EP3347578B1 - Camshaft phaser - Google Patents

Camshaft phaser Download PDF

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Publication number
EP3347578B1
EP3347578B1 EP16770885.8A EP16770885A EP3347578B1 EP 3347578 B1 EP3347578 B1 EP 3347578B1 EP 16770885 A EP16770885 A EP 16770885A EP 3347578 B1 EP3347578 B1 EP 3347578B1
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EP
European Patent Office
Prior art keywords
actuating
housing
plain bearing
output element
shaft
Prior art date
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Active
Application number
EP16770885.8A
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German (de)
French (fr)
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EP3347578A1 (en
Inventor
Mike Kohrs
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Schaeffler Technologies AG and Co KG
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Schaeffler Technologies AG and Co KG
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Publication of EP3347578A1 publication Critical patent/EP3347578A1/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
    • F01L1/352—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 bevel or epicyclic gear
    • 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
    • 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
    • F01L2001/0476—Camshaft bearings
    • 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
    • F01L1/352—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 bevel or epicyclic gear
    • F01L2001/3522—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 bevel or epicyclic gear with electromagnetic brake

Definitions

  • the invention relates to a suitable for a camshaft adjuster an internal combustion engine actuator having a housing, an associated with this drive wheel, an adjusting, in particular three-shaft gear, such as wave gear, as well as for connection to a shaft, in particular the camshaft of the internal combustion engine, provided output member.
  • camshaft adjusters Such adjusting devices in camshaft adjusters are known, for example, from US Pat US 2007/0051332 A1 as well as from the WO 2006/018080 A1 known. In both cases, these are electrically operated camshaft adjusters.
  • camshaft adjusters For the storage of rotatable parts within camshaft adjusters or of rotatable parts, which are connected to components with camshaft adjusters, rolling bearings or sliding bearings are suitable in principle.
  • a camshaft adjuster with a plain bearing is missing US 2013 / 0081587A1 out.
  • Electrically actuated adjusting devices in internal combustion engines can be used not only with camshaft adjusters but, for example, also with devices for adjusting the valve lift and / or the compression.
  • the invention has for its object to further develop a suitable for a camshaft adjuster with respect to the cited prior art in particular with regard to robust, reliable bearings at the same time compact design.
  • suitable adjusting device comprises a composite of any number of individual parts housing, connected to the housing or formed as an integral part of the housing drive wheel, a control gear , In particular in the form of a three-shaft gear, for example, wave gear, as well as a for connection to a driven shaft, in particular camshaft, provided output member.
  • a slide bearing is provided, which, viewed in the axial direction of the driven shaft, is arranged between the actuating gear and the drive wheel. With the output element, a flange is connected to the front side, which projects beyond the output element in the radial direction.
  • the sliding bearing is adjacent to the flange, which may be part of the actuating gear;
  • the sliding bearing is arranged axially between the flange and the drive wheel.
  • the plain bearing is particularly space-saving with a small axial distance to the drive wheel housed in the housing, which means a special insensitivity to tilting due to the low effective Hebelarminn.
  • the output element is at the same time designed as a stop disc for the driven shaft, in particular camshaft.
  • the stop disc which limits an adjustment angle of the driven shaft, preferably has a cylindrical, concentric with the axis of rotation of drive wheel and driven element recess, in which one end of the driven shaft or an intermediate piece connected thereto can be placed to produce a rotationally fixed connection.
  • the housing of the adjusting device in the region of the plain bearing axial grooves and / or has at least one groove extending in the circumferential direction.
  • Such grooves favor in particular the flow of lubricant within the actuator.
  • the adjusting gear has a connected to said flange or integrally formed Abtriebshohlrad, which is mounted in the housing by means of a second sliding bearing.
  • the output ring gear can be internally toothed or firmly connected to a sleeve-shaped, internally toothed component.
  • a particularly robust construction of the adjusting device is realized by the double slide bearing.
  • the two sliding bearings may have different axial dimensions.
  • the first, axially disposed between the actuating gear and the drive bearing plain bearing has a smaller diameter and a greater axial extent than the second, the output ring gear overlapping plain bearing. The lever lengths are shortened again.
  • the advantage of the arrangement of the first sliding bearing axially between the drive wheel and the actuating gear, in particular wave gear, compared to a principle possible sliding bearing of a toothed component, in particular Abtriebshohlrads, in the housing has the particular advantage that particularly low lever length, measured in the axial direction of the camshaft adjuster , are given and thus at most to a small extent not desired, potentially increasing the friction tilting moments are generated within the camshaft adjuster.
  • the at least one sliding bearing of the adjusting device may have friction and / or wear-reducing coatings. It is also possible to incorporate lubricants in lubricating materials or to impregnate the corresponding materials with lubricants, so that particularly advantageous lubricant compounds are given by friction.
