EP2585687B1 - Adjustable camshaft - Google Patents

Adjustable camshaft Download PDF

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Publication number
EP2585687B1
EP2585687B1 EP11758091.0A EP11758091A EP2585687B1 EP 2585687 B1 EP2585687 B1 EP 2585687B1 EP 11758091 A EP11758091 A EP 11758091A EP 2585687 B1 EP2585687 B1 EP 2585687B1
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EP
European Patent Office
Prior art keywords
cam
shaft
camshaft
packages
cams
Prior art date
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Active
Application number
EP11758091.0A
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German (de)
French (fr)
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EP2585687A1 (en
Inventor
Roman Weinmeister
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.)
Neumayer Tekfor Holding GmbH
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Neumayer Tekfor Holding GmbH
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Publication of EP2585687A1 publication Critical patent/EP2585687A1/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
    • 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
    • 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
    • F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
    • F01L13/0015—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque
    • F01L13/0036—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque the valves being driven by two or more cams with different shape, size or timing or a single cam profiled in axial and radial direction
    • 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
    • F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
    • F01L13/0015—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque
    • F01L13/0036—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque the valves being driven by two or more cams with different shape, size or timing or a single cam profiled in axial and radial direction
    • F01L2013/0052—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque the valves being driven by two or more cams with different shape, size or timing or a single cam profiled in axial and radial direction with cams provided on an axially slidable sleeve

