EP0386448B1 - Injection timing advance mechanism for internal combustion engine - Google Patents

Injection timing advance mechanism for internal combustion engine 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
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EP90101873A
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German (de)
French (fr)
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EP0386448A1 (en
Inventor
Gerhard Dipl.-Ing. Geyer
Johann Mendle
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 of EP0386448A1 publication Critical patent/EP0386448A1/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
    • F02D1/18—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)

Description

Stand der TechnikState of the art

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

Ein solcher Einspritzzeitpunktversteller ist bereits aus der DE-PS 33 39 009 bekannt. Die Hubbewegung von in einem Kolbenträger geführten Stellkolben wird hier über Zwischenglieder und an diesen befindliche Übertragungsglieder sowie ein Exzenterverstellgetriebe in eine gegenseitige Verdrehung zweier gleichachsiger Wellen, nämlich einer Antriebs- und einer Abtriebswelle, umgewandelt. Jeweils zwei Stellkolben sind parallel zueinander auf einer Verstellerseite in einer Ebene senkrecht zur Verstellerlängsachse angeordnet. Als Übertragungsglieder zwischen den Stellkolben und den Zwischengliedern dienen Koppelbolzen, von denen jeder in eine Querbohrung in einen der Stellkolben ragt und mit einem der Zwischenglieder fest verbunden ist. Die Längsachsen der Koppelbolzen erstrecken sich dabei senkrecht zur Verstellerlängsachse und senkrecht zu den Längsachsen der Stellkolben.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.

Aufgrund der Exzenterwirkung des Verstellgetriebes wird bei einer Verstellung der beiden Wellen zueinander der Kolbenträger auf seinem Führungsteil verdreht und die zur Verdrehung des Kolbenträgers erforderlichen Kräfte werden durch die in die Stellkolben ragenden Koppelbolzen und die Stellkolben selbst auf den Kolbenträger übertragen. Die Stellkolben werden durch die dabei auftretenden Seitenkräfte zusätzlich beansprucht und können in ihren Führungen im Kolbenträger klemmen und verschleißen.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.

Jeder der Koppelbolzen ragt in eine mittige Bohrung des zugehörigen Stellkolbens, denn es können z. B. nicht zwei parallele Stellkolben mit einem gemeinsamen Koppelbolzen verbunden werden, da sonst die Stellkolben mit ihren Unterkanten zum Durchtritt der Koppelbolzen erforderliche Schlitze im Kolbenträger öffnen würden. Die Koppelbolzen können also nur einseitig mit den Zwischengliedern verbunden werden, wobei aufgrund der geringen Wandstärke der Zwischenglieder nur geringe Verbindungslängen zur Verfügung stehen. Durch die einseitige Lagerung der Koppelbolzen besteht die Gefahr, daß diese sich durchbiegen oder aus der Verbindungsbohrung lösen bzw. schiefstellen, wodurch die Stellkolben sich verklemmen. Die Zwischenglieder bewegen sich bei einer Verstellung radial nach außen bzw. innen und werden dabei nur über die Koppelbolzen und die Stellkolben radial geführt. Aufgrund von Spiel und demzufolge von Verkantungen der Koppelbolzen in den Stellkolben ist es möglich, daß die Zwischenglieder sich bei einer radialen Bewegung verklemmen.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.

Vorteile der ErfindungAdvantages of the invention

Der erfindungsgemäße Einspritzzeitpunktversteller mit den kennzeichnenden Merkmalen des Hauptanspruchs hat den Vorteil, daß die Zwischenglieder über große Flächen auf dem Kolbenträger geführt sind.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.

Durch die Parallelführung der Zwischenglieder direkt auf dem Kolbenträger sind die Funktion der Führung der Zwischenglieder und der Einleitung der Stellkräfte in die Zwischenglieder getrennt. Die zur Verdrehung des Kolbenträgers erforderlichen Kräfte werden über die großen Berührungsflächen zwischen den Zwischengliedern und dem Kolbenträger direkt auf den Kolbenträger übertragen.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.

