EP1860286B1 - Camshaft - Google Patents

Camshaft Download PDF

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Publication number
EP1860286B1
EP1860286B1 EP07106778A EP07106778A EP1860286B1 EP 1860286 B1 EP1860286 B1 EP 1860286B1 EP 07106778 A EP07106778 A EP 07106778A EP 07106778 A EP07106778 A EP 07106778A EP 1860286 B1 EP1860286 B1 EP 1860286B1
Authority
EP
European Patent Office
Prior art keywords
hydraulic
camshaft
inner shaft
specified
valves
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 - Fee Related
Application number
EP07106778A
Other languages
German (de)
French (fr)
Other versions
EP1860286A2 (en
EP1860286A3 (en
Inventor
Falk Schneider
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Mahle International GmbH
Original Assignee
Mahle International GmbH
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Filing date
Publication date
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Publication of EP1860286A2 publication Critical patent/EP1860286A2/en
Publication of EP1860286A3 publication Critical patent/EP1860286A3/en
Application granted granted Critical
Publication of EP1860286B1 publication Critical patent/EP1860286B1/en
Expired - Fee Related legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • F01L1/02—Valve drive
    • F01L1/04—Valve drive by means of cams, camshafts, cam discs, eccentrics or the like
    • F01L1/047—Camshafts
    • 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
    • F01L1/34—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
    • F01L1/34—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
    • F01L1/3442—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 hydraulic chambers with variable volume to transmit the rotating force
    • 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
    • F01L1/053—Camshafts overhead type
    • F01L2001/0537—Double overhead camshafts [DOHC]
    • 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
    • F01L1/3442—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 hydraulic chambers with variable volume to transmit the rotating force
    • F01L2001/34423—Details relating to the hydraulic feeding circuit
    • F01L2001/34426—Oil control valves
    • 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
    • F01L1/3442—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 hydraulic chambers with variable volume to transmit the rotating force
    • F01L2001/34423—Details relating to the hydraulic feeding circuit
    • F01L2001/34426—Oil control valves
    • F01L2001/34433—Location oil control valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L2001/34486—Location and number of the means for changing the angular relationship
    • F01L2001/34493—Dual independent phasing system [DIPS]
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L2001/34486—Location and number of the means for changing the angular relationship
    • F01L2001/34496—Two phasers on different camshafts

