DE102020214554A1 - sliding cam arrangement - Google Patents

Abstract

Sliding cam arrangement, comprising a supporting shaft (1) with a longitudinal axis (L) and at least one sliding cam (2) received on the supporting shaft (1) in a rotationally fixed and axially displaceable manner, the sliding cam arrangement being equipped with a latching device (3) which is set up to releasably fixing the slide cam (2) in a first axial position and at least one second axial position, the slide cam assembly being provided with a braking device (4) adapted to brake the axial movement of the slide cam (2).

Description

The present invention relates to a slide cam assembly according to the preamble of claim 1.

A sliding cam arrangement is known in the art, for example according to US Pat DE102017219287A1 , DE102009048621A1 , W02009/152927A1 , DE102012210922A1 famous.

the DE102017219287A1 shows a valve train comprising a carrier shaft with external teeth, a sliding cam piece with internal teeth, which is arranged slidably in an axial direction on the carrier shaft, the internal teeth of the sliding cam piece engaging in the external teeth of the carrier camshaft, and a locking device for axially securing the sliding cam piece on the Support shaft, wherein the detent device exerts a radial force on the sliding cam piece. The valve train further includes a biasing device which exerts a radial force on the shift cam piece that is at least three times greater than the detent device.

The bracing device has a ball-spring combination in the carrier shaft, which interacts with an inner running surface in the sliding cam and serves to increase the relative speed of the sliding cam piece and the carrier shaft when the system is changed in the toothing with the aid of radial bracing between the carrier camshaft and the sliding cam piece reduce in order to prevent or reduce the acoustic impulse.

The inner running surface in the sliding cam for the ball of the bracing device has no braking flanks / braking contours for axial catching after the shifting process of the sliding cam. Furthermore, the inner running surface, in particular the base of the groove, does not have any shaping design that is intended to influence the friction and braking force, so that the friction between the ball of the tensioning device and the inner running surface, in particular the base of the groove of the sliding cam piece, is described as negligible. The sliding cam is caught axially via an axial stop surface in the hood or on the bearing of the sliding cam.

the DE102009048621A1 describes a valve train in the form of a sliding cam system of an internal combustion engine with at least one rotatable support shaft having external teeth, and at least one sliding cam having complementary internal teeth cooperating with the external teeth and which can be displaced axially on the support shaft between at least two displacement positions spaced apart from one another . So that disturbing noises caused by contact changes in the toothing can be avoided at least in some of the operating states of the internal combustion engine or the corresponding displacement positions of the sliding cams, it is provided that the support shaft and the sliding cam have cooperating means in the form of a spring-ball detent, which in at least one Shift position allow an uninterrupted mutual pressing of opposing tooth flanks of the external and internal teeth. Furthermore, the DE102009048621A1 an embodiment of the valve train in which a further spring ball detent is provided in the sliding cam. In order to ensure a defined position of the sliding cam after axial displacement in its end positions, opposite end faces of the bearing block form stops against which an inner end face of the adjacent sliding cam rests in each of the two end positions.

the WO2009/152927A1 shows a valve train in the form of a slide cam system with a support shaft and a slide cam piece, the slide cam system having a first ball and spring assembly which is provided for axially locking the slide cam piece. For this purpose, the first ball-spring assembly exerts a force in the radial direction, ie a radial force, on the sliding cam piece. Furthermore, the sliding cam system includes a second ball-spring assembly, which also exerts a force in the radial direction, ie a radial force, on the cam piece. The radial force of the first ball and spring assembly has almost the same magnitude as the radial force of the second ball and spring assembly. The second ball-spring package serves to prevent the sliding cam piece from being skewed relative to the carrier shaft, in order to avoid a noise-generating banging of an unsupported part of the sliding cam when a cam runs onto the roller rocker arm of the associated gas exchange valve that interacts with the cam. The axial stop takes place via the end faces of the respective bearings.

the DE102012210922A1 shows a locking device in the carrier shaft, two axially directly adjacent bores, each with a ball or taper pin locking mechanism, are applied, with locking recesses complementary to the locking mechanism being arranged in an inner casing of the sliding cam piece with the same axial distance as the bores and with the locking recesses being present in a number, which is exactly one number greater than the number of Ver sliding positions of the sliding cam piece. Significantly higher latching and frictional forces can be achieved due to the double latching in one length section of the assembly.

