DE102021123117B3 - Adjustable torque limiter - Google Patents

Abstract

The torque limiter 2 includes a support plate 15 on which the tongues 19 of a plate spring 16 rest for applying a contact pressure. The tongues 19 can bear against different connection areas 24 , 25 , 26 which differ in their position in the direction of the axis of rotation 4 . In this way, different preloads of the disk spring 16 can be achieved in the assembled state. The torque limiter 2 can thus be adjusted with regard to its limit torque, which when exceeded causes the friction linings 10 to begin to slip relative to the input part 8 of the torque limiter 2 .

Description

The present invention relates to a torque limiter, for example for use in the drive train of a motor vehicle.

The use of slip clutches as torque limiters is known. These include a friction clutch that frictionally transmits torque via a friction assembly. The friction compound is pressed together with a contact pressure force that essentially determines the limit torque, when this is exceeded the friction partners of the friction compound begin to slip on one another in order to prevent the transmission of torque above the limit torque. The necessary contact pressure is regularly applied by disk springs. Depending on the application, the difference between the limit torque and a minimum torque to be transmitted is small, so that a precise definition of the limit torque is necessary. Due to manufacturing fluctuations, the contact pressure generated by the disc spring varies. Furthermore, tolerances of the components of the torque limiter lead to a fluctuation in the contact pressure over several torque limiters.

From the DE 36 10 735 A1 a torque limiter comprising at least one friction compound comprising at least one input part and at least one output part is known. A friction lining is formed in each case between an input part and an output part which is adjacent in the direction of an axis of rotation of the torque limiter. An output part is connected via a plate spring supported on this to an annular area and a plurality of tongues extending outwards from the annular area, and a support plate is connected in a torque-proof manner to a friction lining. The disc spring exerts a contact pressure on the friction assembly, with two adjacent tongues in the circumferential direction relative to the axis of rotation enclosing a definable tongue angle with the axis of rotation.

The object of the present invention is to at least partially overcome the problems known from the prior art.

This object is achieved with the features of independent claim 1. Further advantageous refinements of the invention are specified in the dependent claims. The features listed individually in the dependent claims can be combined with one another in a technologically meaningful manner and can define further refinements of the invention. In addition, the features specified in the claims are specified and explained in more detail in the description, with further preferred configurations of the invention being presented.

The torque limiter according to the invention, rotatable about an axis of rotation, comprises at least one friction assembly comprising at least one input part and at least one output part, with a friction lining being formed between an input part and an output part adjacent in the direction of the axis of rotation, with an output part having a plate spring supported on it a ring area and a plurality of tongues extending outwards from the ring area and a support plate is connected in a torque-proof manner to a friction lining, with the plate spring exerting a contact pressure force on the friction assembly, with two tongues that are adjacent in the circumferential direction relative to the axis of rotation enclosing a predeterminable tongue angle with the axis of rotation. The torque limiter is characterized in that an end face of the support plate facing the plate spring has several groups of connection areas, at least comprising first connection areas and second connection areas, with the connection areas of each group being at a distance from a reference plane, which extends perpendicularly to the axis of rotation differs from the spacing of another group of attachment areas, wherein the first attachment areas are at a first distance and the second attachment areas are at a second distance from the reference plane, each attachment area having a plate spring cam, the plate spring being oriented such that its tongues are attached to attachment areas of exactly one group abut connection areas and the plate spring cam is accommodated in a recess of the respective tongues.

The support plate of the torque limiter is thus designed in steps and allows the plate spring to be installed in at least two positions, in which the tongues of the plate spring are thus fixed in two positions in the direction of the axis of rotation. This allows a variation of the preload of the plate spring during assembly and thus an adjustment of the contact pressure that is formed by the plate spring on the friction assembly. In this way, fluctuating spring constants of the disk springs caused by production can be compensated. At the same time, tolerances in the direction of the axis of rotation resulting from the tolerances of the individual components of the friction assembly (input part, output part, friction lining, support plate, disc spring) can be compensated for, especially if more than two groups of connection areas are formed. In this way, several limit torques can also be achieved with identical components if this is necessary for the application.