Definitions

  • the invention relates to a camshaft of in particular motor vehicle engines with a coaxially arranged in an outer shaft inner shaft which is rotatably supported against the outer shaft.
  • camshaft adjusters To reduce fuel consumption and pollutant emissions as well as to increase the power and the torque of many Otto engines are usually equipped with camshaft adjusters.
  • camshaft adjusters also known as phase adjusters, change the phasing of the camshaft relative to the crankshaft.
  • a camshaft adjuster for an internal combustion engine with an inserted into a camshaft control valve having a guided in a guide sleeve hydraulic control piston.
  • the actuating unit has an inner body fixedly connected to the camshaft and an outer body rotatably mounted to the camshaft, via which a drive connection extends from a crankshaft to the camshaft, and wherein the control valve is acted upon by an electromagnetic device and supplied with hydraulic medium via the camshaft.
  • an oil guide module is inserted, which serves at least for guiding the hydraulic medium between an interior of the camshaft and the control valve.
  • the disclosed camshaft is designed as a one-piece camshaft.
  • From the DE 44 15 524 A1 is a hydraulic actuator for changing and readjusting the valve timing of a crankshaft driven camshaft of an internal combustion engine known.
  • the rotational position of the camshaft is adjustable by a limited angle of rotation, wherein in a chamber seated wings are subjected to pressure medium.
  • the invention is concerned with the problem of arranging a camshaft adjuster for a camshaft with an inner and an outer shaft minimizing possible space.
  • the invention is based on the general idea, at least part of the phase adjustment, in particular their switchable Arranging hydraulic valves substantially within an inner shaft of the existing of an inner and outer shaft camshaft.
  • the inner shaft is coaxially mounted in the outer shaft and rotatable relative thereto, wherein in addition to each other rotatable first and second cams are provided, of which the first cam fixed to the inner shaft and the second cam are fixedly connected to the outer shaft.
  • the camshaft according to the invention above-mentioned phase adjuster namely a first and a second phaser, wherein the first phaser a phase angle of the inner shaft and the second phaser a phase angle of the Outer shaft respectively relative to the drive, such as a crankshaft, adjusted.
  • the arrangement of belonging to the respective phase adjuster switchable hydraulic valve within the inner shaft allows a particularly space-saving and space-optimizing design. Of particular importance or advantage here is that the time required to control the hydraulic valves oil supply is also located within the inner shaft.
  • an oil supply which is already present for a bearing lubrication of the camshaft, so that no further hydraulic lines must be provided in the cylinder head.
  • the camshaft according to the invention can also be installed on conventional cylinder heads.
  • an actuating device for actuating or controlling the two hydraulic valves which has a first and a second electromagnet, of which the first solenoid, the first hydraulic valve and the second solenoid actuates the second hydraulic valve.
  • the electromagnets, which are part of the actuating device, are preferably arranged stationary in or on the cylinder head and fixed in contrast to the rotating hydraulic valves. Electromagnets can be produced inexpensively today in almost any embodiment and also work extremely precise, whereby a reliable, accurate and at the same time inexpensive control of the hydraulic valves can be created.
  • the second electromagnet has a plunger for actuating the second hydraulic valve, which runs centrally through the first hydraulic valve.
  • This plunger which is arranged essentially coaxially with respect to the first hydraulic valve, makes it possible to control both hydraulic valves from a common side, whereby the tandem arrangement of the two hydraulic valves within the inner shaft becomes possible.
  • the axial channel within the first hydraulic valve required for penetration of the stoichel can thereby be provided without problems, since this area of the first hydraulic valve is not required for actuating the phasers in any way.
  • the existing in the warehouse anyway hydraulic channel serves to a bearing lubrication and can be used in addition to the supply of the two hydraulic valves. Since the hydraulic channel for lubricating the camshaft bearing is present in many conventional engines anyway, the camshaft according to the invention can be easily installed in conventional engines. At the same time, one channel allows a reduction of hydraulic lines to be arranged, whereby the complexity of the components, in particular the inner shaft and the bearing can be significantly reduced.
  • Fig. 1 has a camshaft 1, in particular a camshaft 1 of a motor vehicle engine, a coaxially arranged in an outer shaft 2 inner shaft 3, which is rotatably mounted against the outer shaft 2.
  • the camshaft 1 is mounted via a camshaft-side bearing element 4, which in turn is mounted on a bearing element 5 on the cylinder head side.
  • dash-dotted line 6 symbolizes a dividing line between a region A and a region B, wherein the region A has rotating components, while the region B has fixed components.
  • camshaft 1 is designed as a so-called adjustable camshaft and therefore has mutually rotatable first and second cam, of which the first cam fixed to the inner shaft 3 and the second cam are fixedly connected to the outer shaft 2.
  • the first and second cams are in the Fig. 1 to 3 not drawn.
  • a first phase adjuster 7 and a second phase adjuster 8 are arranged thereon, wherein the first phase adjuster 7 has a phase position of the inner shaft 3 and thus the first cam relative to a drive, for example a crankshaft, not shown , Adjusted, while the second phase adjuster 8 adjusts a phase angle of the outer shaft 2 and thus the second cam relative to the crankshaft.
  • the phase adjuster 7 and 8 thus change the phase position of the camshaft 1 and the inner shaft 3 and the outer shaft 2 relative to the crankshaft and thereby allow a reduction in fuel consumption or pollutant emission and an increase in power and torque.
  • first phase adjuster 7 and the second phaser 8 each have a switchable hydraulic valve 9 and 10 (in FIG Fig. 1 drawn throughout), both of which are arranged inside the inner shaft 3. This allows a space-saving and thus space-minimizing arrangement of the phase adjusters 7, 8 associated hydraulic valves 9, 10 and one at the same time wear-resistant accommodation thereof within the inner shaft. 3
  • the two hydraulic valves 9, 10 in the axial direction of the shafts 2 and 3 adjacent to each other within the inner shaft 3 are arranged.
  • This so-called tandem arrangement requires for the control of the two hydraulic valves 9 and 10, that for controlling in particular the second hydraulic valve 10, the first hydraulic valve 9 by a control, in particular a plunger 11 ', is penetrated.
  • an actuating device 12 is provided which has a first electromagnet 13 and a second electromagnet 14, of which the first electromagnet 13, the first hydraulic valve 9 and the second electromagnet 14 corresponding to the second hydraulic valve 10 is actuated.
  • both the first electromagnet 13 and the second electromagnet 14 in the region B that is arranged in a stationary area.
  • the actuating device 12 is arranged as a whole stationary on a cylinder head, not shown, while the hydraulic valves 9 and 10 are rotatably connected to the inner shaft 3.
  • the annular channel 16 thereby enables the camshaft 1 to rotate without any interruption of a hydraulic line 15 common to the oil supply.
  • the hydraulic channel 17 in the cylinder head side bearing element 5 simultaneously represents an oil supply for lubricating an annular gap between the two bearing elements 4 and 5 and is already present in conventional engines.
  • only one hydraulic line for supplying the two hydraulic valves 9 and 10 is required, whereby the complexity of the components, in particular of the bearing element 4 and the cylinder head side bearing element 5 can be significantly reduced.
  • the common hydraulic line 15 divides within the inner shaft 3 before reaching the two hydraulic valves 9 and 10 in a first hydraulic line 15 ', which supplies the first hydraulic valve 9 and in a second hydraulic line 15 ", which supplies the second hydraulic valve 10.
  • the two hydraulic valves 9 and 10 are formed as spring-loaded slide valves which are biased by the electromagnets 13 and 14 via respective plunger 11, 11 'in each case against a spring 18, 18', the other end at a respective stop 19th , 19 'on the inner shaft 3 is supported.
  • the first hydraulic valve 9 is in accordance with the FIGS. 2 and 3 from the required to actuate the second hydraulic valve 10 ram 11 'penetrated centrally.
  • Fig. 2 promotes a pump 20 continuously hydraulic fluid from a reservoir 21 through the corresponding lines 15 'and 15 "to the first hydraulic valve 9 and the second hydraulic valve 10.
  • the first hydraulic valve 9 is set so that both the first phase adjuster 7 leading channels 23, 23' by means of corresponding projections 22, 22 'on the slide 24 of the first hydraulic valve 9.
  • a vane-type phase adjuster 25 remains in a central position
  • the same position also has the second hydraulic valve 9, so that the second phase adjuster 8 also remains in a central position ,
  • Fig. 3 is caused by the actuator 12 and the first magnet 13 and the second magnet 14, an adjustment of the slider 24 of the first hydraulic valve 9 and an adjustment of the slider 24 'of the second hydraulic valve 10.
  • the second electromagnet 14 moves according to the Fig. 3 the plunger 11 to the right and thereby displaces the slider 24 'also to the right against the force exerted by the spring 18' spring force.
  • the slide 24 of the first hydraulic valve 9 is shifted to the left, whereby the channel 23, which leads to the first phaser 7, is opened.
  • This causes a rotational movement of the vane against the Clockwise and thus an adjustment of the inner shaft 3 and the associated first cam.

