 by two screws 147.
  • the arrangement of the return springs 119 within the piston carrier 109 means that the spring abutments on the intermediate members 122 can be dispensed with, so that their manufacture is simplified and, in addition to the piston carrier 109, there is space for installing further devices, for example for setting the start of delivery of the fuel injection pump.

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

Claims (7)

  1. Dispositif de réglage du début de l'injection pour moteurs à combustion interne, en particulier pour moteurs Diesel, avec des pistons de réglage, logés à l'intérieur du dispositif de réglage tournant autour d'un axe longitudinal (23) et pouvant être actionnés par la pression commandée en fonction de paramètres de marche d'un agent hydraulique à l'encontre d'une force de rappel, pistons de réglage (18), qui d'un agent hydraulique à l'encontre d'une force de rappel, piston de réglage (18), qui sont guidés dans des alésages cylindriques (20) dirigés vers l'extérieur, dont les axes longitudinaux (21) se trouvent dans un plan perpendiculaire à l'axe longitudinal (23) du dispositif de réglage, d'un porte-piston (9) disposé sur un moyeu (10) grâce auxquels au moyen d'organes intermédiaire (22) et d'organes de transmission disposés sur ceux-ci la position angulaire réciproque de l'arbre d'entraînement (2) et de l'arbre mené (3) peut être modifiée au moyen d'un mécanisme de réglage à excentrique (12) reliant l'arbre d'entraînement (2) à l'arbre mené (3), l'arbre d'entraînement (2) et l'arbre mené (3) étant disposés coaxialement par rapport à l'axe longitudinal (23) du dispositif de réglage et le moyeu (10) étant disposé sur l'un des arbres (2, 3), tandis que des éléments d'accouplement (34) disposés perpendiculairement aux axes longitudinaux (21) des alésages cylindriques (20) et reliés aux organes intermédiaires (22) et aux pistons de réglage (18) servent d'organes de transmission pour le mouvement de réglage des pistons de réglage (18) sur les organes intermédiaires (22) et des goujons (28) venant en prise dans le mécanisme de réglage à excentrique (12) et disposés sur les organes intermédiaires (22) servent d'organes de transmission entre les organes intermédiaires (22) et le mécanisme de réglage à excentrique (12), dispositif de réglage du début de l'injection caractérisé en ce que le porte-piston (9) présente des surfaces de délimitation (26) s'étendant parallèlement à l'axe longitudinal du dispositif de réglage (23) et parallèlement aux axes longitudinaux (21) des alésages cylindriques (20) et les organes intermédiaires (22) entourent en forme d'U le porte-piston (9) sur ses surfaces de délimitation (26) et un côté frontal et sont de cette façon guidés radialement sur le porte-piston (9).
  2. Dispositif de réglage du début de l'injection selon la revendication 1, caractérisé en ce que les organe intermédiaires (22) ont la forme d'un U et sont mis perpendiculairement à l'axe longitudinal du dispositif de réglage (23) et consistent essentiellement en une pièce médiane (30) et en des parois (31) partant perpendiculairement de celle-ci en direction du porte-piston (9) et parallèlement à ses surfaces de délimitation (26).
  3. Dispositif de réglage du débit de l'injection selon la revendication 1 ou 2, caractérisé en ce que deux pistons de réglage (18) sont disposés parallèlement l'un à l'autre pour chaque côté du dispositif de réglage et en ce que des goujons d'accouplement (34) s'étendant perpendiculairement à l'axe longitudinal du dispositif de réglage (23) et perpendiculairement aux axes longitudinaux (21) des alésages cylindriques (20) servent d'éléments d'accouplement entre les pistons de réglage (18) et les organes intermédiaires (22), les deux pistons de réglage (18) disposés sur un côté du dispositif de réglage étant reliés respectivement par un goujon unique commun d'accouplement (34) à l'un des organes intermédiaires (22).
  4. Dispositif de réglage du début de l'injection selon la revendication 3, caractérisé en ce que les goujons d'accouplement (34) sont enfoncés par pressage dans les alésages (35a, b) des parois (31) et présentent, sur leur extrémité antérieure (34a), qui est d'abord introduite lors du montage, un plus petit diamètre que sur son extrémité postérieure (34b).
  5. Dispositif de réglage du dispositif de l'injection selon la revendication 3 ou 4, caractérisé en ce que le piston de réglage (18) présente des alésages transversaux (36) servant au passage des goujons d'accouplement (34), alésages qui sont reliés par des ouvertures (38) dans les pistons de réglage (18) à la zone soumise à la pression des alésages cylindriques (20) entre les pistons de réglage (18).
  6. Dispositif de réglage du début de l'injection selon l'une des revendication 1 à 5, caractérisé en ce que au-dessus des alésages cylindriques (120) dans le porte-piston (109) est disposé vers l'extérieur une pièce de fermeture (145) et un ressort de rappel (119) est tendu entre le piston de réglage (118) et la pièce de fermeture (145).
  7. Dispositif de réglage du début de l'injection selon l'une des revendications 1 à 5, avec des ressorts de rappel pour appliquer la force de rappel pour le piston de réglage, caractérisé en ce que les organes intermédiaires (22) portent sur leurs extrémités (22a) tournées les unes vers les autres des consoles (22b) partant à angle droit de leurs parois (31), recevant respectivement un contre-appui de ressort (40) pour les ressorts de rappel (19).
EP90101873A 1989-03-04 1990-01-31 Dispositif de réglage du début d'injection pour moteur à combustion interne Expired - Lifetime EP0386448B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3907026 1989-03-04
DE3907026A DE3907026A1 (de) 1989-03-04 1989-03-04 Einspritzzeitpunktversteller fuer brennkraftmaschinen