Definitions

  • the invention relates to an adjustable camshaft, with at least one shaft, and with at least one cam package, which has at least two different cams and / or cam contours.
  • the cams and / or the cam contours of the cam package have different widths.
  • the cam package is designed axially displaceable along a longitudinal axis of the camshaft by at least one adjusting element is provided, which is axially displaceable along the longitudinal axis, and in that the adjusting element is mechanically coupled via at least one contact element with the cam package.
  • a camshaft has at least one carrier element, also referred to as tube or shaft, and at least one cam.
  • camshafts serve as part of the valvetrain, with the support member rotating about its longitudinal axis.
  • the cams convert the rotary motion into longitudinal movements, thereby controlling the intake and exhaust valves of the engine.
  • adjustment possibilities of camshafts for example which bring different cams into operative engagement with the valves or change the settings, eg the angles of the cams relative to one another.
  • camshaft When adjusting the camshaft is in the prior art usually make sure that the cams are adjusted only when the associated valves run on the base circle of the cam, i. if the cams do not actuate the valves. Therefore, the cams must either be individually adjusted or only groups can be formed from at least during a phase non-engaging with the valves cams. In the latter then the adjustment of the cam is made.
  • the invention has for its object to propose an adjustable camshaft, which allows a greater possibility over the prior art at times for adjusting the camshaft and thus also allows different groupings of the cams of different valves or cylinders.
  • the shaft is designed to be axially displaceable along the longitudinal axis of the camshaft, and that at least one cam package is provided which is fixedly connected to the shaft, so that on the adjusting element and the shaft at least two different cam packages independently are adjustable.
  • a correspondingly wide cam or a sufficiently wide cam contour can serve to enable a cam package to be displaced outside the base circle of a cam.
  • cams or cam packs e.g. be moved axially at the same time, even if a cam is currently operating a valve.
  • the cam package and the adjusting element are axially displaceable along the longitudinal axis of the camshaft, so that a displacement of the adjusting element, a displacement of the cam package causes, whereby the different cams or cam contours of the cam package or possibly the cam packages come into contact with the valves.
  • cam packages Since both the shaft axially displaceable along the longitudinal axis and an axially displaceable adjusting element is provided, at least two different groups of cam packages can be formed, which can be adjusted independently.
  • the cam package, which is firmly connected to the shaft, can also have the same or different widths.
  • the adjusting element is arranged within the shaft.
  • An embodiment of the invention provides that a plurality of cam packages are provided and arranged axially displaceable on the shaft, and that at least two of the cam packages mechanically with the Adjustment are coupled.
  • An embodiment of the invention includes that the adjusting element is designed to be rotatable radially about the longitudinal axis of the camshaft. With this configuration, thus still the angular position and thus the phase of the cams can be adjusted to each other.
  • An embodiment of the invention provides that at least one Axialverstelltechnik is provided, which is connected to the adjusting element, and which at least partially axially displaces the adjusting element.
  • An embodiment of the invention includes that a plurality of adjusting elements are provided which are axially displaceable along the longitudinal axis of the camshaft. By a large number of adjusting elements, a corresponding number of cam packages can be controlled and shifted individually or in groups.
  • An embodiment of the invention provides that the adjusting element is configured as a solid cylinder or as a pipe or as a segment of a cylinder or as a segment of a pipe or as a sheet metal part.
  • a camshaft 1 is shown, which is here to control the valves of four cylinders.
  • the invention can also be applied to engines with a different number of cylinders.
  • Each cylinder - not shown here - two valves are associated with it: the valves of the first cylinder 101, the second cylinder 102, the third cylinder 103 and the fourth cylinder 104.
  • each left shown - valve is a single cam 8 on associated with the camshaft 1, which is axially fixedly mounted on the shaft 3.
  • a cam package 2 is provided, which in particular allows a change in the valve lift.
  • both valves of a cylinder can be controlled differently by changing the cams.
  • Shown here is, for example, the camshaft 1 for the intake valves of the cylinder. Accordingly, such a camshaft 1 can also be used for the exhaust valves.
  • the cam packages 2 each have a slide 20, which is axially displaceable on the shaft 3 along the longitudinal axis - shown here in dash-dotted lines. On the
  • Carriage 20 are in this embodiment, a first cam 21 and a second cam 22.
  • the cams 21, 22 differ in terms their outer profile, for example, at the height of the cam-forming elevation or nose, which determines the valve lift (see Fig. 5 the example of the first cam 21 with nose 21.1).
  • the cams 21, 22 have a different course.
  • at least one cam is a one-piece component of the carriage 20, that is, the carriage 20 may itself also have such a cam contour.
  • the axially displaceable carriage 20 is connected to an adjusting element 4 via a contact element 5, which is, for example, a pin connected in the hollow shaft 3 designed.
  • a contact element 5 which is, for example, a pin connected in the hollow shaft 3 designed.
  • each recesses 30, eg grooves in the shaft 3 are provided.
  • the contact elements 5 extend completely through the adjusting element 4 or the shaft 3. Since the adjusting element 4 itself is designed to be axially displaceable, the cam packs 2 can be displaced axially, ie valve activation with the first cam 21 or with the second cam 22 can be caused.
  • the adjusting element 4 is for example a solid shaft, which optionally consists of a plastic or a composite material.
  • the camshaft 1 is driven, for example, by the crankshaft, not shown here.
  • the torque is - in the example shown here - split and transmitted on the one hand on the outer shaft 3 and the fixed thereto single cam 8 and the other via the adjusting element 4 and the contact elements 5.
  • a corresponding mounting of the adjusting element 4 is provided in the shaft 3 or there is a corresponding pinning instead.
  • the cam packages 2 of the valves of the second 102 and the fourth cylinder 104 are moved.
  • fewer or more cam packages 2 can be grouped accordingly.
  • the cams 21, 22 of the cam packages 2 have different widths.
  • the first cam 21 is narrower than the second cam 22 in the cam packets 2 of the first and third cylinders. Conversely, in the cam packets 2 of the first and third cylinders, the first cam 21 is wider than the second cam 22. Due to the greater width of the first cam Cam 21 can thus be made for example for the valve of the first cylinder 101, the adjustment, even if the valve of the first cylinder 101 just outside the base circle runs, ie when the cam presses the valve, for example via a cam follower against a spring and thus the opening of Valve causes. Only when the adjusting element 4 is moved further, that is, beyond the width of the cam also, the conversion of the cam for the valves of the first 101 and third cylinder 103 takes place.
  • the conversion of a cam package from one cam to the other takes place respectively on the base circle, ie when the cams of the associated cam set do not actuate the associated valve, but during the time in which a cam of another cam set actuates a valve, ie outside the base circle for this other cam-valve combination.
  • the arrangement of the wider or narrower cams here refers only to the illustrated example and can be adapted according to the needs of the engine or the type of control of the cylinder. If the torque is transmitted, for example - in a realization, not shown here - only from the outer shaft 3, so can be done on the adjusting element 4 still twisting, so that a phase change is possible.
  • a Radialverformathü 7 is provided for radial change - relative to the crankshaft and / or relative to the cams to each other - a Radialverformathü 7 is provided.
  • the axial displacement of the adjusting element 4 is accomplished - in this example - by the Axialverstelltechnik 6, in which two actuators 60 engage on matching raceways, so that a linear movement of the actuators 60 perpendicular to the longitudinal axis of the adjusting element 4, an axial displacement of the adjusting element 4 in the direction causes the longitudinal axis.
  • the adjusting element 4 is displaced axially so far that in each case a valve 102, 104 no longer comes into contact with the first cam 21, but with the second cam 22.
  • the - here drawing - left actuator 60 is in the example shown here at the beginning of the axial displacement causing path.
  • the second cam 22 is designed for the illustrated variant such that it causes a shutdown of the associated valve by the valve only runs on the base circle of the - nase- or spy-less - cam 22 and thus is not operated.
  • the illustration Fig. 2 shows the state that a valve of the second 102 and the fourth cylinder 104 is turned off - they are respectively in communication with the second cam 22 - and that also one valve of the first 101 and third cylinder 103 is to be turned off.
  • the shaft 3 and the adjusting element 4 have rotated by 90 °, so that now also the grooves 30 with the contact elements 5 to recognize.
  • the contact elements 5 have no radial clearance in the grooves 30, which would allow rotation about the longitudinal axis of the camshaft 3.
  • Other configurations of the grooves 30 will be discussed below.
  • other angles other than the 90 ° angle are still possible. This is dependent on the control of the valves or the required variant of the adjustment of the camshaft 1.
  • the actuator 60 is located at another area of the track in the Axialverstellmaschine 6.
  • the individual cam 8 fixedly mounted on the shaft 3 actuates the left-hand valve of the fourth cylinder 104, with the right-hand valve of the fourth cylinder 104 running over the second cam 22 of the cam assembly 2 on the base circle and thus, as it were, by a neutral position. Hub is controlled.
  • Fig. 4 there was relative to in the Fig. 3 shown state another 90 ° rotation and the adjusting element 4 is axially displaced so far that the corresponding valves of the first cylinder 101 and the third cylinder 103 come into contact with the narrower second cam 22 of the respective associated cam package 2.
  • valves of the first 101 and third cylinder 103 are shut down due to the outer contour of the second cam 22 of the associated cam packages 2 by running on the base circle, so to say with a zero stroke.
  • the actuator 60 is now at the end of the career arrived and a further axial displacement of the adjusting element 4 no longer takes place.
  • a first cam 21 is shown as applied to a carriage of a cam pack.
  • - not shown - is a hollow cam, which has substantially only an outer contour and a mounting surface for the carriage.
  • the cam is a component of the carriage itself.
  • the base circle and the nose or tip 21.1 are shown.
  • Fig. 6 are three variants a) to c) shown for the configuration of a groove 30 in the shaft 3.
  • the torque can be transmitted via the groove 30 or via the inner shaft.
  • the groove 30 is inclined and the contact element is fixed in the end positions.
  • the S-shaped configuration of Fig. 6c) also allows a fixation of the contact element at the end points of the axial movement.
  • the Fig. 7 illustrates a possible career, over which an actuator shifts the adjustment axially by a distance X1 and in the reverse direction to X2. Shown here is the unwound 360 ° -Außen formation eg a wheel as part of Axialverstelltechnik. Essentially, two shifts take place, which in the above example the FIGS. 1 to 4 Initially cause a shutdown of the valves of the second and fourth cylinders and then the valves of the first and third cylinders (sections a). Between these two shutdowns, a portion (in the figure section b) is provided, which causes no axial displacement of the adjusting element. The two illustrated raceways are here to match the arrangement of the actuators of the figures Fig.
  • the raceways are designed mirror-symmetrically to each other, wherein a raceway causes the displacement in one and the other career, the shift back.
  • the mirror-symmetrical design results here from the fact that the actuators are arranged side by side.
  • the shape of the raceways is therefore also dependent on how the Axialverstelltechnik is configured or how the actuators are arranged and initiate the shift.
  • the four sections a, b correspond here in each case to an angular extent of 90 °, corresponding to the representation of FIGS. 1 to 4 , However, other angles are also possible, especially with other cylinder numbers.
  • the two angles for the displacement of the cams - in each case sections a - and the two angles during which no displacement takes place - denoted by b -, in each case the same and different from each other.
  • the number of angles and their sizes also depends on the number of shifts, ie on the number of affected cam packages.
  • Fig. 8 a) and b) two variants for the design of the radial twisting unit 7 are shown.
  • the Radialverformattician 7 is connected to the adjusting element 4 and allows its rotation relative to the outer shaft 3 and thereby changing the phase of the cam.
  • the two variants differ with regard to the implementation of a length compensation, which is necessary by the axial displacement of the adjusting element 4.
  • a special element is provided for this compensation, whereas in the variant of Fig. 8b) the compensation takes place via an inner and an outer toothing of two partial elements of the adjusting element 4.
  • balls which run in grooves between the sections of the elements which are located inside one another and function correspondingly, for example, in a length compensation element in drive shafts.
  • Fig. 9 a is a part of a camshaft with two adjacent cam packages 2 shown, both of which a lifting (different Cam contour of the first 21 and the second cam 22) and a phase change (rotation about the longitudinal axis of the shaft 3) allow.
  • Fig. 9b) and Fig. 9c) two sections through the shaft 3 are shown in different positions.
  • the embodiments in the shaft 3 allow for an axial guidance of the contact element 5 and at the same time still a radial mobility and on the other hand only an axial guidance, ie radially fixed.
  • the Fig. 10 shows a part of a camshaft whose shaft 3 has two different grooves 30 for the contact elements 5. In the variant shown on the left, only an axial displacement is possible, and the - here on the representation - right-side groove additionally allows a radial rotation, since the contact element 5 laterally has place in the groove 30.
  • the camshaft 1 of Fig. 11 allows the switching of three different contours by each cam package 2 has three different cams: first cam 21, second cam 22 and third cam 23.
  • three different profiles for the control of the valves can be applied.
  • the different valve strokes can be seen here at the different heights of the cams of the cam package 2 for the valve of the first cylinder 101.
  • the axial adjustment unit 6 here also schematically has two raceways each, so that a displacement from the first 21 to the second 22 and from the second 22 to the third cam 23 is possible.
  • two - here mirror-symmetrically designed - raceways are provided for the pushing back accordingly two - here mirror-symmetrically designed - raceways are provided.
  • Per valve also different numbers of cams or cam contours can be provided.
  • the shaft 3 and the adjusting element 4 form a unit which is axially displaceable configured and arranged and which also serves to transmit the torque.
  • the cam packages 2 'in this representation each come into contact with a roller tappet, wherein two roller tappets are provided for the respective two valves for each cylinder: the roller tappets of the first cylinder 111, the roller tappets of the second cylinder 112, the roller tappets of the third cylinder 113 and the roller tappet of the fourth cylinder 114.
  • the bearings 120 are shown, on which the camshaft 1 rests in the installed state.
  • the shaft 3 and the adjusting element 4 is axially displaced via the Axialverstelltechnik 6 and the actuators 60 (indicated by the double arrow). Since the cam packages 2 'are fixedly mounted on the shaft 3, the roller tappets 111, 112, 113 and 114 thus also come into contact with the different cams 20, 21 or cam contours of the packages 2'.
  • the cam packages 2 'can - as shown here - consist of individual cams 20, 21, but it can also be a unit with correspondingly different cam contours.
  • a radial twisting unit 7 is provided to rotate the shaft 3 radially about its longitudinal axis for adjusting the phase of the cams.
  • a housing 131 is provided, in which, for example via the teeth axially movable plug 130 is arranged.
  • the plug 130 is non-rotatable, eg connected to the shaft 3 via interference fit.
  • the axial adjustment between plug 130 and housing 131 takes place as a result of the axial displacement of the shaft 3 by a corresponding internal toothing.
  • the housing 131 is mounted axially.
  • the camshaft 1 of Fig. 13 differs thereby from the variant of Fig. 12 in that the shaft 3 is coupled directly to the housing 131, for example via a corresponding toothing, which allows the axial displacement.
  • An axial adjustment is also possible here by means of balls, which are located in raceways between the shaft 3 and the housing 131.
  • the variants of the camshaft 1 of the figures Fig. 12 and Fig. 13 allow only the displacement of all cam packages 2 'at the same time, since all cam packages 2' are fixedly connected to the shaft 3 and with the adjusting element 4 identical to the shaft 3.
  • the displacement while a cam actuates a valve, ie outside the base circle, is due to the different width cam 21, 22 possible.
  • the variants of Fig. 1 to 4 and Fig. 11 allow it further by the adjusting element 4 in conjunction with the shaft 3, that not all cam packages are moved because the cam packages are firmly connected to the different in these embodiments of the shaft 3 adjustment 4. This possibility that individual cams are not moved allows, for example, in the variant of Fig. 1 the use of a single cam 8, which is not changed.
  • Fig. 14 makes it possible to control both valves of each cylinder with different combinations of cam contours.
  • a cam package 2 'for a valve with the shaft 3 and a cam package 2 via the contact element 5 through the groove 30 with the adjusting element 4 is connected.
  • the adjusting element 4 is axially displaced by the Axialverstelltechnik 6 and the actuators 60 and the tube 3 of the Rajaxialverstelltechnik 9 with its associated actuators 90.
  • the Rajaxialverstelltechnik 9 is mounted laterally in this example shown here.
  • crankshaft not shown here - drive the camshaft 1, for example via a - also not shown here - chain.
  • the cam packages 2, which are displaced with the adjusting element 4, are each a unit in this embodiment, which correspondingly has two different cam contours. The adjustment of a cam during actuation of the associated valve by the cam is also made possible by the appropriately wide cam contour.
  • a section of a further variant of the camshaft 1 is shown. It is possible to form four, for example, different sized groups of cam packages 2, which are each adjusted simultaneously.
  • the shaft 3 are for this purpose four adjusting elements 4, which are each connected via contact elements 5 with the individual cam packages 2.
  • the individual adjusting elements 4 are configured, for example, in the form of superimposed carrier strips, such as in the Fig. 15b ).
  • the shaft 3 has, for example, a rectangular free area in its interior, at the longitudinal sides in each case at least one slot or generally a recess for the contact elements 5, which are also configured here as pins, for example.
  • different fixing elements which have the described inner contour or otherwise provide a guide.
  • the adjusting elements 4 For the displacement of the cam packages 2, which are arranged here axially displaceable on the shaft 3, the adjusting elements 4 have grooves 40.
  • the individual adjusting elements 4 For the excerpt of Fig. 15 a) are in the Fig. 15c) the individual adjusting elements 4 arranged side by side.
  • two contact elements 5 - here on the uppermost and the lowest displacement element 4 - are provided which lie at different axial positions. Since the contact elements 5 project completely through the shaft 3 and thus through all adjusting elements 4, the two other adjusting elements 4 at the height of the contact elements 5 each have grooves 40 which allow the axial displacement of the other elements.
  • the individual adjusting elements 4 can be individually offset axially.
  • the axial movements of the individual adjusting elements 4 can be coupled to one another via the grooves of the adjusting elements 40, ie via their configuration and arrangement. Since it is possible in this variant to move individual cam packages 2 targeted, it is not necessary, for example, that the individual cams have different widths, since the shift is preferably on the base circle can be made. However, a combination is also possible to meet any special requirements for the adjustment of the camshaft 1. With the variant shown here, four groups of cam packages can be formed or only individual cam packages can be controlled separately. A different number of groups is also possible, where appropriate, the number of individual here designed flat adjusting elements 4 is to be increased or increased. The variant of the adjusting 4 of the Fig.
  • adjusting element 4 of Fig. 16 Within the shaft 3, an adjusting element 4 is provided here, which consists of - in this example - four segments, which are individually axially displaceable.
  • a possible radial rotation of the individual segments and thus the respectively associated cam packages show the pictures Fig. 17 a) and b).
  • each two opposing segments can be adjusted radially to each other by a space between the adjacent segments, in which - in this embodiment - a fixing element 10 is introduced.
  • the number of segments can be adjusted according to the needs or the number of cylinders.

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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 bezieht sich auf eine verstellbare Nockenwelle, mit mindestens einer Welle, und mit mindestens einem Nockenpaket, welches mindestens zwei unterschiedliche Nocken und/oder Nockenkonturen aufweist. Dabei weisen die Nocken und/oder die Nockenkonturen des Nockenpakets unterschiedliche Breiten auf. Das Nockenpaket ist axial längs einer Längsachse der Nockenwelle verschiebbar ausgestaltet, indem mindestens ein Verstellelement vorgesehen ist, welches axial längs der Längsachse verschiebbar ausgestaltet ist, und indem das Verstellelement über mindestens ein Kontaktelement mit dem Nockenpaket mechanisch gekoppelt ist.The invention relates to an adjustable camshaft, with at least one shaft, and with at least one cam package, which has at least two different cams and / or cam contours. In this case, the cams and / or the cam contours of the cam package have different widths. The cam package is designed axially displaceable along a longitudinal axis of the camshaft by at least one adjusting element is provided, which is axially displaceable along the longitudinal axis, and in that the adjusting element is mechanically coupled via at least one contact element with the cam package.