In the case of sliding cams, in particular in the case of double sliding cams without an axial stop, the known spring-ball detents in the case of sliding cams with greater mass and/or small displacement angle ranges and/or large displacement paths, in particular double sliding cams or sliding cams in the heavy-duty area, lead to a shifting speed at higher switching speeds axial overshoot of the cam after completion of the switching process. The aim is to keep the axial overshoot and the cam angle-related overshoot angle low in systems without an axial stop, so that the cam does not come into a critical area in relation to the rocker arm.

Known shift cam arrangements do not offer satisfactory solutions to the problem outlined above, so it is an object of the present invention to provide an improved shift cam arrangement, in particular to provide a shift cam arrangement in which overshooting of the cam after the end of the shifting process is significantly reduced and for use in a compatible area is.

According to the invention, this object is achieved by a sliding cam arrangement having the characterizing features of claim 1. Because the sliding cam arrangement is equipped with a braking device that is set up to brake the axial movement of the sliding cam, the disadvantages outlined above can be prevented, or at least reduced. In particular, a camshaft arrangement can be provided in which overshooting of the cam after the end of the shifting process is significantly reduced and is within a tolerable range for the application. In other words, the use of a braking device, in particular a second, spring-loaded element, is proposed, which does not serve to lock the position, but only contributes to increasing the friction and braking force. Oscillation of an actuator pin in the displacement gate, in particular between the leading edge and the trailing edge, can advantageously also be reduced.

Further advantageous refinements of the proposed invention result in particular from the features of the dependent claims. The objects or features of the various claims can in principle be combined with one another as desired.

In a further advantageous embodiment of the invention it can be provided that the braking device comprises a ball-spring combination and a braking groove.

In a further advantageous embodiment of the invention, it can be provided that the ball-spring combination comprises a spring and a ball, which are accommodated in a radially aligned opening in the support shaft. The advantage would be in the use of the same parts with regard to the locking device, if it is assumed that the locking device also includes a ball.

In a further advantageous embodiment of the invention it can be provided that the braking device comprises a cylinder-roller-spring combination and a braking groove.

In a further advantageous embodiment of the invention, it can be provided that the cylinder-roller-spring combination includes a spring and a cylinder roller, which are accommodated in a radially aligned opening in the support shaft. An advantage would be the line contact between the cylindrical roller and the brake groove, especially the bottom of the brake groove.

In a further advantageous embodiment of the invention, it can be provided that the braking groove is designed as an axially aligned groove in the sliding cam and has a braking groove bottom.

In a further advantageous embodiment of the invention, it can be provided that the brake groove base in the axial direction relative to the longitudinal axis has a first area with a sloping brake groove base, a second area with a flat/concave/convex/convex-concave-convex brake groove base and a third area with a rising Bremsnutboden. Different configurations, in particular a concave or convex brake groove base in the second area, can be used to create areas with a higher or lower braking effect. In other words, in particular the amount of the braking effect can be influenced or adjusted as a function of the axial position of the sliding cam.

In a further advantageous embodiment of the invention, it can be provided that the bottom of the brake groove is inclined at between 30° and 60° to the longitudinal axis in the first area and the third area.

In a further advantageous embodiment of the invention it can be provided that the Bremsnutboden is aligned parallel to the longitudinal axis in the second region.

In a further advantageous embodiment of the invention, it can be provided that the braking device is set up so that the braking effect only comes about, or at least to the technically desired extent, when the sliding cam overshoots by 0.01mm-1mm, in particular 0.01mm-0.3mm.

In a further advantageous embodiment of the invention, it can be provided that an offset of 0.01 mm - 1 mm is provided between the ball or the cylindrical roller of the braking device and the first area of the braking groove when the locking device is in a first locking position and/or that an offset of 0.01mm - 1mm is provided between the ball or the cylindrical roller of the braking device and the third area of the braking groove when the locking device is in a second locking position.

In a further advantageous embodiment of the invention, it can be provided that the braking groove and the latching recess are designed differently, in particular that the braking groove is designed axially longer than the latching recess.

In a further advantageous embodiment of the invention it can be provided that the latching device and the braking device are arranged at axially different positions of the sliding cam arrangement.

In a further advantageous embodiment of the invention it can be provided that the latching device and the braking device are arranged radially opposite one another. The advantage here is that the bore in the support shaft is only required once and thus weakening of the support shaft is reduced by only requiring a notch in the support shaft. Furthermore, the processing steps such as hardening / milling / drilling are reduced, which has a beneficial effect on the manufacturing costs. Furthermore, there is a reduction in the required components (spring).

