DE102019118504A1 - Torsional vibration damper - Google Patents

Abstract

The invention relates to a torsional vibration damper (1) with an input part (2) arranged to be rotatable about an axis of rotation (d) and an output part (3) that can be rotated to a limited extent about the axis of rotation (d) against the action of a spring device (4) and a torque limiting device ( 5) for limiting a torque that can be transmitted via the torsional vibration damper (1), the torque limiting device (5) being arranged between a flange part (17) acting on the spring device (4) on the output side and an output hub (31) and a frictional engagement of the torque limiting device (5) a maximum transmittable torque of the torsional vibration damper (1) is set. In order to be able to align the fastening screws (14) of the torsional vibration damper (1) and the through openings (40) in the output part (3) with one another in a simple manner when the torsional vibration damper (1) is removed from a crankshaft of an internal combustion engine, the torque limiting device (5) a release device (37) is provided for releasing the frictional engagement without dismantling the torque limiting device (5).

Description

The invention relates to a torsional vibration damper with an input part rotatable about an axis of rotation and an output part that can be rotated to a limited extent about the axis of rotation counter to the action of a spring device, as well as a torque limiting device for limiting a torque that can be transmitted via the torsional vibration damper, the torque limiting device between a flange part acting on the spring device on the output side and an output hub is arranged and a frictional engagement of the torque limiting device is set to a maximum transmittable torque of the torsional vibration damper.

Torsional vibration dampers, for example in the form of two-mass flywheels, are well known. These are used in drive trains of motor vehicles between an internal combustion engine and a transmission to isolate torsional vibrations of an internal combustion engine with high speed.

Such torsional vibration dampers contain an input part that is rotatable about an axis of rotation, for example, received on a crankshaft of the internal combustion engine, for example with a primary flywheel and an output part that can be rotated to a limited extent around the axis of rotation against the action of a spring device and that can have a secondary flywheel.

In the operating state of the drive train, sudden peak loads, so-called impacts, can arise, for example when the internal combustion engine suddenly comes to a standstill. In particular in the case of a spring device formed from bow springs, these can be subjected to heavy loads for a short time, for example compressed in a block position. Furthermore, transmission elements of a downstream transmission can be damaged.

In order to compensate for such impacts as gently as possible, it is known to provide torsional vibration dampers with a torque limiting device designed as a slip clutch, which only transmits a predetermined limit torque and slips at higher torques.

For example, from the publication DE 197 00 851 A 1, a torsional vibration damper is known in which a torque limiting device is provided between the input part and the output part in the form of two rotating masses that can be rotated relative to one another. The torque limiting device limits the torsional vibration damper from impermissibly high torques and disadvantageous rotary shocks. The pamphlet DE 197 28 422 A 1 furthermore shows a torsional vibration damper with a torque limiting device on the output side, accommodated within an annular chamber for receiving the spring device, which is arranged in series with the spring device and designed as a slip clutch.

From the pamphlet DE 10 2014 211 603 A 1, a torsional vibration damper with a torque limiting device assigned to the secondary part and accommodated in an annular chamber is known. A secondary flange engages in a receptacle provided as a friction device, which is axially delimited by two support disks of different sizes. The smaller-sized supporting disk, which is axially acted upon by a spring element, is arranged between an output hub and the secondary flange.

To fasten the torsional vibration damper to the crankshaft, fastening screws extending through the input part are provided, which are screwed to the crankshaft through openings in the output part. If the torque limiting device is triggered during operation, the output part rotates with respect to the input part, so that in the event of a repair, the access openings are no longer aligned with the fastening openings and the output part is rotated with great effort against the action of the spring device with respect to the input part or the torsional vibration damper or respectively the torque limiting device must be dismantled. The object of the invention is to develop a torsional vibration damper of the generic type. In particular, the object of the invention is to be able to remove the torsional vibration damper from the crankshaft in a simple manner in the event of a repair. The object is achieved by the subject matter of claim 1. The claims dependent on claim 1 reproduce advantageous embodiments of the subject matter of claim 1.