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

Description

Die Erfindung betrifft eine Nockenwelle von insbesondere Kraftfahrzeugmotoren mit einer koaxial in einer Außenwelle angeordneten Innenwelle, die verdrehbar gegen die Außenwelle gelagert ist.The invention relates to a camshaft of in particular motor vehicle engines with a coaxially arranged in an outer shaft inner shaft which is rotatably supported against the outer shaft.

Zur Senkung des Kraftstoffverbrauchs und der Schadstoffemissionen sowie zur Erhöhung der Leistung und des Drehmomentes sind heutzutage viele Otto-Motoren in der Regel mit Nockenwellenverstellern ausgestattet. Diese Nockenwellenversteller, kurz auch Phasenversteller genannt, ändern die Phasenlage der Nockenwelle relativ zur Kurbelwelle.To reduce fuel consumption and pollutant emissions as well as to increase the power and the torque of many Otto engines are usually equipped with camshaft adjusters. These camshaft adjusters, also known as phase adjusters, change the phasing of the camshaft relative to the crankshaft.

Aus der DE 103 46 448 A1 ist ein Nockenwellenversteller für eine Brennkraftmaschine bekannt, mit einem in eine Nockenwelle eingefügten Steuerventil, das einen in einer Führungshülse geführten hydraulischen Steuerkolben aufweist. Mit diesem ist eine Stelleinheit zur Winkelverstellung der Nockenwelle steuerbar. Die Stelleinheit weist einen mit der Nockenwelle fest verbundenen Innenkörper und einen zur Nockenwelle drehbar gelagerten Außenkörper auf, über den eine Antriebsverbindung von einer Kurbelwelle zur Nockenwelle verläuft, und wobei das Steuerventil von einer elektromagnetischen Einrichtung beaufschlagt und über die Nockenwelle mit Hydraulikmedium versorgt wird. In die Nockenwelle ist dabei zusätzlich ein Ölführungsmodul eingefügt, welches zumindest zur Führung des Hydraulikmediums zwischen einem Inneren der Nockenwelle und dem Steuerventil dient. Die offenbarte Nockenwelle ist dabei als einteilige Nockenwelle ausgeführt.From the DE 103 46 448 A1 is known a camshaft adjuster for an internal combustion engine, with an inserted into a camshaft control valve having a guided in a guide sleeve hydraulic control piston. With this an adjusting unit for angular adjustment of the camshaft is controllable. The actuating unit has an inner body fixedly connected to the camshaft and an outer body rotatably mounted to the camshaft, via which a drive connection extends from a crankshaft to the camshaft, and wherein the control valve is acted upon by an electromagnetic device and supplied with hydraulic medium via the camshaft. In the camshaft is In addition, an oil guide module is inserted, which serves at least for guiding the hydraulic medium between an interior of the camshaft and the control valve. The disclosed camshaft is designed as a one-piece camshaft.

Aus der DE 44 15 524 A1 ist eine hydraulische Betätigungseinrichtung zur Änderung und Nachsteuerung der Ventilsteuerzeiten einer von einer Kurbelwelle angetriebenen Nockenwelle einer Brennkraftmaschine bekannt. Die Drehlage der Nockenwelle ist um einen begrenzten Drehwinkel einstellbar, wobei in einer Kammer sitzende Flügel mit Druckmittel beaufschlagt werden.From the DE 44 15 524 A1 is a hydraulic actuator for changing and readjusting the valve timing of a crankshaft driven camshaft of an internal combustion engine known. The rotational position of the camshaft is adjustable by a limited angle of rotation, wherein in a chamber seated wings are subjected to pressure medium.

Aus der GB 2369 175 A1 ist ein phasenverstellbarer Mechanismus zur Stellung eines Antriebes von einer Brennkraftmaschine auf zwei Nockensätze bekannt.From the GB 2369 175 A1 is a phase-adjustable mechanism for providing a drive from an internal combustion engine to two cam sets known.

Aus der DE 10 2004 035 035 A1 und der DE 103 30 449 B3 sind weitere Nockenwellenversteller für Brennkraftmaschinen bekannt.From the DE 10 2004 035 035 A1 and the DE 103 30 449 B3 are more known camshaft adjuster for internal combustion engines.

Die Erfindung beschäftigt sich mit dem Problem, einen Nockenwellenversteller für eine Nockenwelle mit einer Innen- und einer Außenwelle möglichst bauraumminimierend anzuordnen.The invention is concerned with the problem of arranging a camshaft adjuster for a camshaft with an inner and an outer shaft minimizing possible space.

Dieses Problem wird erfindungsgemäß durch den Gegenstand des unabhängigen Anspruchs 1 gelöst. Vorteilhafte Ausführungsformen sind Gegenstand der abhängigen Ansprüche.This problem is solved according to the invention by the subject matter of independent claim 1. Advantageous embodiments are the subject of the dependent claims.

