EP0518898B1 - Drive arrangement for a camshaft - Google Patents

Drive arrangement for a camshaft Download PDF

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Publication number
EP0518898B1
EP0518898B1 EP91904642A EP91904642A EP0518898B1 EP 0518898 B1 EP0518898 B1 EP 0518898B1 EP 91904642 A EP91904642 A EP 91904642A EP 91904642 A EP91904642 A EP 91904642A EP 0518898 B1 EP0518898 B1 EP 0518898B1
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EP
European Patent Office
Prior art keywords
camshaft
pair
gears
switching element
drive wheel
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EP91904642A
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German (de)
French (fr)
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EP0518898A1 (en
Inventor
Richard Clos
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Audi AG
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Audi AG
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/34403—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using helically teethed sleeve or gear moving axially between crankshaft and camshaft
    • F01L1/34406—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using helically teethed sleeve or gear moving axially between crankshaft and camshaft the helically teethed sleeve being located in the camshaft driving pulley
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/02—Valve drive
    • F01L1/04—Valve drive by means of cams, camshafts, cam discs, eccentrics or the like
    • F01L1/047—Camshafts
    • F01L2001/0471—Assembled camshafts
    • F01L2001/0473—Composite camshafts, e.g. with cams or cam sleeve being able to move relative to the inner camshaft or a cam adjusting rod
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L2001/34486—Location and number of the means for changing the angular relationship

Definitions

  • the invention relates to a drive device for a camshaft according to the preamble of claim 1.
  • Such a drive device is described for example in DE-A 19 63 549.
  • the invention has for its object to provide a camshaft drive device of the generic type, the longitudinal extent of which is only extremely slightly greater than the longitudinal extent of a drive device without a camshaft adjusting device.
  • the switching element can be actuated hydraulically by a servomotor, for example in accordance with DE-A 19 63 549 mentioned at the beginning, in which part of the switching element forms a hydraulic piston.
  • a servomotor adjacent to the end of the camshaft facing away from the drive wheel and to connect the actuator of the servomotor to the shifting element by means of a shift rod passing through the camshaft.
  • the servomotor comes with a longitudinally installed internal combustion engine at a point in the engine compartment at which the bonnet rises towards the windshield, so that there is sufficient space for accommodating the servomotor.
  • Fig. 1 denotes the cylinder head of a valve-controlled reciprocating piston internal combustion engine, in which a camshaft 3 is supported via bearings 2, the cams of which actuate intake and / or exhaust valves, not shown, of the internal combustion engine.
  • a tubular extension 4 is screwed to the camshaft 3 by screws 4a, on which a drive wheel 5 is mounted, which is driven by the crankshaft of the internal combustion engine.
  • the holes 4b in the extension 4, through which the screws 4a extend, are designed as elongated holes in order to enable a basic setting of the camshaft 3 relative to the drive wheel 5.
  • a switching element 6 is used, which is non-rotatably connected to the drive wheel via a first pair of teeth 7, 9 and non-rotatably connected to the camshaft extension 4 via a second pair of teeth 8, 11.