In den Unteransprüchen sind vorteilhafte Ausgestaltungen und Weiterbildungen der Erfindung beschrieben. In der Weiterbildung nach Anspruch 3 ist die Durchbiegung der Koppelbolzen verringert bzw. eine Schiefstellung ausgeschlossen, so daß ein Verklemmen der Stellkolben in den Zylinderbohrungen verhindert ist. Durch die Weiterbildung nach Anspruch 4 ist erreicht, daß die Preßsitze der Koppelbolzen in den Zwischengliedern nicht schon bei der Montage der Koppelbolzen beschädigt werden. Durch die Weiterbildung nach Anspruch 5 ist eine sichere Schmierung der Koppelbolzen mit geringen Verlusten erreicht. Durch die Weiterbildung nach Anspruch 6 ist eine einfache Herstellung der Zwischenglieder bei zugleich raumsparender Anordnung der Rückstellfedern, geringer Schwingungsanregung des Gesamtsystems und geringer Anzahl von Bauelementen erreicht.Advantageous refinements and developments of the invention are described in the subclaims. In the development according to claim 3, the deflection of the coupling bolts is reduced or an inclination is excluded, so that jamming of the actuating pistons in the cylinder bores is prevented. The development according to claim 4 ensures that the press fits of the coupling bolts in the intermediate members are not damaged during the assembly of the coupling bolts. The further development according to claim 5 ensures reliable lubrication of the coupling bolts with low losses. Through the development according to claim 6, a simple manufacture of the intermediate links with a space-saving arrangement of the return springs, low vibration excitation of the overall system and a small number of components is achieved.

Zeichnungdrawing

Zwei Ausführungsbeispiele der Erfindung sind in der Zeichnung dargestellt und in der nachfolgenden Beschreibung näher erläutert. Es zeigt Figur 1 ein erstes Ausführungsbeispiel eines Einspritzzeitpunktverstellers als Längsschnitt, Figur 2 den Spritzversteller als Querschnitt, Figur 3 ein Zwischenglied des Spritzverstellers in der Vorderansicht, Figur 4 das Zwischenglied in der Draufsicht und Figur 5 ein zweites Ausführungsbeispiel des Spritzverstellers als Querschnitt.Two embodiments of the invention are shown in the drawing and explained in more detail in the following description. 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, and FIG. 5 shows a second embodiment of the injection adjuster as a cross section.

Beschreibung der AusführungsbeispieleDescription of the embodiments

Der in Figur 1 dargestellte Einspritzzeitpunktversteller 1 ist an eine nicht dargestellte Kraftstoffeinspritzpumpe für Dieselmotoren angebaut, als offener Einbauspritzversteller für den Einbau in ein geschlossenes Antriebsgehäuse bzw. in den Räderkasten der Brennkraftmaschine vorgesehen mit einem in bekannter Weise als Antriebselement dienenden Zahnrad 2. Der Einspritzzeitpunktversteller kann auch als geschlossener Anbauspritzversteller ausgeführt werden. Der Spritzversteller 1 dient, wie anschließend noch näher erläutert, in bekannter Weise zur betriebskenngrößenabhängigen Änderung der gegenseitigen Drehlage zweier gleichachsiger Wellen, einer Antriebswelle und einer Abtriebswelle, wobei die Abtriebswelle entweder zugleich die Nockenwelle der Einspritzpumpe ist oder eine mit dieser gekoppelte Zwischenwelle. Durch die Änderung der Drehlage beider Wellen wird der Einspritzzeitpunkt bzw. der Förderbeginn der Kraftstoffeinspritzpumpe in Abhängigkeit von einer vorgegebenen Gesetzmäßigkeit verändert.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.

