EP2585687A1

EP2585687A1 - Adjustable camshaft

Info

Publication number: EP2585687A1
Application number: EP11758091.0A
Authority: EP
Inventors: Roman Weinmeister
Original assignee: Neumayer Tekfor Holding GmbH
Current assignee: Neumayer Tekfor Holding GmbH
Priority date: 2010-06-25
Filing date: 2011-06-11
Publication date: 2013-05-01
Anticipated expiration: 2031-06-11
Also published as: US8695547B2; EP2585687B1; DE102010025100A1; US20130104824A1; WO2012006992A1

Abstract

The invention relates to an adjustable camshaft, having at least one shaft and having at least one cam pack which has at least two different cams and/or cam contours. The invention provides that the cams and/or the cam contours of the cam pack are of different widths.

Description

Adjustable camshaft

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.

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 movement in longitudinal movements, whereby the inputs and

Outlet valves of the engine are controlled. In order to control the engine optimally depending on the load condition, there are in the prior art

Adjustments of camshafts, e.g. which bring different cams into operative engagement with the valves or adjust the settings, e.g. change the angles of the cams to each other. The publication WO 2010/040439 A1 describes a valve drive device in which a device mounted outside the camshaft displaces individual ones

Cam pairs or groups of cam pairs allowed, so that the different cam contours of the cam pairs serve the valve control. 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. 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, ie when the cams do not operate 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 is larger than the prior art

Possibility at times for adjusting the camshaft allowed and thus also allows different groupings of the cams of different valves or cylinders.

The task is inventively achieved in that the cams and / or the cam contours of the cam package have different widths. 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.

An embodiment of the invention provides that the cam package is axially displaceable along a longitudinal axis of the cam. A

Embodiment of the invention includes that at least one adjusting element is provided, which is designed axially displaceable along the longitudinal axis, and that the adjusting element is mechanically coupled via at least one contact element with the cam package. In this embodiment, an adjusting element is thus provided, which is connected to at least one cam package on the shaft. 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 causes a displacement of the cam package, whereby the different cams or cam contours of the cam package or possibly the cam packages come into contact with the valves. In one embodiment, the adjusting element is arranged within the shaft. An embodiment of the invention is that several

Cam 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 shaft is axially displaceable along the longitudinal axis of the camshaft. In this embodiment, the shaft itself is axial

displaceable. By connected to the shaft cam or cam packages can then change the control of individual valves by the displacement of the shaft. If both the shaft can be displaced axially along the longitudinal axis and an axially displaceable adjusting element is provided, then at least two different groups of cam packages can be formed, which can be adjusted independently of one another. A

Embodiment of the invention provides that at least one individual cam and / or a cam package is provided, which is fixedly connected to the shaft The cam package can also be the same or

have different widths. An embodiment of the invention beinhattet that the adjusting element radially around the longitudinal axis of the

Camshaft is configured rotatable. 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. Through a variety of

Adjustment elements can also control and move a corresponding number of cam packages individually or in groups. An embodiment of

The invention provides that the adjusting element is designed as Votlzylinder or as a pipe or as a segment of a cylinder or as a segment of a pipe or as a sheet metal part.

The invention will be illustrated with reference to some in the figures

Embodiments explained in more detail. Showing: 1 shows a section through a schematic camshaft according to the invention at a first time,

2: the camshaft of Fig. 1 at a second time,

FIG. 3 shows the camshaft of FIG. 1 at a third time, FIG. 4 shows the camshaft of FIG. 1 at a fourth time, FIG. 5 shows a spatial representation of a cam,

FIGS. 6 a) to c): plan 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,

10 is a plan view of a shaft with two different grooves,

11 shows a section through a further variant of the camshaft,

12 shows a section through a further variant of the camshaft with a first type of connection between shaft and housing,

13 shows a section through an alternative to the variant of FIG. 12

Design of the connection between shaft and housing, 14 shows a section through an additional embodiment of the camshaft,

FIGS. 15 a) to c): two sections through a supplementary embodiment of the camshaft, as well as plan views of sections of the adjusting elements of the supplementary embodiment,

FIG. 16: schematic spatial representation of a further variant of the adjusting element, and FIGS. 17 a) and b): two sections through possible states for the radial rotation of the adjusting element of FIG. 16.