  • the pairs of teeth 7, 9 and 8, 11 close different angles the longitudinal central axis of the camshaft 3.
  • the pair of teeth 7, 9 is designed as a straight toothing and the pair of teeth 8, 11 as a helical toothing.
  • the pair of teeth 7, 9 could also be designed as helical teeth and the pair of teeth 8, 11 as straight teeth.
  • axial displacement of the control element 6 causes the camshaft 3 to rotate relative to the drive wheel 5 and thus a change in the valve timing.
  • the axial displacement of the switching element 6 takes place with the aid of a servomotor 15 arranged at the other end of the camshaft 3, the actuator of which in the exemplary embodiment is a hydraulic piston 16 ', is connected to the switching element 6 by a switching rod 17 which penetrates a through hole 18 of the camshaft 3.
  • the switching element 6 is moved from one end position to the other by pressure loading one side of the actuating piston 16 and relieving the pressure on the other piston surface by means of a control slide 20 actuated, for example, by an electromagnet 19.
  • the switchover can take place as a function of operating parameters.
  • the switching rod 17 can be connected to the switching element 6 and to the actuating piston 16 such that they can move in an angular manner.
  • the servomotor 15 is connected in a rotationally fixed manner to the camshaft 3 in the exemplary embodiment.
  • an axial bearing for the camshaft which is required in a stationary servomotor for absorbing the axial actuating forces, is avoided.
  • the pressure medium supply and discharge to the right in FIG. 2 of the actuating piston 16 takes place via the camshaft bearing 2 'and a bore 21 in the camshaft 3 through the hollow shift rod 17 and the hollow screw 22, which connects the actuating piston 16 to the shift rod 17.
  • the pressure medium supply and discharge to or from the left side of the actuating piston 16 also takes place through the camshaft bearing 2 'and a second bore 23 in the camshaft and an annular space 24 between the shift rod 17 and the wall of the through bore 18.
  • a sleeve 25 is pressed into the through hole 18.
  • the switching element 6 is arranged in the tubular camshaft extension 4 and, as can be seen in particular in FIG. 3, the outer teeth 7 of the first pair of teeth and the outer teeth 8 of the second pair of teeth are alternately provided on its circumference.
  • the external toothing 7 is formed by straight toothing extending in the longitudinal direction of the camshaft 3
  • the external toothing 8 is formed by helical toothing sectors which are arranged between adjacent straight toothing sectors 7.
  • Corresponding internal helical gear segments 11 on the inner circumference of the tubular camshaft extension 4 engage with the helical gear sectors 8.
  • This camshaft extension 4 is provided between the segments 11 with openings 10, through which spokes 12 of the drive wheel 5 extend, which engage with the straight-toothed sectors 7 with their straight-toothed ends 9.
  • the spokes 12 are arranged in the openings 10 with such a large circumferential play that the desired angular adjustment of the camshaft 3 relative to the drive wheel 5 is made possible.
  • the helical toothing 7 of the switching element 6 has a larger pitch circle diameter than the straight toothing 8. This enables the helical toothing by hobbing as there is a side outlet for the milling tool.
  • Straight teeth can be made by broaching or butting.
  • the switching element can also be a sintered body in which at least the straight toothing is sintered.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)

