EP0254058B1 - Camshaft for controlling the gas inlet and exhaust valves of an internal-combustion engine - Google Patents

Camshaft for controlling the gas inlet and exhaust valves of an internal-combustion engine Download PDF

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Publication number
EP0254058B1
EP0254058B1 EP87109060A EP87109060A EP0254058B1 EP 0254058 B1 EP0254058 B1 EP 0254058B1 EP 87109060 A EP87109060 A EP 87109060A EP 87109060 A EP87109060 A EP 87109060A EP 0254058 B1 EP0254058 B1 EP 0254058B1
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EP
European Patent Office
Prior art keywords
shaft
camshaft
inner shaft
shafts
rotatable
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP87109060A
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German (de)
French (fr)
Other versions
EP0254058A3 (en
EP0254058A2 (en
Inventor
Hans-Peter Günzrodt
Gerhard Graf
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Sueddeutsche Kolbenbolzenfabrik GmbH
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Sueddeutsche Kolbenbolzenfabrik GmbH
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Publication of EP0254058A2 publication Critical patent/EP0254058A2/en
Publication of EP0254058A3 publication Critical patent/EP0254058A3/en
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Publication of EP0254058B1 publication Critical patent/EP0254058B1/en
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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
    • F01L1/34413—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 composite camshafts, e.g. with cams being able to move relative to the camshaft
    • 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

Definitions

  • the invention relates to a camshaft for controlling the gas inlet and exhaust valves of internal combustion engines according to the preamble of claim 1.
  • Such a camshaft is known from FR-A-2 426 152.
  • the mutual rotation of the cams takes place via a gear transmission in which the gears continuously rotate relative to one another during engine operation.
  • the object of the invention is to create a camshaft with an adjustment drive, in which, at times when the inner and outer shafts of the camshaft are not to be adjusted relative to one another, the gear wheels of the transmission do not rotate relative to one another but rest relative to one another .
  • the planetary gear adjustment system according to the invention differs from the camshaft with the planetary gear according to DE-A-32 04 841 by its specific structure. While the planetary gear according to that document is in operation when the camshaft is driven in that the individual wheels rotate against each other in this state, this is precisely not the case with the invention. In the invention, the planetary gear is used only to adjust the shafts against each other. On the other hand, the shafts are driven directly onto the shaft via the drive wheel when the planet gears are stationary.
  • the angular position of the control cams controlling the exhaust valves on the one hand and the intake valves on the other hand can be changed in a simple manner relative to one another.
  • the change can be achieved on the one hand by the fact that the angular position can be set to different values when the motor is at rest, or by the fact that the adjusting device is part of a control loop through which the angular position between the control cams which are movable relative to one another depends on the prevailing motor operating data certain specifiable values is regulated.
  • the camshaft consists of a hollow outer shaft 1 and a hollow inner shaft 3 mounted therein via bearings 2.
  • Control cams 5 for either the intake or exhaust valves are shrunk on the outer shaft 1.
  • the control cams 4 for the intake and exhaust valves, which are not actuated by the control cams 5, are rotatably mounted on the outer shaft 1 and are fixedly connected to the inner shaft 3 via a pin 7 projecting through a slot 6 in the outer shaft.
  • Radial bores 8 and 9 are provided in the outer shaft 1 for lubricating the bearings 2 in the annular space between the outer shaft 1 and the inner shaft 3.
  • the bores 9 each lie in areas in which the camshaft is supported by the external shaft 1 on the internal combustion engine, of which it is a component, and serve to admit lubricating oil into the annular space. Through the holes 8, which are outside the bearing areas, the lubricating oil can leave the annular space again.
  • an adjusting device 10 is provided with which the outer and inner shafts 1, 3 can be rotated relative to one another.
  • the adjustment device is constructed as follows: A flange 11 is firmly attached to the end of the outer shaft.
  • the inner shaft 3 projects beyond the end of the outer shaft and the flange 11 connected to it.
  • a disc 12 which is axially spaced from the flange 11.
  • An externally toothed gear 13 is rotatably mounted on the inner shaft between the flange 11 and the disk 12.
  • the camshaft is driven by the crankshaft by means of a toothed belt.
  • three slots 14 are provided in the same circumference on the same circumference. Through these slots 14 engage bolts 15 through which the flange 11 and the washer 12 are non-rotatably connected.
  • the gear 13 serves as a planet carrier for planet gears 16 of a planetary gear.
  • the planet gears 16, which are mounted on bearing journals 17 in the gear 13, are located axially between the gear 13 and the disk 12.
  • the planet gears 16 are driven by a sun gear 18, which is fixedly connected to the inner shaft 3.
  • Radially on the outside, the planetary gears 16 mesh in a ring gear 19 fixedly connected to the disk 12.
  • the flange 11, the gear 13 and the disk 12 can be non-positively connected to the ring 20 via a nut 20 engaging the end of the inner shaft 3. Given by the tightened nut 20 a positive connection of the aforementioned parts, the toothed belt coming from the crankshaft drives the camshaft via the toothed wheel 13, specifically the outer and inner shafts 1, 3 with a rigid connection to one another.
  • the setting device 10 is as follows to operate.
  • the sun gear 18, which is fixedly connected to the inner shaft 3 causes the planetary gears 16 to rotate, which in turn, via the ring gear 19, rotate the disk 12, which is firmly connected to the ring gear 19.
  • the flange 11 fixedly attached to the outer shaft 1 is non-rotatably connected. The outer shaft is thus rotated to the same extent as the disk 12.
  • the choice of the transmission ratio in the planetary gear can determine to what extent the outer shaft is rotated in the opposite direction when the inner shaft is rotated in one direction.
  • the gear ratio can be set so that the inner and outer shafts 3, 1 are adjusted by the same angle of rotation in opposite directions. After mutual rotation of the inner and outer shafts 3, 1, the nut 20 is tightened again when the inner shaft 3 and the locked gear 13 are locked in order to produce a non-positive connection between the parts 11, 13 and 12.
  • the inner shaft 3 is secured against sliding into the outer shaft 1 via an annular disk 22 screwed to it.
  • an electric stepper motor 23 is flanged to the disk 12.
  • the output shaft 24 of this stepper motor is rigidly connected to the inner shaft 3 of the camshaft. If the angular position between the control cams 4 and 5 should remain unchanged during motor operation, the stepper motor is controlled electrically so that it exerts alternating opposite directional control impulses on the inner shaft 3 with the result that with a sufficiently high pulse frequency practically a rigid connection between the outer and inner shaft 1, 3 is given.
  • the stepper motor 23 only has to be controlled so that the output shaft 24 is rotated.
  • the planetary gear which corresponds to that of the adjusting device according to FIGS. 1 and 2, can be used to determine the extent to which the control cams 4, 5 are rotated relative to one another by the fixed transmission ratio.
  • the gear ratio can in particular be chosen such that both types of control cams are adjusted by the same amount in opposite directions.
  • the control current for the stepper motor is fed to it via sliding contacts.
  • the stepper motor can be controlled via parameters dependent on specific motor operating states, as a result of which certain angular positions of the control cams 4, 5 can be set or regulated in relation to specific motor operating conditions.
  • a change in the angular position of the control cams 4, 5 depending on the engine operation is also possible with the adjusting devices to be described below.
  • a hydraulic motor 25 fixedly attached to the internal combustion engine is used.
  • a bolt 27 is rotatably axially fixed.
  • This bolt 27 projects axially into the inner shaft 3, the inner shaft 3 and the bolt 27 being rotatable and displaceable relative to one another.
  • the bolt 27 is at the same time mounted in a flange 28 which is fixedly connected to the disk 12, in which it is longitudinally displaceable but not rotatable.
  • the bolt 27 is secured against rotation by a tongue and groove connection 29 between the bolt 27 and the flange 28.
  • a spindle groove 30 is formed in the bolt 27, into which a ball 31 which is mounted in a fixed manner in the inner shaft 3 engages.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)