Eine Nockenwelle verfügt zumindest über ein Trägerelement, auch als Rohr oder Welle bezeichnet, und mindestens einen Nocken. Bei der Anwendung in Motoren dienen Nockenwellen als Teil des Ventiltriebes, wobei sich das Trägerelement um seine Längsachse dreht. Die Nocken wandeln die Drehbewegung in Längsbewegungen um, wodurch die Ein- und Auslassventile des Motors gesteuert werden. Um je nach Lastzustand den Motor optimal steuern zu können, gibt es im Stand der Technik Verstellmöglichkeiten von Nockenwellen, z.B. welche unterschiedliche Nocken in Wirkeingriff mit den Ventilen bringen oder die Einstellungen, z.B. die Winkel der Nocken zueinander ändern. In der Offenlegungsschrift WO 2010/040439 A1 wird eine Ventiltriebvorrichtung beschrieben, in welcher eine außerhalb der Nockenwelle angebrachte Vorrichtung das Verschieben von einzelnen Nockenpaaren oder Gruppen von Nockenpaaren erlaubt, so dass die unterschiedlichen Nockenkonturen der Nockenpaaren der Ventilsteuerung dienen. Der dort beschriebene Aufbau erfordert einen großen Bauraum um die eigentliche Nockenwelle herum. Weiterhin ist die Anzahl der verwendeten Bauteile relativ hoch, was auch mit einer hohen Komplexität einhergeht.A camshaft has at least one carrier element, also referred to as tube or shaft, and at least one cam. When used in engines, camshafts serve as part of the valvetrain, with the support member rotating about its longitudinal axis. The cams convert the rotary motion into longitudinal movements, thereby controlling the intake and exhaust valves of the engine. In order to be able to optimally control the engine depending on the load state, in the prior art there are adjustment possibilities of camshafts, for example which bring different cams into operative engagement with the valves or change the settings, eg the angles of the cams relative to one another. In the published patent application WO 2010/040439 A1 There is described a valvetrain device in which a device mounted outside the camshaft allows for shifting individual cam pairs or groups of cam pairs so that the different cam contours of the cam pairs serve the valve timing. The structure described there requires a large space around the actual camshaft around. Furthermore, the number of components used is relatively high, which is associated with a high complexity.

Bei der Verstellung der Nockenwelle ist im Stand der Technik zumeist darauf zu achten, dass die Nocken nur dann verstellt werden, wenn die zugehörigen Ventile auf dem Grundkreis der Nocken laufen, d.h. wenn die Nocken die Ventile nicht betätigen. Daher müssen die Nocken entweder einzeln verstellt werden oder es können nur Gruppen gebildet werden von zumindest während einer Phase nicht im Eingriff mit den Ventilen stehenden Nocken. Bei letzteren wird dann die Verstellung der Nocken vorgenommen.When adjusting the camshaft is in the prior art usually make sure that the cams are adjusted only when the associated valves run on the base circle of the cam, i. if the cams do not actuate the valves. Therefore, the cams must either be individually adjusted or only groups can be formed from at least during a phase non-engaging with the valves cams. In the latter then the adjustment of the cam is made.

Im Stand der Technik sind verschiedene Ausführungen bekannt, um Nockenwellen zu verstellen, die sich in zwei Gruppen unterteilen (siehe auch die Offenlegungsschrift DE 195 19 048 A1 ). In einer Variante werden mit Schaltkulissen einzelne Nockenpakete entlang der Nockenwelle verschoben. Dies ist beispielsweise beschrieben in der Offenlegungsschrift DE 10 2004 055 852 A1 oder der Patentschrift US 4,794,893 . Alternativ wird die gesamte Nockenwelle axial verschoben (siehe z. B. die Patentschriften GB 186,369 und US 5,129,407 ).In the prior art, various embodiments are known to adjust camshafts, which are divided into two groups (see also the published patent application DE 195 19 048 A1 ). In a variant, individual cam packages are shifted along the camshaft with shift gates. This is described, for example, in the published patent application DE 10 2004 055 852 A1 or the patent US 4,794,893 , Alternatively, the entire camshaft is displaced axially (see, for example, the patents GB 186,369 and US 5,129,407 ).

Der Erfindung liegt die Aufgabe zugrunde, eine verstellbare Nockenwelle vorzuschlagen, die eine gegenüber dem Stand der Technik größere Möglichkeit an Zeitpunkten zum Verstellen der Nockenwelle erlaubt und somit auch unterschiedliche Gruppierungen der Nocken von unterschiedlichen Ventilen bzw. Zylindern ermöglicht.The invention has for its object to propose an adjustable camshaft, which allows a greater possibility over the prior art at times for adjusting the camshaft and thus also allows different groupings of the cams of different valves or cylinders.

Die Aufgabe wird erfindungsgemäß dadurch gelöst, dass die Welle axial längs der Längsachse der Nockenwelle verschiebbar ausgestaltet ist, und dass mindestens ein Nockenpaket vorgesehen ist, welches fest mit der Welle verbunden ist, so dass über das Verstellelement und die Welle zumindest zwei unterschiedliche Nockenpakete unabhängig voneinander verstellbar sind.The object is achieved in that the shaft is designed to be axially displaceable along the longitudinal axis of the camshaft, and that at least one cam package is provided which is fixedly connected to the shaft, so that on the adjusting element and the shaft at least two different cam packages independently are adjustable.

Ein entsprechend breiter Nocken bzw. eine ausreichend breite Nockenkontur kann dazu dienen, dass ein Nockenpaket auch außerhalb des Grundkreises eines Nockens verschoben werden kann. Somit lassen sich auch Nocken oder Nockenpakete gruppieren, die z.B. gleichzeitig axial verschoben werden, auch dann, wenn ein Nocken gerade ein Ventil betätigt.A correspondingly wide cam or a sufficiently wide cam contour can serve to enable a cam package to be displaced outside the base circle of a cam. Thus, cams or cam packs, e.g. be moved axially at the same time, even if a cam is currently operating a valve.

Das Nockenpaket und das Verstellelement sind axial längs der Längsachse der Nockenwelle verschiebbar, so dass eine Verschiebung des Verstellelements ein Verschieben des Nockenpakets bewirkt, wodurch die unterschiedlichen Nocken oder Nockenkonturen des Nockenpakets oder ggf. der Nockenpakete in Kontakt mit den Ventilen gelangen.The cam package and the adjusting element are axially displaceable along the longitudinal axis of the camshaft, so that a displacement of the adjusting element, a displacement of the cam package causes, whereby the different cams or cam contours of the cam package or possibly the cam packages come into contact with the valves.

Da sowohl die Welle axial längs der Längsachse verschiebbar als auch ein axial verschiebbares Verstellelement vorgesehen ist, lassen sich zumindest zwei unterschiedliche Gruppen von Nockenpaketen bilden, welche unabhängig voneinander verstellt werden können. Das Nockenpaket, das fest mit der Welle verbunden ist, kann dabei ebenfalls gleiche oder unterschiedliche Breiten aufweisen.Since both the shaft axially displaceable along the longitudinal axis and an axially displaceable adjusting element is provided, at least two different groups of cam packages can be formed, which can be adjusted independently. The cam package, which is firmly connected to the shaft, can also have the same or different widths.

In einer Ausgestaltung ist das Verstellelement innerhalb der Welle angeordnet. Eine Ausgestaltung der Erfindung sieht vor, dass mehrere Nockenpakete vorgesehen und axial auf der Welle verschiebbar angeordnet sind, und dass mindestens zwei der Nockenpakete mechanisch mit dem Verstellelement gekoppelt sind. Eine Ausgestaltung der Erfindung beinhaltet, dass das Verstellelement radial um die Längsachse der Nockenwelle drehbar ausgestaltet ist. Mit dieser Ausgestaltung lässt sich somit noch die Winkelstellung und damit die Phase der Nocken zueinander einstellen. Eine Ausgestaltung der Erfindung sieht vor, dass mindestens eine Axialverstelleinheit vorgesehen ist, welche mit dem Verstellelement verbunden ist, und welche das Verstellelement zumindest abschnittsweise axial verschiebt. Eine Ausgestaltung der Erfindung beinhaltet, dass mehrere Verstellelemente vorgesehen sind, welche axial längs der Längsachse der Nockenwelle verschiebbar ausgestaltet sind. Durch eine Vielzahl von Verstellelementen lassen sich auch entsprechend viele Nockenpakete einzeln oder in Gruppen ansteuern und verschieben. Eine Ausgestaltung der Erfindung sieht vor, dass das Verstellelement als Vollzylinder oder als Rohr oder als Segment eines Zylinders oder als Segment eines Rohres oder als Blechteil ausgestaltet ist.In one embodiment, the adjusting element is arranged within the shaft. An embodiment of the invention provides that a plurality of cam packages are provided and arranged axially displaceable on the shaft, and that at least two of the cam packages mechanically with the Adjustment are coupled. An embodiment of the invention includes that the adjusting element is designed to be rotatable radially about the longitudinal axis of the camshaft. With this configuration, thus still the angular position and thus the phase of the cams can be adjusted to each other. An embodiment of the invention provides that at least one Axialverstelleinheit is provided, which is connected to the adjusting element, and which at least partially axially displaces the adjusting element. An embodiment of the invention includes that a plurality of adjusting elements are provided which are axially displaceable along the longitudinal axis of the camshaft. By a large number of adjusting elements, a corresponding number of cam packages can be controlled and shifted individually or in groups. An embodiment of the invention provides that the adjusting element is configured as a solid cylinder or as a pipe or as a segment of a cylinder or as a segment of a pipe or as a sheet metal part.