In a further advantageous embodiment of the invention it can be provided that the sliding cam has at least one cam arrangement with a first cam and at least one second cam, the cams preferably differing in terms of their cam contour. With the different cam contours, correspondingly different modulations of the controlled valve can be carried out. More cam arrangements, for example four cam arrangements per sliding cam, can preferably also be provided, so that a number of cylinders or the inlet and outlet valves can be controlled at the same time with one sliding cam.

• 1 eine erfindungsgemäße Schiebenockenanordnung in einer teilweise geschnittenen perspektivischen Ansicht;
• 2 eine erfindungsgemäße Schiebenockenanordnung in einer geschnittenen perspektivischen Ansicht (erste Position);
• 2a eine erfindungsgemäße Schiebenockenanordnung in einer geschnittenen perspektivischen Ansicht (zweite Position);
• 3 eine erfindungsgemäße Schiebenockenanordnung in einer teilweise geschnittenen seitlichen Ansicht;
• 3a ein Schnitt X-X gemäß 3;
• 4 eine erfindungsgemäße Schiebenockenanordnung in einer geschnittenen seitlichen Ansicht mit einer Kugel-Feder-Kombination als Bremsvorrichtung;
• 4a ein Schnitt Y-Y gemäß 4;
• 5 eine erfindungsgemäße Schiebenockenanordnung in einer geschnittenen seitlichen Ansicht mit einer Zylinderrollen-Feder-Kombination als Bremsvorrichtung;
• 5a ein Schnitt Z-Z gemäß 5;
• 6 ein Detail einer erfindungsgemäßen Schiebenockenanordnung (ebener zweiter Bereich);
• 7 ein Detail einer erfindungsgemäßen Schiebenockenanordnung (konkaver zweiter Bereich);
• 8 ein Detail einer erfindungsgemäßen Schiebenockenanordnung (Konvex -konkav - konvexer zweiter Bereich);
• 9 ein Detail einer erfindungsgemäßen Schiebenockenanordnung;
• 10 ein Detail einer erfindungsgemäßen Schiebenockenanordnung;
• 11 ein Detail vergrößert einer erfindungsgemäßen Schiebenockenanordnung;
• 12 eine alternative Variante der erfindungsgemäßen Schiebenockenanordnung in einer geschnittenen seitlichen Ansicht.

Further features and advantages of the present invention become clear from the following description of preferred exemplary embodiments with reference to the attached figures. show in it

• 1 a sliding cam assembly according to the invention in a partially sectioned perspective view;
• 2 a sliding cam arrangement according to the invention in a sectional perspective view (first position);
• 2a a sliding cam assembly according to the invention in a sectional perspective view (second position);
• 3 a sliding cam assembly according to the invention in a partially sectioned side view;
• 3a a cut XX according to 3 ;
• 4 a sliding cam assembly according to the invention in a sectional side view with a ball-spring combination as a braking device;
• 4a a section YY according to 4 ;
• 5 a sliding cam assembly according to the invention in a sectional side view with a cylinder roller spring combination as a braking device;
• 5a a section according to ZZ 5 ;
• 6 a detail of a sliding cam arrangement according to the invention (flat second area);
• 7 a detail of a sliding cam arrangement according to the invention (concave second area);
• 8th a detail of a sliding cam arrangement according to the invention (convex - concave - convex second area);
• 9 a detail of a sliding cam arrangement according to the invention;
• 10 a detail of a sliding cam arrangement according to the invention;
• 11 a detail enlarged of a sliding cam arrangement according to the invention;
• 12 an alternative variant of the sliding cam arrangement according to the invention in a sectional side view.

L

Tragwellenlängsachse

R

Rastierungskontur

K

Bremskontur

V

Versatz

A

erster Bereich (Bremsnute)

B

zweiter Bereich (Bremsnute)

C

dritter Bereich (Bremsnute)

1

Tragwelle

2

Schiebenocken

3

Rastvorrichtung

4

Bremsvorrichtung

11

Schiebeverzahnung

21

erste Nockenanordnung

22

zweite Nockenanordnung

23

Schaltkulisse

24

Öffnung

25

dritte Nockenanordnung

26

vierte Nockenanordnung

31

Rastaussparung

32

Feder

33

Kugel

34

Öffnung

41 (a)

Bremsnute

42(a)

Feder

43(a)