Die Erfindung beruht auf dem allgemeinen Gedanken, zumindest einen Teil der Phasenverstellung, insbesondere deren schaltbare Hydraulikventile im wesentlichen innerhalb einer Innenwelle der aus einer Innen- und Außenwelle bestehenden Nockenwelle anzuordnen. Die Innenwelle ist dabei koaxial in der Außenwelle und verdrehbar gegenüber dieser gelagert, wobei darüber hinaus gegeneinander verdrehbare erste und zweite Nocken vorgesehen sind, von denen die ersten Nocken fest mit der Innenwelle und die zweiten Nocken fest mit der Außenwelle verbunden sind. Zum Verstellen der Innenwelle beziehungsweise der damit verbundene ersten Nocken und der Außenwelle beziehungsweise den damit verbundenen zweiten Nocken weist die erfindungsgemäße Nockenwelle obengenannte Phasenversteller, nämlich einen ersten und einen zweiten Phasenversteller auf, wobei der erste Phasenversteller eine Phasenlage der Innenwelle und der zweite Phasenversteller eine Phasenlage der Außenwelle jeweils relativ zum Antrieb, beispielsweise einer Kurbelwelle, verstellt. Die Anordnung eines zum jeweiligen Phasenversteller gehörenden schaltbaren Hydraulikventils innerhalb der Innenwelle ermöglicht eine besonders platzsparende und bauraumoptimierende Bauweise. Von besonderer Bedeutung beziehungsweise Vorteil ist hierbei dass die zur Steuerung der Hydraulikventile erforderliche Ölzuführung ebenfalls innerhalb der Innenwelle angeordnet ist. Dabei wird vorzugsweise eine Ölzufuhr, welche für eine Lagerschmierung der Nockenwelle ohnehin vorhanden ist genutzt, so dass im Zylinderkopf keine weiteren Hydraulikleitungen vorgesehen werden müssen. Demzufolge kann die erfindungsgemäße Nockenwelle auch an herkömmlichen Zylinderköpfen verbaut werden.The invention is based on the general idea, at least part of the phase adjustment, in particular their switchable Arranging hydraulic valves substantially within an inner shaft of the existing of an inner and outer shaft camshaft. The inner shaft is coaxially mounted in the outer shaft and rotatable relative thereto, wherein in addition to each other rotatable first and second cams are provided, of which the first cam fixed to the inner shaft and the second cam are fixedly connected to the outer shaft. To adjust the inner shaft or the associated first cam and the outer shaft or the associated second cam, the camshaft according to the invention above-mentioned phase adjuster, namely a first and a second phaser, wherein the first phaser a phase angle of the inner shaft and the second phaser a phase angle of the Outer shaft respectively relative to the drive, such as a crankshaft, adjusted. The arrangement of belonging to the respective phase adjuster switchable hydraulic valve within the inner shaft allows a particularly space-saving and space-optimizing design. Of particular importance or advantage here is that the time required to control the hydraulic valves oil supply is also located within the inner shaft. In this case, preferably, an oil supply, which is already present for a bearing lubrication of the camshaft, so that no further hydraulic lines must be provided in the cylinder head. As a result, the camshaft according to the invention can also be installed on conventional cylinder heads.

Bei einer vorteilhaften Ausführungsform der erfindungsgemäßen Lösung ist eine Betätigungseinrichtung zur Betätigung beziehungsweise Steuerung der beiden Hydraulikventile vorgesehen, die einen ersten und einen zweiten Elektromagneten aufweist, wovon der erste Elektromagnet das erste Hydraulikventil und der zweite Elektromagnet das zweite Hydraulikventil betätigt. Die Elektromagneten, welche Teil der Betätigungseinrichtung sind, sind dabei vorzugsweise ortsfest im oder am Zylinderkopf angeordnet und im Gegensatz zu den rotierenden Hydraulikventilen feststehend. Elektromagnete lassen sich heutzutage in nahezu beliebiger Ausführungsform kostengünstig herstellen und arbeiten darüber hinaus überaus präzise, wodurch eine zuverlässige, exakte und gleichzeitig kostengünstige Steuerung der Hydraulikventile geschaffen werden kann.In an advantageous embodiment of the inventive solution, an actuating device for actuating or controlling the two hydraulic valves is provided which has a first and a second electromagnet, of which the first solenoid, the first hydraulic valve and the second solenoid actuates the second hydraulic valve. The electromagnets, which are part of the actuating device, are preferably arranged stationary in or on the cylinder head and fixed in contrast to the rotating hydraulic valves. Electromagnets can be produced inexpensively today in almost any embodiment and also work extremely precise, whereby a reliable, accurate and at the same time inexpensive control of the hydraulic valves can be created.

Bei einer weiteren vorteilhaften Ausführungsform der erfindungsgemäßen Lösung weist der zweite Elektromagnet einen Stößel zur Betätigung des zweiten Hydraulikventils auf, der zentral durch das erste Hydraulikventil hindurch verläuft. Dieser im wesentliche koaxial zum ersten Hydraulikventil angeordnete Stößel ermöglicht die Steuerung beider Hydraulikventile von einer gemeinsamen Seite aus, wodurch die Tandemanordnung der beiden Hydraulikventile innerhalb der Innenwelle erst möglich wird. Der für einen Durchgriff des Stö-βels erforderliche axiale Kanal innerhalb des ersten Hydraulikventils kann dabei problemlos vorgesehen werden, da dieser Bereich des ersten Hydraulikventils zur Betätigung der Phasenversteller in keiner Weise benötigt wird.In a further advantageous embodiment of the solution according to the invention, the second electromagnet has a plunger for actuating the second hydraulic valve, which runs centrally through the first hydraulic valve. This plunger, which is arranged essentially coaxially with respect to the first hydraulic valve, makes it possible to control both hydraulic valves from a common side, whereby the tandem arrangement of the two hydraulic valves within the inner shaft becomes possible. The axial channel within the first hydraulic valve required for penetration of the stoichel can thereby be provided without problems, since this area of the first hydraulic valve is not required for actuating the phasers in any way.