Bei dem in den Figuren 1 bis 4 dargestellten ersten Ausführungsbeispiel dient als Antriebswelle ein Antriebszahnrad 2 und als Abtriebswelle dient eine Nockenwelle 3 der Kraftstoffeinspritzpumpe. In einer Ausdrehung 4 des Antriebszahnrads 2 ist eine mit zwei planparallelen Stirnflächen 6 und 7 versehene Verstellerscheibe 8 gelagert, die als ein flanschförmiger Teil einer Verstellernabe 10 ausgebildet ist. Auf der Nockenwelle 3 ist die Verstellernabe 10 mittels einer Spannschraube 11 befestigt und nimmt auf einem Führungsteil 10a einen Kolbenträger 9 auf. Die Verbindung zwischen dem Antriebszahnrad 2 und der auch als Teil der Nockenwelle 3 anzusehenden Verstellerscheibe 8 wird durch zwei in der Verstellerscheibe 8 drehbar gelagerte Exzenterpaare 12 herbeigeführt, die aus je einem Verstellexzenter 13 und einem Ausgleichsexzenter 14 bestehen. Die Ausgleichsexzenter 14 sind mittels je einem Bolzen 16 mit dem Antriebszahnrad 2 verbunden und dienen dem Ausgleich der Bogenhöhe, die die Mittelpunkte der Verstellexzenter 13 erreichen würden, wenn sie sich um die Bolzen 16 ohne Ausgleichsexzenter 14 drehen würden.In the first exemplary embodiment shown in FIGS. 1 to 4, a drive gear 2 serves as the drive shaft and a camshaft 3 of the fuel injection pump serves as the output shaft. In a recess 4 of the drive gear 2 there is mounted 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 connection between the drive gear 2 and the adjuster disk 8, which is also to be regarded as part of the camshaft 3, is brought about by two eccentric pairs 12 rotatably mounted in the adjuster disk 8, each consisting of an adjusting eccentric 13 and a compensating eccentric 14. 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.

Diese Drehbewegung wird durch je zwei parallel zueinander, d. h. paarweise im Kolbenträger 9 geführte, und vom Druck eines Hydraulikmediums betätigbaren Stellkolben 18 bewirkt, die sich entsprechend dem von einem Steuergerät gesteuerten Druck des Hydraulikmediums entgegen der Kraft von Rückstellfedern 19, in parallel zueinander angeordneten und nach außen weisenden Zylinderbohrungen 20 des Kolbenträgers 9 öldicht geführt, von der Verstellernabe 10 weg nach außen bewegen. Dabei werden über exzentrisch an den Verstellexzentern 13 angreifende Zwischenglieder 22 die Verstellexzenter 13 verdreht. Die Stellkolben 18 sind alle innerhalb einer in Figur 1 strichpunktiert angedeuteten senkrecht zu einer Längsachse 23 des Verstellers liegenden Ebene 24 geführt.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. In this case, 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.

Der Kolbenträger 9 weist zwei parallel zur Längsachse 23 des Verstellers und parallel zu den Längsachsen 21 der Zylinderbohrungen 20 verlaufende ebene Begrenzungsflächen 26 auf. Die Begrenzungsflächen 26 und zwischen den Stellkolben 18 angeordnete Trennwände 27 sind im Bereich der Zylinderbohrungen 20 mit nach außen gerichteten Schlitzen 29 versehen.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.

Die Zwischenglieder 22 bestehen, wie in Figur 3 dargestellt, aus je einem Mittelteil 30, das senkrecht zur Verstellerlängsachse 23 U-förmig ausgebildet ist. Vom Mittelteil 30 stehen senkrecht je zwei Wände 31 ab, die sich parallel zu den Begrenzungsflächen 26 erstrecken und zum Kolbenträger 9 hinweisen. Der Kolbenträger 9 wird jeweils im Bereich der Zylinderbohrungen 20 von den Wänden 31 und dem Mittelteil 30 der Zwischenglieder 22 U-förmig umfaßt. Eine Planfläche 32 am Mittelteil 30 und zwei einander gegenüberliegende Führungsflächen 33 an den Wänden 31 der Zwischenglieder 22 bilden eine Gleitführung für die Zwischenglieder 22. Jeweils zwei parallel zueinander auf einer Verstellerseite angeordnete Stellkolben 18 sind über einen einzigen, gemeinsamen Koppelbolzen 34 mit einem der Zwischenglieder 22 verbunden. Auf der dem Kolbenträger 9 abgewandten Seite der Mittelteile 30 steht je ein einteilig angeformter Bolzen 28 ab, der in einen der Verstellexzenter 13 eingreift.As shown in FIG. 3, 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. On the side of the middle parts 30 facing away from the piston carrier 9, a one-piece molded bolt 28 projects, which engages in one of the adjusting eccentrics 13.

