DE102020102834A1 - Torsional vibration damper - Google Patents

Abstract

The invention relates to a torsional vibration damper (1) with an input part (2) arranged so as to be rotatable about an axis of rotation (d) with fastening openings (15) distributed over the circumference for receiving on a crankshaft of an internal combustion engine and an annular chamber ( 8) of the input part (2) accommodated spring device (4) with respect to this output part (3), which can be rotated to a limited extent about the axis of rotation (d), and contains through openings (40) aligned with the fastening openings (15) prior to assembly of the torsional vibration damper (1) 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) that acts on the spring device (4) on the output side and an output hub (32) and frictional engagement of the torque limiting device (5) a maximum practice The acceptable torque of the torsional vibration damper (1) is set. In order to set the maximum transmissible torque of the torsional vibration damper (1) in a reproducible manner, the torque limiting device (5) contains friction linings (28, 29) outside the annular chamber (8) which form a dry frictional engagement.

Description

The invention relates to a torsional vibration damper with an input part rotatably arranged about an axis of rotation with fastening openings distributed over the circumference for receiving on a crankshaft of an internal combustion engine and an output part that is rotatable to a limited extent about the axis of rotation against the action of a spring device accommodated in an annular chamber of the input part through-openings aligned with the fastening openings prior to assembly of the torsional vibration damper and a torque limiting device for limiting a torque that can be transmitted via the torsional vibration damper, the torque limiting device being arranged between a flange part which acts on the spring device on the output side and an output hub and a frictional engagement of the torque limiting device of the torque limiting device is set to a maximum transmittable torque .

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 support 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 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 input part which is opposite to a spring device the axis of rotation limited rotatable output part. 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. As an alternative or in addition, a secondary flywheel of a subsequent drive train device, for example a double clutch, an electric machine, a hydrodynamic torque converter and / or the like, can be assigned to the output part in a rotationally locked manner.

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, for example divided into two, three or four. 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 is housed in an annular chamber at least partially filled with lubricant, for example oil or grease, which is formed by a disk part having fastening openings on the inlet side for receiving it on the crankshaft and a disk part designed as a cover part facing the output part. The disk parts can have loading devices, for example in the form of embossed areas for loading the spring device on the input side. 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 the flange part that 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.

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 with the counter plate is preferably carried out radially on the outside, so that friction linings can be arranged on both sides in the friction lining cage on both sides radially on the outside. The output hub has a one-piece output flange or one connected to it, for example riveted or welded, which engages the friction lining cage from the radially inside and produces frictional engagement between the friction linings and the friction lining cage. The friction linings can be riveted or glued to the output flange, for example. Alternatively, the output flange can serve as counter friction surfaces for the friction linings attached to the friction lining cage or components connected to it. In the dry mode of operation, the friction linings each form a frictional engagement with the counter-friction surfaces in order 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.

A lining suspension can be provided between the components receiving the friction linings - output flange or components assigned to the friction lining cage, so that the frictional 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 corresponding components.

For example, the plate spring on the counter-disk can be supported against a support disk that forms a frictional contact such as counter-friction surface with one of the friction linings or that receives them and is held non-rotatably on the friction-lining cage. 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 the fastening openings with the fastening screws and pass-through openings twisted against each other, a rotating device for setting a rotational position of the fastening screws with the is located between the input part and the output part Access openings provided by means of a lever tool to restore the aligned position of fastening screws and access openings. The rotating device enables the torsional vibration damper to be removed from the crankshaft without releasing the frictional engagement and without dismantling the torque limiting device. Here, the output part without intervention in the torque limiting device and the input part are rotated against each other against the action of the spring device by means of a lever tool and the fastening screws and the penetration openings are made in alignment with each other again, so that the torsional vibration damper even after the Torque limiting device with a connected rotation between the input part and the output hub is easily possible when the torsional vibration damper is removed from the crankshaft, for example in the event of maintenance.

For this purpose, the rotating device contains a locking device in the cover part facing the torque limiting device and in recesses provided radially at the same height in the friction lining cage, such as recesses for a lever tool, for locking a rotational position set by means of the lever tool engaging in the recesses and rotating the output part and input part against the action of the spring device . This means that the lever tool, for example a screwdriver or a correspondingly prefabricated rotary lever, engages in two recesses offset in the circumferential direction when the torque limiting device is triggered and, based on the leverage of the lever tool, a relative rotation of the input part and output part counter to the effect by applying to the edges of the recesses offset in the circumferential direction the spring device is effected until the fastening screws are aligned with the access openings, the locking device being activated on this rotating device in order to stabilize the aligned rotational position.