Bei einer weiteren vorteilhaften Ausführungsform der erfindungsgemäßen Lösung erfolgt eine Versorgung der beiden Hydraulikventile innerhalb der Innenwelle mit Hydraulikmedium über eine gemeinsame Hydraulikleitung, welche über einen, einem Lager der Nockenwelle zugewandten Ringkanal mit einem im Lager verlaufenden Hydraulikkanal kommuniziert. Der im Lager ohnehin vorhandene Hydraulikkanal dient dabei zu einer Lagerschmierung und kann zusätzlich zur Versorgung der beiden Hydraulikventile genutzt werden. Da der Hydraulikkanal zur Schmierung des Nockenwellenlagers ohnehin bei vielen herkömmlichen Motoren vorhanden ist, kann die erfindungsgemäße Nockenwelle problemlos auch in herkömmliche Motoren eingebaut werden. Gleichzeitig ermöglicht der eine Kanal eine Reduzierung von anzuordnenden Hydraulikleitungen, wodurch die Komplexität der Bauteile, insbesondere der Innenwelle und des Lagers deutlich reduziert werden können.In a further advantageous embodiment of the solution according to the invention, a supply of the two hydraulic valves within the inner shaft with hydraulic medium via a common hydraulic line which communicates via a, a bearing of the camshaft facing annular channel with a running in the bearing hydraulic channel. The existing in the warehouse anyway hydraulic channel serves to a bearing lubrication and can be used in addition to the supply of the two hydraulic valves. Since the hydraulic channel for lubricating the camshaft bearing is present in many conventional engines anyway, the camshaft according to the invention can be easily installed in conventional engines. At the same time, one channel allows a reduction of hydraulic lines to be arranged, whereby the complexity of the components, in particular the inner shaft and the bearing can be significantly reduced.

Weitere wichtige Merkmale und Vorteile der Erfindung ergeben sich aus den Unteransprüchen, aus den Zeichnungen und aus der zugehörigen Figurenbeschreibung anhand der Zeichnungen.Other important features and advantages of the invention will become apparent from the dependent claims, from the drawings and from the associated figure description with reference to the drawings.

Es versteht sich, dass die vorstehend genannten und die nachstehend noch zu erläuternden Merkmale nicht nur in der jeweils angegebenen Kombination, sondern auch in anderen Kombinationen oder in Alleinstellung verwendbar sind, ohne den Rahmen der vorliegenden Erfindung zu verlassen.It is understood that the features mentioned above and those yet to be explained below can be used not only in the particular combination given, but also in other combinations or in isolation, without departing from the scope of the present invention.

Bevorzugte Ausführungsbeispiele der Erfindung sind in den Zeichnungen dargestellt und werden in der nachfolgenden Beschreibung näher erläutert.Preferred embodiments of the invention are illustrated in the drawings and are explained in more detail in the following description.

Dabei zeigen, jeweils schematisch

Fig. 1
einen Längsschnitt durch eine erfindungsgemäße Nockenwelle im Bereich ihrer Phasensteller,
Fig. 2
einen Längsschnitt durch die Innenwelle der Nockenwelle mit systematisch dargestellten Phasenverstellern,
Fig. 3
eine Darstellung wie in Fig. 2, jedoch bei einer anderen Stellung der Hydraulikventile.
Show, each schematically
Fig. 1
a longitudinal section through a camshaft according to the invention in the region of its phaser,
Fig. 2
a longitudinal section through the inner shaft of the camshaft with systematically shown phasing,
Fig. 3
a representation like in Fig. 2 , but in a different position of the hydraulic valves.

Entsprechend Fig. 1 weist eine Nockenwelle 1, insbesondere eine Nockenwelle 1 eines Kraftfahrzeugmotors, eine koaxial in einer Außenwelle 2 angeordnete Innenwelle 3 auf, die verdrehbar gegen die Außenwelle 2 gelagert ist. Gelagert ist die Nockenwelle 1 über ein nockenwellenseitiges Lagerelement 4, welches seinerseits an einem zylinderkopfseitigen Lagerelement 5 gelagert ist. Die in Fig. 1 eingezeichnete, dicke, strichpunktierte Linie 6 symbolisiert dabei eine Trennlinie zwischen einem Bereich A und einem Bereich B, wobei der Bereich A rotierende Bauelemente aufweist, während der Bereich B feststehende Bauelemente aufweist.Corresponding Fig. 1 has a camshaft 1, in particular a camshaft 1 of a motor vehicle engine, a coaxially arranged in an outer shaft 2 inner shaft 3, which is rotatably mounted against the outer shaft 2. The camshaft 1 is mounted via a camshaft-side bearing element 4, which in turn is mounted on a bearing element 5 on the cylinder head side. In the Fig. 1 drawn, thick, dash-dotted line 6 symbolizes a dividing line between a region A and a region B, wherein the region A has rotating components, while the region B has fixed components.

