DE102019120219A1 - Vibration damping unit with a release device for a torque limiter - Google Patents

Abstract

The invention relates to a vibration damping unit (1) for a motor vehicle drive train, with a spring damper (5) having a primary part (2) and a secondary part (4) which is resiliently supported relative to the primary part (2) about a central axis of rotation (3) in one direction of rotation, and a torque limiter (8) having two friction partners (6, 7) permanently connected to one another in a rotationally fixed manner up to a certain torque threshold in one operation, a first friction partner (6) in an axial direction of the axis of rotation (3) between two subsegments (51, 52 ) a second friction partner (7) is clamped with a certain contact pressure, a centrifugal pendulum (9) being present, from which centrifugal pendulum (9) several pendulum masses (11) radially within a contact point (13a, 13b) and at least partially axially at the same height as the first friction partner (6), with a disengagement device (47) which to r receiving one of the two subsegments (51, 52), formed by reducing the contact pressure spreading disengagement means (48) is present.

Description

The invention relates to a vibration damping unit for a (preferably hybrid / hybridized) motor vehicle drive train, such as a drive train of a car, truck, bus or other commercial vehicle, with a primary part and a secondary part which is resiliently supported relative to the primary part about a central axis of rotation in one direction of rotation Spring damper, and a torque limiter that has two friction partners that are permanently connected to each other up to a certain torque threshold in one operation, with a first friction partner (the torque limiter) being clamped in an axial direction of the axis of rotation between two subsegments of a second friction partner (the torque limiter) with a certain contact force is.

The prior art of the generic type is already well known. For example, US 2014/0221106 A1 discloses a device for transmitting drive power in different designs.

In the case of the designs known from the prior art, however, it has been found to be disadvantageous that the implemented vibration damping units are often relatively large. At the same time, the previously known vibration damping units can be dismantled with relatively great effort.

It is therefore the object of the present invention to remedy the disadvantages known from the prior art and in particular to provide a vibration damping unit which has a compact design while developing the most effective vibration damping behavior in a hybrid motor vehicle drive train and easily dismantles what should be .

This is achieved according to the invention in that there is a centrifugal pendulum, of which a plurality (preferably at least four) pendulum masses are arranged radially within a contact point formed between the friction partners and at least partially axially at the same height as the first friction partner, with a release device which is used for Receipt of a release means that spreads the two subsegments, while reducing the contact pressure, is provided

On the one hand, the provision of the centrifugal pendulum enables effective vibration damping. Furthermore, this centrifugal pendulum is nested radially and axially with the torque limiter to save space. At the same time, due to the radially outer arrangement of the torque limiter in relation to the centrifugal pendulum, a safe and effective safety function is made possible by the torque limiter. By providing the disengaging device, the torque limiter can be disengaged in a simple manner during dismantling, so that the dismantling process can be carried out particularly safely.

Further advantageous embodiments are claimed with the subclaims and explained in more detail below.

Accordingly, it is also advantageous if the first friction partner is connected to the secondary part and the second friction partner is part of a housing of the centrifugal pendulum that receives the pendulum masses. The structure of the entire vibration damping unit is thus further simplified and made even more compact.

In this context, it is therefore also expedient if the pendulum masses are arranged radially inside and / or axially offset from a plurality of helical compression springs of the spring damper that are distributed in a circumferential direction.

It has been found to be an advantageous embodiment that is as simple as possible to manufacture if the release device has at least one through hole provided with an internal thread and made in a first partial segment. The corresponding through hole is used for dismantling purposes in a workshop for screwing in a screw, whereby the torque limiter can be disengaged in a few additional work steps.

For the uniform disengagement of the torque limiter it had also been found to be expedient if several, particularly preferably four to twelve, through holes distributed in a circumferential direction are provided in the first sub-segment.

If the at least one through hole is attached radially inside the first friction partner, the dismantling effort is further facilitated.

It is also advantageous if the at least one through hole is arranged so as to overlap radially with respect to a second subsegment which is pressed against the first friction partner by means of a plate spring. Thus, the entire structure of the release device is held securely.

In this context, it is also expedient if the at least one through hole overlaps radially to form one radially is arranged inside protruding tab of the second subsegment.

If the internal thread of the at least one through hole is implemented as a standard thread (preferably a metric ISO thread), the dismantling effort in the workshop is significantly reduced, since existing screws can be used to disengage the torque limiter.