  • Fig. 5 shows a principle possible, unclaimed design of a control device 1 of a camshaft adjuster an internal combustion engine.
  • Fig. 5 shows a principle possible, unclaimed design of a control device 1 of a camshaft adjuster an internal combustion engine.
  • the same reference numerals for basically equivalent parts in connection with Fig. 5 on the one hand and in the embodiments according to the Fig. 1 to 4 used on the other hand.
  • the adjusting devices 1 shown in the various figures have in common that they have a housing 2, wherein a toothed drive wheel 3 is an integral part of the housing 2 or fixedly connected to housing components.
  • the drive wheel 3 is driven by a not shown traction means, that is, a chain or a toothed belt in a conventional manner by the crankshaft of an internal combustion engine.
  • a drive of the adjusting device 1 via gears and / or a king shaft comes into consideration.
  • a control gear 4 which is designed as a three-shaft gear, namely wave gear.
  • an actuating shaft 5 is provided, which is actuated by an electric motor, not shown, of the camshaft adjuster. As long as the shaft of the electric motor with the speed rotates the camshaft also not shown, the internal combustion engine, the phase relation between the camshaft and crankshaft of the internal combustion engine remains constant.
  • the actuating gear 4 is a high-gear transmission, wherein a speed deviation between the camshaft and the actuating shaft 5 leads to a relatively small change in the phase relation between the camshaft and crankshaft.
  • the output member 10 is designed in each of the outlined designs - both in the claimed and in the unclaimed cases - as a stop disc, which is connectable to the camshaft and limits the displacement of the camshaft.
  • the output element 10 always fulfills a dual function.
  • the sliding bearing 8 is arranged axially between the adjusting gear 4 and the drive wheel 3, which contributes significantly to the low lever arm length lk.
  • the sliding bearing 8 is between the output member 10 and a formed overall with the reference numeral 11 designated gear component, which includes the toothed drive wheel 3.
  • the front side of the output element 10 arranged flange 9 is rotatably connected both to the output ring gear 7 and the output member 10 and projects beyond the output member 10 in the radial direction, based on the common axis of rotation of the output ring gear 7, output element 10 and camshaft.
  • the output ring gear 7 in turn is connected to the circumference of the flange 9 with this, that is arranged radially outside of the flange 9.
  • FIGS. 2 and 3 show different variants of the transmission component 11, which in each camshaft adjuster 1 after Fig. 1 are usable.
  • Fig. 2 are on the inner circumference of the transmission component 11, which forms a bearing surface of the sliding bearing 8
  • axial grooves 12 can be seen.
  • Fig. 3 no axially extending grooves in the sliding bearing 8 available.
  • there is a circumferentially extending groove 13 in the region of the sliding bearing 8 on the inner circumference of the transmission component 11 is present.
  • This groove 13 does not favor as much as the axial grooves 12 in the case of Fig. 2 -
  • the distribution of lubricant but also facilitates the processing of the reduced by the circumferential groove 13 bearing surface of the sliding bearing. 8
  • Fig. 4 a further developed embodiment of an adjusting device 1 of a camshaft adjuster.
  • the slide bearing 8 which is located axially between the drive wheel 3 and the actuating gear 4, namely, wave gear
  • another sliding bearing 14 can be seen.
  • the sliding bearing 14 is the output ring gear 7 - comparable to the design Fig. 5 - Slidably mounted in the housing 2.
  • a particularly stable double slide bearing 8,14 is given.
  • the extent of the first primary slide bearing 8 in the axial direction of the actuator 1 is greater than the extension of the second, second slide bearing 14 measured in the same direction.
  • the diagram after Fig. 6 refers to a comparison between the actuator 1 after Fig. 1 and the in Fig. 5 sketched design.
  • K denotes the chain force which acts in the traction means driving the drive wheel 3, ie the chain.
  • L bearing friction in the sliding bearing 8 is designated.
  • the upper, dotted line in Fig. 6 refers to the unclaimed design Fig. 5 ; the lower dashed line on the embodiment according to Fig. 1 , Well recognizable is the reduced bearing friction of the embodiment according to Fig. 1 in all operating states.
  • the same relationship applies to a comparison between the embodiment according to Fig. 4 and the design after Fig. 5 ,

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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 für einen Nockenwellenversteller einer Brennkraftmaschine geeignete Stellvorrichtung, welche ein Gehäuse, ein mit diesem verbundenes Antriebsrad, ein Verstellgetriebe, insbesondere Dreiwellengetriebe, beispielsweise Wellgetriebe, sowie ein zur Verbindung mit einer Welle, insbesondere Nockenwelle der Brennkraftmaschine, vorgesehenes Abtriebselement aufweist.The invention relates to a suitable for a camshaft adjuster an internal combustion engine actuator having a housing, an associated with this drive wheel, an adjusting, in particular three-shaft gear, such as wave gear, as well as for connection to a shaft, in particular the camshaft of the internal combustion engine, provided output member.

Derartige Stellvorrichtungen in Nockenwellenverstellern sind beispielsweise aus der US 2007/0051332 A1 sowie aus der WO 2006/018080 A1 bekannt. In beiden Fällen handelt es sich um elektrisch betätigbare Nockenwellenversteller.Such adjusting devices in camshaft adjusters are known, for example, from US Pat US 2007/0051332 A1 as well as from the WO 2006/018080 A1 known. In both cases, these are electrically operated camshaft adjusters.