Die in Fig. 1 gezeigte Nockenwelle 1 ist als sogenannte verstellbare Nockenwelle ausgebildet und weist daher gegeneinander verdrehbare erste und zweite Nocken auf, von denen die ersten Nocken fest mit der Innenwelle 3 und die zweiten Nocken fest mit der Außenwelle 2 verbunden sind. Die ersten und zweiten Nocken sind in den Fig. 1 bis 3 nicht gezeichnet. Längsendseitig, das heißt im Bereich des Längsendes der Nockenwelle 1 ist an dieser ein erster Phasenversteller 7 und ein zweiter Phasenversteller 8 angeordnet, wobei der erste Phasenversteller 7 eine Phasenlage der Innenwelle 3 und damit der ersten Nocken relativ zu einem Antrieb, beispielsweise einer nicht gezeigten Kurbelwelle, verstellt, während der zweite Phasenversteller 8 eine Phasenlage der Außenwelle 2 und damit der zweiten Nocken relativ zur Kurbelwelle verstellt. Die Phasenversteller 7 und 8 ändern somit die Phasenlage der Nockenwelle 1 beziehungsweise der Innenwelle 3 und der Außenwelle 2 relativ zur Kurbelwelle und erlauben dadurch eine Senkung des Kraftstoffverbrauchs beziehungsweise der Schadstoffemission sowie eine Erhöhung von Leistung und Drehmoment.In the Fig. 1 shown camshaft 1 is designed as a so-called adjustable camshaft and therefore has mutually rotatable first and second cam, of which the first cam fixed to the inner shaft 3 and the second cam are fixedly connected to the outer shaft 2. The first and second cams are in the Fig. 1 to 3 not drawn. Longitudinal end, that is, in the region of the longitudinal end of the camshaft 1, a first phase adjuster 7 and a second phase adjuster 8 are arranged thereon, wherein the first phase adjuster 7 has a phase position of the inner shaft 3 and thus the first cam relative to a drive, for example a crankshaft, not shown , Adjusted, while the second phase adjuster 8 adjusts a phase angle of the outer shaft 2 and thus the second cam relative to the crankshaft. The phase adjuster 7 and 8 thus change the phase position of the camshaft 1 and the inner shaft 3 and the outer shaft 2 relative to the crankshaft and thereby allow a reduction in fuel consumption or pollutant emission and an increase in power and torque.

Der Fig. 1 weiter zu entnehmen ist, dass der erste Phasenversteller 7 und der zweite Phasenversteller 8 jeweils ein schaltbares Hydraulikventil 9 und 10 aufweisen (in Fig. 1 durchgehend gezeichnet), die beide innerhalb der Innenwelle 3 angeordnet sind. Dies erlaubt eine platzsparende und damit bauraumminimierende Anordnung der zu den Phasenverstellern 7, 8 gehörigen Hydraulikventile 9, 10 und eine gleichzeitig verschleißgeschützte Unterbringung derselben innerhalb der Innenwelle 3.Of the Fig. 1 It can also be seen that the first phase adjuster 7 and the second phaser 8 each have a switchable hydraulic valve 9 and 10 (in FIG Fig. 1 drawn throughout), both of which are arranged inside the inner shaft 3. This allows a space-saving and thus space-minimizing arrangement of the phase adjusters 7, 8 associated hydraulic valves 9, 10 and one at the same time wear-resistant accommodation thereof within the inner shaft. 3

Wie den Fig. 1 bis 3 zu entnehmen ist, sind die beiden Hydraulikventile 9, 10 in axialer Richtung der Wellen 2 und 3 benachbart zueinander innerhalb der Innenwelle 3 angeordnet. Diese sogenannte Tandemanordnung erfordert zur Steuerung der beiden Hydraulikventile 9 und 10, dass zur Steuerung insbesondere des zweiten Hydraulikventils 10 das erste Hydraulikventil 9 von einem Steuerelement, insbesondere einem Stößel 11', durchgriffen wird. Generell ist zur Steuerung der beiden Hydraulikventile 9 und 10 eine Betätigungseinrichtung 12 vorgesehen, die einen ersten Elektromagneten 13 und einen zweiten Elektromagneten 14 aufweist, wovon der erste Elektromagnet 13 das erste Hydraulikventil 9 und der zweite Elektromagnet 14 korrespondierend dazu das zweite Hydraulikventil 10 betätigt. Dabei sind sowohl der erste Elektromagnet 13 als auch der zweite Elektromagnet 14 im Bereich B, das heißt in einem stehenden Bereich angeordnet. Dies bedeutet, dass die Betätigungseinrichtung 12 insgesamt ortsfest an einem nicht gezeigten Zylinderkopf angeordnet ist, während die Hydraulikventile 9 und 10 drehfest mit der Innenwelle 3 verbunden sind.Like that Fig. 1 to 3 can be seen, the two hydraulic valves 9, 10 in the axial direction of the shafts 2 and 3 adjacent to each other within the inner shaft 3 are arranged. This so-called tandem arrangement requires for the control of the two hydraulic valves 9 and 10, that for controlling in particular the second hydraulic valve 10, the first hydraulic valve 9 by a control, in particular a plunger 11 ', is penetrated. In general, to control the two hydraulic valves 9 and 10, an actuating device 12 is provided which has a first electromagnet 13 and a second electromagnet 14, of which the first electromagnet 13, the first hydraulic valve 9 and the second electromagnet 14 corresponding to the second hydraulic valve 10 is actuated. In this case, both the first electromagnet 13 and the second electromagnet 14 in the region B, that is arranged in a stationary area. This means that the actuating device 12 is arranged as a whole stationary on a cylinder head, not shown, while the hydraulic valves 9 and 10 are rotatably connected to the inner shaft 3.