Kugel / Zylinderrolle

44(a)

Öffnung

211

erster Nocken

212

zweiter Nocken

221

erster Nocken

222

zweiter Nocken

241

Schiebeverzahnung

411(a)

Bremsnutboden

The following reference symbols are used in the figures:

L

Longitudinal axis of the supporting shaft

R

detent contour

K

braking contour

V

offset

A

first area (brake groove)

B

second area (brake groove)

C

third area (brake groove)

1

supporting shaft

2

sliding cam

3

locking device

4

braking device

11

sliding teeth

21

first cam arrangement

22

second cam arrangement

23

shift gate

24

opening

25

third cam arrangement

26

fourth cam arrangement

31

notch

32

Feather

33

Bullet

34

opening

41 (a)

braking groove

42(a)

Feather

43(a)

ball / cylindrical roller

44(a)

opening

211

first cam

212

second cam

221

first cam

222

second cam

241

sliding teeth

411(a)

brake groove floor

First up 1 referenced.

A sliding cam arrangement essentially comprises a support shaft 1 with at least one sliding cam 2. The sliding cam 2 is non-rotatably, but axially displaceably accommodated on the support shaft. For this purpose it can be provided, for example, that the sliding cam 2 has an opening 24 for receiving the support shaft 1, which is equipped with a sliding toothing 241 and the supporting shaft 1 is also equipped with a sliding toothing 11. The sliding cam 2 has at least one cam arrangement 21 with a first cam 211 and at least one second cam 212 . The cams 211 and 212 differ in terms of their cam contour, which can also be implemented in that the cams have different phase positions. Furthermore, the sliding cam 2 has a shift gate 23 . An actuator pin (not shown) can intervene here and carry out the desired axial displacement of the sliding cam 2 so that either the first cam 211 or the at least second cam 212 controls the associated gas exchange valve of an internal combustion engine (not shown).

Ultimately, the sliding cam can thus be shifted at least between a first and a second axial position on the support shaft 1.

Provision can also preferably be made for the sliding cam 2 to be designed as a so-called double sliding cam, which has four cam arrangements 21 , 22 , 25 , 26 and a shift gate 23 accordingly. A double sliding cam designed in this way can preferably control two cylinders with four valves. As a rule, two valves per cylinder are switched on the intake or exhaust side. However, it is conceivable that a cylinder has only one valve per intake or exhaust side.

The cam arrangements 21, 22, 25 and 26 preferably each have a first cam and at least one second cam. With regard to the configuration of the cams, reference can be made to the statements made above.

With such a double sliding cam, two cylinders of an internal combustion engine can be controlled accordingly, although advantageously only one actuator or actuator pin is required. The function of a sliding cam arrangement and its interaction with gas exchange valves of an internal combustion engine is sufficiently well known to a person skilled in the art, so that no detailed explanation is required here.

The sliding cam arrangement is also equipped with a locking device 3 which is set up to releasably fix the sliding cam 2 on the support shaft 1 in a first axial position and at least one second axial position. The locking device can, for example, comprise a locking recess 31 on the sliding cam side and a ball-spring combination 33 and 32 on the supporting shaft side. Spring 32 and ball 33 are received in a radially oriented opening 34 in the support shaft and urge ball 33 against the detent recess 31. The latching recess 31 is generally designed to run all the way around in the opening 11 of the sliding cam 1.

The latching recess 31 has a latching contour R in the axial direction. The locking contour R has a wavy shape in cross section. Correspondingly, the ball 33 always slides over this detent contour when the sliding cam 2 is axially displaced. Due to the wavy shape, the sliding cam can optionally be in a first position (e.g. in 2 shown) or a second position (e.g. in 2a shown) are axially releasably fixed. The sliding cam 2 is thus releasably fixed axially by the prestressing of the spring 32 or its exertion on the ball 33 . For more details, for example, on the DE 10 2017 219287 A1 to get expelled. A corresponding locking recess is in particular in the 3 and 3a shown.

According to the invention, the sliding cam arrangement is equipped with a braking device 4, in particular in addition to the locking device 3. The braking device 4 is set up or used to reduce axial overshooting of the sliding cam 2 after the axial displacement to a permissible level . In other words, the braking device 4 is set up to brake the axial movement of the slide cam 2 .

The braking device 4 can, for example, be a ball-spring combination (cf. in particular 4 ) or a cylinder-roller-spring combination (cf. in particular 5 ) include. Furthermore, the braking device can comprise a braking groove 41 or 41a.