Die Erfindung wird anhand einiger in den Figuren dargestellter Ausführungsbeispiele näher erläutert. Dabei zeigen:

  • Fig. 1: einen Schnitt durch eine schematische Nockenwelle zu einem ersten Zeitpunkt,
  • Fig. 2: die Nockenwelle der Fig. 1 zu einem zweiten Zeitpunkt,
  • Fig. 3: die Nockenwelle der Fig. 1 zu einem dritten Zeitpunkt,
  • Fig. 4: die Nockenwelle der Fig. 1 zu einem vierten Zeitpunkt,
  • Fig. 5: eine räumliche Darstellung eines Nockens,
  • Fign. 6 a) bis c): Draufsichten auf drei Varianten einer Nut in der Welle,
  • Fig. 7: eine abgewickelte Laufbahn einer Axialverstelleinheit,
  • Fign. 8 a) und b): Schnitte durch zwei Varianten der Verbindung zwischen Verstellelement und Radialverdreheinheit,
  • Fign. 9 a), b) und c): drei Schnitte durch eine weitere Ausgestaltung der Nockenwelle,
  • Fig. 10: eine Draufsicht auf eine Welle mit zwei unterschiedlichen Nuten,
  • Fig. 11: einen Schnitt durch eine weitere Variante der Nockenwelle,
  • Fig. 12: einen Schnitt durch eine weitere Variante der Nockenwelle mit einer ersten Art der Verbindung zwischen Welle und Gehäuse,
  • Fig. 13: einen Schnitt durch eine zur Variante der Fig. 12 alternativen Ausgestaltung der Verbindung zwischen Welle und Gehäuse,
  • Fig. 14: einen Schnitt durch eine erfindungsgemäße Ausgestaltung der Nockenwelle,
  • Fign. 15 a) bis c): zwei Schnitte durch eine Ausgestaltung der Nockenwelle, sowie Draufsichten auf Abschnitte der Verstellelemente der ergänzenden Ausgestaltung,
  • Fig. 16: schematische räumliche Darstellung einer weiteren Variante des Verstellelements, und
  • Fign. 17 a) und b): zwei Schnitte durch mögliche Zustände für das radiale Verdrehen des Verstellelements der Fig. 16.
The invention will be explained in more detail with reference to some embodiments illustrated in the figures. Showing:
  • Fig. 1 FIG. 2: a section through a schematic camshaft at a first time, FIG.
  • Fig. 2 : the camshaft of the Fig. 1 at a second time,
  • Fig. 3 : the camshaft of the Fig. 1 at a third time,
  • Fig. 4 : the camshaft of the Fig. 1 at a fourth time,
  • Fig. 5 : a spatial representation of a cam,
  • FIGS. 6 a) to c) : Top views of three variants of a groove in the shaft,
  • Fig. 7 a developed track of an axial adjustment unit,
  • FIGS. 8 a) and b) : Sections through two variants of the connection between the adjusting element and the radial turning unit,
  • FIGS. 9 a), b) and c) three sections through a further embodiment of the camshaft,
  • Fig. 10 : a top view of a shaft with two different grooves,
  • Fig. 11 : a section through another variant of the camshaft,
  • Fig. 12 a section through a further variant of the camshaft with a first type of connection between shaft and housing,
  • Fig. 13 : a section through a variant of the Fig. 12 alternative embodiment of the connection between shaft and housing,
  • Fig. 14 : a section through an embodiment according to the invention of the camshaft,
  • FIGS. 15 a) to c) Two sections through an embodiment of the camshaft, and plan views of sections of the adjusting elements of the complementary embodiment,
  • Fig. 16 : schematic spatial representation of a further variant of the adjusting element, and
  • FIGS. 17 a) and b) Two cuts through possible conditions for the radial rotation of the adjustment of the Fig. 16 ,

In der Fig. 1 ist eine Nockenwelle 1 dargestellt, welche hier die Ventile von vier Zylindern steuern soll. Anwenden lässt sich die Erfindung auch bei Motoren mit einer anderen Anzahl an Zylindern. Jedem - hier nicht dargestellten - Zylinder sind dabei zwei Ventile zugeordnet: die Ventile des ersten Zylinders 101, des zweiten Zylinders 102, des dritten Zylinders 103 und des vierten Zylinders 104. Jeweils einem - hier jeweils links dargestellten - Ventil ist dabei ein Einzelnocken 8 auf der Nockenwelle 1 zugeordnet, welcher axial fest auf der Welle 3 aufgebracht ist. Für das jeweils andere Ventil - hier jeweils rechts dargestellt - ist ein Nockenpaket 2 vorgesehen, welches insbesondere eine Änderung des Ventilhubs ermöglicht. In einer weiteren - hier nicht dargestellten - Variante lassen sich jeweils beide Ventile eines Zylinders unterschiedlich durch eine Veränderung der Nocken ansteuern. Dargestellt ist hier beispielweise die Nockenwelle 1 für die Einlassventile der Zylinder. Entsprechend kann eine solche Nockenwelle 1 auch für die Auslassventile Anwendung finden. Die Nockenpakete 2 verfügen jeweils über einen Schlitten 20, welcher axial auf der Welle 3 entlang der - hier strichpunktiert eingezeichneten - Längsachse verschiebbar ist. Auf demIn the Fig. 1 is a camshaft 1 is shown, which is here to control the valves of four cylinders. The invention can also be applied to engines with a different number of cylinders. Each cylinder - not shown here - two valves are associated with it: the valves of the first cylinder 101, the second cylinder 102, the third cylinder 103 and the fourth cylinder 104. In each case one - here each left shown - valve is a single cam 8 on associated with the camshaft 1, which is axially fixedly mounted on the shaft 3. For each other valve - shown here on the right - a cam package 2 is provided, which in particular allows a change in the valve lift. In another variant (not shown here), both valves of a cylinder can be controlled differently by changing the cams. Shown here is, for example, the camshaft 1 for the intake valves of the cylinder. Accordingly, such a camshaft 1 can also be used for the exhaust valves. The cam packages 2 each have a slide 20, which is axially displaceable on the shaft 3 along the longitudinal axis - shown here in dash-dotted lines. On the