The distances from the reference plane of at least two groups preferably differ by a definable step height. This allows an adjustability with defined levels, in particular when more than two groups of connection areas are formed with different distances.

Preferably, the height of the disk spring cams in the direction of the axis of rotation is smaller than the step height. This enables the support plate to be formed easily, for example by pressing, and to be assembled easily.

A group of connection areas preferably has friction lining cams on the side opposite the end face, which correspond to recesses in the friction lining. In this way, a simple non-rotatable connection of the friction lining to the support plate can be achieved. The friction lining cams are preferably formed as connection areas which rest flat on the friction lining. By distributing friction lining cams over the circumference of the support plate, the introduction of force into the friction lining over the circumference of the friction lining is evened out.

Third connection areas are preferably formed at a third distance from the reference plane. The third distance is in particular different from the first distance and the second distance. The first, second and third distance preferably each differ by a definable step height.

Several preferred repetition patterns are described below. The connection areas are preferably designed such that in a predefinable circumferential direction relative to the axis of rotation, a second connection area follows a first connection area, a third connection area follows a second connection area and a first connection area follows a third connection area. A predefinable circumferential direction is understood to mean, in particular, a fixed running direction, for example clockwise or counterclockwise. The sequence mentioned here (a first connection area, a second connection area and a third connection area, which is repeated over the circumference of the support plate) achieves a simple installation option, since the tongues can rest against the first connection areas as a result of predeterminable twisting of the plate spring during installation , the second connection areas or the third connection areas can be achieved. The second distance preferably differs by a step height from the first distance and the third distance, so that the positioning of the plate spring tongues in the direction of the axis of rotation changes from the first to the second and finally to the third connection region by the step height. This facilitates the adjustability of the torque limiter during assembly.

Two groups of first attachment areas, one group of second attachment areas and one group of third attachment areas are preferably formed. Thus there are twice as many first connection areas with a first distance from the reference plane as second connection areas or third connection areas. In particular when the first connection areas are also provided with corresponding friction lining cams, a further equalization of the introduction of force into the friction lining can be achieved. An embodiment is preferred in which the connection areas are designed such that the following sequence of connection areas is repeated in a predefinable circumferential direction relative to the axis of rotation: a first connection area, a second connection area, a first connection area and a third connection area. A first connection area then adjoins the third connection area, followed by a second connection area, etc. Each first connection area preferably has a friction lining cam on the side opposite the end face, which corresponds to a recess in the friction lining.

Furthermore, a torsional vibration damper arrangement is proposed. This includes a torsional vibration damper and a torque limiter as proposed here. In particular, the torsional vibration damper arrangement comprises a torsional vibration damper with at least one input flange and at least one output flange, which can be rotated relative to one another about an axis of rotation against the action of a spring device, further comprising a torque limiter as presented here, with at least one output flange of the torsional vibration damper being non-rotatably connected to the input part of the torque limiter is. In particular, the output flange is formed in one piece with the input part of the torque limiter. The torque limiter is preferably arranged radially on the inside inside the torsional vibration damper, so that a space-saving torsional vibration damper arrangement is achieved. Preferably, the torsional vibration damper arrangement also includes a centrifugal pendulum, which is connected to the output part of the torque limiter.

As a precaution, it should be noted that the numerals used here (“first”, “second”,...) are primarily (only) used to distinguish between several of the same kind Objects, variables or processes are used, i.e. in particular do not necessarily specify any dependency and/or sequence of these objects, variables or processes in relation to one another. Should a dependency and/or order be necessary, this is explicitly stated here or it is obvious to the person skilled in the art when studying the specifically described embodiment.