Description

Die Erfindung betrifft eine Nockenwelle zum Steuern der Gasein- und Auslaßventile von Verbrennungsmotoren nach dem Oberbegriff des Patentanspruchs 1.The invention relates to a camshaft for controlling the gas inlet and exhaust valves of internal combustion engines according to the preamble of claim 1.

Eine solche Nockenwelle ist aus FR-A-2 426 152 bekannt. Bei jener bekannten Nockenwelle erfolgt die gegenseitige Verdrehung der Nocken über ein Zahnradgetriebe, bei dem die Zahnräder während des Motorbetriebes kontinuierlich relativ zueinander drehen.Such a camshaft is known from FR-A-2 426 152. In that known camshaft the mutual rotation of the cams takes place via a gear transmission in which the gears continuously rotate relative to one another during engine operation.

Hiervon ausgehend liegt der Erfindung die Aufgabe zugrunde, eine Nockenwelle mit einem Verstellantrieb zu schaffen, bei dem in Zeiten, in denen die Innen- und Außenwelle der Nockenwelle nicht gerade gegeneinander verstellt werden sollen, die Zahnräder des Getriebes nicht gegeneinander drehen, sondern relativ zueinander ruhen.Proceeding from this, the object of the invention is to create a camshaft with an adjustment drive, in which, at times when the inner and outer shafts of the camshaft are not to be adjusted relative to one another, the gear wheels of the transmission do not rotate relative to one another but rest relative to one another .

Gelöst wird diese Aufgabe durch eine Ausführung der Nockenwelle nach den kennzeichnenden Merkmalen des Patentanspruchs 1.This object is achieved by designing the camshaft according to the characterizing features of patent claim 1.

Soweit aus dem Stand der Technik aus DE-A-32 04 841 und DE-PS-14 44 50 verstellbare Nockenwellen bekannt sind, sind diese mit dem Gegenstand der Erfindung nicht direkt vergleichbar. Von der Nockenwelle mit dem Planetengetriebe nach der DE-A-32 04 841 unterscheidet sich das erfingungsgemäße Planetengetriebe Verstellsystem durch seinen konkreten Aufbau. Während das Planetengetriebe nach jener Schrift bei angetriebener Nockenwelle dadurch in Betrieb ist, daß sich die einzelnen Räder bei diesem Zustand gegeneinander drehen, ist dies bei der Erfindung gerade nicht der Fall. Bei der Erfindung dient das Planetengetriebe allein zum Verstellen der Wellen gegeneinander. Der Antrieb der Wellen erfolgt dagegen bei ruhenden Planetenrädern über das Antriebsrad direkt auf die Welle.As far as known from the prior art from DE-A-32 04 841 and DE-PS-14 44 50 adjustable camshafts are, they are not directly comparable with the subject matter of the invention. The planetary gear adjustment system according to the invention differs from the camshaft with the planetary gear according to DE-A-32 04 841 by its specific structure. While the planetary gear according to that document is in operation when the camshaft is driven in that the individual wheels rotate against each other in this state, this is precisely not the case with the invention. In the invention, the planetary gear is used only to adjust the shafts against each other. On the other hand, the shafts are driven directly onto the shaft via the drive wheel when the planet gears are stationary.

Obwohl aus DE-PS-14 450 bereits die Verstellzahnräder nur in Relativbewegung zueinander sind, wenn eine Verdrehung der Wellen gegeneinander erfolgen soll, ist auch der dortige Verstellmechanismus nicht mit dem der Erfindung vergleichbar. Denn nach der Erfindung ist ein auf der Innen- oder Außenwelle drehbar gelagertes Antriebsrad Umlaufträger eines Planetengetriebes, wodurch eine Integration des Antriebsrades in den Verstellmechanismus zur Erzielung einer insgesamt kompakten Einheit möglich ist. Bei der Einrichtung nach DE-PS-14 44 50 muß der Antrieb dagegen über ein zusätzliches Element erfolgen.Although from DE-PS-14 450 the adjustment gears are only in relative movement to one another when the shafts are to be rotated relative to one another, the adjustment mechanism there is also not comparable to that of the invention. Because according to the invention, a drive wheel rotatably mounted on the inner or outer shaft is a planet carrier of a planetary gear, whereby an integration of the drive wheel into the adjustment mechanism is possible to achieve an overall compact unit. In the device according to DE-PS-14 44 50, however, the drive must take place via an additional element.