The proposed torsional vibration damper is intended in particular for a drive train of a motor vehicle with an internal combustion engine subject to torsional vibrations. To dampen the torsional vibrations, the torsional vibration damper has an input part which is arranged so as to be rotatable about an axis of rotation and an output part which can be rotated to a limited extent about the axis of rotation counter to a spring device. The torsional vibration damper can be designed as a two-mass flywheel. For this purpose, the input part has a primary flywheel. The output part can have a secondary flywheel. Alternatively or in addition, the output part can be a rotationally locked Secondary flywheel mass of a subsequent drive train device can be assigned, for example, to a double clutch, an electric machine, a hydrodynamic torque converter and / or the like.

The output part has an output hub via which the torque is transmitted to a subsequent drive train device.

The spring device can be formed from helical compression springs distributed over the circumference, preferably arc springs pre-bent to an insert diameter. Several helical compression springs can be nested inside one another to form spring packages. Nested helical compression springs can be acted upon at different angles of rotation between the input part and the output part, for example in order to form a torsional vibration damper with a multi-stage characteristic curve of the torsional force against the angle of rotation.

The spring device can be accommodated in an annular chamber formed by disk parts of the input part. The disk parts can have embossments for the input-side loading of the spring device. For loading on the output side, a flange part can be provided which has radially widened arms for loading the spring device. The torque limiting device is arranged between a flange part, which acts on the spring device on the output side, and an output hub. Frictional engagement of the torque limiting device is set to a maximum transmittable torque of the torsional vibration damper.

In order to be able to easily remove the torsional vibration damper from the crankshaft when the torque limiting device is triggered during operation of the drive train with fastening screws twisted against each other in the input part and in the output part, a release device is provided on the torque limiting device for releasing the frictional engagement without dismantling the torque limiting device . By releasing the frictional engagement, the output hub and the input part can be rotated against each other independently of the torque limiting device and the fastening screws and the access openings can be set in alignment with one another without high torsional forces.

According to an advantageous embodiment of the torsional vibration damper, the torque limiting device contains a friction lining cage which is formed from a drive plate connected to the flange part, for example riveted, and a counter disk connected to this, for example riveted. The connection of the drive plate to the counter plate is preferably carried out radially on the outside, so that friction linings attached to a friction lining carrier on both sides radially on the outside can be accommodated in the friction lining cage, which in preferably dry operation each form a frictional engagement with opposing friction surfaces of the friction lining cage to generate the frictional torque of the torque limiting device. The friction linings are axially pretensioned by a plate spring. The disc spring is supported axially on the friction lining cage.

The friction lining carrier is connected to the drive hub, for example riveted or formed in one piece with it. A lining suspension can be provided between the friction lining carrier and the friction linings, so that the friction torque is set from the two spring components of the disc spring / lining suspension. Alternatively, the friction linings, for example mixed linings, sintered linings, ceramic linings or the like, can be rigidly received on the friction lining carrier.

For example, the disk spring can be supported on the driver disk against a support disk that forms a frictional contact such as a counter-friction surface with one of the friction linings and is held non-rotatably on the friction lining cage.

To form the release device, the effect of the plate spring can be canceled by means of means effectively used from the outside. For this purpose, the disk spring can be designed to be axially acted upon by means of the means used. For example, an area of application of the plate spring can be axially displaced by the means used in such a way that the plate spring lifts from the area acted upon, for example from a directly acted upon friction lining, the support disc or the like and thus the frictional engagement of both friction linings with respect to the counter-friction surfaces of the friction lining cage or the support disc is canceled becomes. For example, at least one thread can be provided on the friction lining cage for receiving a screw which axially acts on the disk spring. Two or three threads can preferably be provided in the counter disk, distributed over the circumference. In this case, a screw can be screwed into the at least one thread, which cancels out an area of application of the plate spring by releasing the preload against the friction linings.