Schlitten 20 befinden sich in dieser Ausgestaltung ein erster Nocken 21 und ein zweiter Nocken 22. Die Nocken 21, 22 unterscheiden sich hinsichtlich ihres Außenprofils, beispielsweise in der Höhe der den Nocken bildenden Erhebung oder Nase, welche den Ventilhub bestimmt (siehe in Fig. 5 das Beispiel für den ersten Nocken 21 mit Nase 21.1). Alternativ oder ergänzend haben die Nocken 21, 22 einen unterschiedlichen Verlauf. In einer weiteren Ausgestaltung ist mindestens ein Nocken ein einteiliger Bestandteil des Schlittens 20, d.h. der Schlitten 20 kann auch selbst eine solche Nockenkontur aufweisen. Damit die unterschiedlichen Nocken 21, 22 der Nockenpakete 2 bzw. die damit einhergehenden unterschiedlichen Ansteuerungsprofile in Eingriff mit den jeweiligen Ventilen gelangen, ist der axial verschiebbare Schlitten 20 über ein Kontaktelement 5, bei welchem es sich beispielsweise um einen Stift handelt, mit einem Verstellelement 4 in der hohl ausgestalteten Welle 3 verbunden. Für die Kontaktelemente 5 sind jeweils Aussparungen 30, z.B. Nuten in der Welle 3 vorgesehen. In diesem Fall reichen die Kontaktelemente 5 vollständig durch das Verstellelement 4 bzw. die Welle 3 hindurch. Da das Verstellelement 4 selbst axial verschiebbar ausgestaltet ist, können die Nockenpakete 2 axial verschoben werden, d.h. es kann eine Ventilansteuerung mit dem ersten Nocken 21 oder mit dem zweiten Nocken 22 verursacht werden. Das Verstellelement 4 ist beispielsweise eine Vollwelle, welche ggf. aus einem Kunststoff oder aus einem Verbundmaterial besteht. Die Nockenwelle 1 wird z.B. von der- hier nicht dargestellten - Kurbelwelle angetrieben. Das Drehmoment wird dabei - in dem hier gezeigten Beispiel - aufgeteilt und zum einen über die außen liegende Welle 3 und den darauf fest angebrachten Einzelnocken 8 und zum anderen über das Verstellelement 4 und die Kontaktelemente 5 übertragen. Für eine koaxiale Anordnung des Verstellelements 4 in der Welle 3 ist beispielsweise eine entsprechende Lagerung des Verstellelements 4 in der Welle 3 vorgesehen oder es findet eine entsprechende Verstiftung statt. In der vorliegenden Abbildung Fig. 1 werden gleichzeitig die Nockenpakete 2 der Ventile des zweiten 102 und des vierten Zylinders 104 verschoben. In alternativen Ausgestaltungen lassen sich auch weniger oder mehr Nockenpakete 2 entsprechend gruppieren. Die Nocken 21, 22 der Nockenpakete 2 weisen unterschiedliche Breiten auf. Bei den Nockenpaketen 2 für den zweiten und vierten Zylinder ist jeweils der erste Nocken 21 schmäler als der zweite Nocken 22. Umgekehrt ist bei den Nockenpaketen 2 des ersten und dritten Zylinders der erste Nocken 21 breiter als der zweite Nocken 22. Durch die größere Breite des ersten Nockens 21 kann somit beispielsweise für das Ventil des ersten Zylinders 101 die Verstellung vorgenommen werden, auch wenn das Ventil des ersten Zylinders 101 gerade außerhalb des Grundkreises läuft, d.h. wenn der Nocken das Ventil z.B. über einen Schlepphebel gegen eine Feder drückt und somit die Öffnung des Ventils verursacht. Erst wenn das Verstellelement 4 weiter verschoben wird, d.h. über die Breite des Nockens hinaus, findet auch die Umstellung der Nocken für die Ventile des ersten 101 und dritten Zylinders 103 statt. Die Umstellung eines Nockenpakets vom einen zum anderen Nocken erfolgt jeweils auf dem Grundkreis, d.h. wenn die Nocken des zugeordneten Nockenpakets nicht das zugehörige Ventil betätigen, jedoch während der Zeit, in der ein Nocken eines anderen Nockenpakets ein Ventil betätigt, d.h. außerhalb des Grundkreises für diese andere Nocken-Ventil-Kombination. Die Anordnung der breiteren bzw. schmäleren Nocken bezieht sich hier nur auf den dargestellten Beispielfall und kann entsprechend für die Bedürfnisse des Motors bzw. der Art der Ansteuerung der Zylinder angepasst werden. Wird das Drehmoment beispielsweise - in einer hier nicht dargestellten Realisierung - nur von der außen liegenden Welle 3 übertragen, so kann über das Verstellelement 4 noch ein Verdrehen erfolgen, so dass auch eine Phasenänderung möglich ist. Zur radialen Änderung - relativ zu Kurbelwelle und/oder relativ der Nocken zueinander - ist eine Radialverdreheinheit 7 vorgesehen. Die axiale Verschiebung des Verstellelements 4 wird - in diesem Beispiel - durch die Axialverstelleinheit 6 bewerkstelligt, in welche zwei Aktoren 60 über passende Laufbahnen eingreifen, so dass eine lineare Bewegung der Aktoren 60 senkrecht zur Längsachse des Verstellelements 4 eine axiale Verschiebung des Verstellelements 4 in Richtung der Längsachse bewirkt. Der hier - zeichnerisch - linke Aktor 60 erzeugt durch die Laufbahn eine Bewegung nach links und der rechte Aktor 60 die Bewegung zurück. Durch die gestrichelte und vom Aktor 60 ausgehende Linie sei dabei in dieser und in den folgenden Abbildungen angedeutet, an welcher Stelle der Laufbahn der Aktor 60 gerade angreift. Alternativ ist es auch möglich, über die Radialverdreheinheit 7 eine radiale Verdrehung der Nockenpakete 2 zu den fest auf der Welle 3 angebrachten Einzelnocken 8 zu realisieren. Die Anordnung und Ausgestaltung des Verstellelements 4 ist dabei unabhängig von den unterschiedlich breiten Nocken 21, 22 der Nockenpakete 2. Entsprechend lassen sich auch die unterschiedlich breiten Nocken 21, 22 und die damit einhergehende Möglichkeit der Verschiebung außerhalb des Grundkreises mit anderen Realisierungen der Verstellung kombinieren. Dies gilt auch für die folgenden Beispiele. Gleichwohl stellt die Kombination der hier besonders ausgestalteten Nockenpakete mit der hier bereits gezeigten und den noch folgenden Varianten der Verstellung eine Optimierung der Verstellung dar. In der Fig. 1 ist der zeitliche Abschnitt dargestellt, wie - hier bei der einlassseitigen Nockenwelle (entsprechendes lässt sich auch für andere Nockenwellen realisieren) - eine Ventilabschaltung jeweils eines Ventils des zweiten und vierten Zylinders eingeleitet wird. Dabei wird das Verstellelement 4 soweit axial verschoben, dass jeweils ein Ventil 102, 104 nicht mehr mit dem ersten Nocken 21, sondern mit dem zweiten Nocken 22 in Kontakt kommt. Der - hier zeichnerisch - linke Aktor 60 befindet sich dabei im hier gezeigten Beispiel am Anfang der die axiale Verschiebung bewirkenden Bahn. Der zweite Nocken 22 ist für die dargestellte Variante derartig ausgestaltet, dass er eine Abschaltung des zugehörigen Ventils bewirkt, indem das Ventil nur noch auf dem Grundkreis des - nase- oder spitzelosen - Nockens 22 läuft und somit nicht betätigt wird. Die Abbildung Fig. 2 zeigt den Zustand, dass jeweils ein Ventil des zweiten 102 und der vierten Zylinders 104 abgeschaltet ist - sie stehen jeweils in Verbindung mit dem zweiten Nocken 22 - und dass ebenfalls je ein Ventil des ersten 101 und dritten Zylinders 103 abgeschaltet werden soll. Wie zu sehen, haben sich die Welle 3 und das Verstellelement 4 um 90° gedreht, so dass nun auch die Nuten 30 mit den Kontaktelementen 5 zu erkennen sind. Die Kontaktelemente 5 verfügen in den Nuten 30 über keinen radialen Freiraum, welcher ein Verdrehen um die Längsachse der Nockenwelle 3 erlauben würde. Andere Ausgestaltungen der Nuten 30 werden im folgenden besprochen. Alternativ sind weiterhin auch andere Winkel außer dem 90°-Winkel möglich. Dies ist abhängig von der Ansteuerung der Ventile bzw. der erforderlichen Variante der Verstellung der Nockenwelle 1. Wie angedeutet, befindet sich der Aktor 60 an einem anderen Bereich der Laufbahn in der Axialverstelleinheit 6. Von der Nockenwelle 1 werden in diesem Zustand die Ventile des dritten Zylinders 103 angesteuert, d.h. in diesem Moment findet noch keine Verstellung der Nocken für die Ventile des ersten 101 und dritten Zylinders 103 statt. Dies wird dadurch realisiert, dass nach dem Zustand der Fig. 1 das Verstellelement 4 während des hier dargestellten Moments nicht axial verschoben wird. In der Fig. 3 haben sich Welle 3 und Verstellelement 4 weiter um 90° gedreht. Das Verstellelement 4 ist dabei noch auf der gleichen axialen Position wie in der Fig. 2. Wie zu erkennen, werden jetzt die Ventile des vierten Zylinders 104 von der Nockenwelle 1 angesteuert, wobei ein Ventil nicht betätigt wird. Insbesondere betätigt der fest auf der Welle 3 angebrachte Einzelnocken 8 das - hier zeichnerisch - linke Ventil des vierten Zylinders 104, wobei das rechte Ventil des vierten Zylinders 104 über den zweiten Nocken 22 des Nockenpakets 2 auf dem Grundkreis läuft und somit quasi durch einen Null-Hub gesteuert wird. In der Fig. 4 gab es relativ zum in der Fig. 3 dargestellten Zustand eine weitere 90°-Drehung und das Verstellelement 4 ist axial soweit verschoben, dass die entsprechenden Ventile des ersten Zylinders 101 und des dritten Zylinders 103 in Kontakt mit dem schmäleren zweiten Nocken 22 des jeweilig zugeordneten Nockenpaketes 2 kommen. Dies bedeutet in diesem Beispiel, dass auch die Ventile des ersten 101 und dritten Zylinders 103 bedingt durch die Außenkontur des zweiten Nockens 22 der zugehörigen Nockenpakete 2 abgeschaltet sind, indem sie auf dem Grundkreis, sozusagen mit einem Hub von Null laufen. Der Aktor 60 ist nun auch am Ende der Laufbahn angekommen und ein weiteres axiales Verschieben des Verstellelements 4 findet nicht mehr statt.Carriage 20 are in this embodiment, a first cam 21 and a second cam 22. The cams 21, 22 differ in terms their outer profile, for example, at the height of the cam-forming elevation or nose, which determines the valve lift (see Fig. 5 the example of the first cam 21 with nose 21.1). Alternatively or additionally, the cams 21, 22 have a different course. In a further embodiment, at least one cam is a one-piece component of the carriage 20, that is, the carriage 20 may itself also have such a cam contour. In order for the different cams 21, 22 of the cam packages 2 or the different drive profiles associated therewith to engage with the respective valves, the axially displaceable carriage 20 is connected to an adjusting element 4 via a contact element 5, which is, for example, a pin connected in the hollow shaft 3 designed. For the contact elements 5 each recesses 30, eg grooves in the shaft 3 are provided. In this case, the contact elements 5 extend completely through the adjusting element 4 or the shaft 3. Since the adjusting element 4 itself is designed to be axially displaceable, the cam packs 2 can be displaced axially, ie valve activation with the first cam 21 or with the second cam 22 can be caused. The adjusting element 4 is for example a solid shaft, which optionally consists of a plastic or a composite material. The camshaft 1 is driven, for example, by the crankshaft, not shown here. The torque is - in the example shown here - split and transmitted on the one hand on the outer shaft 3 and the fixed thereto single cam 8 and the other via the adjusting element 4 and the contact elements 5. For a coaxial arrangement of the adjusting element 4 in the shaft 3, for example, a corresponding mounting of the adjusting element 4 is provided in the shaft 3 or there is a corresponding pinning instead. In the present illustration Fig. 1 At the same time the cam packages 2 of the valves of the second 102 and the fourth cylinder 104 are moved. In alternative embodiments, fewer or more cam packages 2 can be grouped accordingly. The cams 21, 22 of the cam packages 2 have different widths. at The first cam 21 is narrower than the second cam 22 in the cam packets 2 of the first and third cylinders. Conversely, in the cam packets 2 of the first and third cylinders, the first cam 21 is wider than the second cam 22. Due to the greater width of the first cam Cam 21 can thus be made for example for the valve of the first cylinder 101, the adjustment, even if the valve of the first cylinder 101 just outside the base circle runs, ie when the cam presses the valve, for example via a cam follower against a spring and thus the opening of Valve causes. Only when the adjusting element 4 is moved further, that is, beyond the width of the cam also, the conversion of the cam for the valves of the first 101 and third cylinder 103 takes place. The conversion of a cam package from one cam to the other takes place respectively on the base circle, ie when the cams of the associated cam set do not actuate the associated valve, but during the time in which a cam of another cam set actuates a valve, ie outside the base circle for this other cam-valve combination. The arrangement of the wider or narrower cams here refers only to the illustrated example and can be adapted according to the needs of the engine or the type of control of the cylinder. If the torque is transmitted, for example - in a realization, not shown here - only from the outer shaft 3, so can be done on the adjusting element 4 still twisting, so that a phase change is possible. For radial change - relative to the crankshaft and / or relative to the cams to each other - a Radialverdrehheinheit 7 is provided. The axial displacement of the adjusting element 4 is accomplished - in this example - by the Axialverstelleinheit 6, in which two actuators 60 engage on matching raceways, so that a linear movement of the actuators 60 perpendicular to the longitudinal axis of the adjusting element 4, an axial displacement of the adjusting element 4 in the direction causes the longitudinal axis. The here - graphically - left actuator 60 generated by the track movement left and the right actuator 60 the movement back. By the dashed and outgoing from the actuator 60 line is indicated in this and in the following figures, at which point of the career of the actuator 60 just attacks. Alternatively, it is also possible, via the Radialverdreheinheit 7 to realize a radial rotation of the cam packages 2 to the fixedly mounted on the shaft 3 single cam 8. The arrangement and configuration of the adjusting element 4 is independent of the differently wide cam 21, 22 of the cam packages 2. Accordingly, the different width cam 21, 22 and the associated possibility of displacement outside the base circle with other implementations of the adjustment can be combined. This also applies to the following examples. Nevertheless, the combination of the here particularly designed cam packages with the already shown here and the following variants of the adjustment is an optimization of the adjustment. In the Fig. 1 is the temporal section shown how - here at the inlet side camshaft (the same can be realized for other camshafts) - a valve shutdown of each valve of the second and fourth cylinder is initiated. In this case, the adjusting element 4 is displaced axially so far that in each case a valve 102, 104 no longer comes into contact with the first cam 21, but with the second cam 22. The - here drawing - left actuator 60 is in the example shown here at the beginning of the axial displacement causing path. The second cam 22 is designed for the illustrated variant such that it causes a shutdown of the associated valve by the valve only runs on the base circle of the - nase- or spy-less - cam 22 and thus is not operated. The illustration Fig. 2 shows the state that a valve of the second 102 and the fourth cylinder 104 is turned off - they are respectively in communication with the second cam 22 - and that also one valve of the first 101 and third cylinder 103 is to be turned off. As can be seen, the shaft 3 and the adjusting element 4 have rotated by 90 °, so that now also the grooves 30 with the contact elements 5 to recognize. The contact elements 5 have no radial clearance in the grooves 30, which would allow rotation about the longitudinal axis of the camshaft 3. Other configurations of the grooves 30 will be discussed below. Alternatively, other angles other than the 90 ° angle are still possible. This is dependent on the control of the valves or the required variant of the adjustment of the camshaft 1. As indicated, the actuator 60 is located at another area of the track in the Axialverstelleinheit 6. From the camshaft 1 in this state, the valves of the third Cylinder 103 controlled, ie at this moment finds no adjustment of the cam for the valves of the first 101 and third cylinder 103 instead. This is realized by the condition of the Fig. 1 the adjusting element 4 is not displaced axially during the moment shown here. In the Fig. 3 have wave 3 and adjusting 4 further rotated by 90 °. The adjusting element 4 is still at the same axial position as in the Fig. 2 , As can be seen, now the valves of the fourth cylinder 104 are driven by the camshaft 1, wherein a valve is not actuated. In particular, the individual cam 8 fixedly mounted on the shaft 3 actuates the left-hand valve of the fourth cylinder 104, with the right-hand valve of the fourth cylinder 104 running over the second cam 22 of the cam assembly 2 on the base circle and thus, as it were, by a neutral position. Hub is controlled. In the Fig. 4 there was relative to in the Fig. 3 shown state another 90 ° rotation and the adjusting element 4 is axially displaced so far that the corresponding valves of the first cylinder 101 and the third cylinder 103 come into contact with the narrower second cam 22 of the respective associated cam package 2. This means in this example that the valves of the first 101 and third cylinder 103 are shut down due to the outer contour of the second cam 22 of the associated cam packages 2 by running on the base circle, so to say with a zero stroke. The actuator 60 is now at the end of the career arrived and a further axial displacement of the adjusting element 4 no longer takes place.