Publications (2)

Publication Number Publication Date
EP0386448A1 EP0386448A1 (fr) 1990-09-12
EP0386448B1 true EP0386448B1 (fr) 1993-09-22

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP90101873A Expired - Lifetime EP0386448B1 (fr) 1989-03-04 1990-01-31 Dispositif de réglage du début d'injection pour moteur à combustion interne

Country Status (5)

Country Link
US (1) US4998523A (fr)
EP (1) EP0386448B1 (fr)
JP (1) JPH02277930A (fr)
DE (2) DE3907026A1 (fr)
ES (1) ES2044248T3 (fr)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0566236U (ja) * 1992-02-17 1993-09-03 株式会社ゼクセル 内燃機関の燃料噴射時期調整装置
US5630402A (en) * 1996-06-19 1997-05-20 Timing Systems, Inc. Fuel injection timing system
US7252073B1 (en) * 2006-09-08 2007-08-07 Kubota Corporation Engine timer for cold-start advance
JP5912543B2 (ja) * 2012-01-10 2016-04-27 ダイムラー・アクチェンゲゼルシャフトＤａｉｍｌｅｒ ＡＧ コモンレール式燃料噴射装置のサプライポンプ用ビスカスダンパ取付構造

Family Cites Families (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1316118A (en) * 1969-10-10 1973-05-09 Simms Group Research Dev Ltd Speed responsive devices
GB1357534A (en) * 1970-09-30 1974-06-26 Simms Group Research Dev Ltd Drive couplings
DE2826800A1 (de) * 1978-06-19 1980-01-03 Bosch Gmbh Robert Einspritzzeitpunktversteller fuer brennkraftmaschinen
FR2445440A1 (fr) * 1978-12-29 1980-07-25 Renault Vehicules Ind Dispositif automatique hydraulique incorpore d'avance a l'injection pour un moteur diesel
DE2950544A1 (de) * 1979-12-15 1981-06-19 Robert Bosch Gmbh, 7000 Stuttgart Einspritzzeitpunktversteller fuer brennkraftmaschinen
JPS57188735A (en) * 1981-05-15 1982-11-19 Diesel Kiki Co Ltd Fuel injection timing regulator
JPS58104326U (ja) * 1982-01-11 1983-07-15 株式会社デンソー 内燃機関用燃料噴射装置
FR2526867A2 (fr) * 1982-05-14 1983-11-18 Renault Vehicules Ind Dispositif automatique hydraulique incorpore d'avance a l'injection pour un moteur diesel
JPS595836A (ja) * 1982-07-01 1984-01-12 Nippon Denso Co Ltd 内燃機関用燃料噴射時期調整装置
JPS5968142U (ja) * 1982-10-29 1984-05-09 株式会社ボッシュオートモーティブ　システム 液圧式燃料噴射時期調整装置
JPS6049234U (ja) * 1983-09-14 1985-04-06 株式会社ボッシュオートモーティブ　システム オ−トマチックタイマ装置
DE3440055C2 (de) * 1984-11-02 1986-10-16 Daimler-Benz Ag, 7000 Stuttgart Hydraulischer Spritzversteller für eine Einspritzpumpe

Also Published As

Publication number Publication date
EP0386448A1 (fr) 1990-09-12
ES2044248T3 (es) 1994-01-01
DE59002782D1 (de) 1993-10-28
DE3907026A1 (de) 1990-09-06
US4998523A (en) 1991-03-12
JPH02277930A (ja) 1990-11-14

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