Abstract

A drive arrangement for a camshaft (3) of an internal combustion engine has a device which rotates the camshaft (3) relative to a coaxial drive wheel (5). The device has a control element (6) which co-operates with the drive wheel through a first spur-cut pair (7, 9) and with the camshaft (3) through a second helical-cut pair (8, 11) and which can be displaced axially by a positioning motor. The teeth of the gear pairs are arranged one behind the other in the peripheral direction between the control element (6) and the drive wheel (5) on the one hand and between the control element (6) and the camshaft (3) on the other hand, i.e., a gear pair between control element (6) and drive wheel (5) follows a gear pair between control element (6) and camshaft (3) in the peripheral direction. As a result, minimal space is required for adjustement of the camshaft.

Description

Die Erfindung bezieht sich auf eine Antriebsvorrichtung für eine Nockenwelle entsprechend dem Oberbegriff des Anspruchs 1.The invention relates to a drive device for a camshaft according to the preamble of claim 1.

Eine derartige Antriebsvorrichtung ist beispielsweise in der DE-A 19 63 549 beschrieben.Such a drive device is described for example in DE-A 19 63 549.

Eine Hauptforderung bei der Konstruktion derartiger sogenannter Verstell-Nockenwellen besteht darin, daß kein oder nur wenig zusätzlicher Raum gegenüber nicht verstellbaren Nockenwellen in Längsrichtung erforderlich ist, da sonst aufgrund der äußerst beengten Platzverhältnisse im Motorraum eines Kraftfahrzeuges die Unterbringung einer Brennkraftmaschine mit Verstell-Nockenwelle(n) oftmals nicht oder nur bei kostspieliger Änderung der Karosserie möglich ist. Bei der Antriebsvorrichtung gemäß der DE-A 19 63 549 ist der Raumbedarf für die Nockenwellenverstellung in Längsrichtung der Nockenwelle gegenüber anderen bekannten Lösungen (z.B. DE-C 33 16 162) bereits erheblich reduziert. Trotzdem ergibt sich dadurch, daß das Schaltelement die Stirnfläche des Antriebsrades bzw. des mit der Nockenwelle verbundenen Fortsatzes überdeckt, eine Vergrößerung der Länge des Nockenwellenantriebes in Nockenwellenlängsrichtung um die Dicke des Schaltelements und dessen Verstellweg.A main requirement in the construction of such so-called adjustable camshafts is that little or no additional space is required in relation to non-adjustable camshafts in the longitudinal direction, since otherwise the internal combustion engine with an adjustable camshaft (n ) is often not possible or is only possible with costly changes to the body. In the drive device according to DE-A 19 63 549, the space required for adjusting the camshaft in the longitudinal direction of the camshaft is already considerably reduced compared to other known solutions (for example DE-C 33 16 162). Nevertheless, the fact that the switching element covers the end face of the drive wheel or of the extension connected to the camshaft results in an increase in the length of the camshaft drive in the longitudinal direction of the camshaft by the thickness of the switching element and its adjustment path.

Der Erfindung liegt die Aufgabe zugrunde, eine Nockenwellen-Antriebsvorrichtung der gattungsgemäßen Art zu schaffen, deren Längserstreckung nur äußerst geringfügig größer ist als die Längserstreckung einer Antriebsvorrichtung ohne Nockenwellen-Verstelleinrichtung.The invention has for its object to provide a camshaft drive device of the generic type, the longitudinal extent of which is only extremely slightly greater than the longitudinal extent of a drive device without a camshaft adjusting device.

Diese Aufgabe wird erfindungsgemäß durch die im Kennzeichen des Anspruchs 1 angegebenen Merkmale gelöst.This object is achieved by the features specified in the characterizing part of claim 1.

Durch die Anordnung der beiden Verzahnungspaare in Umfangsrichtung hintereinander und nicht, wie sonst üblich radial übereinander oder axial nebeneinander wird ein außerordentlich kleiner Bauraum für die Unterbringung der Nockenwellen-Verstelleinrichtung benötigt, so daß diese weitgehend innerhalb des Antriebsrades untergebracht werden kann. Daher läßt sich eine Brennkraftmaschine mit derartigen Verstell-Nockenwellen problemlos im Motorraum eines bestehenden Kraftfahrzeuges unterbringen, das wahlweise mit einer Brennkraftmaschine mit oder ohne Nockenwellen-Verstellung ausgestattet sein soll.The arrangement of the two pairs of teeth in the circumferential direction one behind the other and not, as is usually the case radially one above the other or axially next to one another, requires an extraordinarily small installation space for accommodating the camshaft adjusting device, so that it can be accommodated largely within the drive wheel. Therefore, an internal combustion engine with such adjusting camshafts can easily be accommodated in the engine compartment of an existing motor vehicle, which is to be optionally equipped with an internal combustion engine with or without camshaft adjustment.

