EP0386454B1 - Injection timing advance mechanism for internal combustion engines - Google Patents

Injection timing advance mechanism for internal combustion engines Download PDF

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Publication number
EP0386454B1
EP0386454B1 EP90101994A EP90101994A EP0386454B1 EP 0386454 B1 EP0386454 B1 EP 0386454B1 EP 90101994 A EP90101994 A EP 90101994A EP 90101994 A EP90101994 A EP 90101994A EP 0386454 B1 EP0386454 B1 EP 0386454B1
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EP
European Patent Office
Prior art keywords
advance mechanism
injection timing
eccentric
flyweight
timing advance
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
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EP90101994A
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German (de)
French (fr)
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EP0386454A1 (en
Inventor
Hermann-Josef Dipl.-Ing. Dillmann (Fh)
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication date
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Publication of EP0386454A1 publication Critical patent/EP0386454A1/en
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    • 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
    • F02D1/162—Adjustment of injection timing by mechanical means dependent on engine speed for angular adjustment of driving and driven shafts

Definitions

  • the invention is based on an injection timing adjuster for internal combustion engines according to the preamble of claim 1.
  • a return spring is clamped between one of the ends of the flyweights and one end of one of the stud bolts, so that two return springs are required for each stud bolt.
  • the return springs rest on the flyweights and on the ends of the studs on a spring plate. The many individual parts to be assembled should be avoided. There is also the risk that the spring plate will come loose under heavy shaking stress.
  • the injection timing adjuster according to the invention with the characterizing features of claim 1 has the advantage that an exact mutual guidance of the centrifugal weights is achieved by the design of the centrifugal weights with the guide surfaces and the boundary surfaces and tilting is avoided.
  • the development according to claim 2 ensures that a continuous compression spring can be used as a return spring and thus the number of individual parts to be assembled is reduced.
  • a reduction in the mass of the flyweight counteracting the actual flyweight mass is achieved by the development according to claim 5. Due to the configuration according to claim 6, two identical flyweights per adjuster, mounted on a cover, can be used.
  • FIG. 1 shows the injection timing adjuster in cross section
  • FIG. 2 shows the injection adjuster in longitudinal section
  • FIG. 3 shows a centrifugal weight in a partially sectioned view
  • FIG. 3a shows a section of a variant of the centrifugal weight according to FIG. 3
  • FIG. 4 shows the centrifugal weight in section along the line IV-IV in Figure 3 and Figure 5, the flyweight in plan view.
  • FIG. 1 shows an injection timing adjuster for a fuel injection pump for diesel engines, which is provided as an open built-in injection adjuster for installation in a closed drive housing or in the wheel housing of the engine.
  • the injection timing adjuster is used in a known manner to change the mutual rotational position of two coaxial shafts, a driving and a driven shaft, as a function of the speed, as a result of which the injection timing of the fuel injection pump is changed.
  • a drive part 1 designed as a drive gear serves as the driving shaft, and the camshaft 2 of the injection pump, which is only partially shown, with the adjuster hub 5 provided with a bearing flange 3, the hub part 6 of which receives a fastening nut 8 as the driven shaft.
  • an adjuster disk 14 provided with two plane-parallel end faces 11 and 12 and a cylindrical extension 13 is inserted and is firmly connected to the drive part 1 by means of screws 16.
  • An annular groove-shaped cavity formed by one end face 11 of the adjusting disk 14 and a hollow cylindrical recess 18 in the drive part 1 receives the bearing flange 3 and thus forms an axial and radial bearing 19 for the drive part 1.