Zur Lagerung von rotierbaren Teilen innerhalb von Nockenwellenverstellern oder von rotierbaren Teilen, welche mit Komponenten mit Nockenwellenverstellern verbunden sind, sind prinzipiell Wälzlagerungen oder Gleitlagerungen geeignet. Ein Nockenwellenversteller mit einer Gleitlagerung geht aus US 2013/0081587A1 hervor.For the storage of rotatable parts within camshaft adjusters or of rotatable parts, which are connected to components with camshaft adjusters, rolling bearings or sliding bearings are suitable in principle. A camshaft adjuster with a plain bearing is missing US 2013 / 0081587A1 out.

Elektrisch betätigte Stellvorrichtungen in Brennkraftmaschinen sind nicht nur bei Nockenwellenverstellern, sondern beispielsweise auch bei Vorrichtungen zur Verstellung des Ventilhubs und/oder der Verdichtung einsetzbar.Electrically actuated adjusting devices in internal combustion engines can be used not only with camshaft adjusters but, for example, also with devices for adjusting the valve lift and / or the compression.

Der Erfindung liegt die Aufgabe zugrunde, eine für einen Nockenwellenversteller geeignete Stellvorrichtung gegenüber dem genannten Stand der Technik insbesondere hinsichtlich robuster, zuverlässiger Lagerungen bei zugleich kompaktem Aufbau weiterzuentwickeln.The invention has for its object to further develop a suitable for a camshaft adjuster with respect to the cited prior art in particular with regard to robust, reliable bearings at the same time compact design.

Diese Aufgabe wird erfindungsgemäß gelöst durch eine Stellvorrichtung mit den Merkmalen des Anspruchs 1. Vorteilhafte Ausgestaltungen sind Gegenstand der abhängigen Ansprüche.This object is achieved by an adjusting device with the features of claim 1. Advantageous embodiments are the subject of the dependent claims.

Die insbesondere für einen Nockenwellenversteller, jedoch auch für sonstige Verstellmechanismen, insbesondere zur Ventilhub- oder Verdichtungsverstellung einer Brennkraftmaschine, geeignete Stellvorrichtung weist ein aus einer beliebigen Anzahl an Einzelteilen zusammengesetztes Gehäuse, ein mit dem Gehäuse verbundenes oder als integraler Bestandteil des Gehäuses ausgebildetes Antriebsrad, ein Stellgetriebe, insbesondere in Form eines Dreiwellengetriebes, beispielsweise Wellgetriebes, sowie ein zur Verbindung mit einer anzutreibenden Welle, insbesondere Nockenwelle, vorgesehenes Abtriebselement auf. Zur Lagerung des Abtriebselements in dem Gehäuse ist eine Gleitlagerung vorgesehenen, welche, in axialer Richtung der anzutreibenden Welle betrachtet, zwischen dem Stellgetriebe und dem Antriebsrad angeordnet ist. Mit dem Abtriebselement ist stirnseitig ein Flansch verbunden, welcher das Abtriebselement in radialer Richtung überragt. Die Gleitlagerung ist dem Flansch, welcher Teil des Stellgetriebes sein kann, benachbart; insbesondere ist die Gleitlagerung axial zwischen dem Flansch und dem Antriebsrad angeordnet. Auf diese Weise ist die Gleitlagerung besonders raumsparend mit einem nur geringen axialen Abstand zum Antriebsrad im Gehäuse aufgenommen, was aufgrund der geringen effektiven Hebelarmlängen eine besondere Unempfindlichkeit bezüglich Verkippungen bedeutet.The particular for a camshaft adjuster, but also for other adjustment mechanisms, in particular for Ventilhub- or compression adjustment of an internal combustion engine, suitable adjusting device comprises a composite of any number of individual parts housing, connected to the housing or formed as an integral part of the housing drive wheel, a control gear , In particular in the form of a three-shaft gear, for example, wave gear, as well as a for connection to a driven shaft, in particular camshaft, provided output member. For the storage of the output element in the housing a slide bearing is provided, which, viewed in the axial direction of the driven shaft, is arranged between the actuating gear and the drive wheel. With the output element, a flange is connected to the front side, which projects beyond the output element in the radial direction. The sliding bearing is adjacent to the flange, which may be part of the actuating gear; In particular, the sliding bearing is arranged axially between the flange and the drive wheel. In this way, the plain bearing is particularly space-saving with a small axial distance to the drive wheel housed in the housing, which means a special insensitivity to tilting due to the low effective Hebelarmlängen.