Das Schaltelement kann, wie bekannt, hydraulisch durch einen Stellmotor, beispielsweise entsprechend der eingangs genannten DE-A 19 63 549, betätigt werden, bei der ein Teil des Schaltelements einen hydraulischen Kolben bildet. Vorteilhafter ist es jedoch, den Stellmotor dem vom Antriebsrad abgewandten Ende der Nockenwelle benachbart anzuordnen und das Stellglied des Stellmotors mit dem Schaltelement durch eine die Nockenwelle durchsetzende Schaltstange zu verbinden. Dadurch kommt der Stellmotor bei längs eingebauter Brennkraftmaschine an eine Stelle im Motorraum, an welcher die Motorhaube zur Windschutzscheibe hin ansteigt, so daß genügend Platz für die Unterbringung des Stellmotors vorhanden ist.As is known, the switching element can be actuated hydraulically by a servomotor, for example in accordance with DE-A 19 63 549 mentioned at the beginning, in which part of the switching element forms a hydraulic piston. However, it is more advantageous to arrange the servomotor adjacent to the end of the camshaft facing away from the drive wheel and to connect the actuator of the servomotor to the shifting element by means of a shift rod passing through the camshaft. As a result, the servomotor comes with a longitudinally installed internal combustion engine at a point in the engine compartment at which the bonnet rises towards the windshield, so that there is sufficient space for accommodating the servomotor.

Vorteilhafte Weiterbildungen der Erfindung ergeben sich aus den Unteransprüchen.Advantageous developments of the invention result from the subclaims.

Ein Ausführungsbeispiel der Erfindung wird im folgenden unter Bezugnahme auf die Zeichnungen beschrieben. Es zeigt:

Fig. 1
einen Teil-Längsschnitt eines Zylinderkopfes einer Brennkraftmaschine in einer waagrechten, durch eine Nockenwelle gelegten Ebene,
Fig. 2
einen Schnitt des Nockenwellenantriebs entlang Linie 2-2 in Fig. 1, und
Fig. 3
eine perspektivische Darstellung des Schaltelements.
An embodiment of the invention is described below with reference to the drawings. It shows:
Fig. 1
2 shows a partial longitudinal section of a cylinder head of an internal combustion engine in a horizontal plane through a camshaft,
Fig. 2
a section of the camshaft drive along line 2-2 in Fig. 1, and
Fig. 3
a perspective view of the switching element.

In Fig. 1 ist mit 1 der Zylinderkopf einer ventilgesteuerten Hubkolben-Brennkraftmaschine bezeichnet, in dem über Lager 2 eine Nockenwelle 3 gelagert ist, deren Nocken nicht gezeigte Einlaß- und/oder Auslaßventile der Brennkraftmaschine betätigen. An ihrem in Fig. 1 linken Ende ist an die Nockenwelle 3 durch Schrauben 4a ein rohrförmiger Fortsatz 4 angeschraubt, auf dem ein Antriebsrad 5 gelagert ist, das von der Kurbelwelle der Brennkraftmaschine angetrieben wird. Die Löcher 4b im Fortsatz 4, durch welche sich die Schrauben 4a erstrecken, sind als Langlöcher ausgebildet, um eine Grundeinstellung der Nockenwelle 3 relativ zum Antriebsrad 5 zu ermöglichen.In Fig. 1, 1 denotes the cylinder head of a valve-controlled reciprocating piston internal combustion engine, in which a camshaft 3 is supported via bearings 2, the cams of which actuate intake and / or exhaust valves, not shown, of the internal combustion engine. At its left end in FIG. 1, a tubular extension 4 is screwed to the camshaft 3 by screws 4a, on which a drive wheel 5 is mounted, which is driven by the crankshaft of the internal combustion engine. The holes 4b in the extension 4, through which the screws 4a extend, are designed as elongated holes in order to enable a basic setting of the camshaft 3 relative to the drive wheel 5.