• 1: ein Bespiel eines Drehschwingungsdämpferanordnung mit einem ersten Beispiel eines Drehmomentbegrenzers und Fliehkraftpendel;
• 2: das erste Beispiel eines Drehmomentbegrenzers im Schnitt;
• 3: das erste Beispiel eines Drehmomentbegrenzers in Draufsicht;
• 4: einen Ausschnitt des ersten Beispiels eines Drehmomentbegrenzers;
• 5: ein Stützblech nach dem ersten Beispiel eines Drehmomentbegrenzers;
• 6: eine Tellerfeder nach dem ersten Beispiel eines Drehmomentbegrenzers;
• 7 - 9: perspektivische Ansichten eines Ausschnittes des Stützbleches nach dem ersten Beispiel eines Drehmomentbegrenzers;
• 10: eine seitliche Ansicht eines Ausschnittes des Stützbleches nach dem ersten Beispiel eines Drehmomentbegrenzers;
• 11: schematisch ein Detail eins Stützblechs nach dem ersten Beispiel eines Drehmomentbegrenzers;
• 12 - 13: zwei Ansichten des ersten Beispiels eines Drehmomentbegrenzers in einer ersten Montageposition;
• 14 - 15: zwei Ansichten des ersten Beispiels eines Drehmomentbegrenzers in einer zweiten Montageposition;
• 16 - 17: zwei Ansichten des ersten Beispiels eines Drehmomentbegrenzers in einer dritten Montageposition;
• 18: ein zweites Beispiel eines Drehmomentbegrenzers in Draufsicht;
• 19: ein Ausschnitt des zweiten Beispiels eines Drehmomentbegrenzers in einer perspektivischen Ansicht; und
• 20 - 21: verschiedene Ansichten eines Stützblechs nach dem zweiten Beispiel eines Drehmomentbegrenzers.

The invention and the technical environment are explained in more detail below with reference to the figures. It should be pointed out that the invention should not be limited by the exemplary embodiments shown. In particular, unless explicitly stated otherwise, it is also possible to extract partial aspects of the facts explained in the figures and to combine them with other components and findings from the present description and/or figures. In particular, it should be pointed out that the figures and in particular the proportions shown are only schematic. The same reference symbols designate the same objects, so that explanations from other figures can be used as a supplement if necessary. Show it:

• 1 : an example of a torsional vibration damper arrangement with a first example of a torque limiter and centrifugal pendulum;
• 2 : the first example of a torque limiter in section;
• 3 : the first example of a torque limiter in top view;
• 4 : a section of the first example of a torque limiter;
• 5 : a gusset according to the first example of a torque limiter;
• 6 : a disc spring according to the first example of a torque limiter;
• 7 - 9 1: perspective views of a section of the support plate according to the first example of a torque limiter;
• 10 : a side view of a section of the support plate according to the first example of a torque limiter;
• 11 : schematically a detail of a support plate according to the first example of a torque limiter;
• 12 - 13 : two views of the first example of a torque limiter in a first mounting position;
• 14 - 15 : two views of the first example of a torque limiter in a second mounting position;
• 16 - 17 : two views of the first example of a torque limiter in a third mounting position;
• 18 : a second example of a torque limiter in plan view;
• 19 : a section of the second example of a torque limiter in a perspective view; and
• 20 - 21 : different views of a support plate according to the second example of a torque limiter.

1 shows a section through a torsional vibration damper 1 with a torque limiter 2 and a centrifugal pendulum 3, which are designed to be rotatable about an axis of rotation 4 and form a torsional vibration damper arrangement 39. The torque limiter 2 is formed radially inside the torsional vibration damper 1 .

The torsional vibration damper 1 has an input flange 5, which is preferably non-rotatably connected to a crankshaft, not shown, of an internal combustion engine, not shown. Furthermore, the torsional vibration damper 1 has an output flange 6 . The input flange 5 and the output flange 6 can be rotated relative to one another about the axis of rotation 4 against the action of spring devices 7 in order to dampen rotational irregularities. The output flange 6 of the torsional vibration damper 1 is at the same time an input part 8 of the torque limiter 2.