In Fig. 1, a camshaft 1 according to the invention is shown, which is to control the valves of four cylinders here. 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), in each case both valves of a cylinder can be controlled differently by changing the cams according to the invention. 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, in the amount of the cam-forming elevation or nose, which determines the valve lift (see in 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, i. the carriage 20 may also have such a cam contour itself. 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, recesses 30, e.g. Grooves provided in the shaft 3. In this case, the

Contact elements 5 completely through the adjustment 4 and the shaft 3 therethrough. Since the adjusting element 4 itself is designed axially displaceable, the cam packages 2 can be displaced axially, i. It may be a valve control with the first cam 21 or the second cam 22 are 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 e.g. from the - not shown - driven crankshaft. 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, the cam packages 2 of the valves of the second 102 and fourth cylinders 104 are displaced simultaneously. 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 cam packages 2 for the second and fourth cylinders, respectively, the first cam 21 is narrower than the second cam 22. Conversely, in the

Cam lobes 2 of the first and third cylinders of the first cam 21 wider than the second cam 22. Due to the greater width of the first cam 21 can thus, for example, for the valve of the first cylinder 101, the

Adjustment be made, even if the valve of the first cylinder 101 just outside the base circle runs, i. if the cam is the valve e.g. pushes against a spring via a rocker arm and thus causes the opening of the valve. Only when the adjusting element 4 is moved further, i. beyond the width of the cam also takes place, the conversion of the cams for the valves of the first 101 and third cylinder 03 instead. The conversion of a cam package from one to the other cam is carried out in each case on the base circle, i. if the cams of the associated cam package do not actuate the associated valve, but during the time that a cam of another cam package actuates a valve, i. 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. For example, if the torque is - not in one here

shown implementation - only transmitted from the outer shaft 3, it 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 cam to each other - is a

Radial twisting unit 7 is provided. The axial displacement of the

Adjustment 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 causes in the direction of 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 a radial rotation of the cam packages 2 to the fixed on the shaft. 3

attached single cam 8 to realize. The arrangement and

Design of the adjusting element 4 is independent of the

Accordingly, the differently wide cams 21, 22 and the associated possibility of displacement outside the base circle can be combined with other implementations of the adjustment. 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 Fig. 1, the temporal portion is shown as - here at the

inlet-side camshaft (the same can also be realized for other cam times) - a valve deactivation of a respective 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. 2 shows the state that one valve of the second 102 and the fourth cylinder 104 is switched off - they are in each case in connection with the second cam 22 - and that also a valve of the first 101 and third cylinder 103 are turned off should. 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 in the grooves 30 via no radial clearance, which is a rotation about the longitudinal axis of the

Camshaft 3 would allow. 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, the valves of the third cylinder 103 are driven in this state, i. At this moment, no adjustment of the cams for the valves of the first 101 and third cylinder 103 takes place. This is realized in that after the state of Fig. 1, the adjusting element 4 is not displaced axially during the moment shown here. In Fig. 3, shaft 3 and adjusting 4 have further rotated by 90 °. The adjusting element 4 is still in the same axial position as in Fig. 2. As can be seen, now the valves of the fourth cylinder 104 of the

Camshaft 1 driven, 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 Fig. 4 there were relative to the state shown in FIG. 3, a further 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 in contact with the narrower second Cam 22 of the respective associated cam package 2 come. This means in this example that the valves of the first 101 and third cylinder 103 are shut down due to the Au enkontur 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 Fig. 5 is shown as an example a first cam 21, as it is applied to a carriage of a cam package. 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.

FIG. 6 shows three variants a) to c) for the embodiment 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. 6 b), the groove 30 is inclined and the contact element is fixed in the end positions. The S-shaped embodiment of Fig. 6 c) also allows a fixation of the contact element at the end points of the axial movement. 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. In this case, essentially two shifts take place, which in the above example of FIGS. 1 to 4, as an exemplary implementation of the possibilities of the invention, initially shuts off 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 raceways shown are here designed to match the arrangement of the actuators of the figures Fig. 1 to 4 mirror-symmetrical 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 tracks 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 here correspond in each case to an angular extent of 90 °, corresponding to the representation of FIGS. 1 to 4. However, other angles are particularly applicable to others

Number of cylinders also possible. 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, i. from the number of affected cam packages.

FIGS. 8 a) and b) show two variants of the embodiment of the radial twisting unit 7. 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 by the axial displacement of the

Adjustment element 4 is necessary. In the variant of FIG. 8 a), a special element for this compensation is provided, whereas in the variant of FIG. 8 b) the compensation takes place via an inner and an outer toothing of two partial elements of the adjusting element 4. Alternatively, balls may also be used which run in grooves between the intermeshing sections of the elements and, correspondingly e.g. one

Length compensation element for cardan shafts work. In Fig. 9 a) is a part of a camshaft with two adjacent

Cam packages 2 shown, which both a lifting (different Cam contour of the first 21 and the second cam 22) and a

Allow phase change (rotation about the longitudinal axis of the shaft 3). In FIGS. 9 b) and 9 c), two sections through the shaft 3 are shown at 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, i. radially fixed. 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. 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.