Zur Übertragung des Antriebs vom Antriebsrad 5 auf die Nockenwelle 3 dient ein Schaltelement 6, das über ein erstes Verzahnungspaar 7, 9 drehfest mit dem Antriebsrad und über ein zweites Verzahnungspaar 8, 11 drehfest mit dem Nockenwellenfortsatz 4 verbunden ist. Die Verzahnungspaare 7, 9 und 8, 11 schließen unterschiedliche Winkel mit der Längsmittelachse der Nockenwelle 3 ein. Im Ausführungsbeispiel ist das Verzahnungspaar 7, 9 als Geradverzahnung und das Verzahnungspaar 8, 11 als Schrägverzahnung ausgebildet. Es könnte jedoch auch das Verzahnungspaar 7,9 als Schrägverzahnung und das Verzahnungspaar 8, 11 als Geradverzahnung ausgebildet sein. Schließlich besteht auch die Möglichkeit, beide Verzahnungspaare als Schrägverzahnung, jedoch mit entgegengesetzter oder unterschiedlicher Schrägstellung auszuführen. In jedem Falle wird durch Axialverschiebung des Stellelementes 6 eine Verdrehung der Nockenwelle 3 relativ zum Antriebsrad 5 und damit eine Veränderung der Ventilsteuerzeiten bewirkt. Die Axialverschiebung des Schaltelements 6 erfolgt mit Hilfe eines am anderen Ende der Nockenwelle 3 angeordneten Stellmotors 15, dessen Stellglied im Ausführungsbeispiel ein Hydraulikkolben 16', durch eine Schaltstange 17, welche eine Durchgangsbohrung 18 der Nockenwelle 3 durchdringt, mit dem Schaltelement 6 verbunden ist. Durch Druckbelastung einer Seite des Stellkolbens 16 und Druckentlastung der anderen Kolbenfläche mittels eines z.B. durch einen Elektromagneten 19 betätigten Steuerschiebers 20 wird das Schaltlement 6 von der einen Endstellung in die andere gebracht. Die Umschaltung kann, wie bekannt, in Abhängigkeit von Betriebsparametern erfolgen. Zur Vermeidung von Verzwängungen kann die Schaltstange 17 mit dem Schaltelement 6 und mit dem Stellkolben 16 winkelbeweglich verbunden sein.To transfer the drive from the drive wheel 5 to the camshaft 3, a switching element 6 is used, which is non-rotatably connected to the drive wheel via a first pair of teeth 7, 9 and non-rotatably connected to the camshaft extension 4 via a second pair of teeth 8, 11. The pairs of teeth 7, 9 and 8, 11 close different angles the longitudinal central axis of the camshaft 3. In the exemplary embodiment, the pair of teeth 7, 9 is designed as a straight toothing and the pair of teeth 8, 11 as a helical toothing. However, the pair of teeth 7, 9 could also be designed as helical teeth and the pair of teeth 8, 11 as straight teeth. Finally, there is also the possibility of designing both pairs of teeth as helical teeth, but with opposite or different oblique positions. In any case, axial displacement of the control element 6 causes the camshaft 3 to rotate relative to the drive wheel 5 and thus a change in the valve timing. The axial displacement of the switching element 6 takes place with the aid of a servomotor 15 arranged at the other end of the camshaft 3, the actuator of which in the exemplary embodiment is a hydraulic piston 16 ', is connected to the switching element 6 by a switching rod 17 which penetrates a through hole 18 of the camshaft 3. The switching element 6 is moved from one end position to the other by pressure loading one side of the actuating piston 16 and relieving the pressure on the other piston surface by means of a control slide 20 actuated, for example, by an electromagnet 19. As is known, the switchover can take place as a function of operating parameters. In order to avoid squeezing, the switching rod 17 can be connected to the switching element 6 and to the actuating piston 16 such that they can move in an angular manner.