Zweckmäßige Ausgestaltungen der Erfindung sind Gegenstand der Unteransprüche. Nähere Einzelheiten können der nachfolgenden Beschreibung in der Zeichnung dargestellter Ausführungsbeispiele entnommen werden.Appropriate embodiments of the invention are the subject of the dependent claims. Further details can be found in the following description of exemplary embodiments shown in the drawing.

Gemeinsam ist allen Ausführungsformen, daß die Winkellage der die Auslaßventile einerseits und die Einlaßventile andererseits steuernden Steuernocken auf einfache Weise zueinander verändert werden kann. Die Veränderung kann zum einen dadurch erreicht werden, daß die Winkellage bei ruhendem Motor auf unterschiedliche Werte fest eingestellt werden kann oder auch dadurch, daß die Verstelleinrichtung Teil eines Regelkreises ist, durch den die Winkellage zwischen den gegeneinander beweglichen Steuernocken in Abhängigkeit der jeweils herrschenden Motorbetriebsdaten auf bestimmte vorgebbare Werte geregelt wird.Common to all the embodiments is that the angular position of the control cams controlling the exhaust valves on the one hand and the intake valves on the other hand can be changed in a simple manner relative to one another. The change can be achieved on the one hand by the fact that the angular position can be set to different values when the motor is at rest, or by the fact that the adjusting device is part of a control loop through which the angular position between the control cams which are movable relative to one another depends on the prevailing motor operating data certain specifiable values is regulated.

Ausführungsbeispiele sind in der Zeichnung dargestellt. Es zeigen

Fig. 1
einen Schnitt durch eine Nockenwelle mit einer Verstelleinrichtung
Fig. 2
einen Schnitt durch die Nockenwelle nach Linie II - II in Fig. 1
Fig. 3
einen Schnitt durch die Nockenwelle nach Linie III - III in Fig. 1
Fig. 4
einen Schnitt durch die Nockenwelle nach Linie IV - IV in Fig. 1
Fig. 5
einen Schnitt durch eine alternative Verstelleinrichtung
Fig. 6
einen Schnitt durch eine weitere Variante einer Verstelleinrichtung
Exemplary embodiments are shown in the drawing. Show it
Fig. 1
a section through a camshaft with an adjusting device
Fig. 2
a section through the camshaft according to line II - II in Fig. 1st
Fig. 3
a section through the camshaft along line III - III in Fig. 1st
Fig. 4
a section through the camshaft according to line IV - IV in Fig. 1st
Fig. 5
a section through an alternative adjustment
Fig. 6
a section through a further variant of an adjusting device

Die Nockenwelle besteht aus einer hohlen Außenwelle 1 und einer darin über Lager 2 gelagerten hohlen Innenwelle 3. Auf der Außenwelle 1 sind Steuernocken 5 für entweder die Ein- oder Auslaßventile fest aufgeschrumpft. Die Steuernocken 4 für die Ein- bzw. Auslaßventile, die nicht von den Steuenocken 5 betätigt werden, sind auf der Außenwelle 1 drehbar gelagert und über einen durch einen Schlitz 6 in der Außenwelle ragenden Stift 7 fest mit der Innenwelle 3 verbunden. Zur Schmierung der Lager 2 im Ringraum zwischen Außenwelle 1 und Innenwelle 3 sind in der Außenwelle 1 radiale Bohrungen 8 und 9 vorgesehen. Die Bohrungen 9 liegen jeweils in Bereichen, in denen die Nockenwelle über die Außenwelle 1 an dem Verbrennungsmotor, von dem sie jeweils ein Bestandteil ist, gelagert ist und dienen dazu, Schmieröl in den Ringraum einzulassen. Durch die Bohrungen 8, die außerhalb der Lagerbereiche liegen, kann das Schmieröl den Ringraum wieder verlassen.The camshaft consists of a hollow outer shaft 1 and a hollow inner shaft 3 mounted therein via bearings 2. Control cams 5 for either the intake or exhaust valves are shrunk on the outer shaft 1. The control cams 4 for the intake and exhaust valves, which are not actuated by the control cams 5, are rotatably mounted on the outer shaft 1 and are fixedly connected to the inner shaft 3 via a pin 7 projecting through a slot 6 in the outer shaft. Radial bores 8 and 9 are provided in the outer shaft 1 for lubricating the bearings 2 in the annular space between the outer shaft 1 and the inner shaft 3. The bores 9 each lie in areas in which the camshaft is supported by the external shaft 1 on the internal combustion engine, of which it is a component, and serve to admit lubricating oil into the annular space. Through the holes 8, which are outside the bearing areas, the lubricating oil can leave the annular space again.

An einem Ende der Nockenwelle ist eine Verstelleinrichtung 10 vorgesehen, mit der die Außen- und Innenwelle 1, 3 gegeneinander verdrehbar sind.At one end of the camshaft, an adjusting device 10 is provided with which the outer and inner shafts 1, 3 can be rotated relative to one another.