Die Koppelbolzen 34 sind in Bohrungen 35a, b in den Wänden 31 der Zwischenglieder 22 eingepreßt, können durch die Schlitze 29 in den Begrenzungsflächen 26 und den Trennwänden 27 durch den Kolbenträger 9 treten und werden von Querbohrungen 36 in den Stellkolben 18 aufgenommen. Die Koppelbolzen 34 erstrecken sich senkrecht zur Verstellerlängsachse 23 und senkrecht zu den Längsachsen 21 der Zylinderbohrungen 20. Die Koppelbolzen 34 sind an ihrem vorderen Ende 34a, mit dem sie bei der Montage zuerst eingeführt werden, mit einem etwas kleineren Durchmesser versehen, als an ihrem hinteren Ende 34b. Entsprechend sind auch die Bohrungen 35b, durch die die Koppelbolzen 34 zuerst eingeführt werden, in ihrem Durchmesser etwas größer als die gegenüberliegenden Bohrungen 35a. Durch die unterschiedlichen Durchmesser wird verhindert, daß die Passung der Bohrung 35 b schon bei der Montage der Koppelbolzen 34 zerstört wird.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.

Die Stellkolben 18 sind als Hohlkolben ausgeführt und die Querbohrungen 36 zum Durchtritt des Koppelbolzens 34 sind über je eine Bohrung 38 mit den Innenräumen der Stellkolben 18 und damit mit den druckbeaufschlagten Bereichen der Zylinderbohrungen 20 unterhalb der Stellkolben 18 verbunden.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.

Vier an Konsolen 22b an den einander zugewandten Enden 22a der Zwischenglieder 22 angreifende Druckfedern 19 dienen als Rückstellfedern und wirken zugleich rückstellend und stabilisierend. Die Druckfedern 19 sind zwischen Federwiderlagern 39 und 40 eingespannt. Die Federwiderlager 39 sind als Federteller ausgebildet und jeweils an den Enden je eines die Druckfedern 19 zusammenhaltenden, freischwingenden Führungsbolzens 42 befestigt. Die Federwiderlager 40 werden von den rechtwinklig abstehenden und durchbohrten Konsolen 22b der Zwischenglieder 22 aufgenommen und sind ebenfalls als hülsenförmige Federteller ausgebildet. Das Hydraulikmedium wird in die Zylinderbohrungen 20 unter den Stellkolben 18 durch die Bohrungen 44 in der Verstellernabe 10 zugeführt.Four 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.

In der in den Figuren 1 und 2 gezeichneten Ausgangslage der Stellkolben 18 nimmt das Antriebszahnrad 2 eine vorbestimmte Drehlage gegenüber der Verstellernabe 10 ein. Die Zwischenglieder 22 stützen sich mit ihren Enden 22a unter der Vorspannkraft der Rückstellfedern 19 aneinander ab, wodurch die Ausgangslage festgelegt ist. Eine Stellbewegung der Stellkolben 18 wird über die Koppelbolzen 34 auf die Zwischenglieder 22 und von diesen über die angeformten Bolzen 28 auf die Verstellexzenter 13 übertragen. Die Zwischenglieder 22 bewegen sich dabei, vom Kolbenträger 9 geführt, radial nach außen bzw. innen und führen gleichzeitig eine Drehbewegung um die Verstellerlängsachse 23 aus. Der Kolbenträger 9 wird über die Führungsflächen 33 mitgenommen und macht die Drehbewegung der Zwischenglieder 22 mit. Der größtmögliche Hub der Stellkolben 18 und damit die maximale Verstellung der gegenseitigen Drehlage zwischen dem Antriebszahnrad 2 und der Verstellernabe 10 wird durch zwei Absätze 45 am Kolbenträger 9 begrenzt, an den die Mittelteile 30 der Zwischenglieder 22 bei Erreichen ihrer äußersten Endlage anschlagen.In the starting position of the actuating pistons 18 shown in FIGS. 1 and 2, 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 greatest possible stroke of the actuating piston 18 and thus the maximum adjustment of the mutual rotational position between the drive gear 2 and the adjuster hub 10 is limited by two shoulders 45 on the piston carrier 9, against which the middle parts 30 of the intermediate members 22 strike when they reach their extreme end position.