For example, the at least one thread can be introduced radially on the outside in the counter disk, wherein in the driver disk in A recess is provided in a peripheral region of the at least one thread. In this way, for example, by appropriate reshaping of the counter disk during manufacture, its sheet metal thickness can be increased so that an increased thread length is achieved. In the area of the recess, the plate spring overlaps the drive plate radially and forms an area of application for the screw screwed into the at least one thread.

According to an alternative embodiment of the release device, the plate spring can have at least one application area, which is radially expanded beyond the friction lining cage, for the axial application. When axially applied by means of a tool, for example a screwdriver or the like, the application area causes the disc spring to detach from the friction linings and to cancel the frictional engagement using the resulting lever. Several such tools or, for example, a combination tool with several pressure peaks arranged distributed over the circumference can act on the plate spring distributed over the circumference at several application areas.

The impingement area can be designed to be closed over the circumference, with recesses being provided radially within the impingement area and the driver disk and the counter disk being connected to one another by means of tabs of the driver disk that extend through the recesses.

After the frictional engagement has been canceled, the output hub can be rotated against the input part and the passage openings can be aligned with the fastening screws by rotating it. The established orientation can be fixed by re-establishing the frictional engagement by establishing the prestress.

According to an advantageous embodiment of the torsional vibration damper, in addition to the torsional vibration damping of the spring device, a speed-adaptive torsional vibration damper can be provided to improve the insulation behavior with respect to torsional vibrations. For example, a centrifugal pendulum can be received in the torsional vibration damper, in particular on the output side. For this purpose, the friction lining carrier can also form a pendulum mass carrier, on which pendulum masses distributed over the circumference on both sides in the centrifugal force field of the torsional vibration damper rotating about the axis of rotation are accommodated by means of self-aligning bearings along a predetermined pendulum path. The self-aligning bearings can each be provided on axially opposite pendulum masses and the pendulum mass carrier by making recesses with arcuate tracks that determine the pendulum track in the pendulum masses and in the pendulum mass carrier, on which tracks a pendulum roller that crosses the recesses rolls. Axially opposite pendulum masses are each connected to pendulum mass units distributed over the circumference.

In an alternative embodiment of the centrifugal pendulum, axially opposite pendulum masses can be connected to pendulum mass units by means of central parts arranged in recesses of the pendulum mass carrier, the self-aligning bearings each having raceways of the central parts and the recesses arranged radially one above the other in a single plane and each rolling a spherical roller on these raceways .

• 1 den oberen Teil eines um eine Drehachse verdrehbaren Drehschwingungsdämpfers im Schnitt,
• 2 ein Detail des Drehschwingungsdämpfers der 1 entlang der Schnittlinie der 1,
• 3 ein Detail des Drehschwingungsdämpfers der 1 entlang einer Schnittlinie bei gegenüber der Schnittlinie der Figur geändertem Umfang,
• 4 ein Detail des Drehschwingungsdämpfers der 1 vor der Anwendung der Löseeinrichtung,
• 5 ein Detail des Drehschwingungsdämpfers der 1 nach der Anwendung der Löseeinrichtung,
• 6 den oberen Teil eines gegenüber dem Drehschwingungsdämpfer der 1 bis 5 abgeänderten Drehschwingungsdämpfers mit abgeänderter Löseeinrichtung im Schnitt,
• 7 ein Detail des Drehschwingungsdämpfers der 6 bei nicht angewendeter Löseeinrichtung und
• 8 ein Detail des Drehschwingungsdämpfers der 6 bei angewendeter Löseeinrichtung.