Bei der Ausführung nach den Fig. 1 und 2 ist die Verstelleinrichtung folgendermaßen aufgebaut:
Auf das Ende der Außenwelle ist ein Flansch 11 fest aufgebracht. Die Innenwelle 3 ragt über das Ende der Außenwelle und den mit ihr verbundenen Flansch 11 hinaus. Im Endbereich der Innenwelle 3 ist auf diese drehbar eine Scheibe 12 aufgebracht, die axial Abstand gegenüber dem Flansch 11 aufweist. Zwischen dem Flansch 11 und der Scheibe 12 ist auf der Innenwelle ein außen verzahntes Zahnrad 13 drehbar gelagert. Über dieses Zahnrad 13 wird die Nockenwelle mittels eines Zahnriemens von der Kurbelwelle angetrieben. In dem Zahnrad 13 sind auf einem gleichen Kreisumfang drei in Umfangsrichtung verlaufende Schlitze 14 vorgesehen. Durch diese Schlitze 14 greifen Bolzen 15, durch die der Flansch 11 und die Scheibe 12 unverdrehbar miteinander verbunden sind. Das Zahnrad 13 dient als Umlaufträger für Planetenzahnräder 16 eines Planetengetriebes. Die an Lagerzapfen 17 in dem Zahnrad 13 gelagerten Planetenräder 16 befinden sich axial zwischen dem Zahnrad 13 und der Scheibe 12. Die Planetenzahnräder 16 werden von einem Sonnenrad 18 angetrieben, das fest mit der Innenwelle 3 verbunden ist. Radial außen kämmen die Planetenzahnräder 16 in einem fest mit der Scheibe 12 verbundenen Hohlrad 19. Über eine an dem Ende der Innenwelle 3 angreifende Mutter 20 sind der Flansch 11, das Zahnrad 13 und die Scheibe 12 mit dem fest daran angebundenen Hohlrad 19 kraftschlüssig verbindbar. Bei durch die angezogene Mutter 20 gegebener kraftschlüssiger Verbindung der vorgenannten Teile treibt der von der Kurbelwelle kommende Zahnriemen die Nockenwelle über das Zahnrad 13 an und zwar die Außen- und Innenwelle 1, 3 mit starrer Verbindung zueinander.In the embodiment according to FIGS. 1 and 2, the adjustment device is constructed as follows:
A flange 11 is firmly attached to the end of the outer shaft. The inner shaft 3 projects beyond the end of the outer shaft and the flange 11 connected to it. In the end region of the inner shaft 3 is on this rotatably applied a disc 12 which is axially spaced from the flange 11. An externally toothed gear 13 is rotatably mounted on the inner shaft between the flange 11 and the disk 12. About this gear 13, the camshaft is driven by the crankshaft by means of a toothed belt. In the gear 13 three slots 14 are provided in the same circumference on the same circumference. Through these slots 14 engage bolts 15 through which the flange 11 and the washer 12 are non-rotatably connected. The gear 13 serves as a planet carrier for planet gears 16 of a planetary gear. The planet gears 16, which are mounted on bearing journals 17 in the gear 13, are located axially between the gear 13 and the disk 12. The planet gears 16 are driven by a sun gear 18, which is fixedly connected to the inner shaft 3. Radially on the outside, the planetary gears 16 mesh in a ring gear 19 fixedly connected to the disk 12. The flange 11, the gear 13 and the disk 12 can be non-positively connected to the ring 20 via a nut 20 engaging the end of the inner shaft 3. Given by the tightened nut 20 a positive connection of the aforementioned parts, the toothed belt coming from the crankshaft drives the camshaft via the toothed wheel 13, specifically the outer and inner shafts 1, 3 with a rigid connection to one another.

Um die fest mit der Außenwelle 1 verbundenen Steuernocken 5 in ihrer umfangsmäßigen Winkellage gegenüber den fest auf der Innenwelle 3 gelagerten Steuernocken 4 zu verändern, ist die Einstellvorrichtung 10 wie folgt zu betätigen.In order to change the circumferential angular position of the control cams 5 fixedly connected to the outer shaft 1 compared to the control cams 4 fixedly mounted on the inner shaft 3, the setting device 10 is as follows to operate.

Bei in seiner Umfangsstellung arretiertem Zahnrad 13 wird bei in Umfangsrichtung ebenfalls arretierter Stellung der Innenwelle 3 die Mutter 20 gelöst, so daß die kraftschlüssige Verbindung zwischen der Scheibe 12 mit dem Hohlrad 19, dem Zahnrad 13 und dem Flansch 11 aufgehoben ist. Bei weiterhin arretierter Umfangsstellung des Zahnrades 13 wird die Innenwelle 3 verdreht. Um die Innenwelle 3 in Umfangsrichtung verdrehen bzw. arretieren zu können, ist sie an ihrem Ende mit einem Greifnocken 21 zum Ansetzen eines Werkzeugschlüssels versehen.When the gear 13 is locked in its circumferential position, the nut 20 is loosened when the inner shaft 3 is also locked in the circumferential direction, so that the non-positive connection between the disk 12 with the ring gear 19, the gear 13 and the flange 11 is canceled. With the circumferential position of the gear 13 still locked, the inner shaft 3 is rotated. In order to be able to turn or lock the inner shaft 3 in the circumferential direction, it is provided at its end with a gripping cam 21 for attaching a tool key.

Durch ein Verdrehen der Innenwelle 3 bei gleichzeitig arretiertem Zahnrad 13 bewirkt das fest mit der Innenwelle 3 verbundene Sonnenrad 18 eine Drehung der Planetenzahnräder 16, die wiederum über das Hohlrad 19 die fest mit dem Hohlrad 19 verbundene Scheibe 12 verdrehen. Mit der Scheibe 12 ist jedoch wiederum der fest auf die Außenwelle 1 aufgebrachte Flansch 11 unverdrehbar verbunden. Damit wird also die Außenwelle in gleichem Maße verdreht wie die Scheibe 12.By rotating the inner shaft 3 with the gear 13 locked at the same time, the sun gear 18, which is fixedly connected to the inner shaft 3, causes the planetary gears 16 to rotate, which in turn, via the ring gear 19, rotate the disk 12, which is firmly connected to the ring gear 19. With the disk 12, however, the flange 11 fixedly attached to the outer shaft 1 is non-rotatably connected. The outer shaft is thus rotated to the same extent as the disk 12.