  • the connection between the adjuster hub 5 connected to the driven shaft 2 and the drive gear wheel forming the drive part 1 is achieved by two eccentric pairs 20 which are rotatably mounted in the adjuster disk 14 and each consist of an adjusting eccentric 21 and a compensating eccentric 22.
  • the compensation eccentrics 22 are connected to the bearing flange 3 of the adjuster hub 5 by means of a bolt 23 each and serve to compensate for the arc height which the center points of the adjusting eccentrics 21 would reach if they would rotate about the bolts 23 without a compensation eccentric 22.
  • This rotary movement is effected by centrifugal weights designated 25, which can move radially away from the hub part 6 against the force of return springs 26 in accordance with the centrifugal forces increasing with increasing rotational speed and which rotate the adjusting eccentrics 21 via bearing bolts 27 which engage eccentrically in the adjusting eccentric 21.
  • the flyweights 25 have a U-shaped basic shape in cross section perpendicular to the longitudinal axis 29 of the adjuster.
  • Two legs 31 protrude from a weight body 30 containing the main part of the flyweight mass.
  • the weight body is provided with two flat boundary surfaces 32 which extend parallel to the longitudinal axis 29 of the adjuster.
  • a wall 33 protrudes from each of the two legs 31, the two walls 33 of a centrifugal weight 25 being provided on their mutually facing sides with guide surfaces 34 parallel to the boundary surfaces 32 and between the walls 33 a space for receiving the weight body 30 with its boundary surfaces 32 is present.
  • the walls 33 and the weight body 30 are connected via webs 39, the end faces 39a of which form a flat surface with the end face of the weight body 30.
  • a bracket 36 forming a spring abutment 35 projects from each of the legs 1 on the side opposite the guide surface 34 perpendicular to the guide surface 34.
  • the console 36 is provided with a recess 37 into which the ends of the return springs 26 are inserted. As shown in FIG. 3a, a pin 38 can also be inserted into the console 36, which protrudes into the ends of the return springs 26 to accommodate them.
  • the centrifugal weights 25 are arranged at 180 ° about the longitudinal axis 29 of the adjuster and mirror-inverted to one another, that is to say on an envelope, so that the weight body 30 of each centrifugal weight 25 lies between the legs 1 of the respective other centrifugal weight. Between the opposing spring abutments 35 of the flyweights 25, a compression spring is clamped in each case as a return spring 26.
  • the webs 39 are provided on their side opposite the weight body 30 with openings 40 and the brackets 36 each with a bore 41, as a result of which the mass of the flyweights 25 counteracting the actual flyweight mass is reduced.
  • the weight body 30 has a bore 42 extending parallel to the longitudinal axis 29 of the adjuster, into which the bearing pin 27 is pressed for connection to the adjusting eccentric 21. Depending on the installation position of the centrifugal weight, the bearing pin 27 is pressed into the bore 42 from one or the other side.
  • the cylindrical extension 13 of the adjusting disk 14 serves as an external stop for the flyweights 25.
  • the injection adjuster is closed by a cover part 44 which has an opening for the passage of a tool required for tightening or loosening the fastening nut 8.
  • centrifugal weights 25 move radially outwards under the influence of the centrifugal forces through the boundary surfaces 32 and the guide surfaces 34 of the respective other centrifugal weights, or inwardly by the return springs 26. Due to the large guide surfaces 34 and boundary surfaces 32, the centrifugal weights 25 are guided precisely so that they cannot tilt.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • High-Pressure Fuel Injection Pump Control (AREA)

Description

Stand der TechnikState of the art

Die Erfindung geht aus von einem Einspritzzeitpunktversteller für Brennkraftmaschinen nach der Gattung des Patentanspruchs 1.The invention is based on an injection timing adjuster for internal combustion engines according to the preamble of claim 1.