In der Fig. 5 ist als Beispiel ein erster Nocken 21 dargestellt, wie er auf einen Schlitten eines Nockenpakets aufgebracht wird. In einer alternativen - nicht dargestellten - Ausgestaltung handelt es sich um einen hohlen Nocken, welcher im Wesentlichen nur eine Außenkontur und eine Befestigungsfläche für den Schlitten aufweist. In einer weiteren Ausgestaltung ist der Nocken ein Bestandteil des Schlittens selbst. Zu sehen sind der Grundkreis und die Nase oder Spitze 21.1.In the Fig. 5 By way of example, a first cam 21 is shown as applied to a carriage of a cam pack. In an alternative embodiment - not shown - is a hollow cam, which has substantially only an outer contour and a mounting surface for the carriage. In a further embodiment, the cam is a component of the carriage itself. The base circle and the nose or tip 21.1 are shown.

In der Fig. 6 sind drei Varianten a) bis c) für die Ausgestaltung einer Nut 30 in der Welle 3 dargestellt. In der ersten Variante Fig. 6 a) kann das Drehmoment über die Nut 30 oder über die Innenwelle übertragen werden. In der Ausgestaltung der Fig. 6 b) ist die Nut 30 schräg und das Kontaktelement wird in den Endpositionen fixiert. Die S-förmige Ausgestaltung der Fig. 6 c) erlaubt ebenfalls eine Fixierung des Kontaktelements an den Endpunkten der axialen Bewegung.In the Fig. 6 are three variants a) to c) shown for the configuration of a groove 30 in the shaft 3. In the first variant Fig. 6 a) the torque can be transmitted via the groove 30 or via the inner shaft. In the embodiment of Fig. 6b) the groove 30 is inclined and the contact element is fixed in the end positions. The S-shaped configuration of Fig. 6c) also allows a fixation of the contact element at the end points of the axial movement.

Die Fig. 7 verdeutlicht eine mögliche Laufbahn, über welche ein Aktor das Verstellelement axial um eine Strecke X1 bzw. in umgekehrter Richtung um X2 verschiebt. Dargestellt ist hier die abgewickelte 360°-Außenfläche z.B. eines Rades als Teil der Axialverstelleinheit. Dabei finden im Wesentlichen zwei Verschiebungen statt, welche im obigen Beispiel der Figuren 1 bis 4 zunächst eine Abschaltung der Ventile des zweiten und vierten Zylinders und dann der Ventile des ersten und dritten Zylinders bewirken (Abschnitte a). Zwischen diesen beiden Abschaltungen ist ein Abschnitt (in der Figur Abschnitt b) vorgesehen, welcher keine axiale Verschiebung des Verstellelements bewirkt. Die beiden dargestellten Laufbahnen sind hier passend zu der Anordnung der Aktoren der Figuren Fig. 1 bis 4 spiegelsymmetrisch zueinander ausgestaltet, wobei eine Laufbahn das Verschieben in die eine und die andere Laufbahn die Verschiebung zurück bewirkt. Die spiegelsymmetrische Ausgestaltung resultiert hier daraus, dass die Aktoren nebeneinander angeordnet sind. Die Form der Laufbahnen ist somit auch davon abhängig, wie die Axialverstelleinheit ausgestaltet ist bzw. wie die Aktoren angeordnet sind und die Verschiebung einleiten. Die insgesamt vier Abschnitte a, b entsprechen hier jeweils einem Winkelmaß von 90°, entsprechend der Darstellung der Figuren 1 bis 4. Andere Winkel sind jedoch insbesondere bei anderen Zylinderzahlen auch möglich. In einer Ausgestaltung sind dabei die beiden Winkel für das Verschieben der Nocken - jeweils Abschnitte a - und die beiden Winkel, während dessen keine Verschiebung stattfindet - bezeichnet mit b -, jeweils gleich und unterschiedliche zueinander. Die Anzahl der Winkel und deren Größen hängt dabei auch von der Anzahl der Verschiebungen, d.h. von der Anzahl der betroffenen Nockenpakete ab.The Fig. 7 illustrates a possible career, over which an actuator shifts the adjustment axially by a distance X1 and in the reverse direction to X2. Shown here is the unwound 360 ° -Außenfläche eg a wheel as part of Axialverstelleinheit. Essentially, two shifts take place, which in the above example the FIGS. 1 to 4 Initially cause a shutdown of the valves of the second and fourth cylinders and then the valves of the first and third cylinders (sections a). Between these two shutdowns, a portion (in the figure section b) is provided, which causes no axial displacement of the adjusting element. The two illustrated raceways are here to match the arrangement of the actuators of the figures Fig. 1 to 4 designed mirror-symmetrically to each other, wherein a raceway causes the displacement in one and the other career, the shift back. The mirror-symmetrical design results here from the fact that the actuators are arranged side by side. The shape of the raceways is therefore also dependent on how the Axialverstelleinheit is configured or how the actuators are arranged and initiate the shift. The four sections a, b correspond here in each case to an angular extent of 90 °, corresponding to the representation of FIGS. 1 to 4 , However, other angles are also possible, especially with other cylinder numbers. In one embodiment, the two angles for the displacement of the cams - in each case sections a - and the two angles during which no displacement takes place - denoted by b -, in each case the same and different from each other. The number of angles and their sizes also depends on the number of shifts, ie on the number of affected cam packages.

In den Abbildungen Fig. 8 a) und b) sind zwei Varianten für die Ausgestaltung der Radialverdreheinheit 7 dargestellt. Die Radialverdreheinheit 7 ist dabei mit dem Verstellelement 4 verbunden und erlaubt dessen Verdrehen gegenüber der äußeren Welle 3 und dadurch die Änderung der Phase der Nocken. Die beiden Varianten unterscheiden sich hinsichtlich der Umsetzung eines Längenausgleiches, welches durch das axiale Verschieben des Verstellelements 4 notwendig ist. In der Variante der Fig. 8 a) ist ein spezielles Element für diesen Ausgleich vorgesehen, wohingegen in der Variante der Fig. 8 b) der Ausgleich über eine Innen- und eine Außenverzahnung von zwei Teilelementen des Verstellelements 4 erfolgt. Alternativ können auch Kugeln verwendet werden, welche in Rillen zwischen den ineinander befindlichen Abschnitten der Elemente laufen und entsprechend z.B. einem Längenausgleichselement bei Gelenkwellen funktionieren.In the pictures Fig. 8 a) and b) two variants for the design of the radial twisting unit 7 are shown. The Radialverdreheinheit 7 is connected to the adjusting element 4 and allows its rotation relative to the outer shaft 3 and thereby changing the phase of the cam. The two variants differ with regard to the implementation of a length compensation, which is necessary by the axial displacement of the adjusting element 4. In the variant of Fig. 8 a) a special element is provided for this compensation, whereas in the variant of Fig. 8b) the compensation takes place via an inner and an outer toothing of two partial elements of the adjusting element 4. Alternatively, it is also possible to use balls which run in grooves between the sections of the elements which are located inside one another and function correspondingly, for example, in a length compensation element in drive shafts.

In der Fig. 9 a) ist ein Teil einer Nockenwelle mit zwei benachbarten Nockenpaketen 2 dargestellt, welche beide eine Hub- (unterschiedliche Nockenkontur des ersten 21 und des zweiten Nockens 22) und eine Phasenänderung (Verdrehung um die Längsachse der Welle 3) erlauben. In den Abbildungen Fig. 9 b) und Fig. 9 c) sind zwei Schnitte durch die Welle 3 auf unterschiedlichen Positionen dargestellt. Die Ausgestaltungen in der Welle 3 ermöglichen zum einen eine axiale Führung des Kontaktelements 5 und gleichzeitig noch eine radiale Beweglichkeit und zum anderen nur eine axiale Führung, d.h. radial fest. Die Fig. 10 zeigt einen Teil einer Nockenwelle, deren Welle 3 zwei unterschiedliche Nuten 30 für die Kontaktelemente 5 aufweist. Bei der links dargestellten Variante ist nur eine axiale Verschiebung möglich, und die - hier auf der Darstellung - rechts befindliche Nut erlaubt zusätzlich ein radiales Verdrehen, da das Kontaktelement 5 seitlich Platz in der Nut 30 hat.In the Fig. 9 a) is a part of a camshaft with two adjacent cam packages 2 shown, both of which a lifting (different Cam contour of the first 21 and the second cam 22) and a phase change (rotation about the longitudinal axis of the shaft 3) allow. In the pictures Fig. 9b) and Fig. 9c) two sections through the shaft 3 are shown in different positions. The embodiments in the shaft 3 allow for an axial guidance of the contact element 5 and at the same time still a radial mobility and on the other hand only an axial guidance, ie radially fixed. The Fig. 10 shows a part of a camshaft whose shaft 3 has two different grooves 30 for the contact elements 5. In the variant shown on the left, only an axial displacement is possible, and the - here on the representation - right-side groove additionally allows a radial rotation, since the contact element 5 laterally has place in the groove 30.