Der Stellmotor 15 ist im Ausführungsbeispiel drehfest mit der Nockenwelle 3 verbunden. Dadurch wird ein Axiallager für die Nockenwelle, das bei einem stationär angeordneten Stellmotor für die Aufnahme der axialen Stellkräfte erforderlich ist, vermieden. Die Druckmittelzu- und -abführung zu der in Fig. 2 rechten Seite des Stellkolbens 16 erfolgt über das Nockenwellenlager 2' und eine Bohrung 21 in der Nockenwelle 3 durch die hohle Schaltstange 17 und die Hohlschraube 22, welche den Stellkolben 16 mit der Schaltstange 17 verbindet. Die Druckmittelzu- und -abführung zu bzw. von der linken Seite des Stellkolbens 16 erfolgt ebenfalls durch das Nockenwellenlager 2' und eine zweite Bohrung 23 in der Nockenwelle sowie einen Ringraum 24 zwischen der Schaltstange 17 und der Wand der Durchgangsbohrung 18. Zur Abdichtung der beiden Bohrungen 21 und 23 voneinander ist in die Durchgangsbohrung 18 eine Hülse 25 eingepreßt.The servomotor 15 is connected in a rotationally fixed manner to the camshaft 3 in the exemplary embodiment. As a result, an axial bearing for the camshaft, which is required in a stationary servomotor for absorbing the axial actuating forces, is avoided. The pressure medium supply and discharge to the right in FIG. 2 of the actuating piston 16 takes place via the camshaft bearing 2 'and a bore 21 in the camshaft 3 through the hollow shift rod 17 and the hollow screw 22, which connects the actuating piston 16 to the shift rod 17. The pressure medium supply and discharge to or from the left side of the actuating piston 16 also takes place through the camshaft bearing 2 'and a second bore 23 in the camshaft and an annular space 24 between the shift rod 17 and the wall of the through bore 18. For sealing the two Holes 21 and 23 from each other, a sleeve 25 is pressed into the through hole 18.

Das Schaltelement 6 ist in dem rohrförmigen Nockenwellen-Fortsatz 4 angeordnet und an seinem Umfang ist, wie insbesondere aus Fig. 3 ersichtlich, abwechselnd die Außenverzahnung 7 des ersten Verzahnungspaares und die Außenverzahnung 8 des zweiten Verzahnungspaares vorgesehen. Die Außenverzahnung 7 wird im Ausführungsbeispiel von in Längsrichtung der Nockenwelle 3 verlaufenden Geradverzahnungen gebildet, während die Außenverzahnung 8 von Schrägverzahnungs-Sektoren gebildet ist, die zwischen benachbarten Geradverzahnungs-Sektoren 7 angeordnet sind. Mit den Schrägverzahnungs-Sektoren 8 sind entsprechende Innen-Schrägverzahnungs-Segmente 11 am Innenumfang des rohrförmigen Nockenwellen-Fortsatzes 4 im Eingriff. Die Umfangswand dieses Nockenwellen-Fortsatzes 4 ist zwischen den Segmenten 11 mit Durchbrüchen 10 versehen, durch welche sich Speichen 12 des Antriebsrades 5 erstrecken, die mit ihren geradverzahnten Enden 9 in die Geradverzahnungs-Sektoren 7 eingreifen. Die Speichen 12 sind in den Durchbrüchen 10 mit einem so großen Spiel in Umfangsrichtung angeordnet, daß die gewünschte Winkelverstellung der Nockenwelle 3 relativ zum Antriebsrad 5 ermöglicht wird.The switching element 6 is arranged in the tubular camshaft extension 4 and, as can be seen in particular in FIG. 3, the outer teeth 7 of the first pair of teeth and the outer teeth 8 of the second pair of teeth are alternately provided on its circumference. In the exemplary embodiment, the external toothing 7 is formed by straight toothing extending in the longitudinal direction of the camshaft 3, while the external toothing 8 is formed by helical toothing sectors which are arranged between adjacent straight toothing sectors 7. Corresponding internal helical gear segments 11 on the inner circumference of the tubular camshaft extension 4 engage with the helical gear sectors 8. The circumferential wall of this camshaft extension 4 is provided between the segments 11 with openings 10, through which spokes 12 of the drive wheel 5 extend, which engage with the straight-toothed sectors 7 with their straight-toothed ends 9. The spokes 12 are arranged in the openings 10 with such a large circumferential play that the desired angular adjustment of the camshaft 3 relative to the drive wheel 5 is made possible.