Aus der DE-PS 27 25 414 ist ein Einspritzzeitpunktversteller der vorgenannten Bauart bekannt. Die Fliehgewichte des Spritzverstellers bewegen sich entsprechend den mit der Drehzahl zunehmenden Fliehkräften entgegen der Kraft von Rückstellfedern, durch Stehbolzen radial geführt, nach außen. Die Stehbolzen treten durch Bohrungen in den Enden der Fliehgewichte hindurch. Da die Fliehgewichte nur über kurze Berührungsflächen im Bereich der Bohrungen auf den Stehbolzen geführt sind, können sie sich auf den Stehbolzen verkanten und somit klemmen, was wiederum zu einem erhöhten Verschleiß führt.From DE-PS 27 25 414 an injection timing adjuster of the aforementioned type is known. The centrifugal weights of the injection adjuster move outwards in accordance with the centrifugal forces increasing with the speed, counter to the force of return springs, guided radially by stud bolts. The stud bolts pass through holes in the ends of the flyweights. Since the centrifugal weights are only guided over short contact surfaces in the area of the bores on the stud bolts, they can jam on the stud bolts and thus jam, which in turn leads to increased wear.

Zwischen einem der Enden der Fliehgewichte und einem Ende eines der Stehbolzen ist jeweils eine Rückstellfeder eingespannt, so daß für jeden Stehbolzen zwei Rückstellfedern erforderlich sind. Die Rückstellfedern liegen an den Fliehgewichten und an den Enden der Stehbolzen jeweils an einem Federteller an. Die vielen zu montierenden Einzelteile sollten vermieden werden. Außerdem besteht die Gefahr, daß sich die Federteller unter starker Schüttelbelastung lösen.A return spring is clamped between one of the ends of the flyweights and one end of one of the stud bolts, so that two return springs are required for each stud bolt. The return springs rest on the flyweights and on the ends of the studs on a spring plate. The many individual parts to be assembled should be avoided. There is also the risk that the spring plate will come loose under heavy shaking stress.

Vorteile der ErfindungAdvantages of the invention

Der erfindungsgemäße Einspritzzeitpunktversteller mit den kennzeichnenden Merkmalen des Patentanspruchs 1 hat den Vorteil, daß durch die Ausbildung der Fliehgewichte mit den Führungsflächen und den Begrenzungsflächen eine exakte gegenseitige Führung der Fliehgewichte erreicht und ein Verkanten vermieden ist.The injection timing adjuster according to the invention with the characterizing features of claim 1 has the advantage that an exact mutual guidance of the centrifugal weights is achieved by the design of the centrifugal weights with the guide surfaces and the boundary surfaces and tilting is avoided.

In den Unteransprüchen sind vorteilhafte Ausgestaltungen und Weiterbildungen des Spritzverstellers gekennzeichnet. Durch die Weiterbildung nach Anspruch 2 ist erreicht, daß als Rückstellfeder jeweils eine durchgehende Druckfeder verwendet werden kann und somit die Zahl der zu montierenden Einzelteile verringert ist. Eine Reduzierung der der eigentlichen Fliehgewichtsmasse entgegenwirkenden Masse des Fliehgewichts ist durch die Weiterbildung nach Anspruch 5 erreicht. Durch die Ausgestaltung nach Anspruch 6 können zwei identische Fliehgewichte pro Versteller, auf Umschlag montiert, eingesetzt werden.Advantageous refinements and developments of the injection adjuster are characterized in the subclaims. The development according to claim 2 ensures that a continuous compression spring can be used as a return spring and thus the number of individual parts to be assembled is reduced. A reduction in the mass of the flyweight counteracting the actual flyweight mass is achieved by the development according to claim 5. Due to the configuration according to claim 6, two identical flyweights per adjuster, mounted on a cover, can be used.

Zeichnungdrawing

Ein Ausführungsbeispiel der Erfindung ist in der Zeichnung anhand mehrerer Figuren dargestellt und in der nachfolgenden Beschreibung näher erläutert. Es zeigt Figur 1 den Einspritzzeitpunktversteller im Querschnitt, Figur 2 den Spritzversteller im Längsschnitt, Figur 3 ein Fliehgewicht in teilweise geschnittener Ansicht, Figur 3a einen Ausschnitt einer Variante des Fliehgewichts nach Figur 3, Figur 4 das Fliehgewicht im Schnitt entlang der Linie IV-IV in Figur 3 und Figur 5 das Fliehgewicht in der Draufsicht.An embodiment of the invention is shown in the drawing using several figures and explained in more detail in the following description. FIG. 1 shows the injection timing adjuster in cross section, FIG. 2 shows the injection adjuster in longitudinal section, FIG. 3 shows a centrifugal weight in a partially sectioned view, FIG. 3a shows a section of a variant of the centrifugal weight according to FIG. 3, FIG. 4 shows the centrifugal weight in section along the line IV-IV in Figure 3 and Figure 5, the flyweight in plan view.