Durch die Wahl des Übersetzungsverhältnisses in dem Planetengetriebe läßt sich bestimmen, in welchem Maße bei einer Verdrehung der Innenwelle in eine Richtung die Außenwelle in die entgegengesetzte Richtung verdreht wird. Dabei läßt sich das Übersetzungsverhältnis so einstellen, daß Innen- und Außenwelle 3, 1 um jeweils einen gleichen Drehwinkel in entgegengesetzte Richtungen verstellt wird. Nach erfolgter gegenseitiger Verdrehung von Innen- und Außenwelle 3, 1 wird die Mutter 20 bei arretierter Innenwelle 3 und arretiertem Zahnrad 13 wieder fest zur Erzeugung einer kraftschlüssigen Verbindung zwischen den Teilen 11, 13 und 12 angezogen.The choice of the transmission ratio in the planetary gear can determine to what extent the outer shaft is rotated in the opposite direction when the inner shaft is rotated in one direction. The gear ratio can be set so that the inner and outer shafts 3, 1 are adjusted by the same angle of rotation in opposite directions. After mutual rotation of the inner and outer shafts 3, 1, the nut 20 is tightened again when the inner shaft 3 and the locked gear 13 are locked in order to produce a non-positive connection between the parts 11, 13 and 12.

An dem der Verstelleinrichtung 10 entgegengesetzten Ende ist die Innenwelle 3 über eine an ihr angeschraubte Ringscheibe 22 gegen ein Hineingleiten in die Außenwelle 1 gesichert.At the end opposite the adjusting device 10, the inner shaft 3 is secured against sliding into the outer shaft 1 via an annular disk 22 screwed to it.

Bei einer Ausführungsform der Verstelleinrichtung 10 nach Fig. 5 ist es möglich, die Winkellage der Steuernocken 4 und 5 während des Betriebs des Verbrennungsmotors zu verändern. Zu diesem Zweck ist ein elektrischer Schrittmotor 23 an der Scheibe 12 angeflanscht. Die Abtriebswelle 24 dieses Schrittmotors ist starr mit der Innenwelle 3 der Nockenwelle verbunden. Soll die Winkellage zwischen den Steuernocken 4 und 5 während des Motorbetriebes unverändert bleiben, so wird der Schrittmotor elektrisch so gesteuert, daß er abwechselnd drehrichtungsmäßig entgegengerichtete Stellimpulse auf die Innenwelle 3 ausübt mit der Folge, daß bei ausreichend hoher Impulsfrequenz praktisch eine starre Verbindung zwischen Außen- und Innenwelle 1, 3 gegeben ist. Zur Winkellageveränderung muß der Schrittmotor 23 lediglich so gesteuert werden, daß eine Verdrehung der Abtriebswelle 24 erfolgt. Durch das Planetengetriebe, das mit demjenigen der Verstelleinrichtung nach den Fig. 1 und 2 übereinstimmt, kann durch das festgelegte Übersetzungsverhältnis bestimmt werden, in welchem Maße die Steuernocken 4, 5 gegeneinander verdreht werden. Dabei kann das Übersetzungsverhältnis insbesondere derart gewählt werden, daß beide Arten von Steuernocken um das gleiche Maß in entgegengesetze Richtungen verstellt werden. Der Steuerstrom für den Schrittmotor wird diesem über Schleifkontakte zugeführt. Der Schrittmotor kann über von bestimmten Motorbetriebszuständen abhängige Kenngrößen gesteuert werden, wodurch zu bestimmten Motorbetriebsverhältnissen bestimmte Winkellagen der Steuernocken 4, 5 einstell- bzw. regelbar sind.In one embodiment of the adjusting device 10 according to FIG. 5, it is possible to change the angular position of the control cams 4 and 5 during the operation of the internal combustion engine. For this purpose, an electric stepper motor 23 is flanged to the disk 12. The output shaft 24 of this stepper motor is rigidly connected to the inner shaft 3 of the camshaft. If the angular position between the control cams 4 and 5 should remain unchanged during motor operation, the stepper motor is controlled electrically so that it exerts alternating opposite directional control impulses on the inner shaft 3 with the result that with a sufficiently high pulse frequency practically a rigid connection between the outer and inner shaft 1, 3 is given. To change the angular position, the stepper motor 23 only has to be controlled so that the output shaft 24 is rotated. The planetary gear, which corresponds to that of the adjusting device according to FIGS. 1 and 2, can be used to determine the extent to which the control cams 4, 5 are rotated relative to one another by the fixed transmission ratio. The gear ratio can in particular be chosen such that both types of control cams are adjusted by the same amount in opposite directions. The control current for the stepper motor is fed to it via sliding contacts. The stepper motor can be controlled via parameters dependent on specific motor operating states, as a result of which certain angular positions of the control cams 4, 5 can be set or regulated in relation to specific motor operating conditions.

Eine motorbetriebsabhängige Veränderung der Winkellage der Steuernocken 4, 5 ist auch mit den nachfolgend noch zu beschreibenden Verstelleinrichtungen möglich.A change in the angular position of the control cams 4, 5 depending on the engine operation is also possible with the adjusting devices to be described below.

Bei der Verstelleinrichtung nach Fig. 6 entspricht der Aufbau mit einem Planetengetriebe demjenigen der Ausführungsformen nach den Figuren 1 und 2 sowie 5. Lediglich der Verstellmotor und dessen Anlenkung an die Verstelleinrichtung unterscheidet sich gegenüber der Ausführungsform nach Fig. 5.6 corresponds to that of the embodiments according to FIGS. 1 and 2 and 5. Only the adjustment motor and its linkage to the adjustment device differ from the embodiment according to FIG. 5.