Furthermore, it is also expedient if the first sub-segment directly forms a first side plate of the housing and / or the second sub-segment directly forms the pressure plate. This cleverly integrates the torque limiter in the centrifugal pendulum.

The second subsegment also advantageously has a support point / support collar (preferably formed by a tab) which, in the pressed-on position of the torque limiter, is applied to an axially fixed component.

In other words, according to the invention, a vibration damping unit with a release device is implemented for a torque limiter. This damping unit is proposed to be provided as an assembly consisting of a torsional vibration damper (spring damper) and a downstream torque limiter or slipping clutch, the torsional vibration damper being screwable on the input side to the crankshaft or the flywheel on the internal combustion engine. According to the invention, a centrifugal pendulum is provided radially and axially within the torque limiter so that no two-part hub needs to be used. In order to nevertheless enable the dismantling of the complete assembly (separation of the screw connection on the input side) after the torque limiter has triggered, it is also proposed to use a device for disengaging the torque limiter - preferably a threaded hole for screwing in a screw which, when screwed in, the pressure plate or the disc spring disengages - to be provided.

The invention will now be explained in more detail below with reference to figures.

• 1 eine Längsschnittdarstellung einer erfindungsgemäßen Schwingungsdämpfungseinheit nach einem bevorzugten Ausführungsbeispiel, wobei mehrere einen Drehmomentbegrenzer ausdrückende Schrauben bereits in einem Teilsegment des Drehmomentbegrenzers / eines Fliehkraftpendels eingeschraubt sind,
• 2 eine Längsschnittdarstellung eines in 1 eingesetzten Teilzusammenbaus aufweisend den Drehmomentbegrenzer und das Fliehkraftpendel, wobei die Schnittebene derart versetzt zu einer in 1 gewählten Schnittebene ist, dass nun zwei der vorhandenen Schrauben geschnitten dargestellt sind,
• 3 eine Detailansicht des in 2 mit „III“ gekennzeichneten Bereiches,
• 4 eine Vollansicht des Teilzusammenbaus nach 2 von einer Rückseite,
• 5 eine Längsschnittdarstellung des Teilzusammenbaus, ähnlich zu 2, wobei zur Veranschaulichung eines die Schrauben aufnehmenden Durchgangslochs die Schrauben weggelassen sind,
• 6 eine Detailansicht des in 5 mit „VI“ gekennzeichneten Bereiches, sowie
• 7 eine Vollansicht des Teilzusammenbaus nach 5 von einer Vorderseite.

Show it:

• 1 a longitudinal sectional view of a vibration damping unit according to the invention according to a preferred embodiment, wherein several screws expressing a torque limiter are already screwed into a sub-segment of the torque limiter / a centrifugal pendulum,
• 2 a longitudinal sectional view of an in 1 The subassembly used has the torque limiter and the centrifugal pendulum, the sectional plane being offset in this way to an in 1 selected cutting plane is that two of the existing screws are now shown cut,
• 3 a detailed view of the in 2 with "III" marked area,
• 4th a full view of the partial assembly according to 2 from a back,
• 5 a longitudinal sectional view of the partial assembly, similar to FIG 2 The screws are omitted to illustrate a through-hole receiving the screws,
• 6 a detailed view of the in 5 area marked with "VI", as well as
• 7th a full view of the partial assembly according to 5 from a front.

The figures are merely of a schematic nature and are used exclusively for understanding the invention. The same elements are provided with the same reference symbols.

With 1 is a vibration damping unit according to the invention 1 according to a preferred embodiment shown clearly in terms of their structure. The vibration damping unit 1 is designed for a hybrid motor vehicle drive train. Consequently, the vibration damping unit serves 1 for vibration damping of torsional vibrations that occur during operation of the motor vehicle drive train. The vibration damping unit 1 is typically used between a crankshaft of an internal combustion engine and a transmission of the drive train viewed along a torque transmission path. The vibration damping unit 1 essentially has three components. A first component is a spring damper 5 realized, a second component as a torque limiter 8th and a third component as a centrifugal pendulum 9 . These three components 5 , 8th , 9 are arranged in series / behind one another along the torque transmission path.

Regarding the spring damper 5 is in 1 continue to recognize that this is a primary part 2 has, which in operation in a typical manner via one or more (first) screws distributed in the circumferential direction 28 is firmly attached to the crankshaft of the internal combustion engine or a flywheel / flywheel. The primary part 2 is designed like a housing and takes in a receiving space 34 (axial receiving space) a secondary part 4th on that in one certain angle of rotation range in relation to a central axis of rotation 3 relatively rotatable to the primary part 2 is arranged. The spring damper 5 is thus implemented as a two-mass flywheel.