Beschreibung des AusführungsbeispielsDescription of the embodiment

In Figur 1 ist ein Einspritzzeitpunktversteller für eine Kraftstoffeinspritzpumpe für Dieselmotoren dargestellt, der als offener Einbauspritzversteller für den Einbau in ein geschlossenes Antriebsgehäuse bzw. in den Räderkasten des Motors vorgesehen ist.1 shows an injection timing adjuster for a fuel injection pump for diesel engines, which is provided as an open built-in injection adjuster for installation in a closed drive housing or in the wheel housing of the engine.

Der Einspritzzeitpunktversteller dient in bekannter Weise zur drehzahlabhängigen Änderung der gegenseitigen Drehlage zweier gleichachsiger Wellen, einer treibenden und einer getriebenen Welle, wodurch der Einspritzzeitpunkt der Kraftstoffeinspritzpumpe geändert wird.The injection timing adjuster is used in a known manner to change the mutual rotational position of two coaxial shafts, a driving and a driven shaft, as a function of the speed, as a result of which the injection timing of the fuel injection pump is changed.

Als treibende Welle dient ein als Antriebszahnrad ausgebildetes Antriebsteil 1 und als getriebene Welle die nur teilweise dargestellte Nockenwelle 2 der Einspritzpumpe mit der mit einem Lagerflansch 3 versehenen Verstellernabe 5, deren Nabenteil 6 eine Befestigungsmutter 8 aufnimmt.A drive part 1 designed as a drive gear serves as the driving shaft, and the camshaft 2 of the injection pump, which is only partially shown, with the adjuster hub 5 provided with a bearing flange 3, the hub part 6 of which receives a fastening nut 8 as the driven shaft.

In einer Ausdrehung 9 des Antriebsteils 1 ist eine mit zwei planparallelen Stirnflächen 11 und 12 sowie einem zylinderförmigen Ansatz 13 versehene Verstellerscheibe 14 eingesetzt und mittels Schrauben 16 mit dem Antriebsteil 1 fest verbunden. Ein von der einen Stirnfläche 11 der Verstellerscheibe 14 und einer hohlzylindrischen Ausnehmung 18 im Antriebsteil 1 gebildeter ringnutförmiger Hohlraum nimmt den Lagerflansch 3 auf und bildet somit ein Axial- und Radiallager 19 für das Antriebsteil 1.In a recess 9 of the drive part 1, an adjuster disk 14 provided with two plane-parallel end faces 11 and 12 and a cylindrical extension 13 is inserted and is firmly connected to the drive part 1 by means of screws 16. An annular groove-shaped cavity formed by one end face 11 of the adjusting disk 14 and a hollow cylindrical recess 18 in the drive part 1 receives the bearing flange 3 and thus forms an axial and radial bearing 19 for the drive part 1.