The invention is based on the in the 1 to 8th illustrated embodiments explained in more detail. These show:

• 1 the upper part of a torsional vibration damper that can be rotated about an axis of rotation in section,
• 2 a detail of the torsional vibration damper of 1 along the cutting line of the 1 ,
• 3 a detail of the torsional vibration damper of 1 along a cutting line with a changed circumference compared to the cutting line in the figure,
• 4th a detail of the torsional vibration damper of 1 before using the release device,
• 5 a detail of the torsional vibration damper of 1 after using the release device,
• 6th the upper part of the opposite to the torsional vibration damper 1 to 5 modified torsional vibration damper with modified release device in section,
• 7th a detail of the torsional vibration damper of 6th if the release device is not used and
• 8th a detail of the torsional vibration damper of 6th with the release device used.

The 1 shows the upper part of the around the axis of rotation d rotatably arranged torsional vibration damper 1 on average. The torsional vibration damper 1 contains the input part 2 and that against the spring device 4th opposite the entrance part 2 Limited rotatable output part 3 as well as the torque limiting device assigned to the output part 5 .

The entrance part 2 is designed as a primary flywheel with a given primary flywheel and contains the disc part 6th and the lid part 7th , which are tightly connected to one another radially on the outside, are welded here and the annular chamber 8th to accommodate the arc springs distributed over the circumference 9 the spring device 4th form. The bow feathers 9 are supported radially by means of the sliding shells 10 at the annular chamber 8th from. The ring chamber 8th can at least partially lubricate the bow springs 9 and its sliding contact on the sliding cups 10 be filled with lubricant. For loading the bow springs on the input side 9 are on the disc part 6th and on the lid part 7th embossed, in the annular chamber 8th extended, between the circumferentially adjacent end faces of the bow springs 9 intervening exposure areas 11 , 12 intended.

Radially outside are on the annular chamber 8th here on the folded cover part 7th Encoder markings 13 intended for engine management. The torsional vibration damper 1 is intended for a hybrid drive train and does not contain a starter ring gear for a separate starter. Further embodiments can be on the outer circumference of the annular chamber 8th have a starter ring gear.

The disc part 6th contains the preferably hardened run-on washer radially on the inside 16 for the fastening screws 14th for fastening the torsional vibration damper 1 on a crankshaft of an internal combustion engine. The disc part 6th and the washer 16 have mounting holes 15th for the fastening screws 14th on. The fastening screws 14th are through the access openings 40 of the output part 3 screwed. The fastening screws are for this purpose 14th and the access openings 40 in the relaxed state of the spring device 4th each arranged in alignment with one another.

The application of the arc springs on the output side 9 takes place by means of the flange part 17th . The radially enlarged arms 18th of the flange part 17th engage from the radial inside between the end faces of the arc springs that are adjacent in the circumferential direction 9 one.

The flange part 17th is radially inside by means of the main riveting 19th with the rivets distributed over the circumference 20th with the torque limiting device 5 connected. With the main rivet 19th is also the disc spring membrane 21st connected, which is radially outward by means of the friction ring 22nd against the cover part 7th and the output part 3 the axial sealing ring 23 against the entrance part 2 axially preloaded. The disc spring membrane 21st , the friction ring 22nd and the axial seal 23 seal the annular chamber 8th also radially outwards and form a basic friction between the input part 2 and the output part 3 with a relative rotation of this about the axis of rotation d .

The torque limiting device 5 contains the one with the flange part 17th by means of the rivet 20th connected drive plate 24 and the radially outside with the drive plate 24 Counter-disk connected by means of a non-visible rivet 25th . The drive plate 24 and the counter disc 25th form the friction lining cage 26th , which the friction linings 27 , 28 records. The friction linings 27 , 28 are radially outside on both sides of the friction lining carrier 29 attached, for example glued or hung with this. The friction lining 29 is radially inside by means of the rivet 30th with the output hub 31 connected by means of the internal teeth 32 is rotationally connected to an external toothing of a downstream drive train device, for example a double clutch, a torque converter, the rotor of an electric machine or the like and can provide a secondary mass.