The axial, radial and circumferential directions used herein relate to the central axis of rotation 3 the vibration damping unit 1 so that under the axial direction / axial a direction along / parallel to the axis of rotation 3 , under radial direction / radial a direction perpendicular to the axis of rotation 3 and under the circumferential direction, a direction tangential to a direction concentric about the axis of rotation 3 is to be understood circumferential line.

Primary part 2 and abutment 4th are typically distributed over several helical compression springs in the circumferential direction 14th in a direction of rotation / the circumferential direction are resiliently supported relative to one another. The spring damper 5 is designed in this version as a bow spring damper, the helical compression springs 14th extend in a substantially arcuate manner in the circumferential direction. Radially outside the helical compression springs 14th arranged shells 35 serve to guide / support the respective helical compression spring 14th . The helical compression spring is available in other versions 14th Can also be designed in other ways, for example in the form of a helical compression spring extending in a straight line.

As in 1 can be seen with the secondary part shaped as a disk / wheel 4th the torque limiter 8th connected. The torque limiter 8th has a receiving element 30th on that on the abutment 4th is attached. The receiving element 30th is also implemented essentially in the form of a disk. The receiving element 30th is via a (second) riveted joint 33 on the secondary part 4th attached. One of several fastening means distributed in the circumferential direction 32 the (second) riveted joint 33 is in 1 to recognize. From this riveted joint 33 the receiving element extends from 30th in the radial direction outwards and in the axial direction away from the secondary part 4th so that it is adjacent to the helical compression springs on its radial outside in the axial direction 14th as well as the primary part 2 is offset.

For the further construction of the torque limiter 8th also be on the 2 to 7th referenced. From this it is clear in each case that on the receiving element 30th a first friction partner 6 of the torque limiter 8th directly attached / attached. A second friction partner 7th is according to the invention in a housing 12th of the centrifugal pendulum 9 directly integrated. The first friction partner 6 is between two side panels 10 , 18th of the housing 12th / of the second friction partner 7th held clamped / frictionally applied with a pretensioning force.

The torque limiter 8th is typically implemented as a slip clutch. The torque limiter 8th is therefore designed in such a way that the two friction partners 6 , 7th are permanently coupled to one another in a rotationally fixed manner below a certain torque threshold during operation of the drive train. The first friction partner is below the torque threshold 6 such between the side panels 10 , 18th is pinched that the two friction partners 6 , 7th are rotatably connected up to the torque threshold. When the specific torque threshold is exceeded, the torque limiter opens 8th self-employed. The axial frictional force / adhesive force between the two friction partners 6 , 7th is therefore so large that the two friction partners 6 , 7th are rotated relative to one another only after the torque threshold has been exceeded and then moved relative to one another with targeted friction.

The first friction partner 6 has a carrier made of sheet metal 29 on, which is from one with the receiving element 30th connected fastening area 37 extends radially inwardly away. The carrier 29 is about several rivets 36 (alternatively also screws) on the receiving element 30th attached ( 2 ). On a radial inside of the carrier 29 are friction linings on each axial side 24a , 24b arranged. A first friction lining 24a is to a first axial side on the carrier 29 appropriate; a second friction lining 24b is on a second axial side opposite the first axial side on the carrier 29 appropriate.

In this context goes out 3 also shows that the second friction partner 7th directly through a first side panel 10 is trained with. The first side panel 10 is to the first axial side of the beam 29 arranged towards. A second side panel 18th is axially spaced from the first side plate 10 arranged and takes the first friction partner 6 between its the first side panel 10 facing axial side and the first side plate 10 on. The second side panel 18th is also indirect via a disc spring 38 as well as one through the disc spring 38 pressurized pressure plate 39 frictionally with the first friction partner 6 coupled. A first point of contact 13a is between the first friction partner 6 / the first friction lining 24a and a side face 17th of the first side panel 10 implemented while a second contact point 13b between the pressure plate 39 and the first friction partner 6 / the second friction lining 24b is implemented.

Hence is a first sub-segment 51 of the second friction partner 7th completely and solely through the first side panel 10 implemented. A second Sub-segment 52 of the second friction partner 7th is through the pressure plate 39 implemented. The second subsegment is in further versions 52 but also as an alternative to the disc spring 38 or the second side panel 18th educated. Accordingly, the first friction partner is 6 axially between the two subsegments 51 , 52 trapped.