The braking groove 41 or 41a, which is preferably arranged on the sliding cam side, is preferably designed as an axially aligned groove with a braking groove bottom 411 or 411a.

With regard to the design of the ball-spring combination, reference can essentially be made to the statements made above regarding the ball-spring combination of the locking device 3 . Also in the case of the ball-spring combination of the braking device 4, a radially aligned opening 44 is preferably provided in the support shaft 1, in which a spring 42 and a ball 43 are accommodated. The ball 43 presses with a preload generated by the spring 42 in the direction of the brake groove 41 in the sliding cam 2, in particular in the direction of the brake groove base 411.

The cylinder-roller-spring combination preferably includes a radially directed opening 44a in the support shaft, in which a spring 42a and a cylinder roller 43a are accommodated. The cylindrical roller 43a presses with a preload generated by the spring 42a in the direction of the brake groove 41a in the sliding cam 2, in particular in the direction of the brake groove bottom 411a.

The braking grooves for the ball-spring combination or the cylinder-roller-spring combination can be designed the same or different, in particular adapted to the geometric boundary conditions of a ball or a cylinder roller with regard to the braking effect to be achieved. A preferred embodiment of the brake groove is to be described in more detail below, which can be used both for a ball-spring combination and for a cylinder-roller-spring combination.

The brake groove, in particular the bottom of the brake groove, preferably has a first area A, a second area B and a third area C in the axial direction. These can be seen as brake contour K in a cross-sectional representation.

• - Erster Bereich A: abfallender Bremsnutboden
• - Zweiter Bereich B: ebener, konkaver und/oder konvexer Bremsnutboden, kann in einer Ausgestaltung auch Konvex - Konkav - Konvex ausgestaltet sein
• - Dritter Bereich C: ansteigender Bremsnutboden

In the axial direction, the following characteristics of the areas with the longitudinal axis L as a reference result in particular:

• - First area A: sloping bottom of the brake groove
• - Second area B: flat, concave and/or convex Bremsnutboden, can also convex - concave - convex designed in one embodiment
• - Third area C: rising brake groove bottom

In principle, other combinations of flat, concave and/or convex shapes are conceivable for the bottom of the brake groove.

Some forms of Bremsnuten are in particular in the 6 until 9 shown in connection with a cylindrical roller-spring combination. The explanations can be transferred to the ball-spring combination.

In the radial direction, there is a further feature, in particular, that the second area is further away from the longitudinal axis L than the first area and the third area. The _second area thus represents, so to speak, a recessed area compared to the _first area and the third area is. Furthermore, it is preferably provided that the bottom of the brake groove is aligned parallel to the longitudinal axis L in the second region. The cross-section of the brake groove essentially results in a trough-shaped shape.

The braking device is preferably designed in such a way that the braking effect only comes about, or at least to the technically desired extent, when the sliding cam overshoots by 0.01 mm - 1 mm. This can be achieved, for example, by providing an offset V of 0.01mm-1mm between the ball or the cylindrical roller and the first area of the brake groove when the locking device is in a first locking position. For the opposite axial direction, this can be achieved, for example, by providing an offset V of 0.01mm-1mm between the ball or the cylindrical roller and the third area of the braking groove when the locking device is in a second locking position.

• Die Bremsvorrichtung 4 zeichnet sich insbesondere dadurch aus, dass die Bremsnute 41 und die Rastaussparung 31 unterschiedlich ausgestaltet sind.

The present invention is characterized in particular by further features:

• The braking device 4 is characterized in particular by the fact that the braking groove 41 and the locking recess 31 are configured differently.

The braking device 4 is characterized in particular by the fact that the braking groove 41 is designed to be axially longer than the latching recess 31 .

The bottom of the brake groove may have areas of higher or lower friction. This can be used in particular to influence the uniformity of the movement of the shift cam during the shifting process.

The design of the spring can further influence the braking behavior.

Both are particularly dependent on the respective engine concept, for example on the masses, in which switching angle range and/or at which speeds the respective sliding cam element is to be switched in the specific application.

Basically, it is provided that the latching device 3 and the braking device 4 are arranged at axially different positions of the sliding cam arrangement. Alternatively, it can also be provided that the latching device 3 and the braking device 4 are radially opposite one another. This makes it possible, for example, for the ball 33 of the locking device 3 and the ball 43 or the cylindrical roller 43a of the braking device 4 to be acted upon by the same spring 32 or 42 or 42a. It is also advantageous in terms of manufacturing technology that basically only one operation is necessary for the manufacture of the opening 34 or 44 or 44a for the latching device 3 or braking device 4 .