Gemäß einer vorteilhaften Ausgestaltung ist das Abtriebselement zugleich als Anschlagscheibe für die anzutreibende Welle, insbesondere Nockenwelle, ausgebildet. Die Anschlagscheibe, welche einen Verstellwinkel der anzutreibenden Welle begrenzt, weist vorzugsweise eine zylindrische, zur Rotationsachse von Antriebsrad und Abtriebselement konzentrische Ausnehmung auf, in welcher zur Herstellung einer drehfesten Verbindung ein Ende der anzutreibenden Welle oder ein mit dieser verbundenes Zwischenstück platzierbar ist.According to an advantageous embodiment, the output element is at the same time designed as a stop disc for the driven shaft, in particular camshaft. The stop disc, which limits an adjustment angle of the driven shaft, preferably has a cylindrical, concentric with the axis of rotation of drive wheel and driven element recess, in which one end of the driven shaft or an intermediate piece connected thereto can be placed to produce a rotationally fixed connection.

Vorteilhafte Ausführungsformen sehen vor, dass das Gehäuse der Stellvorrichtung im Bereich der Gleitlagerung Axialnuten und/oder mindestens eine in Umfangsrichtung verlaufende Nut aufweist. Derartige Nuten begünstigen insbesondere den Schmiermittelfluss innerhalb der Stellvorrichtung.Advantageous embodiments provide that the housing of the adjusting device in the region of the plain bearing axial grooves and / or has at least one groove extending in the circumferential direction. Such grooves favor in particular the flow of lubricant within the actuator.

Das Stellgetriebe weist ein mit dem genannten Flansch verbundenes oder einteilig ausgebildetes Abtriebshohlrad auf, welches mittels einer zweiten Gleitlagerung im Gehäuse gelagert ist. Das Abtriebshohlrad kann innenverzahnt oder mit einem hülsenförmigen, innenverzahnten Bauteil fest verbunden sein. In jedem Fall ist durch die doppelte Gleitlagerung eine besonders robuste Konstruktion der Stellvorrichtung verwirklicht. Hierbei können die beiden Gleitlagerungen unterschiedliche axiale Ausdehnungen aufweisen. In diesem Fall weist bevorzugt das erste, axial zwischen dem Stellgetriebe und dem Antriebsrad angeordnete Gleitlager einen geringeren Durchmesser und eine größere axiale Ausdehnung als das zweite, das Abtriebshohlrad lagernde Gleitlager auf. Die auftretenden Hebellängen sind nochmals verkürzt.The adjusting gear has a connected to said flange or integrally formed Abtriebshohlrad, which is mounted in the housing by means of a second sliding bearing. The output ring gear can be internally toothed or firmly connected to a sleeve-shaped, internally toothed component. In any case, a particularly robust construction of the adjusting device is realized by the double slide bearing. Here, the two sliding bearings may have different axial dimensions. In this case, preferably, the first, axially disposed between the actuating gear and the drive bearing plain bearing has a smaller diameter and a greater axial extent than the second, the output ring gear overlapping plain bearing. The lever lengths are shortened again.

Der Vorteil der Anordnung der ersten Gleitlagerung axial zwischen dem Antriebsrad und dem Stellgetriebe, insbesondere Wellgetriebe, hat gegenüber einer prinzipiell möglichen Gleitlagerung eines eine Verzahnung aufweisenden Bauteils, insbesondere Abtriebshohlrads, im Gehäuse den besonderen Vorteil, dass besonders geringe Hebellängen, in axialer Richtung des Nockenwellenverstellers gemessen, gegeben sind und somit höchstens in geringem Maße nicht gewünschte, potentiell die Reibung erhöhende Kippmomente innerhalb des Nockenwellenverstellers erzeugt werden.The advantage of the arrangement of the first sliding bearing axially between the drive wheel and the actuating gear, in particular wave gear, compared to a principle possible sliding bearing of a toothed component, in particular Abtriebshohlrads, in the housing has the particular advantage that particularly low lever length, measured in the axial direction of the camshaft adjuster , are given and thus at most to a small extent not desired, potentially increasing the friction tilting moments are generated within the camshaft adjuster.

Die mindestens eine Gleitlagerung der Stellvorrichtung kann reibungs- und/oder verschleißmindernde Beschichtungen aufweisen. Auch ist es möglich, in Gleitmaterialien Schmierstoffe einzubauen oder die entsprechenden Materialien mit Schmierstoffen zu tränken, so dass reibungstechnisch besonders vorteilhafte Schmierstoff-Compounds gegeben sind.The at least one sliding bearing of the adjusting device may have friction and / or wear-reducing coatings. It is also possible to incorporate lubricants in lubricating materials or to impregnate the corresponding materials with lubricants, so that particularly advantageous lubricant compounds are given by friction.