Die Verbindung zwischen der mit der getriebenen Welle 2 verbundenen Verstellernabe 5 und dem das Antriebsteil 1 bildenden Antriebszahnrad wird durch zwei in der Verstellerscheibe 14 drehbar gelagerte Exzenterpaare 20 erreicht, die aus je einem Verstellexzenter 21 und einem Ausgleichsexzenter 22 bestehen. Die Ausgleichsexzenter 22 sind mittels je eines Bolzens 23 mit dem Lagerflansch 3 der Verstellernabe 5 verbunden und dienen dem Ausgleich der Bogenhöhe, die die Mittelpunkte der Verstellexzenter 21 erreichen würden, wenn sie sich um die Bolzen 23 ohne Ausgleichsexzenter 22 drehen würden. Diese Drehbewegung wird durch mit 25 bezeichnete Fliehgewichte bewirkt, die sich entsprechend den mit zunehmender Drehzahl ansteigenden Fliehkräften entgegen der Kraft von Rückstellfedern 26 radial vom Nabenteil 6 weg nach außen bewegen können und über exzentrisch in die Verstellexzenter 21 eingreifende Lagerbolzen 27 die Verstellexzenter 21 verdrehen.The connection between the adjuster hub 5 connected to the driven shaft 2 and the drive gear wheel forming the drive part 1 is achieved by two eccentric pairs 20 which are rotatably mounted in the adjuster disk 14 and each consist of an adjusting eccentric 21 and a compensating eccentric 22. The compensation eccentrics 22 are connected to the bearing flange 3 of the adjuster hub 5 by means of a bolt 23 each and serve to compensate for the arc height which the center points of the adjusting eccentrics 21 would reach if they would rotate about the bolts 23 without a compensation eccentric 22. This rotary movement is effected by centrifugal weights designated 25, which can move radially away from the hub part 6 against the force of return springs 26 in accordance with the centrifugal forces increasing with increasing rotational speed and which rotate the adjusting eccentrics 21 via bearing bolts 27 which engage eccentrically in the adjusting eccentric 21.

Die Fliehgewichte 25 weisen im Querschnitt senkrecht zur Verstellerlängsachse 29 eine U-förmige Grundform auf. Von einem den Hauptteil der Fliehgewichtsmasse enthaltenden Gewichtskörper 30 stehen zwei Schenkel 31 ab. Der Gewichtskörper ist mit zwei ebenen Begrenzungsflächen 32 versehen, die sich parallel zur Verstellerlängsachse 29 erstrecken. Von den beiden Schenkeln 31 steht jeweils eine Wand 33 ab, wobei die beiden Wände 33 eines Fliehgewichts 25 auf ihren einander zugewandten Seiten mit zu den Begrenzungsflächen 32 parallelen Führungsflächen 34 versehen sind und zwischen den Wänden 33 ein Raum zur Aufnahme des Gewichtskörpers 30 mit seinen Begrenzungsflächen 32 vorhanden ist. Die Wände 33 und der Gewichtskörper 30 sind über Stege 39 verbunden, deren Stirnseiten 39a mit der Stirnseite des Gewichtskörpers 30 eine ebene Fläche bilden. Von jedem der Schenkel 1 steht auf der der Führungsfläche 34 gegenüberliegenden Seite senkrecht zur Führungsfläche 34 eine ein Federwiderlager 35 bildende Konsole 36 ab. Die Konsole 36 ist mit einer Vertiefung 37 versehen, in die die Enden der Rückstellfedern 26 eingesetzt sind. Wie in Figur 3a dargestellt,kann in die Konsole 36 auch ein Zapfen 38 eingefügt werden, der zur Aufnahme der Rückstellfedern 26 in deren Enden hineinragt.The flyweights 25 have a U-shaped basic shape in cross section perpendicular to the longitudinal axis 29 of the adjuster. Two legs 31 protrude from a weight body 30 containing the main part of the flyweight mass. The weight body is provided with two flat boundary surfaces 32 which extend parallel to the longitudinal axis 29 of the adjuster. A wall 33 protrudes from each of the two legs 31, the two walls 33 of a centrifugal weight 25 being provided on their mutually facing sides with guide surfaces 34 parallel to the boundary surfaces 32 and between the walls 33 a space for receiving the weight body 30 with its boundary surfaces 32 is present. The walls 33 and the weight body 30 are connected via webs 39, the end faces 39a of which form a flat surface with the end face of the weight body 30. A bracket 36 forming a spring abutment 35 projects from each of the legs 1 on the side opposite the guide surface 34 perpendicular to the guide surface 34. The console 36 is provided with a recess 37 into which the ends of the return springs 26 are inserted. As shown in FIG. 3a, a pin 38 can also be inserted into the console 36, which protrudes into the ends of the return springs 26 to accommodate them.