With the drive plate 24 is the support disc 33 rotatably connected, for example here radially outside rotationally fixed in the drive plate 24 hung. Between the support disc 33 and the drive plate 24 is the disc spring 34 arranged here, for example, radially outwardly rotationally fixed in the drive plate 24 is attached. Axially between the support disc 33 and the counter disc 25th are those on both sides of the friction lining 29 attached friction linings 27 , 28 axially from the disc spring 34 arranged prestressed. Frictional engagement is formed between the friction surfaces of the friction linings 27 , 28 and the counter friction surfaces 35 , 36 the support disc 33 and the counter disc 25th with a specified friction torque, which is the maximum over the torsional vibration damper 1 sets transmittable torque. This is for example dependent on the friction surface of the frictional engagement and by means of the plate spring 34 set. Between the friction linings 27 , 28 and the friction lining 29 a pad suspension can be provided.

Exceeds this on the torsional vibration damper 1 applied torque, for example as a result of impacts, the frictional torque of the torque limiting device 5 , it slips through, so that the components of the torsional vibration damper 1 and the downstream drive train device, for example gear components of a downstream gear, are protected from overload.

Due to an activated torque limiting device 5 with one facing the entrance part 2 twisting Output hub 31 can use the fastening screws 14th and the access openings 40 be rotated against each other, so that a dismantling of the torsional vibration damper is necessary for the given occasion 1 is made difficult by the crankshaft. The torque limiting device 5 therefore has the release device 37 to the frictional engagement of the torque limiting device 5 to pick up and the output hub 31 essentially without the influence of the torque limiting device 5 opposite the entrance part 2 to be able to turn so that the fastening screws 14th and the access openings 40 align again without the torsional vibration damper 1 having to disassemble it yourself.

For this purpose, in the embodiment shown, the release device 37 from at least one in the counter pane 25th introduced thread 38 formed in the one in the direction of the arrow 39 effective means such as a screw is inserted that the disc spring 34 axially loaded on the outside, whereby this from the support disc 33 lifts off and the frictional engagement between the counter friction surfaces 35 , 36 and the friction linings 27 , 28 cancels.

The torsional vibration damper is designed to improve torsional vibration isolation 1 via the centrifugal pendulum acting on the output side 41 . The friction lining is used for this purpose 29 as a pendulum mass carrier, on which the pendulum masses shown only schematically are distributed over the circumference on both sides 42 are absorbed pendulum. The 2 shows a sectional detail of FIG 1 in the area of the torque limiting device 5 with the one from the drive plate 24 and the counter disc 25th formed friction lining cage 26th and the one received by it on the friction lining carrier 29 attached friction linings 27 , 28 . These are from the disc spring 34 between the support disc 33 and the counter disc 25th biased. The disc spring 34 is supported radially on the inside on the drive plate 24 and offset radially outwards to form a two-armed lever on the support disc 33 and forms the area of application radially on the outside 43 by means of the release device 37 with the thread 38 . The thread 38 is, for example, machining into the, for example, shaped thickening 44 the counter disc 25th brought in.

The 3 shows a sectional detail of the torsional vibration damper 1 of the 1 along a circumferential direction opposite the intersection line of 2 twisted cutting line with the drive plate 24 and the counter disc 25th , the radially outside by means of the rivets distributed over the circumference 45 to form the friction lining cage 26th are connected to each other and axially between them the friction lining 29 with the friction linings 27 , 28 , the support disc 33 and the disc spring 34 record, tape. The disc spring expanded radially outwards 34 points at least in the area of the rivet 45 Recesses 46 on.

The 4th and 5 show a sectional detail of the torsional vibration damper 1 of the 1 before releasing the torque limiting device 5 by means of the release device 37 ( 4th ) and after releasing the torque limiting device 5 by means of the release device 37 . In the 4th is the frictional engagement between the friction linings 27 , 28 and the counter friction surfaces 35 , 36 the counter disc 25th and the support disc 33 still formed by the disc spring 34 the support disc 33 axially preloaded. The middle 47 in the form of the screw 48 is not yet in the thread 38 brought in.