Of course, features and details that are described in connection with a method also apply in connection with the device according to the invention and vice versa, so that with regard to the disclosure of the individual aspects of the invention reference is or can always be made to one another. In addition, an optionally described method according to the invention can be carried out with the device according to the invention.

QUOTES INCLUDED IN DESCRIPTION

This list of documents cited by the applicant was generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Patent Literature Cited

• DE 102017219287 A1 [0002, 0003, 0036]
• DE 102009048621 A1 [0002, 0006]
• WO 2009/152927 A1 [0002, 0007]
• DE 102012210922 A1 [0002, 0008]

Claims (14)

Sliding cam arrangement, comprising a support shaft (1) with a longitudinal axis (L) and at least one sliding cam (2) received on the support shaft (1) in a rotationally fixed and axially displaceable manner, the sliding cam arrangement being equipped with a latching device (3) which is set up to to releasably fix the slide cam (2) in a first axial position and at least one second axial position, characterized in that the slide cam arrangement is equipped with a braking device (4) which is adapted to brake the axial movement of the slide cam (2). sliding cam arrangement claim 1 , characterized in that the braking device (4) comprises a ball-spring combination and a braking groove (41). Sliding cam arrangement according to at least one of the preceding claims, characterized in that the ball-spring combination comprises a spring (42) and a ball (43) received in a radially directed opening (44) in the support shaft (1). Sliding cam arrangement according to at least one of the preceding claims, characterized in that the braking device comprises a cylinder-roller-spring combination and a braking groove (41a). Sliding cam arrangement according to at least one of the preceding claims, characterized in that the cylinder-roller-spring combination comprises a spring (42a) and a cylinder roller (43a) received in a radially directed opening (44a) in the support shaft (1). Sliding cam arrangement according to at least one of the preceding claims, characterized in that the braking groove (41 or 41a) is designed as an axially aligned groove in the sliding cam (2) and has a braking groove base (411 or 411a). Sliding cam arrangement according to at least one of the preceding claims, characterized in that the brake groove base (411 or 411a) in the axial direction relative to the longitudinal axis (L) has a first area (A) with a sloping brake groove base, a second area (B) with a flat Has concave, convex and/or convex-concave-convex Bremsnutboden and a third area (C) with a rising Bremsnutboden. Sliding cam arrangement according to at least one of the preceding claims, characterized in that the brake groove bottom (411 or 411a) in the first area (A) and the third area (C) is between α ₁ = 30° and α ₂ = 60° to the longitudinal axis (L ) is inclined and/or that the brake groove bottom (411 or 411a) is aligned parallel to the longitudinal axis (L) in the second region (B). Sliding cam arrangement according to at least one of the preceding claims, characterized in that the braking device (4) is set up so that the braking effect only comes about, or at least to the technically desired extent, when the sliding cam (2) overshoots by 0.01mm - 1mm. Sliding cam arrangement according to at least one of the preceding claims, characterized in that an offset (V) of 0.01mm - 1mm between the ball (43) or the cylindrical roller (43a) of the braking device (4) and the first area (A) of the braking groove ( 41 or 41a) is provided when the locking device (3) is in a first locking position and/or that an offset (V) of 0.01mm - 1mm between the ball (43) or the cylindrical roller (43a) of the braking device ( 4) and the third area (C) of the braking groove (41) is provided when the locking device (3) is in a second locking position. Sliding cam arrangement according to at least one of the preceding claims, characterized in that the locking device comprises a locking recess (31) and a ball-spring combination. Sliding cam arrangement according to at least one of the preceding claims, characterized in that the braking groove (41) and the latching recess (31) are designed differently, in particular that the braking groove (41) is axially longer than the latching recess (31). Sliding cam arrangement according to at least one of the preceding claims, characterized in that the latching device (3) and the braking device (4) are arranged at axially different positions of the sliding cam arrangement or that the latching device (3) and the braking device (4) are arranged radially opposite one another. Sliding cam arrangement according to at least one of the preceding claims, characterized in that the sliding cam (2) has at least one cam arrangement (21), preferably four cam arrangements (21, 22, 25, 26), with a first cam (211) and at least one second cam (212), the cams (211 or 212) preferably differing in terms of their cam contour.

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