It is also located between the second side panel 18th and the second sub-segment 52 the disc spring 38 . That of the plate spring 38 has a first end area directly on the second side panel 18th supported and with a second end region directly on the second subsegment 52 supported so that the second subsegment 52 / the pressure plate 39 with a certain axial preload against the first friction partner 6 (/ second friction lining 24b ) is pressed.

According to the invention is now a release device 47 in which the torque limiter 8th with training area of the housing 12th integrated. The release device 47 serves to accommodate one of the two subsegments 51 , 52 for dismantling purposes expanding release agent 48 . The release agent 48 is with the 1 to 3 shown in detail. The release agent 48 is realized by several screws arranged distributed in the circumferential direction. The release agent 48 forming screws are implemented as standard screws. In particular, the release device 47 for receiving the release means 48 one then with the 5 to 7th (first) through hole to be seen more closely 50 on.

Hence, there are a plurality of first through holes 50 , in this version four first through holes 50 , intended. The first through holes 50 are in this version directly the first subsegment 51 / Page sheet 10 brought in. Every first through hole 50 penetrates the first subsegment 51 radially within the first friction partner 6 in the axial direction. Every first through hole 50 has an internal thread 49 and is consequently implemented as a threaded hole. The internal thread 49 is, as already mentioned, implemented as a standard thread.

As well as particularly good from the 2 , 3 , 5 and 6 is the respective first through hole 50 in the radial direction level with / overlapping with the pressure plate 39 arranged. The pressure plate 39 / the second sub-segment 52 for this purpose has a radially inward over the first friction partner 6 protruding tab 40 on. The tab 40 is slightly axial in this embodiment, from the first subsegment 51 away, bent. This results in the release means when the respective one is screwed in 48 forming screw into the first through hole 50 to a face contact of this screw 48 on the pressure plate 39 and thus to an axial pressing apart of the two subsegments 51 , 52 . Thus becomes the torque limiter 8th fully ventilated / disengaged.

In the completely (manually) by the release means 48 disengaged position of the torque limiter 8th is the second sub-segment 52 with a radial inside of one support point 53 forming bent end of the tab 40 axially on the second side plate 18th at. In 3 is this support point 53 but still to the second side panel 18th spaced.

Furthermore, it should be noted in this context that in 3 it can also be seen that a spacer bolt described in more detail below 21st for non-rotatable support of the pressure plate 39 via its tab protruding radially inwards 40 is arranged.

It is also with the 2 , 3 and 7th also recognizable that the two side panels 10 , 18th over a plurality of spacer elements distributed in the circumferential direction and in the radial direction 19th , 20th , 21st are firmly connected. A first group of first spacer bolts 20th is arranged on a radially smaller circumference than a second group of second spacer bolts 21st . Furthermore, as in connection with the 1 and 7th Also illustrated are a plurality of spacer plates distributed in the circumferential direction, one of which in FIG 1 is easy to recognize in the section. The spacer plate 19th on the one hand radially outside of the spacer bolts 20th , 21st arranged and on the other hand radially outside of several pendulum masses 11 arranged.

The respective spacer plate 19th is towards its axial end faces over a caulking area 22nd / Riveting area with the respective side plate 10 , 18th connected / riveted / caulked. In this context, the spacer device of the WO 2007/124709 A1 referenced, their design for the connection between the spacer plate 19th and the respective side panel 10 , 18th is deemed to be incorporated therein. Hence the spacer plate 19th via finger-shaped, integral projections 46 that the caulking area 22nd form directly with, in radial recesses 45 of the respective side plate 10 , 18th , riveted. The recesses 45 that have some kind of tooth contour 44 train are in 7th using the first side plate as an example 10 shown.

Coming back to that 1 and 2 is the further construction of the centrifugal pendulum 9 clear. In this context, in 1 one of several, here four, pendulum masses distributed in the circumferential direction 11 recognizable. The respective pendulum mass 11 is independent of the other pendulum masses 11 in a typical way according to the implementation as a centrifugal pendulum 9 recorded freely oscillating in a centrifugal force field. In 7th are guide pins in this context 41a , 41b the respective pendulum mass 11 , each guided in a setting 42a , 42b of the side panels 10 , 18th illustrated. Along these scenes 42a , 42b the pendulum masses oscillate 11 consequently both in the circumferential direction and in the radial direction.