The recesses can be arranged in the circumferential direction in such a way that an angle of rotation corresponding to the pitch angle of the fastening screws, for example 60 ° with six fastening screws distributed over the circumference, to achieve the locked position of rotation when the fastening screws and access openings are aligned, at least by rotating the output part accordingly , for example, the friction lining cage opposite the cover part clockwise or counterclockwise is achieved. In this case, if there is a corresponding rotation between the friction lining cage and the output hub when the torque limiting device is triggered, several stages of rotation between the input part and the output part can be achieved by means of corresponding recesses offset in the circumferential direction and circumferentially offset to different extents on the various, for example, in a two-part arc spring arranged diametrically opposite recesses of the Be provided cover part. For example, four stages of rotation between 0 ° and 7.7 °, 7.5 ° and 15 °, 15 ° and 22.5 ° and 22.5 ° and 30 ° can be provided by arranging the recesses and their edges accordingly over the circumference, with a maximum angle of rotation of 30 ° at a pitch angle of 60 °, the adjustment is made to the next aligned pairing of fastening screw and access opening.

The recesses such as cutouts can be provided as axial embossments in the cover part. Embossings can be particularly advantageous which form the loading devices of the arc springs of the spring device axially inwards in the cover part, for example two diametrically opposite axially formed recesses when the arc springs are divided into two. The recesses on the outlet side, such as cutouts, can be designed to be closed or open radially on the outside. For example, the recesses in the friction lining cage can be formed from radially outwardly expanded projections arranged distributed over the circumference, at least some of the projections being able to serve to rivet the drive plate to the counter plate.

The locking device can be formed from locking openings which are aligned in the input part and in the output part when the fastening openings and access openings are aligned, and a locking pin extending through them. For example, corresponding locking openings can be provided in the output flange or in the output hub, which are aligned at a radial height with a corresponding rotational position in the axial direction with locking openings of the disk part having the fastening openings or with a cover disk between the screw heads of the fastening screws and this disk part. The locking openings can be arranged in the circumferential direction between the fastening screws. For example, three to six locking openings distributed over the circumference can each be provided in the input part and output part. A locking pin, for example a steel needle, is inserted through the locking openings when the rotational position is in alignment and the rotational position is thus secured while the torsional vibration damper is removed from the crankshaft.

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 output flange 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 around the axis of rotation are pendulum supported along a given pendulum path by means of self-aligning bearings. The self-aligning bearings can each be provided on axially opposite pendulum masses and the pendulum mass carrier by in the Pendulum masses and in the pendulum mass carrier recesses with arcuate tracks that determine the pendulum track are introduced, 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 eine Ansicht des Drehschwingungsdämpfers der 1 bei nicht ausgelöster Drehmomentbegrenzungseinrichtung,
• 3 eine Ansicht des Drehschwingungsdämpfers der 1 und 2 bei um 30° gegenüber dem die Bogenfedern beaufschlagenden Flanschteil verdrehter Ausgangsnabe und
• 4 - 11 Teilansichten des Drehschwingungsdämpfers der 1 bis 3 bei unterschiedlichen Verdrehzuständen.

The invention is based on the in the 1 to 11 illustrated embodiment 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 view of the torsional vibration damper 1 if the torque limiting device has not been triggered,
• 3 a view of the torsional vibration damper 1 and 2 when the output hub is rotated by 30 ° in relation to the flange part acting on the arc springs and
• 4th - 11 Partial views of the torsional vibration damper of 1 to 3 with different twisting conditions.

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 starting part 3 assigned torque limiting device 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 loading devices 11 , 12 provided, which are designed here as embossments.

Radially outside are on the annular chamber 8th , here on the folded lid 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 by means of the rivet 25th connected counter disc 26th . The drive plate 24 and the counter disc 26th form the friction lining cage 27 , which the friction linings 28 , 29 records. The friction linings 28 , 29 are radially outside on both sides of the output flange 30th attached, for example glued or hung with this. The output flange 30th is radially inside by means of the rivet 31 with the output hub 32 connected by means of the internal teeth 33 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 counter disc 26th is the support disc 34 rotatably connected, for example here radially outside rotationally fixed in the counter disc 26th hung. Between the support disc 34 and the counter disc 26th is the disc spring 35 arranged, which in a manner not shown rotatably with the friction lining cage 27 connected is. Axially between the support disc 34 and the counter disc 26th are on both sides of the output flange 30th attached friction linings 28 , 29 axially from the disc spring 35 arranged prestressed. Frictional engagement is formed between the friction surfaces of the friction linings 28 , 29 and the counter friction surfaces of the support disc 34 and the drive plate 24 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 35 set. Between the friction linings 28 , 29 and the outlet flange 30th 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 32 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 rotating device 36 to reduce the twist between output hub 32 and the input part 2 reset 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 are the on the cover part 7th as a loading device 12 formed embossing as an axially formed recess 37 and in the circumferential direction on the friction lining cage 27 several not visible recesses formed, which by means of a lever tool to rotate the output part 3 opposite the entrance part 2 are acted upon against each other. The execution of such a rotation is described in detail in the following figures.