Die Schrägverzahnung 7 des Schaltelements 6 hat einen größeren Teilkreisdurchmesser als die Geradverzahnung 8. Dadurch läßt sich die Schrägverzahnung durch Wälzfräsen herstellen, da ein seitlicher Auslauf für das Fräswerkzeug vorhanden ist. Die Geradverzahnung kann durch Räumen oder Stoßen hergestellt werden. Das Schaltelement kann jedoch auch ein Sinterkörper sein, bei dem zumindest die Geradverzahnung fertig gesintert ist.The helical toothing 7 of the switching element 6 has a larger pitch circle diameter than the straight toothing 8. This enables the helical toothing by hobbing as there is a side outlet for the milling tool. Straight teeth can be made by broaching or butting. However, the switching element can also be a sintered body in which at least the straight toothing is sintered.

Abweichend von dem dargestellten Ausführungsbeispiel könnten zwischen den Schrägverzahnungs-Sektoren 8 anstelle der Geradverzahnungs-Sektoren 7 entweder Längsnuten oder auch eine Schrägverzahnung mit einer anderen Schrägstellung vorgesehen werden. Die Enden 9 der Speichen 12 müßten dann entsprechend ausgeführt sein.In a departure from the exemplary embodiment shown, between the helical gear sectors 8, instead of the spur gear sectors 7, either longitudinal grooves or also helical teeth with a different inclined position could be provided. The ends 9 of the spokes 12 would then have to be designed accordingly.

Claims (6)

  1. A drive arrangement for a camshaft (3) mounted in the cylinder head (1) of an internal combustion engine, with a facility for rotating the camshaft relative to a coaxial drive wheel (5) which is in driving connection with the crankshaft of the engine, which facility has a switching element (6) which is coaxial to the camshaft (3) and which can shifted axially between two end positions by a servomotor and interacts through a first pair of gears (7,9) with the drive wheel (5) and through a second pair of gears (8,11) with the camshaft (3), each pair of gears comprising an external toothing (7 and 9, resp.) provided on the switching element (6) and an internal toothing (9 and 11, resp.) provided on the drive wheel (5) and the camshft (3), resp., both pair of gears enclosing different angles with the longitudinal center line of the camshaft, and the drive wheel (5) being supported on a tubular extension (4) of the camshaft (3), characterized by the following features:
    a) the switching element (6) is arranged within the camshaft extension (4) and is provided at its periphery alternately with the external toothing (7) of the first pair of gears (7, 9) and the external toothing (8) of the second pair of gears (8, 11),
    b) the peripheral wall of the tubular camshaft extension (4) is provided with openings (10) and between said openings with internal toothing segments (11) which are in engagement with the external toothings (8) of the second pair of gears on the switching element (6),
    c) the drive wheel (5) comprises spokes (12) which extend radially through the openings (10), the ends (9) of said spokes being in engagement with the external toothings (7) of the first pair of gears (7, 9) on the switching element (6), said spokes (12) being arranged within the openings (10) with a circumferential play, which corresponds to the necessary angle of rotation between the camshaft (3) and the drive wheel (5).
  2. The drive arrangement of claim 1, characterized in that the first pair of gears (7, 9) is in the shape of a splined shaft toothing, and the spokes (12) engage with their radially inner ends (9) in straight toothings (7) in the peripheral surface of the switching element (6) between adjacent external toothings (8) of the second pair of gears (8, 11).
  3. The drive arrangement of claim 1, characterized in that the servomotor (15) is arranged adjacent to that end of the camshaft (3) which is away from the drive wheel (5), and that the actuating member (16) of the servomotor (15) is connected to the switching element (6) by a control rod (17) passing through the camshaft (3).
  4. The drive arrangement of claim 3, characterized in that the control rod (17) is angularly movably connected to the switching element (6) and/or to the actuating member (16).
  5. The drive arrangement of claim 3, characterized in that the servomotor (15), the acutating member (16) and the control rod (17) are non-rotatably connected to the camshaft (3).
  6. The drive arrangement of claim 1, characterized in that the tubular extension (4) can be fixed in different angular positions of the camshaft (3).
EP91904642A 1990-03-07 1991-02-25 Drive arrangement for a camshaft Expired - Lifetime EP0518898B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4007181A DE4007181A1 (en) 1990-03-07 1990-03-07 DRIVE DEVICE FOR A CAMSHAFT
DE4007181 1990-03-07