For the following remarks, in addition to 1 on too 2 Reference is made, which shows a first example of a torque limiter 2 in section. In this example, the input part 8 is located centrally between two output parts 9. A friction lining 10 is formed between the input part 8 and an output part 9 in each case. The friction linings 10 are connected to the output parts 9 in a torque-proof manner. For this purpose, for example, a first output part 11 has friction lining cams 12 which interact with corresponding recesses 13 in the friction lining to form a positive connection between the friction lining 10 and the first output part 11 .

A second output part 14 is connected to the friction lining 10 via a support plate 15 and a disk spring 16 . The support plate 15 lies flat against the friction lining 10 and also has friction lining cams 12 which engage in corresponding recesses 13 of the friction lining 10 (cf. 8th ). The friction linings 10 are designed in the shape of a circular ring.

The plate spring 16 is supported on the second output part 14 and exerts an axial contact pressure the support plate 15, the friction lining 10, the input part 8, the friction lining 10 and the first output part 11, which forms a friction assembly 17 made up of the first output part 11, friction lining 10, input part 8, friction lining 10, support plate 15, plate spring 16 and the second output part 14 . Torque is transmitted via the friction compound 17 between the input part 8 and the output parts 11, 14, which in turn are connected to the centrifugal pendulum 3 in a torque-proof manner. Together with the coefficients of friction of the friction lining 10 and the input part 8 and the geometric design of the friction lining 10 and the input part 8 (in particular by the size of the rubbing surface between the friction linings 10 and the input part 8, as well as the inner and outer radii of the rubbing surface, the contact pressure force is defined based on the axis of rotation 4) a limit torque. If the torque to be transmitted is above the limit torque, the friction linings 10 begin to slip in relation to the input part 8 and thus interrupt the transmission of the torque. The torque limiter 2 can thus prevent torque peaks, which can lead to damage to other components, from not being transmitted.

Based on 3 until 11 the structure of the support plate 15 and the connection of the disc spring 16 to the support plate 15 will now be described. Unless explicit reference is made to a figure, the description relates to all figures. The support plate 15 has an end face 18 which is aligned in the axial direction in relation to the axis of rotation 4 in the direction of the plate spring 16 and the second output part 14 . The disc spring 16 has a plurality of tongues 19, each having a recess 20 and which are formed on an annular ring area 34 and point outwards from it. In this example, each tongue 19 comprises two partial tongues 21, between which the respective recess 20 lies (see in particular 6 ).

The end face 18 of the support plate 15 has several connection areas 22. Each connection area 22 has a cup spring cam 23, the dimensions of which correspond to the recess 20 of the tongues 19 of the cup spring 16, so that the tongues 19 of the cup spring when the torque limiter 2 is installed in Circumferentially based on the axis of rotation 4 fixed to the respective connection areas 22 abut. The number of connection areas 22 is a multiple of the number of tongues 19, for example in the present example the number of tongues 19 is eight and the number of connection areas 22 is twenty-four.

The connection areas 22 are formed in groups. A first group 35 includes first attachment areas 24, a second group 36 includes second attachment areas 25, and a third group 37 includes third attachment areas 26, each of which is stepped, i.e. differing in their axial position in relation to the axis of rotation 4. The tongues 19 each rest against a group of attachment areas 24, 25, 26, i.e. either on the first attachment areas 24 or the second attachment areas 25 or the third attachment areas 26. Each two adjacent first attachment areas 24 of the first group 35 enclose an attachment area angle 27 , based on the axis of rotation 4 and measured from the center of the respective cup spring cams 23 (see esp. 5 ). This connection area angle 27 is 45° in the present example. The same attachment area angle 27 is present between each pair of adjacent first attachment areas 24 , second attachment areas 25 of the second group 36 or third attachment areas 26 of the third group 37 in the circumferential direction relative to the axis of rotation 4 . The connection area angle 27 is identical to a tongue angle 28 between two tongues 19 that are adjacent in the circumferential direction in relation to the axis of rotation 4 (cf. esp. 6 ). Thus, the plate spring 16 can be applied to the first connection areas 24, the second connection areas 25 or the third connection areas 26, respectively. 3 and 4 show in detail a situation in which the tongues 19 are in contact with the first connection areas 24 in each case. The second connection areas 25 and the third connection areas 26 remain free.