The torsional vibration damper is designed to improve torsional vibration isolation 1 via the centrifugal pendulum acting on the output side 38 . The outlet flange is used for this 30th as a pendulum mass carrier, on which the pendulum masses shown only schematically are distributed over the circumference on both sides 39 are absorbed pendulum. The 2 and 3 show the around the axis of rotation d rotatable torsional vibration damper 1 of the 1 in view with the starting part 3 and the input part in the background 2 with the encoder markings 13 of the lid part 7th . The bow springs of the spring device are divided into two, so that in the cover part 7th two diametrically opposite, in the lid part 7th axially formed recesses as loading devices for the arc springs 37 , 41 are provided. The recesses 37 , 41 form the input-side part of the rotating device 36 of the torsional vibration damper 1 to allow easy removal of the torsional vibration damper when the torque limiting device is triggered 1 from a crankshaft of an internal combustion engine. The output-side part of the rotating device 36 is by means of the diametrically on both sides of the circumference of the recesses 37 , 41 arranged projections 42 , 43 provided recesses 44 , 45 , 46 , 47 , 48 , 49 , 50 , 51 educated. Depending on the angle of rotation between the output hub 32 and the input part 2 after the torque limiting device has been triggered 5 ( 1 ) is made by means of a lever tool with support on one of the recesses 37 , 41 the output part 3 opposite the entrance part 2 using a lever on one edge of one of the recesses 44 , 45 , 46 , 47 , 48 , 49 , 50 , 51 twisted in one or more stages against the action of the spring device. After reaching the twisted position with aligned fastening screws 14th and access openings 40 is on at least one of the on the output part 3 provided locking openings 52 a fixing of the rotational position relative to the input part is provided by means of a locking pin, for example by inserting it into a complementary locking opening of the input part.

The 2 shows the torsional vibration damper 1 if the torque limiting device has not been activated beforehand 5 so that the at the Output hub 32 provided access openings 40 with the fastening screws 14th of the input part align.

The 3 shows the torsional vibration damper 1 with activated torque limiting device 5 ( 2 ) with a 30 ° opposite the input part 2 twisted output hub 32 of the output part 3 so that direct access to the fastening screws via the access openings 40 not possible.

The 4th to 11 show a multi-stage reverse rotation of the twisted state of the torsional vibration damper 1 corresponding 3 . Here, in each figure, a detail of the corresponding rotational position is above a 3D partial view of the torsional vibration damper 1 with the position of the lever tool before and after the partial rotation of a stage.

The 4th shows the initial state of the reverse rotation from the rotated position I. at an angle of 7.5 °. This is where the lever tool 53 obliquely between the recess 37 and that of the lead 42 next recess 44 inserted and in the direction of the arrow 54 relocated. The friction lining cage 27 and thus the starting part 3 shifts by 7.5 ° compared to the cover part 7th and thus opposite the entrance part 2 according to the twist position II of the 5 .

Starting from the twist position II of the 6th is in the twisted position after locking II the lever tool 53 or possibly another lever tool between the recess 41 of the lid part 7th and the one opposite the projection 42 circumferentially extended projection 43 next recess 45 inserted and in the direction of the arrow 54 twisted so that the starting part 3 by a further 7.5 ° to 15 ° opposite the entrance part 2 in the twisted position III of the 7th is twisted.

From the in 8th rotation position shown III a further 7.5 ° rotation takes place using the lever tool 53 into the recess 37 and in the opposite of the ledge 42 next but one recess 46 inserted and in the direction of the arrow 54 in the twisted position IV of the 9 is twisted.

From the twisted position IV of the 10 there is a last rotation to the last rotation position E. of the 11 if the fastening screws are in alignment with the access openings, by using the lever tool 53 into the recess 41 and in the opposite of the ledge 43 other next recess 49 inserted and in the direction of the arrow 54 is twisted.

It goes without saying that a rotation in the opposite direction of rotation against the arrow 54 by alternating use of the recesses 48 , 49 , 50 , 45 can be done. The recesses 47 , 51 can be used for further rotation options.