Eine Versorgung der beiden Hydraulikventile 9 und 10 mit Hydraulikmedium, beispielsweise Öl, erfolgt über eine gemeinsame Hydraulikleitung 15 welche über einen, dem zylinderkopfseitigen Lagerelement 5 zugewandten Ringkanal 16 mit einem im zylinderkopfseitigen Lagerelement 5 verlaufenden Hydraulikkanal 17 kommuniziert. Der Ringkanal 16 ermöglicht dabei ein Rotieren der Nockenwelle 1 ohne dass hierbei eine für die Ölzufuhr gemeinsame Hydraulikleitung 15 unterbrochen werden würde. Der Hydraulikkanal 17 im zylinderkopfseitigen Lagerelement 5 stellt gleichzeitig eine Ölversorgung zur Schmierung eines Ringspaltes zwischen den beiden Lagerelementen 4 und 5 dar und ist ohnehin in herkömmlichen Motoren vorhanden. Somit ist lediglich eine Hydraulikleitung zur Versorgung der beiden Hydraulikventile 9 und 10 erforderlich, wodurch die Komplexität der Bauteile, insbesondere des Lagerelementes 4 und des zylinderkopfseitigen Lagerelementes 5 deutlich reduziert werden kann.A supply of the two hydraulic valves 9 and 10 with hydraulic medium, for example oil, via a common hydraulic line 15 which via one, the cylinder head side bearing member 5 facing annular channel 16 extending in the cylinder head side bearing element 5 Hydraulic channel 17 communicates. The annular channel 16 thereby enables the camshaft 1 to rotate without any interruption of a hydraulic line 15 common to the oil supply. The hydraulic channel 17 in the cylinder head side bearing element 5 simultaneously represents an oil supply for lubricating an annular gap between the two bearing elements 4 and 5 and is already present in conventional engines. Thus, only one hydraulic line for supplying the two hydraulic valves 9 and 10 is required, whereby the complexity of the components, in particular of the bearing element 4 and the cylinder head side bearing element 5 can be significantly reduced.

Wie in den Fig. 2 und 3 dargestellt teilt sich die gemeinsame Hydraulikleitung 15 innerhalb der Innenwelle 3 vor erreichen der beiden Hydraulikventile 9 und 10 in eine erste Hydraulikleitung 15', welche das erste Hydraulikventil 9 versorgt und in eine zweite Hydraulikleitung 15", welche das zweite Hydraulikventil 10 versorgt. Ebenfalls den Fig. 2 und 3 zu entnehmen ist, dass die beiden Hydraulikventile 9 und 10 als federbeaufschlagte Schieberventile ausgebildet sind, welche von den Elektromagneten 13 und 14 über entsprechende Stößel 11, 11' jeweils gegen eine Feder 18, 18' vorgespannt werden, die sich anderenends an einem jeweiligen Anschlag 19, 19' an der Innenwelle 3 abstützt. Das erste Hydraulikventil 9 ist dabei gemäß den Fig. 2 und 3 von dem zur Betätigung des zweiten Hydraulikventils 10 erforderlichen Stößel 11' zentral durchgriffen.As in the FIGS. 2 and 3 illustrated the common hydraulic line 15 divides within the inner shaft 3 before reaching the two hydraulic valves 9 and 10 in a first hydraulic line 15 ', which supplies the first hydraulic valve 9 and in a second hydraulic line 15 ", which supplies the second hydraulic valve 10. Auch die FIGS. 2 and 3 It can be seen that the two hydraulic valves 9 and 10 are formed as spring-loaded slide valves which are biased by the electromagnets 13 and 14 via respective plunger 11, 11 'in each case against a spring 18, 18', the other end at a respective stop 19th , 19 'on the inner shaft 3 is supported. The first hydraulic valve 9 is in accordance with the FIGS. 2 and 3 from the required to actuate the second hydraulic valve 10 ram 11 'penetrated centrally.

Im Folgenden soll nun kurz die Funktionsweise der beiden Hydraulikventile 9 und 10 im Zusammenhang mit den beiden zugehörigen Phasenverstellern 7 und 8 erläutert werden.In the following, the mode of operation of the two hydraulic valves 9 and 10 in connection with the two associated phase adjusters 7 and 8 will now be briefly explained.

In Fig. 2 fördert eine Pumpe 20 kontinuierlich Hydraulikmedium aus einem Reservoir 21 durch die entsprechenden Leitungen 15' und 15" zum ersten Hydraulikventil 9 beziehungsweise zum zweiten Hydraulikventil 10. Das erste Hydraulikventil 9 ist dabei so gestellt, dass beide zum ersten Phasenversteller 7 führende Kanäle 23, 23' durch entsprechende Vorsprünge 22, 22' am Schieber 24 des ersten Hydraulikventils 9 verschlossen sind. Somit bleibt ein Flügelzellen-Phasenverstellers 25 in einer Mittenlage. Die gleiche Stellung weist auch das zweite Hydraulikventil 9 auf, so dass auch der zweite Phasenversteller 8 in einer Mittenstellung verbleibt.In Fig. 2 promotes a pump 20 continuously hydraulic fluid from a reservoir 21 through the corresponding lines 15 'and 15 "to the first hydraulic valve 9 and the second hydraulic valve 10. The first hydraulic valve 9 is set so that both the first phase adjuster 7 leading channels 23, 23' by means of corresponding projections 22, 22 'on the slide 24 of the first hydraulic valve 9. Thus, a vane-type phase adjuster 25 remains in a central position The same position also has the second hydraulic valve 9, so that the second phase adjuster 8 also remains in a central position ,