Nachfolgend werden mehrere Ausführungsbeispiele der Erfindung anhand einer Zeichnung näher erläutert. Hierin zeigen:

Fig. 1
ein erstes Ausführungsbeispiel einer Stellvorrichtung für einen Nockenwellenversteller in einer Schnittdarstellung,
Fig. 2 und 3
jeweils in perspektivischer Ansicht verschiedene Varianten eines Bauteils für eine Stellvorrichtung eines Nockenwellenverstellers,
Fig. 4
in einer Darstellung analog Fig. 1 ein zweites Ausführungsbeispiel einer Stellvorrichtung eines Nockenwellenverstellers,
Fig. 5
in einer Darstellung analog Fig. 1 und Fig. 4 eine nicht beanspruchte Bauform einer Stellvorrichtung eines Nockenwellenverstellers,
Fig. 6
in einem Diagramm einen Vergleich zwischen der Stellvorrichtung nach Fig. 1 und der Vorrichtung nach Fig. 5.
Several embodiments of the invention will be explained in more detail with reference to a drawing. Herein show:
Fig. 1
A first embodiment of an adjusting device for a camshaft adjuster in a sectional view,
FIGS. 2 and 3
in each case in perspective view different variants of a component for an adjusting device of a camshaft adjuster,
Fig. 4
in a representation analog Fig. 1 A second embodiment of an adjusting device of a camshaft adjuster,
Fig. 5
in a representation analog Fig. 1 and Fig. 4 an unclaimed design of an actuator of a camshaft adjuster,
Fig. 6
in a diagram after a comparison between the actuator after Fig. 1 and the device according to Fig. 5 ,

Im Folgenden wird zunächst auf Fig. 5 eingegangen, die eine prinzipiell mögliche, nicht beanspruchte Bauform einer Stellvorrichtung 1 eines Nockenwellenverstellers einer Brennkraftmaschine zeigt. Generell werden gleiche Bezugszeichen für prinzipiell gleichwirkende Teile im Zusammenhang mit Fig. 5 einerseits sowie bei den Ausführungsbeispielen nach den Fig. 1 bis 4 andererseits verwendet.The following is first on Fig. 5 received, which shows a principle possible, unclaimed design of a control device 1 of a camshaft adjuster an internal combustion engine. In general, the same reference numerals for basically equivalent parts in connection with Fig. 5 on the one hand and in the embodiments according to the Fig. 1 to 4 used on the other hand.

Den in den verschiedenen Figuren dargestellten Stellvorrichtungen 1 ist gemeinsam, dass diese ein Gehäuse 2 aufweisen, wobei ein verzahntes Antriebsrad 3 integraler Bestandteil des Gehäuses 2 oder fest mit Gehäusebauteilen verbunden ist. Das Antriebsrad 3 wird über ein nicht dargestelltes Zugmittel, das heißt eine Kette oder einen Zahnriemen, in an sich bekannter Weise von der Kurbelwelle einer Brennkraftmaschine angetrieben. Prinzipiell kommt auch ein Antrieb der Stellvorrichtung 1 über Zahnräder und/oder eine Königswelle in Betracht.The adjusting devices 1 shown in the various figures have in common that they have a housing 2, wherein a toothed drive wheel 3 is an integral part of the housing 2 or fixedly connected to housing components. The drive wheel 3 is driven by a not shown traction means, that is, a chain or a toothed belt in a conventional manner by the crankshaft of an internal combustion engine. In principle, a drive of the adjusting device 1 via gears and / or a king shaft comes into consideration.

Innerhalb des Gehäuses 2 befindet sich ein Stellgetriebe 4, welches als Dreiwellengetriebe, nämlich Wellgetriebe, ausgeführt ist. Zusätzlich zum Antriebsrad 3 ist eine Stellwelle 5 vorgesehen, die von einem nicht dargestellten Elektromotor des Nockenwellenverstellers betätigt wird. Solange die Welle des Elektromotors mit der Drehzahl der ebenfalls nicht dargestellten Nockenwelle der Brennkraftmaschine rotiert, bleibt die Phasenrelation zwischen Nockenwelle und Kurbelwelle der Brennkraftmaschine konstant. Bei dem Stellgetriebe 4 handelt es sich um ein hoch untersetztes Getriebe, wobei eine Drehzahlabweichung zwischen der Nockenwelle und der Stellwelle 5 zu einer relativ kleinen Änderung der Phasenrelation zwischen Nockenwelle und Kurbelwelle führt.Within the housing 2 is a control gear 4, which is designed as a three-shaft gear, namely wave gear. In addition to the drive wheel 3, an actuating shaft 5 is provided, which is actuated by an electric motor, not shown, of the camshaft adjuster. As long as the shaft of the electric motor with the speed rotates the camshaft also not shown, the internal combustion engine, the phase relation between the camshaft and crankshaft of the internal combustion engine remains constant. The actuating gear 4 is a high-gear transmission, wherein a speed deviation between the camshaft and the actuating shaft 5 leads to a relatively small change in the phase relation between the camshaft and crankshaft.