Bei der Verstelleinrichtung nach Fig. 6 wird ein ortsfest an dem Verbrennungsmotor angebrachter Hydraulikmotor 25 verwendet. In einem längs der Nockenwellenachse verschiebbaren Stempel 26 des Hydraulikmotors 25 ist ein Bolzen 27 drehbar axial fixiert. Dieser Bolzen 27 ragt axial in die Innenwelle 3 hinein, wobei die Innenwelle 3 und der Bolzen 27 relativ zueinander verdreh- und verschiebbar sind. Der Bolzen 27 ist gleichzeitig in einem fest mit der Scheibe 12 verbundenen Flansch 28 gelagert, in dem er längsverschiebbar aber nicht drehbar ist. Gegen Verdrehung ist der Bolzen 27 durch eine Nut-Feder-Verbindung 29 zwischen dem Bolzen 27 und dem Flansch 28 gesichert. In dem Bolzen 27 ist eine Spindelnut 30 eingeformt, in die eine ortsfest in der Innenwelle 3 gelagerte Kugel 31 eingreift. Zwischen dem Flansch 28 und dem Stempel 26 greift eine Druckfeder 32 an, die den Stempel 26 in Richtung von dem Flansch 28 entfernt belastet. Bei einer Längsverschiebung des Bolzens 27 wird über die in der Spindelnut 30 gleitende Kugel 31 die Innenwelle 3 verdreht. Damit läßt sich mit dem Hydraulikmotor 25 die gleiche Winkellageverstellung der Steuernocken 4, 5 während des Motorbetriebes erreichen wie mit dem Schrittmotor 23 bei der Verstelleinrichtung nach Fig. 5. Insbesondere können dem Hydraulikmotor 25 die gleichen Steuerimpulse zugeführt werden wie dem Schrittmotor.6, a hydraulic motor 25 fixedly attached to the internal combustion engine is used. In a plunger 26 of the hydraulic motor 25 which is displaceable along the camshaft axis, a bolt 27 is rotatably axially fixed. This bolt 27 projects axially into the inner shaft 3, the inner shaft 3 and the bolt 27 being rotatable and displaceable relative to one another. The bolt 27 is at the same time mounted in a flange 28 which is fixedly connected to the disk 12, in which it is longitudinally displaceable but not rotatable. The bolt 27 is secured against rotation by a tongue and groove connection 29 between the bolt 27 and the flange 28. A spindle groove 30 is formed in the bolt 27, into which a ball 31 which is mounted in a fixed manner in the inner shaft 3 engages. Between the flange 28 and the punch 26, a compression spring 32 engages, which loads the punch 26 in the direction away from the flange 28. With a longitudinal displacement of the bolt 27, the inner shaft 3 is rotated via the ball 31 sliding in the spindle groove 30. With the hydraulic motor 25, the same angular position adjustment of the control cams 4, 5 can be achieved during motor operation as with the stepper motor 23 in the adjusting device according to FIG. 5. In particular, the same control pulses can be supplied to the hydraulic motor 25 as the stepper motor.

Claims (7)

  1. A camshaft for controlling the gas inlet and exhaust valves of internal combustion engines, consisting of two shafts (1, 3) concentrically mounted to be rotatable within each other and of which one is rigidly connected to the cams (4, 5) for the inlet valves while the other is rigidly connected to the cams (5, 4) for the exhaust valves, the outer shaft (1) having radial recesses (6) by which the cams (4) associated with the inner shafts (3) can be rigidly connected therewith, and an adjusting means (10) by which the two shafts (1, 3) can be fixed in oppositely rotated positions, the cams (4) connected to the inner shaft (3) being rotatably mounted on the outer shaft (1) and in which the outer shaft is mounted to be rotatable and axially fixed in rigidly disposed bearings and has in a peripheral direction slots through which fitting pieces displaceable in a peripheral direction through a rotatable angle protrude radially, connecting the inner shaft to the control cams which are rotatably mounted on the outer shaft, the outer and inner shafts being displaceable in respect of each other through an angle of rotation corresponding to the displacement path of the fitting pieces predetermined in the peripheral direction and adapted to be locked in any position attainable in the process, characterised by the following features:
    a) a drive wheel (13) rotatably mounted on the inner or outer shaft (3, 1) as a rotatable carrier of a planetary gearing can be peripherally locked in relation to both shafts (1, 3),
    b) the planetary gears (16) mounted in the rotatable carrier are engaged on the one hand with a sun wheel (18) rigidly mounted on a first of the two shafts (1, 3) and on the other with a hollow wheel (19) which is rigidly connected to the second shaft.
  2. A camshaft according to claim 1, characterised in that the drive wheel (13) is disposed between two webs (11, 12) which can be force-lockingly applied to the drive wheel and of which one is connected rigidly to the inner and one is rigidly connected to the outer shaft (3, 1).
  3. A camshaft according to claim 2, characterised in that a flange (11) is rigidly connected to the outer shaft (1) and has bolts which pass axially with clearance and in a peripheral direction through the drive wheel (13) by which it is connected in torsion-free fashion to a disc (12) mounted on the inner shaft (3) and carrying the hollow wheel (19) of the planetary gearing and which, via a fixing means (20) engaging the inner shaft (3), can be frictionally connected to the latter.
  4. A camshaft according to claim 3, characterised in that the fixing means is a nut (20).
  5. A camshaft according to claim 3, characterised in that the fixing means is an electric stepping motor (23) by which the housing is rigidly connected to the disc (12) while the drive shaft (24) is rigidly connected to the inner shaft (3).
  6. A camshaft according to claim 3, characterised by a fixing means having the following features:
    a) a bolt (27) provided with a spindle groove (30) projects into the inner shaft (3),
    b) the bolt (27) is mounted for axial displacement but is non-rotatable in relation to the disc (12)
    c) inner shaft (3) and bolt 27) are rotatable and longitudinally displaceable in relation to each other,
    d) a ball (31) mounted in a fixed location in the inner shaft (3) engages into the spindle groove (30) on the bolt (27),
    e) the bolt (27) is axially fixed and mounted for rotation on a piston (26) displaceable longitudinally of the camshaft axis and forming part of a hydraulic motor rigidly mounted on the internal combustion engine,
    f) a thrust spring (32) operates between the piston (26) and the disc (12),
    g) the axial position of the piston (26) can be adjusted by the application of pressure by the hydraulic motor (25).
  7. A camshaft according to claim 5 or 6, characterised in that the stepping motor (23) and/or the piston (26) of the hydraulic motor (25) can be controlled as a function of engine operating data such as in particular the quantity of intake air.
EP87109060A 1986-07-23 1987-06-24 Camshaft for controlling the gas inlet and exhaust valves of an internal-combustion engine Expired - Lifetime EP0254058B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19863624827 DE3624827A1 (en) 1986-07-23 1986-07-23 ADJUSTMENT FOR A CAMSHAFT FOR CONTROLLING THE GAS INLET AND EXHAUST VALVES OF COMBUSTION ENGINES
DE3624827 1986-07-23