Über die großen Führungsflächen 33 und Begrenzungsflächen 26 werden die Zwischenglieder 22 radial sicher und exakt durch den Kolbenträger 9 geführt. Dadurch wird ein Verklemmen der Zwischenglieder 22 bei radialer Bewegung auf den Führungsbolzen 42 vermieden. Von den Zwischengliedern 22 bei ihrer Drehbewegung auf den Kolbenträger 9 ausgeübte Seitenkräfte und aus Drehschwingungen resultierende Seitenkräfte auf den Kolbenträger 9 werden ebenfalls über die großen Führungsflächen 33 und Begrenzungsflächen 26 übertragen, so daß sich geringe Flächenpressungen und eine große Dauerhaltbarkeit des Verstellers ergeben. Durch die mit jeweils zwei der Stellkolben 18 verbundenen und in beiden Wänden 31 je eines Zwischenglieds 22 eingepreßten Koppelbolzen 34 ist eine exakte Führung der Stellkolben 18 in den Zylinderbohrungen 20 erreicht, da die Koppelbolzen 34 sich nur wenig durchbiegen und die Stellkolben 18 daher nicht kippen und sich verklemmen können. Über die Bohrungen 38 in den Stellkolben 18 ist eine gezielte Schmierung der Koppelbolzen 34 mit geringen Verlusten erreicht.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.

Bei einem in Figur 5 dargestellten zweiten Ausführungsbeispiel sind die Zylinderbohrungen 120 im Kolbenträger 109, abweichend vom ersten Ausführungsbeispiel, nach außen durch je ein als Federjoch dienendes Abschlußteil 145 abgedeckt. Zwischen je einem Stellkolben 118 und dem Federjoch 145 ist eine als Rückstellfeder 119 dienende Druckfeder eingespannt. Die Druckfedern sind in stirnseitigen Vertiefungen 146 in den Stellkolben 118 und in Ansenkungen 148 im Federjoch 145 geführt. Das Federjoch 145 ist über zwei Schrauben 147 mit dem Kolbenträger 109 verbunden.In a second exemplary embodiment shown in FIG. 5, the cylinder bores 120 in the piston carrier 109, unlike the first exemplary embodiment, 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.

Durch die Anordnung der Rückstellfedern 119 innerhalb des Kolbenträgers 109 können die Federwiderlager an den Zwischengliedern 122 entfallen, so daß deren Herstellung vereinfacht ist und neben dem Kolbenträger 109 Raum zum Einbau weiterer Einrichtungen, beispielsweise zur Förderbeginneinstellung der Kraftstoffeinspritzpumpe, vorhanden ist.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.

Claims (7)

  1. Injection timing adjuster for internal-combustion engines, in particular for diesel engines, having setting pistons (18) which are accommodated within the adjuster rotating about a longitudinal axis (23) and are actuable against a resetting force by the pressure, which is controlled as a function of operating parameters, of a hydraulic medium, which setting pistons (18) are guided in outwardly directed cylinder bores (20), whose longitudinal axes (21) are located in a plane at right angles to the adjuster longitudinal axis (23), of a piston carrier (9) arranged on a hub part (10) and, by means of which setting pistons (18), the rotational position of a driving shaft (2) relative to a driven shaft (3) can be changed by means of intermediate elements (22) and transmission elements attached to the latter, via an eccentric adjusting gear (12) connecting the driving shaft (2) to the driven shaft (3), the driving shaft (2) and the driven shaft (3) being arranged coaxial to the adjuster longitudinal axis (23) and the hub part (10) being arranged on one of the shafts (2; 3), with coupling elements (34), which are arranged at right angles to the longitudinal axes (21) of the cylinder bores (20) and are connected to the intermediate elements (22) and the setting pistons (18), acting as the transmission elements for the setting motion of the setting pistons (18) on the intermediate elements (22), and pins (28), which are attached to the intermediate elements (22) and engage in the eccentric adjusting gear (12), acting as the transmission elements between the intermediate elements (22) and the eccentric setting gear (12), characterised in that the piston carrier (9) has boundary surfaces (26) extending parallel to the adjuster longitudinal axis (23) and parallel to the longitudinal axes (21) of the cylinder bores (20), and the intermediate elements (22) enclose the piston carrier (9) in U-shape on its boundary surfaces (26) and one end face and, by this means, are guided radially on the piston carrier (9).
  2. Injection timing adjuster according to Claim 1, characterised in that the intermediate elements (22) are configured in U-shape at right angles to the adjuster longitudinal axis (23) and consist essentially of a central part (30) and walls (31), which protrude at right angles from the central part (30) towards the piston carrier (9) and parallel to the boundary surfaces (26) of the latter.
  3. Injection timing adjuster according to Claim 1 or 2, characterised in that two setting pistons (18) per adjuster side are arranged parallel to one another and in that coupling pins (34), which extend at right angles to the adjuster longitudinal axis (23) and at right angles to the longitudinal axes (21) of the cylinder bores (20), act as the coupling elements between the setting pistons (18) and the intermediate elements (22), in each case the two setting pistons (18) arranged on an adjuster side being connected by means of a single, common coupling pin (34) to one of the intermediate elements (22).
  4. Injection timing adjuster according to Claim 3, characterised in that the coupling pins (34) are pressed into holes (35a, b) in the walls (31) and have a smaller diameter at their front end (34a), which is introduced first on assembly, than at their rear end (34b).
  5. Injection timing adjuster according to Claim 3 or 4, characterised in that the setting pistons (18) have transverse holes (36) used for the passage of the coupling pins (34), which transverse holes (36) are connected via openings (38) in the setting pistons (18) to the region of the cylinder bores (20), between the setting pistons (18), which is subjected to pressure.
  6. Injection timing adjuster according to one of Claims 1 to 5, characterised in that one shut-off part (145) is arranged towards the outside above each cylinder bore (120) in the piston carrier (109) and a return spring (119) is clamped between each setting piston (118) and the shut-off part (145).
  7. Injection timing adjuster according to one of Claims 1 to 5, with return springs for the application of the resetting force for the setting pistons, characterised in that the ends (22a), facing towards one another, of the intermediate elements (22) carry brackets (22b) protruding at right angles from their walls (31), each bracket accommodating a spring abutment (40) for the return springs (19).
EP90101873A 1989-03-04 1990-01-31 Injection timing advance mechanism for internal combustion engine Expired - Lifetime EP0386448B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3907026A DE3907026A1 (en) 1989-03-04 1989-03-04 INJECTION TIMING ADJUSTMENT FOR INTERNAL COMBUSTION ENGINES
DE3907026 1989-03-04