Die Fliehgewichte 25 sind um 180° um die Verstellerlängsachse 29 und spiegelverkehrt zueinander, also auf Umschlag angeordnet, so daß der Gewichtskörper 30 eines jeden Fliehgewichts 25 zwischen den Schenkeln 1 des jeweils anderen Fliehgewichts liegt. Zwischen den einander gegenüberliegenden Federwiderlagern 35 der Fliehgewichte 25 ist als Rückstellfeder 26 jeweils eine Druckfeder eingespannt. Die Stege 39 sind auf ihrer dem Gewichtskörper 30 gegenüberliegenden Seite mit Öffnungen 40 und die Konsolen 36 mit jeweils einer Bohrung 41 versehen, wodurch die der eigentlichen Fliehgewichtsmasse entgegenwirkende Masse der Fliehgewichte 25 verringert ist.The centrifugal weights 25 are arranged at 180 ° about the longitudinal axis 29 of the adjuster and mirror-inverted to one another, that is to say on an envelope, so that the weight body 30 of each centrifugal weight 25 lies between the legs 1 of the respective other centrifugal weight. Between the opposing spring abutments 35 of the flyweights 25, a compression spring is clamped in each case as a return spring 26. The webs 39 are provided on their side opposite the weight body 30 with openings 40 and the brackets 36 each with a bore 41, as a result of which the mass of the flyweights 25 counteracting the actual flyweight mass is reduced.

Der Gewichtskörper 30 weist eine sich parallel zur Verstellerlängsachse 29 erstreckende Bohrung 42 auf, in die der Lagerbolzen 27 zur Verbindung mit dem Verstellexzenter 21 eingepreßt ist. Entsprechend der Einbaulage des Fliehgewichts ist der Lagerbolzen 27 von der einen oder von der anderen Seite her in die Bohrung 42 eingepreßt. Der zylinderförmige Ansatz 13 der Verstellerscheibe 14 dient als Außenanschlag für die Fliehgewichte 25.The weight body 30 has a bore 42 extending parallel to the longitudinal axis 29 of the adjuster, into which the bearing pin 27 is pressed for connection to the adjusting eccentric 21. Depending on the installation position of the centrifugal weight, the bearing pin 27 is pressed into the bore 42 from one or the other side. The cylindrical extension 13 of the adjusting disk 14 serves as an external stop for the flyweights 25.

Der Spritzversteller wird durch ein Deckelteil 44 abgeschlossen, das eine Öffnung zum Durchtritt eines zum Anziehen bzw. Lösen der Befestigungsmutter 8 erforderlichen Werkzeugs aufweist.The injection adjuster is closed by a cover part 44 which has an opening for the passage of a tool required for tightening or loosening the fastening nut 8.

Die Fliehgewichte 25 bewegen sich unter dem Einfluß der Fliehkräfte radial durch die Begrenzungsflächen 32 und die Führungsflächen 34 des jeweils anderen Fliehgewichts geführt nach außen, bzw. durch die Rückstellfedern 26 bewirkt nach innen. Durch die großen Führungsflächen 34 und Begrenzungsflächen 32 sind die Fliehgewichte 25 exakt geführt, so daß sie sich nicht verkanten können.The centrifugal weights 25 move radially outwards under the influence of the centrifugal forces through the boundary surfaces 32 and the guide surfaces 34 of the respective other centrifugal weights, or inwardly by the return springs 26. Due to the large guide surfaces 34 and boundary surfaces 32, the centrifugal weights 25 are guided precisely so that they cannot tilt.