Mit dem Gehäuse 2 und damit auch mit dem Antriebsrad 3 ist ein innerhalb des Gehäuses 2 liegendes Antriebshohlrad 6 fest verbunden, welches als Eingangswelle des Stellgetriebes 4 fungiert. Die Rotation des Antriebshohlrades 6 wird mittels des Stellgetriebes 4 umgesetzt in eine Rotation eines Abtriebshohlrades 7. Da das Abtriebshohlrad 7 eine von der Winkelgeschwindigkeit des Gehäuses 2 abweichende Winkelgeschwindigkeit, nämlich im Fall einer Verstellung der Nockenwelle, aufweisen kann, ist innerhalb des Gehäuses 2 eine Gleitlagerung 8 zwischen dem Abtriebshohlrad 7 und dem Gehäuse 2 vorgesehen. Das Abtriebshohlrad 7 überträgt seine Rotation über einen Flansch 9 auf ein Abtriebselement 10, wobei das Abtriebshohlrad 7 einteilig mit dem Flansch 9 ausgebildet sein kann. Das Abtriebselement 10 ist bei jeder der skizzierten Bauformen - sowohl in den beanspruchten als auch in den nicht beanspruchten Fällen - als Anschlagscheibe gestaltet, welche mit der Nockenwelle verbindbar ist und den Verstellwinkel der Nockenwelle begrenzt. Somit erfüllt das Abtriebselement 10 stets eine Doppelfunktion.With the housing 2 and thus also with the drive wheel 3, a lying within the housing 2 Antriebshohlrad 6 is firmly connected, which acts as an input shaft of the adjusting gear 4. Since the output ring gear 7 can deviate from the angular velocity of the housing 2 angular velocity, namely in the case of adjustment of the camshaft, within the housing 2 is a sliding bearing 8 is provided between the output ring gear 7 and the housing 2. The output ring gear 7 transmits its rotation via a flange 9 to an output element 10, wherein the output ring gear 7 can be integrally formed with the flange 9. The output member 10 is designed in each of the outlined designs - both in the claimed and in the unclaimed cases - as a stop disc, which is connectable to the camshaft and limits the displacement of the camshaft. Thus, the output element 10 always fulfills a dual function.

Zwischen der - in axialer Richtung betrachtet - Mitte des Antriebsrades 3 und der in derselben Richtung festgelegten Mitte der Gleitlagerung 8 ist ein axialer Abstand gegeben, wobei die entsprechende Hebelarmlänge mit lk bezeichnet ist. Ein Vergleich der Figuren 5 und 1 zeigt, dass die Hebelarmlänge lk im Fall von Fig. 5 wesentlich länger als im Fall von Fig. 1 ist, was hinsichtlich der mechanischen Beanspruchung sowie der auftretenden Reibung ungünstiger ist.Between the - viewed in the axial direction - center of the drive wheel 3 and the center fixed in the same direction of the sliding bearing 8 is given an axial distance, wherein the corresponding lever arm length is designated lk. A comparison of Figures 5 and 1 shows that the lever arm length lk in the case of Fig. 5 much longer than in the case of Fig. 1 is what is less favorable in terms of mechanical stress and the friction occurring.

Im Ausführungsbeispiel nach Fig. 1 ist die Gleitlagerung 8 axial zwischen dem Stellgetriebe 4 und dem Antriebsrad 3 angeordnet, was maßgeblich zur geringen Hebelarmlänge lk beiträgt. Die Gleitlagerung 8 ist zwischen dem Abtriebselement 10 und einem insgesamt mit dem Bezugszeichen 11 gekennzeichneten Getriebebauteil gebildet, welches das verzahnte Antriebsrad 3 umfasst. Der stirnseitig des Abtriebselements 10 angeordnete Flansch 9 ist sowohl mit dem Abtriebshohlrad 7 als auch mit dem Abtriebselement 10 drehfest verbunden und überragt das Abtriebselement 10 in radialer Richtung, bezogen auf die gemeinsame Rotationsachse von Abtriebshohlrad 7, Abtriebselement 10 und Nockenwelle. Das Abtriebshohlrad 7 wiederum ist am Umfang des Flansches 9 mit diesem verbunden, das heißt radial außerhalb des Flansches 9 angeordnet.In the embodiment according to Fig. 1 the sliding bearing 8 is arranged axially between the adjusting gear 4 and the drive wheel 3, which contributes significantly to the low lever arm length lk. The sliding bearing 8 is between the output member 10 and a formed overall with the reference numeral 11 designated gear component, which includes the toothed drive wheel 3. The front side of the output element 10 arranged flange 9 is rotatably connected both to the output ring gear 7 and the output member 10 and projects beyond the output member 10 in the radial direction, based on the common axis of rotation of the output ring gear 7, output element 10 and camshaft. The output ring gear 7 in turn is connected to the circumference of the flange 9 with this, that is arranged radially outside of the flange 9.