As in particular in 7 and 8th can be seen in detail, the first connection areas 24, the second connection areas 25 and the third connection areas 26 are offset in steps in the direction of the axis of rotation 4. This will now be referred to 11 explained in more detail. 11 shows very schematically a section of the end face 18 of the support plate 15 with first connection areas 24, a second connection area 25 and a third connection area 26. For the sake of clarity, the corresponding disk spring cams 23 are not shown in any of the connection areas 24, 25, 26. 11 FIG. 12 also shows a reference plane 29 which is perpendicular to the axis of rotation 4. FIG. All connection areas 24 , 25 , 26 are aligned parallel to the reference plane 29 and thus perpendicular to the axis of rotation 4 . The first connection areas 24 have a first distance 30 from the reference plane 29 , while the second connection areas 25 have a second distance 31 and the third connection areas 26 have a third distance 32 , each from the reference plane 29 . The second connection areas 25 protrude beyond the first connection areas 24 in the direction of rotation axis 4 by a step height 33. The third connection areas 26 project beyond the second connection areas 35 in the direction of the axis of rotation 4 by the step height 33. The distance in the direction of the axis of rotation 4 between the third connection areas 26 and the first connection areas 24 is therefore twice the step height 33. The step height 33 is preferably smaller than the extension of the disk spring cams 23 in the direction of the axis of rotation 4. In this first example, the connection areas 24, 25, 26 are arranged in such a way that there is always a sequence of a first connection area 24, a second connection area 25, a second connection area 25 , a third attachment area 26 and then again a first attachment area 24 (and so on). This sequence can vary (cf. the second example and there in particular 22 ), but it is always designed in such a way that connecting areas 22 of the same type that are adjacent in the circumferential direction always enclose the connecting area angle 27 with one another.

The different distances 30, 31, 32 of the connection areas 24, 25, 26 make it possible to mount the plate spring 16 in different planes. In this way, different contact pressure forces—and thus different limit torques—can be achieved with one and the same disc spring 16 by resting either on the first connection areas 24 or the second connection areas 25 or the third connection areas 26 . At the same time, it is possible to compensate for manufacturing tolerances in the plate spring 16, since, depending on the individual spring force of the plate spring 16, one of the connection areas 24, 25, 26 can be selected so that the most homogeneous possible contact pressure is achieved via a large number of torque limiters 2. The different connection areas 24, 25, 26 can also be used to compensate for tolerance widths of other components such as the support plate 15, the friction linings 10, the input part 8 and the output parts 9, 11, 14 in the direction of the axis of rotation 4.

The effect of the different mounting options on the plate spring 16 is in 12 until 17 shown where 12 , 14 and 16 each a top view and 13 , 15 and 17 show a cut. 12 and 13 show a situation in which the tongues 19 of the plate spring 16 rest against the first connection areas 24 of the support plate 15. 14 and 15 show a situation in which the tongues 19 of the plate spring 16 are in contact with the second connection areas 25 of the support plate 15. 16 and 17 show a situation in which the tongues 19 of the disc spring 16 are in contact with the third connection areas 26 of the support plate 15. By comparing the 12 until 17 is the influence of changing the distance 30, 31, 32 (cf. 11 ) on the preload of the plate spring 16 can be seen. When the tongues 19 are in contact with the first connection areas 24, the friction lining 10 is in contact with the area of the support plate 15 into which the pressing force is introduced (cf. 13 ). When the tongues 19 rest on the second connection areas 25 ( 15 ) and on the third connection areas 26 ( 17 ) this is not the case due to the potting to form the second connection areas 25 and the third connection areas 26 .