Claims (7)

  1. Injection timing advance mechanism for changing, as a function of the rotational speed, the injection timing of internal combustion engines, having two diametrically arranged flyweights (25) which are guided radially and can be displaced against the force of return springs (26) and, per flyweight, one eccentric pair (20) consisting of an advance mechanism eccentric (21) and a compensating eccentric (22), which eccentric pair can be rotated by means of the flyweight (25) hinged eccentrically on the advance mechanism eccentric (21) for the purpose of changing the angular position of two shafts on the same axis, a driven shaft (2) relative to a driving shaft (1), and the advance mechanism eccentric (21) of which eccentric pair (20) is supported within an advance mechanism disc (14) connected to one of the shafts and accepts the compensating eccentric (22) which is connected to the other shaft via a connecting element (23), the injection advance mechanism provided with a driving part (1) acting as the driving shaft being connected to the driven shaft (2) via an advance mechanism hub (5) fastened to this driven shaft (2), characterised in that each of the flyweights (25) has an essentially U-shaped basic shape in cross-section at right angles to the longitudinal axis (29) of the advance mechanism, with a weight body (30), which contains the main proportion of the flyweight mass, and two arms (31) projecting from the weight body, which arms (31) enclose the weight body (30) of the other flyweight (25) at the side and are guided by means of guide surfaces (34) facing one another and parallel to one another on two plane boundary surfaces (32) of the weight body (30) extending at the side parallel to the longitudinal axis (29) of the advance mechanism.
  2. Injection timing advance mechanism according to Claim 1, characterised in that a bracket (36) forming a spring abutment (35) projects at right angles to the guide surfaces (34) from each arm (31) on the sides opposite to the guide surfaces (34) and that at least one compression spring is clamped as return spring (26) between each two spring abutments (35) located opposite to one another.
  3. Injection timing advance mechanism according to Claim 2, characterised in that the spring abutments (35) have depressions (37) for accepting the compression springs (26), the ends of the compression springs (26) being inserted in these depressions (37).
  4. Injection timing advance mechanism according to Claim 2, characterised in that the spring abutments (35) have pegs (38) for accepting the compression springs (26), the pegs (38) protruding into the ends of the compression springs (26).
  5. Injection timing advance mechanism according to Claim 3, characterised in that the arms (31) and/or the brackets (36) projecting from the arms (31) are provided with openings (40, 41) in the region of the depressions (37).
  6. Injection timing advance mechanism according to one of the preceding claims, characterised in that the weight body (30) of each flyweight (25) has a hole (42) extending parallel to the longitudinal axis (29) of the advance mechanism, a bearing pin (27) being pressed into this hole and the two bearing pins (27) respectively projecting from the same side of two flyweights (25), fitted so that one is turned over relative to the other.
  7. Injection timing advance mechanism according to one of the preceding claims, characterised in that the weight body (30) and the brackets (36) with the arms (31) carrying the guide surfaces (34) of each flyweight (25) are connected by means of flat webs (39) located to one side and on an end surface.
EP90101994A 1989-03-04 1990-02-01 Injection timing advance mechanism for internal combustion engines Expired - Lifetime EP0386454B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3907024A DE3907024A1 (en) 1989-03-04 1989-03-04 INJECTION TIMING ADJUSTMENT FOR INTERNAL COMBUSTION ENGINES
DE3907024 1989-03-04

Publications (2)

Publication Number Publication Date
EP0386454A1 EP0386454A1 (en) 1990-09-12
EP0386454B1 true EP0386454B1 (en) 1993-01-13

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP90101994A Expired - Lifetime EP0386454B1 (en) 1989-03-04 1990-02-01 Injection timing advance mechanism for internal combustion engines

Country Status (3)

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EP (1) EP0386454B1 (en)
JP (1) JPH03202639A (en)
DE (2) DE3907024A1 (en)

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2725414C2 (en) * 1977-06-04 1985-04-25 Robert Bosch Gmbh, 7000 Stuttgart Centrifugal adjuster for changing the ignition or injection point in internal combustion engines

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Publication number Publication date
JPH03202639A (en) 1991-09-04
DE3907024A1 (en) 1990-09-06
EP0386454A1 (en) 1990-09-12
DE59000730D1 (en) 1993-02-25

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