Publications (2)

Publication Number Publication Date
EP0518898A1 EP0518898A1 (en) 1992-12-23
EP0518898B1 true EP0518898B1 (en) 1993-08-04

Family

ID=6401625

Family Applications (1)

Application Number Title Priority Date Filing Date
EP91904642A Expired - Lifetime EP0518898B1 (en) 1990-03-07 1991-02-25 Drive arrangement for a camshaft

Country Status (3)

Country Link
EP (1) EP0518898B1 (en)
DE (2) DE4007181A1 (en)
WO (1) WO1991014082A2 (en)

Families Citing this family (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH04350311A (en) * 1990-12-28 1992-12-04 Atsugi Unisia Corp Valve timing control device for internal combustion engine
JPH0547309U (en) * 1991-11-28 1993-06-22 株式会社ユニシアジェックス Valve timing control device for internal combustion engine
DE10211468A1 (en) * 2002-03-15 2003-09-25 Daimler Chrysler Ag Camshaft adjuster for internal combustion engine has control piston in separate guide casing
US6883479B2 (en) 2002-11-04 2005-04-26 Borgwarner Inc. VCT phaser having an electromagnetic lock system for shift and lock operation
US6814037B1 (en) * 2003-06-24 2004-11-09 Borgwarner Inc. Variable camshaft timing for internal combustion engine with actuator locking
DE10346446A1 (en) * 2003-10-07 2005-05-12 Daimler Chrysler Ag Camshaft adjuster for internal combustion engine with hydraulic medium guides has at least one hydraulic medium guide connected directly or via handover unit and/or channel outside camshaft to control unit of camshaft adjuster
DE102005039751A1 (en) * 2005-08-23 2007-03-01 Mahle International Gmbh camshaft
CN101737110B (en) * 2009-12-15 2011-11-16 重庆大学 Single overhead camshaft air inlet phase continuous variable mechanism of motorcycle engine
FR3060645B1 (en) * 2016-12-19 2018-11-30 Renault S.A.S. CAMSHAFT HAVING A DEPHASING SYSTEM
US11280228B2 (en) * 2020-07-07 2022-03-22 Borgwarner, Inc. Variable camshaft timing assembly

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE900505C (en) * 1943-11-06 1953-12-28 Bosch Gmbh Robert Injection start or ignition timing adjuster for internal combustion engines
IT1152959B (en) * 1982-05-17 1987-01-14 Alfa Romeo Spa DEVICE FOR AUTOMATIC VARIATION OF THE TIMING OF A CAMSHAFT
NL8301347A (en) * 1983-04-18 1984-11-16 Ernst Bernhard Leopold Laqueui Four stroke turbocharged IC engine - has inlet valve closure controlled as function of charge air pressure to optimise end compression level
DE3503740A1 (en) * 1985-02-05 1986-08-07 Miklos Dipl.-Ing. 6800 Mannheim Csongrady Device for adjusting the valve timing in internal combustion engines with valve timing gear

Also Published As

Publication number Publication date
WO1991014082A2 (en) 1991-09-19
WO1991014082A3 (en) 1991-10-31
DE4007181A1 (en) 1991-09-12
DE59100260D1 (en) 1993-09-09
EP0518898A1 (en) 1992-12-23

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