In the 18 until 21 a second example of a torque limiter 2 is shown. To avoid repetition, reference is made to the description of the first example. Only the differences to the first example are described here. If a figure is not explicitly referred to, all of them are used below 18 until 22 described together. In contrast to the first example, the arrangement of the connection areas 24, 25, 26 is changed in the second example. In the second example, there are four groups of connection areas, of which the first group 35 and a fourth group 38 have first connection areas 24 at a first distance 30 from the reference plane 29, while, as in the first example, a second group 36 has the second connection areas 25 and one third group 37 includes the third connection areas 26 . While in the first example - viewed clockwise - the sequence: first connection area 24 (as part of the first group 35), second connection area 25 (as part of the second group 36), third connection area 26 (as part of the third group 37), etc. was selected, in the second example a sequence is: first connection area 24 (as part of the first group 35), second connection area 25 (as part of the second group 36), first connection area 24 (as part of the fourth group 38), third connection area 26 ( selected as part of the third group 37), etc. At the same time, the total number of connection areas 24, 25, 26 was increased and thus the width of a connection area 24, 25, 26 in the circumferential direction relative to the axis of rotation 4 was reduced in comparison to the first example. This ensures that there is always a group 35, 36, 37, 38 connection areas 24, 25, 26, in which in the circumferential direction relative to the axis of rotation 4 adjacent connection areas 24, 25, 26 of the respective group 35, 36, 37. 38 a Include connection area angle 27, which corresponds to tongue angle 28.

Thus, in the second example, the end face 18 of the support plate 15 has a first group 35 and a fourth group 38 of first connection areas 24 (whereby it applies to each group 35, 38 that for each two in the circumferential direction in relation to the axis of rotation 4 adjacent first connection areas 24 that these enclose the connection area angle 27 with each other, which corresponds to the tongue angle 28) and each have a second group 36 of second connection areas 25 and a third group 37 of third connection areas 26. In each case two second attachment areas 25 that are adjacent in the circumferential direction relative to the axis of rotation 4 enclose the attachment area angle 27 . In each case, two third attachment areas 26 that are adjacent in the circumferential direction relative to the axis of rotation 4 enclose the attachment area angle 27 . The design of the support plate 15 according to the second example makes the introduction of force into the friction lining 10 lying against the support plate 15 opposite the end face 18 more even, since the first connection regions 24 (which, due to the cupping of the support plate 15, alone cause the contact pressure force to be introduced into the friction lining 10 ) are distributed more evenly over the circumferential direction of the friction lining 10 compared to the first example due to the higher number.

The torque limiter 2 includes a support plate 15 on which the tongues 19 of a plate spring 16 rest for applying a contact pressure. The tongues 19 can bear against different connection areas 24 , 25 , 26 which differ in their position in the direction of the axis of rotation 4 . In this way, different preloads of the disk spring 16 can be achieved in the assembled state. The torque limiter 2 can thus be adjusted with regard to its limit torque, which when exceeded causes the friction linings 10 to begin to slip relative to the input part 8 of the torque limiter 2 .