Die Figuren 2 und 3 zeigen verschiedene Varianten des Getriebebauteils 11, welche jeweils im Nockenwellenversteller 1 nach Fig. 1 verwendbar sind. Im Fall von Fig. 2 sind am Innenumfang des Getriebebauteils 11, welcher eine Lagerfläche der Gleitlagerung 8 bildet, Axialnuten 12 erkennbar. Dagegen sind im Fall von Fig. 3 keine in Axialrichtung verlaufenden Nuten im Bereich der Gleitlagerung 8 vorhanden. Es ist jedoch eine in Umfangsrichtung verlaufende Nut 13 im Bereich der Gleitlagerung 8 am Innenumfang des Getriebebauteils 11 vorhanden. Diese Nut 13 begünstigt nicht nurebenso wie die Axialnuten 12 im Fall von Fig. 2 - die Verteilung von Schmiermittel, sondern erleichtert auch die Bearbeitung der durch die umlaufende Nut 13 verkleinerten Lagerfläche der Gleitlagerung 8.The FIGS. 2 and 3 show different variants of the transmission component 11, which in each camshaft adjuster 1 after Fig. 1 are usable. In case of Fig. 2 are on the inner circumference of the transmission component 11, which forms a bearing surface of the sliding bearing 8, axial grooves 12 can be seen. In contrast, in the case of Fig. 3 no axially extending grooves in the sliding bearing 8 available. However, there is a circumferentially extending groove 13 in the region of the sliding bearing 8 on the inner circumference of the transmission component 11 is present. This groove 13 does not favor as much as the axial grooves 12 in the case of Fig. 2 - The distribution of lubricant, but also facilitates the processing of the reduced by the circumferential groove 13 bearing surface of the sliding bearing. 8

In Fig. 4 ist eine weiterentwickelte Ausführungsform einer Stellvorrichtung 1 eines Nockenwellenverstellers dargestellt. In diesem Fall ist zusätzlich zur Gleitlagerung 8, welche sich axial zwischen dem Antriebsrad 3 und dem Stellgetriebe 4, nämlich Wellgetriebe, befindet, eine weitere Gleitlagerung 14 erkennbar. Mit der Gleitlagerung 14 ist das Abtriebshohlrad 7 - vergleichbar mit der Bauform nach Fig. 5 - im Gehäuse 2 gleitgelagert. Somit ist eine besonders stabile zweifache Gleitlagerung 8,14 gegeben. Der Durchmesser der zweiten Gleitlagerung 14 ist größer als der Durchmesser der ersten Gleitlagerung 8. Gleichzeitig ist die Ausdehnung der ersten, primären Gleitlagerung 8 in axialer Richtung der Stellvorrichtung 1 größer als die in derselben Richtung gemessene Ausdehnung der zweiten, sekundären Gleitlagerung 14.In Fig. 4 is shown a further developed embodiment of an adjusting device 1 of a camshaft adjuster. In this case, in addition to the slide bearing 8, which is located axially between the drive wheel 3 and the actuating gear 4, namely, wave gear, another sliding bearing 14 can be seen. With the sliding bearing 14 is the output ring gear 7 - comparable to the design Fig. 5 - Slidably mounted in the housing 2. Thus, a particularly stable double slide bearing 8,14 is given. At the same time, the extent of the first primary slide bearing 8 in the axial direction of the actuator 1 is greater than the extension of the second, second slide bearing 14 measured in the same direction.

Das Diagramm nach Fig. 6 bezieht sich auf einen Vergleich zwischen der Stellvorrichtung 1 nach Fig. 1 und der in Fig. 5 skizzierten Bauform. Hierbei bezeichnet K die Kettenkraft, welche in dem das Antriebsrad 3 antreibenden Zugmittel, das heißt der Kette, wirkt. Mit L ist die Lagerreibung in der Gleitlagerung 8 bezeichnet. Die obere, strichpunktierte Linie in Fig. 6 bezieht sich auf die nicht beanspruchte Bauform nach Fig. 5; die untere, gestrichelte Linie auf das Ausführungsbeispiel nach Fig. 1. Gut erkennbar ist die verringerte Lagerreibung des Ausführungsbeispiels nach Fig. 1 in allen Betriebszuständen. Prinzipiell der gleiche Zusammenhang gilt für einen Vergleich zwischen der Ausführungsform nach Fig. 4 und der Bauform nach Fig. 5.The diagram after Fig. 6 refers to a comparison between the actuator 1 after Fig. 1 and the in Fig. 5 sketched design. Here, K denotes the chain force which acts in the traction means driving the drive wheel 3, ie the chain. With L bearing friction in the sliding bearing 8 is designated. The upper, dotted line in Fig. 6 refers to the unclaimed design Fig. 5 ; the lower dashed line on the embodiment according to Fig. 1 , Well recognizable is the reduced bearing friction of the embodiment according to Fig. 1 in all operating states. In principle, the same relationship applies to a comparison between the embodiment according to Fig. 4 and the design after Fig. 5 ,

BezugszeichenlisteLIST OF REFERENCE NUMBERS

11
Stellvorrichtunglocking device
22
Gehäusecasing
33
Antriebsraddrive wheel
44
Stellgetriebeactuating mechanism
55
Stellwelleactuating shaft
66
Antriebshohlraddrive internal gear
77
Abtriebshohlradoutput ring
88th
erste Gleitlagerungfirst plain bearing
99
Flanschflange
1010
Abtriebselementoutput element
1111
Getriebebauteiltransmission component
1212
Axialnutaxial groove
1313
umlaufende Nutcircumferential groove
1414
zweite Gleitlagerungsecond sliding bearing
lklk
Hebelarmlängelever arm
KK
Kettenkraftchain force