Die Nockenwelle 1 der Fig. 11 erlaubt das Schalten von drei unterschiedlichen Konturen, indem jedes Nockenpaket 2 drei unterschiedliche Nocken aufweist: erster Nocken 21, zweiter Nocken 22 und dritter Nocken 23. Somit lassen sich drei unterschiedliche Profile für die Ansteuerung der Ventile anwenden. Die unterschiedlichen Ventilhübe sind hier an den unterschiedlichen Höhen der Nocken des Nockenpakets 2 für das Ventil des ersten Zylinders 101 zu erkennen. Um das Verschieben der drei unterschiedlichen Nocken 21, 22, 23 zu ermöglichen, weist die Axialverstelleinheit 6 hier auch schematisch jeweils zwei Laufbahnen auf, so dass eine Verschiebung von der ersten 21 zur zweiten 22 und von der zweiten 22 zur dritten Nocke 23 möglich ist. Für das Zurückschieben sind entsprechend auch zwei - hier spiegelsymmetrisch ausgestaltete - Laufbahnen vorgesehen. Pro Ventil können auch jeweils unterschiedliche Anzahlen von Nocken bzw. Nockenkonturen vorgesehen sein.The camshaft 1 of Fig. 11 allows the switching of three different contours by each cam package 2 has three different cams: first cam 21, second cam 22 and third cam 23. Thus, three different profiles for the control of the valves can be applied. The different valve strokes can be seen here at the different heights of the cams of the cam package 2 for the valve of the first cylinder 101. In order to enable the shifting of the three different cams 21, 22, 23, the axial adjustment unit 6 here also schematically has two raceways each, so that a displacement from the first 21 to the second 22 and from the second 22 to the third cam 23 is possible. For the pushing back accordingly two - here mirror-symmetrically designed - raceways are provided. Per valve also different numbers of cams or cam contours can be provided.

Bei der Nockenwelle 1 der Fig. 12 bilden die Welle 3 und das Verstellelement 4 eine Einheit, die axial verschiebbar ausgestaltet und angeordnet ist und welche auch der Übertragung des Drehmomentes dient. In dieser Ausgestaltung sind daher die Nockenpakete 2' fest auf der Welle 3 bzw. auf dem Verstellelement 4 aufgebracht. Die Nockenpakete 2' treten in dieser Darstellung jeweils in Kontakt mit einem Rollenstößel, wobei für jeden Zylinder zwei Rollenstößel für die jeweils zwei Ventile vorgesehen sind: die Rollenstößel des ersten Zylinders 111, die Rollenstößel des zweiten Zylinders 112, die Rollenstößel des dritten Zylinders 113 und die Rollenstößel des vierten Zylinders 114. Weiterhin sind die Lager 120 eingezeichnet, auf welchen die Nockenwelle 1 im eingebauten Zustand ruht. Die Welle 3 bzw. das Verstellelement 4 wird über die Axialverstelleinheit 6 und die Aktoren 60 axial verschoben (angedeutet durch den Doppelpfeil). Da die Nockenpakete 2' fest auf der Welle 3 aufgebracht sind, kommen somit auch die Rollenstößel 111, 112, 113 und 114 in Kontakt mit den unterschiedlichen Nocken 20, 21 bzw. Nockenkonturen der Pakete 2'. Die Nockenpakete 2' können dabei - wie hier dargestellt- aus einzelnen Nocken 20, 21 bestehen, es kann sich aber auch um eine Einheit mit entsprechend unterschiedlichen Nockenkonturen handeln. Zusätzlich ist eine Radialverdreheinheit 7 vorgesehen, um die Welle 3 radial um ihre Längsachse für die Einstellung der Phase der Nocken zu drehen. Für die Übertragung des Drehmomentes, welches beispielsweise im eingebauten Zustand von der Kurbelwelle kommt, ist hier ein Gehäuse 131 vorgesehen, in welchem z.B. über die Verzahnung axial beweglich ein Stopfen 130 angeordnet ist. Der Stopfen 130 selbst wiederum ist drehfest, z.B. über Übermaßpassung mit der Welle 3 verbunden. Alternativ erfolgt die Axialverstellung zwischen Stopfen 130 und Gehäuse 131 in Folge der axialen Verschiebung der Welle 3 durch eine entsprechende Innenverzahnung. Das Gehäuse 131 ist dabei axial gelagert. Die Nockenwelle 1 der Fig. 13 unterscheidet sich dadurch von der Variante der Fig. 12, dass die Welle 3 direkt mit dem Gehäuse 131 z.B. über eine entsprechende Verzahnung, welche die axiale Verschiebung erlaubt, gekoppelt ist. Eine Axialverstellung ist hier ebenfalls möglich durch Kugeln, welche sich in Laufbahnen zwischen der Welle 3 und dem Gehäuse 131 befinden.In the camshaft 1 of Fig. 12 the shaft 3 and the adjusting element 4 form a unit which is axially displaceable configured and arranged and which also serves to transmit the torque. In this Design are therefore the cam packages 2 'firmly applied to the shaft 3 and on the adjusting element 4. The cam packages 2 'in this representation each come into contact with a roller tappet, wherein two roller tappets are provided for the respective two valves for each cylinder: the roller tappets of the first cylinder 111, the roller tappets of the second cylinder 112, the roller tappets of the third cylinder 113 and the roller tappet of the fourth cylinder 114. Furthermore, the bearings 120 are shown, on which the camshaft 1 rests in the installed state. The shaft 3 and the adjusting element 4 is axially displaced via the Axialverstelleinheit 6 and the actuators 60 (indicated by the double arrow). Since the cam packages 2 'are fixedly mounted on the shaft 3, the roller tappets 111, 112, 113 and 114 thus also come into contact with the different cams 20, 21 or cam contours of the packages 2'. The cam packages 2 'can - as shown here - consist of individual cams 20, 21, but it can also be a unit with correspondingly different cam contours. In addition, a radial twisting unit 7 is provided to rotate the shaft 3 radially about its longitudinal axis for adjusting the phase of the cams. For the transmission of the torque, which comes for example in the installed state of the crankshaft, here a housing 131 is provided, in which, for example via the teeth axially movable plug 130 is arranged. The plug 130, in turn, is non-rotatable, eg connected to the shaft 3 via interference fit. Alternatively, the axial adjustment between plug 130 and housing 131 takes place as a result of the axial displacement of the shaft 3 by a corresponding internal toothing. The housing 131 is mounted axially. The camshaft 1 of Fig. 13 differs thereby from the variant of Fig. 12 in that the shaft 3 is coupled directly to the housing 131, for example via a corresponding toothing, which allows the axial displacement. An axial adjustment is also possible here by means of balls, which are located in raceways between the shaft 3 and the housing 131.

Die Varianten der Nockenwelle 1 der Figuren Fig. 12 und Fig. 13 erlauben nur die Verschiebung alle Nockenpakete 2' gleichzeitig, da alle Nockenpakete 2' fest mit der Welle 3 bzw. mit dem mit der Welle 3 identischen Verstellelement 4 verbunden sind. Das Verschieben während ein Nocken ein Ventil betätigt, d.h. außerhalb des Grundkreises, ist dabei bedingt durch die unterschiedlich breiten Nocken 21, 22 möglich. Die Varianten der Fig. 1 bis 4 und Fig. 11 erlauben es weiterhin durch das Verstellelement 4 in Verbindung mit der Welle 3, dass nicht alle Nockenpakete verschoben werden, da die Nockenpakete mit dem in diesen Ausgestaltungen von der Welle 3 unterschiedlichen Verstellelement 4 fest verbunden sind. Diese Möglichkeit, dass einzelne Nocken nicht verschoben werden, erlaubt z.B. bei der Variante der Fig. 1 die Verwendung eines Einzelnockens 8, welcher nicht verändert wird. Die Variante der Fig. 14 ermöglicht es, beide Ventile jedes Zylinders mit unterschiedlichen Kombinationen von Nockenkonturen zu steuern. Hierfür ist jeweils ein Nockenpaket 2' für ein Ventil mit der Welle 3 und ein Nockenpaket 2 über das Kontaktelement 5 durch die Nut 30 mit dem Verstellelement 4 verbunden. Es werden somit zwei getrennte Systeme für das Verstellen der Nockenwelle 1 verwendet. Das Verstellelement 4 wird dabei von der Axialverstelleinheit 6 und den Aktoren 60 axial verschoben und das Rohr 3 von der Zusatzaxialverstelleinheit 9 mit den ihr zugeordneten Aktoren 90. Um weiterhin eine Radialverdreheinheit 7 am anderen Ende der Nockenwelle 1 und somit die radiale Verdrehung der Nocken zueinander zu ermöglichen, ist die Zusatzaxialverstelleinheit 9 hier in diesem dargestellten Beispiel seitlich angebracht. Auch in diesem Beispiel möge - die hier nicht dargestellte - Kurbelwelle z.B. über eine - hier ebenfalls nicht dargestellte - Kette die Nockenwelle 1 antreiben. Die Nockenpakete 2, welche mit dem Verstellelement 4 verschoben werden, sind in dieser Ausgestaltung jeweils eine Einheit, welche entsprechend zwei unterschiedliche Nockenkonturen aufweist. Das Verstellen eines Nockens während der Betätigung des zugehörigen Ventils durch den Nocken wird ebenfalls durch die passend breite Nockenkontur ermöglicht.The variants of the camshaft 1 of the figures Fig. 12 and Fig. 13 allow only the displacement of all cam packages 2 'at the same time, since all cam packages 2' are fixedly connected to the shaft 3 and with the adjusting element 4 identical to the shaft 3. The displacement while a cam actuates a valve, ie outside the base circle, is due to the different width cam 21, 22 possible. The variants of Fig. 1 to 4 and Fig. 11 allow it further by the adjusting element 4 in conjunction with the shaft 3, that not all cam packages are moved because the cam packages are firmly connected to the different in these embodiments of the shaft 3 adjustment 4. This possibility that individual cams are not moved allows, for example, in the variant of Fig. 1 the use of a single cam 8, which is not changed. The variant of Fig. 14 makes it possible to control both valves of each cylinder with different combinations of cam contours. For this purpose, in each case a cam package 2 'for a valve with the shaft 3 and a cam package 2 via the contact element 5 through the groove 30 with the adjusting element 4 is connected. Thus, two separate systems for adjusting the camshaft 1 are used. The adjusting element 4 is axially displaced by the Axialverstelleinheit 6 and the actuators 60 and the tube 3 of the Zusatzaxialverstelleinheit 9 with its associated actuators 90. In order to continue a Radialverdreheinheit 7 at the other end of the camshaft 1 and thus the radial rotation of the cams to each other allow, the Zusatzaxialverstelleinheit 9 is mounted laterally in this example shown here. Also in this example may - the crankshaft, not shown here - drive the camshaft 1, for example via a - also not shown here - chain. The cam packages 2, which are displaced with the adjusting element 4, are each a unit in this embodiment, which correspondingly has two different cam contours. The adjustment of a cam during actuation of the associated valve by the cam is also made possible by the appropriately wide cam contour.