In the 5 is the means 47 in the form of the screw 48 the release device 37 into the thread 38 screwed in such that the disc spring 34 at their exposure area 43 is axially displaced and from the support disc 33 takes off. This results in the frictional engagement between the friction linings 27 , 28 and the support disc 33 and the counter disc 25th lifted and the friction lining 29 can opposite the drive plate 24 without the friction of the torque limiting device 5 twisted so that the mounting screws 14th and the access openings 40 ( 1 ) on top of each other without dismantling the torsional vibration damper 1 ( 1 ) can be aligned.

The 6th shows the upper part of the opposite to the torsional vibration damper 1 regarding its release device 37a modified around the axis of rotation d rotatably arranged torsional vibration damper 1a on average. In contrast to the release device 37 of the 1 has the release device 37a over at least one exposure area 43a the disc spring 34a , the opposite of the drive plate 24a and the counter disc 25a is expanded radially. To the release device 37a no additional precautions need to be taken on the torque limiting device 5a necessary. Rather, a commercially available means such as, for example, a screwdriver or the like, only acts on the area of application 43a axially in the direction of the spring device 4a loaded and thus the frictional engagement of the torque limiting device 5a canceled.

The 7th shows a sectional detail of the torsional vibration damper 1a of the 6th in the area of the torque limiting device 5a if the release device is not effective 37a . The disc spring 34a tension the support disc 33a with support radially inwards on the drive plate 24a before so that the friction linings 27a , 28a between the support disc 33a and the counter disc 25a are clamped and develop a predetermined friction torque. The drive plate 24a and the counter disc 25a are radially outward by means of rivets distributed over the circumference 45a riveted together. Here, flaps that are expanded and potted radially outward appear 49a through recesses 46a the disc spring 34a . On the outer circumference of the disc spring 34a can have one or more exposure areas distributed over the circumference 43a be provided. Alternatively, the application area 43a be designed as a circumferential ring, the rivet 45a into the recesses 46a the disc spring 34a immerse.

The 8th shows a sectional detail of the torque limiting device 5a with by means of the release device 37a repealed frictional engagement of the friction linings 27a , 28a opposite the support disc 33a and the counter disc 25a . In this case, a means (not shown), for example one or more screwdrivers or one on several circumferences, moves the areas of application 43a in the direction of the arrow 39a acting combination means the disc spring 34a towards the cover part 7a so that the disc spring 34a from the support disc 33a lifts and the frictional engagement between the friction linings 27a , 28a and the support disc 33a and the counter disc 25a lifted and the friction lining 29a opposite the drive plate 24a without that from the torque limiting device 5a in the not triggered state provided frictional torque can be rotated.