Publications (3)

Publication Number Publication Date
EP0254058A2 EP0254058A2 (en) 1988-01-27
EP0254058A3 EP0254058A3 (en) 1989-08-09
EP0254058B1 true EP0254058B1 (en) 1992-09-16

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EP87109060A Expired - Lifetime EP0254058B1 (en) 1986-07-23 1987-06-24 Camshaft for controlling the gas inlet and exhaust valves of an internal-combustion engine

Country Status (2)

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EP (1) EP0254058B1 (en)
DE (2) DE3624827A1 (en)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2014509711A (en) * 2011-03-30 2014-04-21 ボーグワーナー インコーポレーテッド Concentric camshaft phaser torsion drive mechanism
EP2920435B1 (en) 2012-11-13 2016-09-14 Mahle International GmbH Camshaft

Families Citing this family (47)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4993370A (en) * 1988-10-29 1991-02-19 Mazda Motor Corporation Valve driving mechanism for internal combustion engine
DE3921923A1 (en) * 1989-07-04 1991-01-17 Gkn Automotive Ag Cam shaft for IC engine
IT9020789A1 (en) * 1989-07-04 1991-01-05 Gkn Automotive Ag CAMSHAFT
DE3937628A1 (en) * 1989-11-11 1991-05-16 Audi Ag DRIVE DEVICE FOR A CAMSHAFT BEARED IN THE CYLINDER HEAD OF AN INTERNAL COMBUSTION ENGINE
DE3943426C1 (en) * 1989-12-22 1991-04-11 Gkn Automotive Ag, 5200 Siegburg, De
DE3943427C1 (en) * 1989-12-22 1991-04-04 Gkn Automotive Ag, 5200 Siegburg, De
DE4110195C2 (en) * 1991-03-28 2000-02-10 Schaeffler Waelzlager Ohg Adjustment device for a camshaft
DE4230074A1 (en) * 1992-09-09 1994-03-10 Bayerische Motoren Werke Ag Stroke-piston IC engine with two gas exchange valves per cylinder
DE4306606A1 (en) * 1993-03-03 1994-09-08 Bayerische Motoren Werke Ag Reciprocating piston internal combustion engine with a camshaft timing adjustment unit
IT1268966B1 (en) * 1994-05-12 1997-03-18 Carraro Spa SINGLE SHAFT DISTRIBUTION SYSTEM, IN PARTICULAR FOR INTERNAL COMBUSTION ENGINES.
GB2302391B (en) * 1995-06-14 1999-08-18 Nippon Denso Co Control apparatus for varying the rotational or angular phase between two rotational shafts
DE19733322A1 (en) * 1997-08-01 1999-02-04 Mwp Mahle J Wizemann Pleuco Gm Valve control of an internal combustion engine that can be switched as a drive or brake
DE69818946T2 (en) * 1997-11-21 2004-05-13 Mazda Motor Corp. Device for controlling the rotation phase
US6328006B1 (en) * 1999-03-23 2001-12-11 Tcg Unitech Aktiengesellschaft Device for adjusting the phase angle of a camshaft of an internal combustion engine
CH694812A5 (en) * 2000-08-18 2005-07-29 Karl Merz Camshaft arrangement with inner and outer camshafts, has torque coupling part connecting outer camshaft sections and extending through cams on inner camshaft
DE10054796A1 (en) * 2000-11-04 2002-06-13 Ina Schaeffler Kg Adjustment for the rotary angle of a shaft comprises swing wing adjuster, eccentric gear, connections for crank shaft and cam shaft, rotor and stator,
FR2843997B1 (en) 2002-08-29 2006-02-10 Renault Sa VARIABLE CALIBRATION AND SPREADING DISTRIBUTION SYSTEM FOR CONTROLLING THE VALVES OF AN INTERNAL COMBUSTION ENGINE
DE102004018947A1 (en) * 2004-04-20 2005-11-17 Daimlerchrysler Ag Adjusting gear for a camshaft arrangement
DE102004020124A1 (en) * 2004-04-24 2005-11-17 Aft Atlas Fahrzeugtechnik Gmbh Device for adjusting valve timing and internal combustion engine with such a device
DE102004054301A1 (en) * 2004-11-09 2006-05-11 Mahle Ventiltrieb Gmbh Camshaft for in particular motor vehicle engines
DE102005014680A1 (en) 2005-02-03 2006-08-10 Mahle International Gmbh Camshaft with mutually rotatable cam for motor vehicles in particular
DE102005004976A1 (en) * 2005-02-04 2006-08-10 Mahle International Gmbh Camshaft with mutually rotatable cam for motor vehicle engines in particular
GB2424256A (en) * 2005-03-16 2006-09-20 Mechadyne Ltd SCP assembly with spring mounted on camshaft rather than within phaser housing
GB0505497D0 (en) * 2005-03-18 2005-04-20 Mechadyne Plc Camshaft to phaser coupling
JP2007023814A (en) * 2005-07-13 2007-02-01 Toyota Motor Corp Variable valve gear for internal combustion engine
GB2431977A (en) 2005-11-02 2007-05-09 Mechadyne Plc Camshaft assembly
DE102006028611B4 (en) 2006-06-22 2014-12-31 Mahle International Gmbh Adjustable camshaft
DE202006020694U1 (en) 2006-09-07 2009-06-18 Mahle International Gmbh Adjustable camshaft
JP2011504558A (en) 2007-07-02 2011-02-10 ボーグワーナー・インコーポレーテッド Concentric cam with check valve in spool for phaser
DE102007042053A1 (en) * 2007-09-05 2009-03-12 Mahle International Gmbh piston engine
DE102008033230B4 (en) 2008-01-04 2010-05-27 Hydraulik-Ring Gmbh Double camshaft adjuster in layer construction
US7841311B2 (en) 2008-01-04 2010-11-30 Hilite International Inc. Variable valve timing device
DE102008023098A1 (en) 2008-05-09 2009-12-17 Hydraulik-Ring Gmbh Valve operating mechanism for internal combustion engine, has camshaft and swiveling camshaft for changing relative position of camshaft adjuster to shaft
CN102144079B (en) 2008-09-19 2014-03-05 博格华纳公司 Phaser built into camshaft or concentric camshafts
DE102008043671A1 (en) * 2008-11-12 2010-05-20 Zf Friedrichshafen Ag Adjustment system for camshafts of an internal combustion engine
US8113163B2 (en) 2009-03-09 2012-02-14 GM Global Technology Operations LLC Concentric camshaft and method of assembly
DE102009034990A1 (en) * 2009-07-28 2011-02-03 Daimler Ag Valve drive device
DE102010033296A1 (en) 2010-08-04 2012-02-09 Hydraulik-Ring Gmbh Camshaft adjuster, especially with camshaft
DE102011001301B4 (en) 2011-03-16 2017-09-21 Hilite Germany Gmbh Schwenkmotorversteller
DE102011120815A1 (en) 2011-12-10 2013-06-13 Volkswagen Aktiengesellschaft Adjustable camshaft drive
DE102013216567A1 (en) * 2013-08-21 2015-02-26 Mahle International Gmbh alignment
DE102013113255A1 (en) * 2013-11-29 2015-06-03 Thyssenkrupp Presta Teccenter Ag Adjustable camshaft
DE102014112464A1 (en) 2014-08-29 2016-03-03 Thyssenkrupp Presta Teccenter Ag Adjustment unit for a camshaft of an internal combustion engine
DE102015224015A1 (en) * 2015-12-02 2017-06-08 Mahle International Gmbh Adjustable camshaft
DE102016217860A1 (en) 2016-09-19 2018-03-22 Robert Bosch Gmbh Adjustment device of a camshaft with failure protection
DE102017207905A1 (en) 2017-05-10 2018-11-15 Robert Bosch Gmbh Camshaft phaser and camshaft and internal combustion engine comprising such a camshaft phaser
FR3109797B1 (en) * 2020-04-29 2023-07-28 Renault Camshaft with internal bearings.