Publications (2)

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

Family

ID=6375563

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Application Number Title Priority Date Filing Date
EP90101873A Expired - Lifetime EP0386448B1 (en) 1989-03-04 1990-01-31 Injection timing advance mechanism for internal combustion engine

Country Status (5)

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US (1) US4998523A (en)
EP (1) EP0386448B1 (en)
JP (1) JPH02277930A (en)
DE (2) DE3907026A1 (en)
ES (1) ES2044248T3 (en)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0566236U (en) * 1992-02-17 1993-09-03 株式会社ゼクセル Fuel injection timing adjusting device for internal combustion engine
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 (en) * 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 Viscous damper mounting structure for supply pump of common rail fuel injection system

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 (en) * 1978-06-19 1980-01-03 Bosch Gmbh Robert INJECTION TIMING ADJUSTMENT FOR INTERNAL COMBUSTION ENGINES
FR2445440A1 (en) * 1978-12-29 1980-07-25 Renault Vehicules Ind AUTOMATIC HYDRAULIC DEVICE INCORPORATED INJECTION INJECTION FOR A DIESEL ENGINE
DE2950544A1 (en) * 1979-12-15 1981-06-19 Robert Bosch Gmbh, 7000 Stuttgart INJECTION TIMING ADJUSTMENT FOR INTERNAL COMBUSTION ENGINES
JPS57188735A (en) * 1981-05-15 1982-11-19 Diesel Kiki Co Ltd Fuel injection timing regulator
JPS58104326U (en) * 1982-01-11 1983-07-15 株式会社デンソー Fuel injection device for internal combustion engines
FR2526867A2 (en) * 1982-05-14 1983-11-18 Renault Vehicules Ind AUTOMATIC HYDRAULIC DEVICE INCORPORATING INJECTION ADVANCE FOR A DIESEL ENGINE
JPS595836A (en) * 1982-07-01 1984-01-12 Nippon Denso Co Ltd Fuel injection timing adjusting apparatus for internal combustion engine
JPS5968142U (en) * 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 Hydraulic fuel injection timing adjustment device
JPS6049234U (en) * 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 automatic timer device
DE3440055C2 (en) * 1984-11-02 1986-10-16 Daimler-Benz Ag, 7000 Stuttgart Hydraulic injection adjuster for an injection pump

Also Published As

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

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