List of reference symbols

1

Torsional vibration damper

1a

Torsional vibration damper

2

Input part

3

Output part

4th

Spring device

4a

Spring device

5

Torque limiting device

5a

Torque limiting device

6th

Disc part

7th

Cover part

7a

Cover part

8th

Annular chamber

9

Bow feather

10

Sliding cup

11

Loading area

12

Loading area

13

Encoder marking

14th

Fastening screw

15th

Mounting hole

16

Run-up disc

17th

Flange part

18th

poor

19th

Main riveting

20th

rivet

21st

Disc spring diaphragm

22nd

Friction ring

23

Axial sealing ring

24

Drive plate

24a

Drive plate

25th

Counter disc

25a

Counter disc

26th

Friction lining cage

27

Friction lining

27a

Friction lining

28

Friction lining

28a

Friction lining

29

Friction lining

29a

Friction lining

30th

rivet

31

Output hub

32

Internal gearing

33

Support disc

33a

Support disc

34

Disc spring

34a

Disc spring

35

Counter friction surface

36

Counter friction surface

37

Release device

37a

Release device

38

thread

39

arrow

39a

arrow

40

Access opening

41

Centrifugal pendulum

42

Pendulum mass

43

Loading area

43a

Loading area

44

thickening

45

rivet

45a

rivet

46

Recess

46a

Recess

47

medium

48

screw

49a

Tab

d

Axis of rotation

QUOTES INCLUDED IN THE DESCRIPTION

This list of the documents listed 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 19700851 A [0006]
• DE 19728422 A [0006]
• DE 102014211603 A [0007]

Claims (10)

Torsional vibration damper (1, 1 a) with an input part (2) arranged to be rotatable about an axis of rotation (d) and an output part (3) which can be rotated to a limited extent about the axis of rotation (d) against the action of a spring device (4, 4a) and a torque limiting device (5, 5a) for limiting a torque that can be transmitted via the torsional vibration damper (1, 1a), the torque limiting device (5, 5a) being arranged between a flange part (17) acting on the spring device (4, 4a) on the output side and an output hub (31) and a frictional engagement of the torque limiting device (5, 5a) is set to a maximum transmittable torque of the torsional vibration damper (1, 1a), characterized in that a releasing device (37, 37a) for releasing the frictional engagement without disassembling the torque limiting device (5, 5a) the torque limiting device (5, 5a) is provided. Torsional vibration damper (1, 1a) according to Claim 1 , characterized in that the torque limiting device (5, 5a) has a friction lining cage (26) made up of a driving disk (24, 24a) connected to the flange part (17) and a counter-disk (25, 25a) connected to it and in the friction lining cage (26) recorded friction linings (27, 27a, 28, 28a) which are attached to a friction lining carrier (29, 29a) connected to the output hub (31) and which adjust the friction torque with the friction lining cage (26), which by means of a disc spring supported on the friction lining cage (26) (34, 34a) are axially biased contains. Torsional vibration damper (1, 1a) according to Claim 2 , characterized in that the disc spring (34, 34a) is supported on the drive plate (24, 24a) against a support disc (33, 33a) which is held in a rotationally fixed manner on the friction lining cage (26) and forms frictional contact with one of the friction linings (27, 27a) is. Torsional vibration damper (1, 1a) according to Claim 2 or 3 , characterized in that the release device (37, 37a) is formed from the plate spring (34, 34a) and means (47) which cancel its effect. Torsional vibration damper (1) Claim 4 , characterized in that at least one thread (38) is provided on the friction lining cage (26) for receiving a screw (48) which axially acts on the plate spring (34). Torsional vibration damper (1) Claim 5 , characterized in that the at least one thread (38) is introduced radially on the outside in the counter disk (25) and a recess is provided in the drive disk (24) in a circumferential area of the at least one thread (38). Torsional vibration damper (1a) Claim 3 or 4th , characterized in that the plate spring (34a) has at least one application area (43a), which is radially expanded beyond the friction lining cage, for the axial application. Torsional vibration damper (1a) Claim 7 , characterized in that the impingement area (43a) is designed to be closed over the circumference and recesses (46a) are provided in radially inside the impingement area (43a) and the drive plate (24a) and the counter disc (25a) penetrate through the recesses (46a) Lugs (49a) of the drive plate (24a) are connected to one another. Torsional vibration damper (1, 1a) according to one of the Claims 1 to 8th , characterized in that a centrifugal pendulum (41) is received in the torsional vibration damper (1, 1a), in particular on the output side. Torsional vibration damper (1, 1 a) according to Claim 9 , characterized in that pendulum masses (42) distributed over the circumference on both sides of the friction lining carrier (29, 29a) in the centrifugal force field of the torsional vibration damper (1, 1a) rotating about the axis of rotation (d) are accommodated by means of self-aligning bearings along a predetermined pendulum path.

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