Family Cites Families (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE144450C (en) *
DE446744C (en) * 1927-07-11 Siemens Schuckertwerke G M B H Device for the mechanical transmission of a movement from a relatively stationary to a relatively moving body
DE254135C (en) * 1910-11-01 1912-11-23 Ruthardt & Co SPRINGLESS REGULATORY CLUTCH FOR ONE DRIVEN AND ONE CONACHIAL DRIVEN SHAFT
GB191500889A (en) * 1914-01-26 1915-12-30 Ferruccio Valobra Differential Gear Control for Distributing Mechanisms in Reciprocating Engines.
GB154543A (en) * 1919-11-26 1921-12-29 Louis Damblanc Improvements in and relating to transmission of movement
US1527456A (en) * 1924-02-29 1925-02-24 Woydt Edward Valve-operating means
FR593322A (en) * 1925-01-06 1925-08-20 Differential device, allowing the adjustment, advance or retardation, of the admission, ignition and exhaust in internal combustion engines
US1957181A (en) * 1932-02-27 1934-05-01 Edward W Mitchel Automatic valve timing device
US3416502A (en) * 1965-04-22 1968-12-17 Weiss Joseph Internal combustion engines
US3516394A (en) * 1968-07-16 1970-06-23 Roy G Nichols Device for simultaneously advancing intake cam lobes and retarding exhaust cam lobes of an internal combustion engine while the engine is running
DE2822147C3 (en) * 1978-05-20 1982-02-11 Volkswagenwerk Ag, 3180 Wolfsburg Camshaft arrangement, in particular for an internal combustion engine
DE3029858A1 (en) * 1979-08-08 1981-02-19 Denzel Kraftfahrzeug Wolfgang Adjustable timing chain of IC engine - has stepless adjustment using friction drive between chain wheel and camshaft
DE3204841A1 (en) * 1982-02-11 1983-08-18 Volkswagenwerk Ag, 3180 Wolfsburg Reciprocating-piston internal combustion engine with a device for adjusting the angle of the camshafts relative to one another
JPS58162708A (en) * 1982-03-24 1983-09-27 Toyota Motor Corp Valve timing control device for internal-combustion engine
DE3247916A1 (en) * 1982-12-24 1984-06-28 Robert Bosch Gmbh, 7000 Stuttgart DEVICE FOR CONTROLLING THE VALVES OF AN INTERNAL COMBUSTION ENGINE OVER A CAMSHAFT
JPS60119309A (en) * 1983-11-30 1985-06-26 Suzuki Motor Co Ltd Valve timing angle leading device of 4-cycle engine
DE3415861A1 (en) * 1984-04-28 1985-10-31 Pierburg Gmbh & Co Kg, 4040 Neuss DEVICE FOR CONTROLLING A COUPLING DEVICE

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2014509711A (en) * 2011-03-30 2014-04-21 ボーグワーナー インコーポレーテッド Concentric camshaft phaser torsion drive mechanism
EP2920435B1 (en) 2012-11-13 2016-09-14 Mahle International GmbH Camshaft

Also Published As

Publication number Publication date
DE3624827A1 (en) 1988-02-04
DE3781736D1 (en) 1992-10-22
EP0254058A3 (en) 1989-08-09
EP0254058A2 (en) 1988-01-27

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