Claims (9)

  1. Actuating apparatus of a shaft of an internal combustion engine having
    a housing (2),
    a drive gear (3) which is connected to the latter,
    an actuating mechanism (4),
    an output element (10) which is provided for connection to a shaft to be driven, and
    a plain bearing (8) which is provided for mounting the output element (10) in the housing (2),
    the plain bearing (8) being arranged, as viewed in the axial direction of the shaft to be driven, between the actuating mechanism (4) and the drive gear (3), adjacently with respect to a flange (9) which adjoins the output element (10) on the end side, is connected fixedly to the said output element (10) so as to rotate with it, and protrudes beyond the said output element (10) in the radial direction, characterized in that the actuating mechanism (4) has a hollow output gear (7) which is connected to the flange (9) and is mounted in the housing (2) by means of a second plain bearing (14).
  2. Actuating apparatus according to Claim 1, characterized in that the two plain bearings (8, 14) have different diameters.
  3. Actuating apparatus according to Claim 1 or 2, characterized in that the two plain bearings (8, 14) have different axial extents.
  4. Actuating apparatus according to Claim 2 or 3, characterized in that the first plain bearing (8) which is arranged axially between the actuating mechanism (4) and the drive gear (3) has a smaller diameter and a greater axial extent than the second plain bearing (14).
  5. Actuating apparatus according to one of Claims 1 to 4, characterized in that the output element (10) is configured as a stop ring which limits an adjusting angle of the shaft to be driven.
  6. Actuating apparatus according to one of Claims 1 to 5, characterized in that the actuating mechanism (4) is configured as a three-shaft mechanism, in particular a harmonic drive.
  7. Actuating apparatus according to one of Claims 1 to 6, characterized in that the housing (2) has axial grooves (12) in the region of the plain bearing (8).
  8. Actuating apparatus according to one of Claims 1 to 7, characterized in that the housing (2) has at least one groove (13) which runs in the circumferential direction in the region of the plain bearing (8).
  9. Actuating apparatus according to one of the preceding claims, characterized in that the actuating apparatus is part of an electric camshaft adjuster or part of an apparatus for changing the compression ratio of the internal combustion engine.
EP16770885.8A 2015-09-10 2016-09-07 Camshaft phaser Active EP3347578B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102015217296 2015-09-10
PCT/DE2016/200420 WO2017041801A1 (en) 2015-09-10 2016-09-07 Camshaft adjuster

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EP3347578A1 EP3347578A1 (en) 2018-07-18
EP3347578B1 true EP3347578B1 (en) 2019-06-19

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EP (1) EP3347578B1 (en)
JP (1) JP6800959B2 (en)
CN (1) CN108026799B (en)
DE (1) DE102016216927A1 (en)
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Publication number Priority date Publication date Assignee Title
US10287932B2 (en) * 2016-09-19 2019-05-14 Schaeffler Technologies AG & Co. KG Camshaft phasing system including idler gear phaser for internal combustion engines
DE102017115882B4 (en) 2017-07-14 2023-11-09 Schaeffler Technologies AG & Co. KG Electric camshaft adjuster for variable adjustment of the valve timing of an internal combustion engine
DE102017128423A1 (en) 2017-11-30 2019-06-06 Schaeffler Technologies AG & Co. KG The wave gear
DE102018128930B4 (en) 2018-11-19 2023-06-29 Schaeffler Technologies AG & Co. KG Waveform gear, method for manufacturing a strainwave gear and camshaft adjuster with a strainwave gear

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US7089897B2 (en) * 2002-07-11 2006-08-15 Ina-Schaeffler Kg Electrically driven camshaft adjuster
DE102004038681B4 (en) 2004-08-10 2017-06-01 Schaeffler Technologies AG & Co. KG Electromotive camshaft adjuster
JP4390078B2 (en) 2005-09-05 2009-12-24 株式会社デンソー Valve timing adjustment device
JP4900286B2 (en) * 2008-03-04 2012-03-21 株式会社デンソー Valve timing adjustment device
JP5288311B2 (en) * 2009-04-03 2013-09-11 Ｎｔｎ株式会社 Variable valve timing device
US8555836B2 (en) * 2010-12-10 2013-10-15 Delphi Technologies, Inc. Electric drive camshaft phaser with torque rate limit at travel stops
US8516983B2 (en) 2011-09-30 2013-08-27 Delphi Technologies, Inc. Harmonic drive camshaft phaser with a harmonic drive ring to prevent ball cage deflection
JP2013167181A (en) * 2012-02-15 2013-08-29 Hitachi Automotive Systems Ltd Valve timing control apparatus for internal combustion engine
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Publication number Publication date
EP3347578A1 (en) 2018-07-18
JP2018530695A (en) 2018-10-18
WO2017041801A1 (en) 2017-03-16
CN108026799B (en) 2020-06-30
DE102016216927A1 (en) 2017-03-16
CN108026799A (en) 2018-05-11
JP6800959B2 (en) 2020-12-16

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