In the case of the camshaft 1 of FIG. 12, the shaft 3 and the adjusting element 4 form a unit which is designed and arranged to be axially displaceable 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. In this illustration, the cam packages 2 * each come into contact with a roller tappet, wherein two roller tappets for the two valves are provided for each cylinder: the

Roller tappet of the first cylinder 11 1, the roller tappet of the second cylinder 1 12, the roller tappet of the third cylinder 1 13 and the roller tappet of the fourth cylinder 1 14. Furthermore, the bearings 120 are drawn 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, thus also come the roller tappets 1 1 1, 1 12, 1 13 and 114 in contact with the different cams 20, 21 and cam contours of the packets 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 a plug 130 is arranged. The plug 130 itself is non-rotatable, e.g. connected via interference fit with the shaft 3. Alternatively, the

Axial adjustment between plug 130 and housing 131 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 from the variant of FIG. 12, 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 FIGS. 12 and 13 allow only the displacement of all the cam packages 2 'simultaneously, since all the cam packages 2' are firmly connected to the shaft 3 or to 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 FIGS. 1 to 4 and FIG. 11 furthermore allow the adjusting element 4 in conjunction with the shaft 3 to prevent all the cam packs from being displaced, since the cam packs differ from the shaft 3 in this embodiment

Adjustment 4 are firmly connected. This possibility that individual

Cams can not be displaced, allowed e.g. 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 thereby of the

Axialverstelleinheit 6 and the actuators 60 axially displaced and the tube 3 of the Zusatzaxialverstelleinheit 9 with its associated actuators 90. In order to further allow a Radialverdreheinheit 7 at the other end of the camshaft 1 and thus the radial rotation of the cams to each other, the Zusatzaxialverstelleinheit 9 here laterally mounted in this illustrated example. Also in this example, let the crankshaft, not shown here, be e.g. via a - not shown here - chain drive the camshaft 1. The cam packages 2, which with the

Adjustment 4 are moved, in this embodiment, in each case one unit, which has two different cam contours accordingly. 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 Fig. 15 a), a portion 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, as shown for example in FIG. 15 b). 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, there are 3 different ones in a completely hollow shaft

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, have the

Adjustment 4 grooves 40 on. For the section of FIG. 15 a), the individual adjusting elements 4 are arranged side by side in FIG. 15 c). 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 the 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 elements 4 of 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 adjusting elements 4 and pipes can eg

be telescopically arranged one inside the other. The realization of several groups of simultaneously actuated cam packages also allows this

Adjusting element 4 of Fig. 16. Within the shaft 3 is here

Adjustment element 4 is provided, which consists of - in this example - four segments which are individually axially displaceable.

A possible radial rotation of the individual segments and thus the respective associated cam packages show the figures 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

claims

1. Adjustable camshaft,

with at least one wave,

and

with at least one cam package, which at least two

has different cams and / or cam contours,

characterized,

that the cams and / or the cam contours of the cam package

have different widths.

2. Camshaft according to claim 1,

characterized,

in that the cam assembly is designed to be displaceable axially along a longitudinal axis of the camshaft.

3. Camshaft according to claim 2,

characterized,

that at least one adjusting element is provided, which is designed to be displaceable axially along the longitudinal axis,

and

that the adjusting element via at least one contact element with the

Cam package is mechanically coupled.

4. Camshaft according to claim 3,

characterized,

that a plurality of cam packs are provided and are arranged axially displaceable on the shaft,

and

in that at least two of the cam packages are mechanically coupled to the adjusting element.

5. Camshaft according to one of claims 1 to 4,

characterized,

that the shaft is axially displaceable along the longitudinal axis of the camshaft.

6. Camshaft according to one of claims 1 to 5,

characterized,

that at least one individual cam and / or a cam package is provided, which is firmly connected to the shaft.

7. Camshaft according to one of claims 3 to 6,

characterized,

that the adjustment element is designed to be rotatable radially about the longitudinal axis of the camshaft.

8. Camshaft according to one of claims 3 to 7,

characterized,

that at least one Axialverstelleinheit is provided, which is connected to the adjusting element, and which at least partially axially displaces the adjusting element.

9. Camshaft according to one of claims 3 to 8,

characterized,

that a plurality of adjusting elements are provided, which are axially displaceable along the longitudinal axis of the camshaft.

10. Camshaft according to one of claims 3 to 9,

characterized,

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.