Reference List

1

torsional vibration damper

2

torque limiter

3

centrifugal pendulum

4

axis of rotation

5

input flange

6

output flange

7

spring device

8th

input part

9

output part

10

friction lining

11

First output part

12

friction lining cam

13

return

14

Second output part

15

gusset

16

disc spring

17

friction compound

18

face

19

Tongue

20

recess

21

part tongue

22

connection area

23

plate spring cams

24

First connection area

25

Second connection area

26

Third connection area

27

connection area angle

28

tongue angle

29

reference plane

30

First distance

31

second distance

32

Third distance

33

step height

34

ring area

35

First group

36

second group

37

third group

38

fourth group

39

Torsional vibration damper arrangement

Claims (10)

Torque limiter (2), rotatable about an axis of rotation (4), comprising at least one friction assembly (17) comprising at least one input part (8) and at least one output part (9, 11, 14), wherein in each case between an input part (8) and an in A friction lining (10) is formed on the output part (9, 11, 14) adjacent in the direction of the axis of rotation (4), with an output part (14) having a ring area (34) and a plurality of 34) outwardly extending tongues (19) and a support plate (15) is non-rotatably connected to a friction lining (10), with the plate spring (16) and exerting a contact pressure on the friction assembly (17), with two each in the circumferential direction relative to the Tongues (19) adjacent to the axis of rotation (4) enclose a predeterminable tongue angle (28) with the axis of rotation (4), characterized in that an end face (18) of the Support plate (15) has several groups (35, 36, 37, 38) of connection areas (22, 24, 25, 26), at least comprising first connection areas (24) and second connection areas (25), wherein the connection areas (24, 25, 26) each group (35, 36, 37, 38) have a distance (30, 31, 32) from a reference plane (29) extending perpendicularly to the axis of rotation (4), which differs from the distance (30, 31, 32) of the connection areas (24, 25, 26) of another group (35, 36, 37, 38), the first connection areas (24) having a first distance (30) and the second connection areas (25) having a second distance (31 ) from the reference plane (29), each connection area (22, 24, 25, 26) having a plate spring cam (23), the plate spring (16) being aligned in such a way that its tongues (19) are attached to the connection areas of a group (35 , 36, 37, 38) of connection areas (24, 25, 26) and the plate spring cam (23) in a recess (20) of the respective tongue e (19) is included. Torque limiter (2) after claim 1 , in which the distances (30, 31, 32) from the reference plane (29) of at least two groups (35, 36, 37, 38) differ by a definable step height (33). Torque limiter (2) after claim 2 , in which the height of the disk spring cams (23) in the direction of the axis of rotation (4) is smaller than the step height (33). Torque limiter (2) according to one of the preceding claims, in which a group (35, 36, 37, 38) of connection areas (24, 25, 26) on the side opposite the end face (18) has friction lining cams (12) which have recesses (13) in the friction lining (10) correspond. Torque limiter (2) according to one of the preceding claims, in which third connection areas (26) are formed at a third distance (32) from the reference plane (29). Torque limiter (2) after claim 5 , in which the connection areas (24, 25, 26) are designed in such a way that, in a predefinable circumferential direction relative to the axis of rotation (4), a second connection area (25) on a first connection area (24) and a second connection area (25). third connection area (26) and a third connection area (26) is followed by a first connection area (24). Torque limiter (2) after claim 5 , in which two groups (35, 38) of first connection areas (24), a group (36) of second connection areas (25) and a group (37) of third connection areas (26) are formed. Torque limiter (2) after claim 7 , in which the connection areas (24, 25, 26) are designed in such a way that the following sequence of connection areas (24, 25, 26) is repeated in a predeterminable circumferential direction in relation to the axis of rotation (4): a first connection area (24), a second connection area (25), a first connection area (24) and a third connection area (26). Torque limiter (2) after claim 8 , in which each first connection region (24) has a friction lining cam (12) on the side opposite the end face (18), which corresponds to a recess (13) in the friction lining (10). Torsional vibration damper arrangement (39), comprising a torsional vibration damper (1) with at least one input flange (5) and at least one output flange (6), which can be rotated relative to one another about an axis of rotation (4) against the action of a spring device (7), further comprising a Torque limiter (2) according to one of the preceding claims, wherein at least one output flange (6) of the torsional vibration damper (1) is non-rotatably connected to the input part (8) of the torque limiter (2).

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