In Fig. 3 wird durch die Betätigungseinrichtung 12 beziehungsweise der erste Magnet 13 und der zweite Magnet 14 eine Verstellung des Schiebers 24 des ersten Hydraulikventiles 9 und eine Verstellung des Schiebers 24' des zweiten Hydraulikventils 10 bewirkt. Der zweite Elektromagnet 14 bewegt gemäß der Fig. 3 den Stößel 11 nach rechts und verschiebt dadurch den Schieber 24' ebenfalls nach rechts entgegen der von der Feder 18' ausgeübten Federkraft. In dazu entgegengesetzter Richtung ist der Schieber 24 des ersten Hydraulikventils 9 nach links verschoben, wodurch der Kanal 23, welcher zum ersten Phasenversteller 7 führt, geöffnet wird. Dies bewirkt eine Drehbewegung der Flügelzelle entgegen dem Uhrzeigersinn und damit eine Verstellung der Innenwelle 3 beziehungsweise der damit verbundenen ersten Nocken. Analog dazu funktioniert die Verstellung des Flügelrades 25' im Uhrzeigersinn beim zweiten Phasenversteller 8.In Fig. 3 is caused by the actuator 12 and the first magnet 13 and the second magnet 14, an adjustment of the slider 24 of the first hydraulic valve 9 and an adjustment of the slider 24 'of the second hydraulic valve 10. The second electromagnet 14 moves according to the Fig. 3 the plunger 11 to the right and thereby displaces the slider 24 'also to the right against the force exerted by the spring 18' spring force. In the opposite direction of the slide 24 of the first hydraulic valve 9 is shifted to the left, whereby the channel 23, which leads to the first phaser 7, is opened. This causes a rotational movement of the vane against the Clockwise and thus an adjustment of the inner shaft 3 and the associated first cam. Analogously, the adjustment of the impeller 25 'clockwise at the second phase adjuster. 8

Claims (9)

  1. A camshaft (1) of motor vehicle engines in particular,
    - having an inner shaft (3) that is coaxially arranged in an outer shaft (2) and is rotatably mounted against the outer shaft (2),
    - having first and second cams that are rotatable one against the other and of which the first cam is connected in a fixed manner to the inner shaft (3) while the second cam is likewise connected in a fixed manner to the outer shaft (2),
    - having a first and a second phase adjuster (7, 8) of which the first phase adjuster (7) adjusts a phase position of the inner shaft (3) and thus of the first cam relative to a drive, while the second phase adjuster (8) adjusts a phase position of the outer shaft (2) and thus of the second cam relative to the drive,
    - wherein the first and the second phase adjuster (7, 8) respectively have a switchable hydraulic valve (9, 10), both of which being substantially arranged within the inner shaft (3).
  2. The camshaft as specified in claim 1,
    characterised in that
    both of the hydraulic valves (9, 10) are arranged in the inner shaft (3) adjacent to one another in the axial direction.
  3. The camshaft as specified in claim 1 or claim 2,
    characterised in that
    an actuating device (12) for controlling both of the hydraulic valves (9, 10) is provided that has a first and a second electromagnet (13, 14), the first electromagnet (13) actuating the first hydraulic valve (9) and the second electromagnet (14) actuating the second hydraulic valve (10).
  4. The camshaft as specified in claim 3,
    characterised in that
    the actuating device (12) is arranged on the cylinder head in a locationally-fixed manner, while the hydraulic valves (9, 10) are connected to the inner shaft (3) in a rotationally-fixed manner.
  5. The camshaft as specified in any one of the claims 2 to 4,
    characterised in that
    both of the hydraulic valves (9, 10) are supplied with hydraulic medium by means of a common hydraulic line (15) that, by means of ring canal (16) opposite a bearing (5) of the camshaft (1), communicates with a hydraulic canal (17) extending in the bearing (5).
  6. The camshaft as specified in claim 5,
    characterised in that
    the common hydraulic line (15) divides in the inner shaft (3), namely into hydraulic lines (15', 15") that respectively supply the first hydraulic valve (9) and the second hydraulic valve (10).
  7. The camshaft as specified in any one of the claims 1 to 6,
    characterised in that
    both of the hydraulic valves (9, 10) are arranged in an axial end region of the camshaft (1).
  8. The camshaft as specified in any one of the claims 2 to 7,
    characterised in that
    both of the hydraulic valves (9, 10) are configured as spring-loaded slide valves.
  9. The camshaft as specified in any one of the claims 3 to 8,
    characterised in that
    the second electromagnet (14) has a tappet (11') for actuating the second hydraulic valve (10) that extends centrally through the first hydraulic valve (9).
EP07106778A 2006-05-27 2007-04-24 Camshaft Expired - Fee Related EP1860286B1 (en)

Applications Claiming Priority (1)

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DE102006024793A DE102006024793A1 (en) 2006-05-27 2006-05-27 camshaft

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EP1860286A3 EP1860286A3 (en) 2008-05-21
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US20070272183A1 (en) 2007-11-29
US7536986B2 (en) 2009-05-26
EP1860286A2 (en) 2007-11-28
EP1860286A3 (en) 2008-05-21
DE102006024793A1 (en) 2007-11-29
DE502007002976D1 (en) 2010-04-15

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