In der Fig. 15 a) ist ein Abschnitt einer weiteren Variante der Nockenwelle 1 dargestellt. Hierbei ist es möglich, vier beispielsweise unterschiedlich große Gruppen an Nockenpaketen 2 zu bilden, welche jeweils gleichzeitig verstellt werden. In der Welle 3 befinden sich für diesen Zweck vier Verstellelemente 4, welche jeweils über Kontaktelemente 5 mit den einzelnen Nockenpaketen 2 verbunden sind. Die einzelnen Verstellelemente 4 sind dabei z.B. in Form von übereinander angeordneten Trägerstreifen ausgestaltet, wie z.B. in der Fig. 15b) gezeigt. Die Welle 3 weist dafür beispielsweise einen rechteckigen freien Bereich in ihrem Inneren auf, an dessen Längsseiten sich jeweils mindestens ein Schlitz oder allgemein eine Aussparung für die Kontaktelemente 5, welche auch hier beispielsweise als Stifte ausgestaltet sind, anschließt. Alternativ befinden sich in einer vollständig hohlen Welle 3 unterschiedliche Fixierelemente, welche die beschriebene Innenkontur aufweisen oder sonst für eine Führung sorgen. Für das Verschieben der Nockenpakete 2, die hier auf der Welle 3 axial verschiebbar angeordnet sind, weisen die Verstellelemente 4 Nuten 40 auf. Für den Ausschnitt der Fig. 15 a) sind in der Fig. 15 c) die einzelnen Verstellelemente 4 nebeneinander angeordnet. Für die dargestellten zwei Nockenpakete 2 sind zwei Kontaktelemente 5 - hier auf dem obersten und dem untersten Verschiebeelement 4 - vorgesehen, welche an unterschiedlichen axialen Positionen liegen. Da die Kontaktelemente 5 vollständig durch die Welle 3 und somit durch alle Verstellelemente 4 hindurchragen, weisen die beiden anderen Verstellelemente 4 auf der Höhe der Kontaktelemente 5 jeweils Nuten 40 auf, welche das axiale Verschieben der anderen Elemente erlauben. Somit können die einzelnen Verstellelemente 4 einzeln axial versetzt werden. Alternativ lassen sich über die Nuten der Verstellelemente 40, d.h. über deren Ausgestaltung und Anordnung, auch die axialen Bewegungen der einzelnen Verstellelemente 4 miteinander koppeln. Da es in dieser Variante möglich ist, einzelne Nockenpakete 2 gezielt zu verschieben, ist es z.B. auch nicht erforderlich, dass die einzelnen Nocken unterschiedliche Breiten aufweisen, da die Verschiebung vorzugsweise auf dem Grundkreis vorgenommen werden kann. Eine Kombination ist jedoch auch möglich, um ggf. besondere Anforderungen für das Verstellen der Nockenwelle 1 zu erfüllen. Mit der hier gezeigten Variante lassen sich vier Gruppen an Nockenpaketen bilden oder es lassen sich auch nur einzelne Nockenpakete gesondert ansteuern. Eine andere Anzahl von Gruppen ist auch möglich, wobei ggf. die Anzahl der einzelnen hier flach ausgestalteten Verstellelemente 4 zu verringern oder zu erhöhen ist. Die Variante der Verstellelemente 4 der Fig. 15 lässt sich passend auch mit den obigen Varianten kombinieren, wenn z.B. ein Ventil gesondert, die anderen jedoch gruppenweise verschoben werden sollen. Alternativ oder ergänzend zu den blech- oder streifenartigen Verstellelementen 4 können auch Rohre z.B. teleskopartig ineinander angeordnet sein. Die Realisierung von mehreren Gruppen von gleichzeitig betätigten Nockenpaketen erlaubt auch das Verstellelement 4 der Fig. 16. Innerhalb der Welle 3 ist hier ein Verstellelement 4 vorgesehen, welches aus - in diesem Beispiel - vier Segmenten besteht, welche einzeln axial verschiebbar sind.In the Fig. 15 a) a section of a further variant of the camshaft 1 is shown. It is possible to form four, for example, different sized groups of cam packages 2, which are each adjusted simultaneously. In the shaft 3 are for this purpose four adjusting elements 4, which are each connected via contact elements 5 with the individual cam packages 2. The individual adjusting elements 4 are configured, for example, in the form of superimposed carrier strips, such as in the Fig. 15b ). The shaft 3 has, for example, a rectangular free area in its interior, at the longitudinal sides in each case at least one slot or generally a recess for the contact elements 5, which are also configured here as pins, for example. Alternatively located in a completely hollow shaft 3 different fixing elements, which have the described inner contour or otherwise provide a guide. For the displacement of the cam packages 2, which are arranged here axially displaceable on the shaft 3, the adjusting elements 4 have grooves 40. For the excerpt of Fig. 15 a) are in the Fig. 15c) the individual adjusting elements 4 arranged side by side. For the illustrated two cam packages 2, two contact elements 5 - here on the uppermost and the lowest displacement element 4 - are provided which lie at different axial positions. Since the contact elements 5 project completely through the shaft 3 and thus through all adjusting elements 4, the two other adjusting elements 4 at the height of the contact elements 5 each have grooves 40 which allow the axial displacement of the other elements. Thus, the individual adjusting elements 4 can be individually offset axially. Alternatively, the axial movements of the individual adjusting elements 4 can be coupled to one another via the grooves of the adjusting elements 40, ie via their configuration and arrangement. Since it is possible in this variant to move individual cam packages 2 targeted, it is not necessary, for example, that the individual cams have different widths, since the shift is preferably on the base circle can be made. However, a combination is also possible to meet any special requirements for the adjustment of the camshaft 1. With the variant shown here, four groups of cam packages can be formed or only individual cam packages can be controlled separately. A different number of groups is also possible, where appropriate, the number of individual here designed flat adjusting elements 4 is to be increased or increased. The variant of the adjusting 4 of the Fig. 15 can be suitably combined with the above variants, if, for example, a valve separately, but the others are to be moved in groups. Alternatively or in addition to the sheet-metal or strip-like adjustment elements 4, pipes can also be arranged telescopically, for example. The realization of several groups of simultaneously actuated cam packages also allows the adjusting element 4 of Fig. 16 , Within the shaft 3, an adjusting element 4 is provided here, which consists of - in this example - four segments, which are individually axially displaceable.

Ein mögliches radiales Verdrehen der einzelnen Segmente und damit der jeweils damit verbundenen Nockenpakete zeigen die Abbildungen Fig. 17 a) und b). Dabei lassen sich - in der dargestellten Konfiguration - jeweils zwei einander gegenüberliegende Segmente radial zueinander verstellen, indem zwischen den benachbarten Segmenten ein Freiraum besteht, in welchen - in dieser Ausgestaltung - ein Fixierelement 10 eingebracht wird. Die Anzahl der Segmente lässt sich entsprechend den Bedürfnissen bzw. der Anzahl der Zylinder anpassen.A possible radial rotation of the individual segments and thus the respectively associated cam packages show the pictures Fig. 17 a) and b). In this case - in the illustrated configuration - each two opposing segments can be adjusted radially to each other by a space between the adjacent segments, in which - in this embodiment - a fixing element 10 is introduced. The number of segments can be adjusted according to the needs or the number of cylinders.

Claims (6)

  1. Adjustable cam shaft (1),
    with at least one shaft (3),
    and
    with at least one cam package (2), which has at least two
    different cams (21, 22) and/or cam contours,
    whereby the cams (21, 22) and/or the cam contours of the cam package have (2) different widths,
    whereby the cam package (2) is designed to be movable axially along one longitudinal axis of the cam shaft (1),
    whereby at least one adjustment element (4) which is designed to be movable axially along the longitudinal axis is provided for,
    and
    whereby the adjustment element (4) is mechanically coupled with the cam package (2) by at least one contact element (5),
    characterised in
    that the shaft (3) is designed to be movable axially along the
    longitudinal axis of the cam shaft (1),
    and
    that at least one cam package (2') which is firmly connected to the shaft (3) is provided for,
    so that at least two different cam packages (2, 2') are adjustable independently of one another
    via the adjustment element (4) and the shaft (3).
  2. Cam shaft in accordance with claim 1,
    characterised in
    that several cam packages (2) are provided for and arranged to be moved axially on the shaft (3),
    and that at least two of the cam packages (2) are mechanically coupled with the adjustment element (4).
  3. Cam shaft (1) in accordance with claim 1 or 2,
    characterised in
    that the adjustment element (4) is designed to be rotated radially around the longitudinal axis of the cam shaft (1).
  4. Cam shaft in accordance with one of the claims 1 to 3,
    characterised in
    that at least one axial adjustment unit (6) which is connected to the adjustment element (4) is provided for, and which slides the adjustment element (4) axially at least in sections.
  5. Cam shaft in accordance with one of the claims 1 to 4,
    characterised in
    that several adjustment elements (4), which are designed to be movable axially along the longitudinal axis of the cam shaft (1), are provided for.
  6. Cam shaft (1) in accordance with one of the claims 1 to 5,
    characterised in
    that the adjustment element (4) is designed as a full cylinder or as a pipe or as a segment of a cylinder or as a segment of a pipe or as a sheet metal part.
EP11758091.0A 2010-06-25 2011-06-11 Adjustable camshaft Active EP2585687B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102010025100A DE102010025100A1 (en) 2010-06-25 2010-06-25 Adjustable camshaft
PCT/DE2011/001205 WO2012006992A1 (en) 2010-06-25 2011-06-11 Adjustable camshaft

Publications (2)

Publication Number Publication Date
EP2585687A1 EP2585687A1 (en) 2013-05-01
EP2585687B1 true EP2585687B1 (en) 2014-09-03

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP11758091.0A Active EP2585687B1 (en) 2010-06-25 2011-06-11 Adjustable camshaft

Country Status (4)

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US (1) US8695547B2 (en)
EP (1) EP2585687B1 (en)
DE (1) DE102010025100A1 (en)
WO (1) WO2012006992A1 (en)

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US12031460B2 (en) 2020-08-12 2024-07-09 Thyssenkrupp Dynamic Components Gmbh Sliding cam system

Also Published As

Publication number Publication date
US8695547B2 (en) 2014-04-15
EP2585687A1 (en) 2013-05-01
US20130104824A1 (en) 2013-05-02
WO2012006992A1 (en) 2012-01-19
DE102010025100A1 (en) 2011-12-29

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