List of reference symbols

1

Torsional vibration damper

2

Input part

3

Output part

4th

Spring device

5

Torque limiting device

6th

Disc part

7th

Cover part

8th

Annular chamber

9

Bow feather

10

Sliding cup

11

Loading device

12

Loading device

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

25th

rivet

26th

Counter disc

27

Friction lining cage

28

Friction lining

29

Friction lining

30th

Outlet flange

31

rivet

32

Output hub

33

Internal gearing

34

Support disc

35

Disc spring

36

Rotating device

37

Recess

38

Centrifugal pendulum

39

Pendulum mass

40

Access opening

41

Recess

42

head Start

43

head Start

44

Recess

45

Recess

46

Recess

47

Recess

48

Recess

49

Recess

50

Recess

51

Recess

52

Locking opening

53

Lever tool

54

arrow

I.

Twist position

II

Twist position

III

Twist position

IV

Twist position

E.

Twist position

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) with an input part (2) arranged so as to be rotatable about an axis of rotation (d) with fastening openings (15) distributed over the circumference for receiving on a crankshaft of an internal combustion engine and an annular chamber (8) of the input part that is counter to the action in a lubricant (2) received spring device (4) with respect to this limited about the axis of rotation (d) rotatable output part (3) containing with the fastening openings (15) aligned before mounting of the torsional vibration damper (1) and a torque limiting device (5) for limitation a torque which 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 (32) and a frictional engagement of the torque limiting device (5) on a maximum transmittable torque of the Dre hschwingungsdämpfers (1) is set, characterized in that the torque limiting device (5) outside of the annular chamber (8) contains friction linings (28, 29) which form a dry frictional engagement. Torsional vibration damper (1) Claim 1 , characterized in that the torque limiting device (5) received a friction lining cage (27) made up of a drive plate (24) connected to the flange part (17) and a counter-disc (26) connected to it and in the friction lining cage (27), between these and a with the output hub (32) connected output flange (30) effectively received, with the friction lining cage (27) the friction torque setting friction linings (28, 29) which are axially pretensioned by means of a plate spring (35) supported on the friction lining cage (27). Torsional vibration damper (1) Claim 2 , characterized in that the plate spring (35) is supported on the counter-disk (26) against a support disk (34) which forms a frictional contact with one of the friction linings (29) and is held non-rotatably on the friction lining cage (27). Torsional vibration damper (1) according to one of the Claim 3 , characterized in that the friction linings (28, 29) are attached to the output flange (30) or to the drive plate (24) and the support plate (34). Torsional vibration damper (1) according to one of the Claims 2 to 4th , characterized in that the output flange (30) is centered with respect to the friction lining cage (27), in particular with respect to the drive plate (24). Torsional vibration damper (1) according to one of the Claims 1 to 4th , characterized in that between the input part (2) and output part (3) a rotating device (36) for restoring the aligned fastening openings (15) and penetration openings (40) after the torque limiting device (5) has been triggered when the torsional vibration damper (1) is removed from the Crankshaft is provided for maintenance. Torsional vibration damper (1) Claim 6 , characterized in that the rotating device (36) in the circumference of a cover part (7) facing the torque limiting device (5) and recesses (37, 41, 44, 45, 46, 47, 48) provided in the friction lining cage (27) at the same radial height , 49, 50, 51) for a lever tool (53) and a locking device for locking an output part (3rd part) that engages in the recesses (37, 41, 44, 45, 46, 47, 48, 49, 50, 51) ) and input part (2) against the action of the spring device (4) twisting lever tool (53) set rotational position (I, II, III, IV, E). Torsional vibration damper (1) Claim 7 , characterized in that the recesses (37, 41) in the cover part (7) as embossings of input-side loading devices (12) of the cover part (7) and the recesses (44, 45, 46, 47, 48, 49, 50, 51) are formed in the friction lining cage (27) between radially outwardly expanded projections (42, 43) distributed over the circumference. Torsional vibration damper (1) Claim 7 or 8th , characterized in that the locking device consists of in the input part (2) and in the output part (3) in the rotational positions (II, III, IV, E) set by the lever tool (53), in particular with aligned fastening openings (15) and through openings (40) aligned locking openings (52) and a locking pin extending through these is formed. Torsional vibration damper (1) according to one of the Claims 1 to 9 , characterized in that in the torsional vibration damper (1) on the output side a centrifugal pendulum (38) is arranged with pendulum masses (39) pendulously received on both sides of the output flange (30) radially inside the friction linings (28, 29).

Images