With 1 is also the arrangement according to the invention between the three components of the vibration damping unit 1 to recognize. It can be seen here that spring damper 5 , Torque limiter 8th and centrifugal pendulum 9 are arranged relative to one another that the pendulum masses 11 radially within between the friction partners 6 , 7th trained contact points 13a , 13b as well as axially at the same height as the first friction partner 6 are located. The side panels 10 , 18th extend while forming the housing 12th , so far in the radial direction inward from the first friction partner 6 away that the pendulum masses 11 axially between these side plates 10 , 18th are added and axially protruded from these.

The first side panel 10 also has a deliberately resilient stop 15th on. This attack 15th is by an axially bent or deep-drawn collar area 16 of the first side panel 10 implemented. The attack 15th is to the radial inside of the first side panel 10 , radially within the pendulum masses 11 , arranged. This attack 15th serves specifically for resilient support / as resilient end stop for the respective pendulum mass 11 in a radially inwardly deflected position. When this radially inwardly deflected position is reached, the stop is 15th targeted by the respective pendulum mass 11 elastically deformed to the impact energy of the pendulum mass 11 record.

In this context, it should also be noted that in the illustrated embodiment, the stop 15th as a ring-shaped, ie completely circumferential, collar area 16 is implemented. In further embodiments according to the invention, the stop is 15th however, it is also realized by a plurality of subregions distributed in the circumferential direction and spaced apart from one another. Preferably each pendulum mass 11 a separate section is provided. In further embodiments according to the invention, it is also not only on the first side panel 10 , but also on the second side panel 18th an attack 15th realized. Alternatively to this is the stop 15th also exclusively in further embodiments according to the invention on the second side panel 18th educated.

The second side panel 18th is next to a central hub 25th non-rotatably attached. The hub 25th is prepared in the usual way for non-rotatable connection with another shaft, such as a connecting shaft or a transmission input shaft. The hub 25th has for this purpose on its radial inner side a cup area provided with a serration / internal toothing 43 on ( 1 ). hub 25th and second side panel 18th are via a (first) riveted connection 26th non-rotatably connected to each other.

In the hub 25th are also several, each with a screw 28 in an initial position of the vibration damping unit 1 aligned / aligned second through holes 27 brought in. Every other through hole 27 serves to push the screw through 28 during installation. The second through hole 27 is consequently dimensioned larger than a maximum diameter of the screw 28 .

Furthermore, as in 1 indicated in principle with regard to its possible position, it is also advantageous if each pendulum mass 11 axially with at least one friction element 23 , preferably in the form of a disk. The respective friction element 23 is preferably made of a plastic. The friction element 23 is axial between the pendulum mass 11 and the first side panel 10 , alternatively or additionally also between the pendulum mass 11 and the second side panel 18th , used. The friction element 23 is preferred on the pendulum mass 11 held and is located with the respective side panel 10 , 18th in frictional contact. The friction element 23 is also axially against the respective side plate by means of a spring element 10 , 18th pressed on.

It should also be noted that both side panels 10 , 18th with axial windows 31 are provided which windows 31 each greater than a first friction partner 6 indirect (or the receiving element 30th direct) non-rotatably on the secondary part 4th fixing fastener 32 , which is implemented as a rivet, are formed, as in the 1 and 2 to recognize.

In other words, is the vibration damping unit according to the invention 1 designed to improve the damping of the system. A centrifugal pendulum is used for this 9 used. As the installation position of the centrifugal pendulum 9 becomes the space below the torque limiter 8th used. This makes a two-part hub 25th not possible or less useful. A solution is therefore made available to reduce the slip torque of the torque limiter 8th to take back during its dismantling phase without the need for additional parts.

This results in the following individual additional ideas that are in principle independent of one another 1 to 10 : 1. There is / are one / more hole (s) (first through holes) 50 ) with internal thread 49 present, being in the bore 27 no part is initially screwed in the end product. 2. When screwing in a screw (release means 48 ) into this hole 50 the transmitted torque is reduced. The transmitted torque can advantageously be reduced to ONm. 3. The screw 48 actuates a pressure plate via its axial movement 39 or a disc spring 38 that are involved in the axial flow of force to generate slipping torque. 4. On the pressure plate 39 or the phone pen 38 there is a contact to the screw on one side 48 provided and on the other side a support point 53 that is only used when pressing. 5. The thread 49 is a standard thread. One advantage of this is that standard screws are available in every workshop. 6. The number of tapped holes is located between four and twelve. This guarantees a clean lift.

Furthermore, with the 1 to 7th the moment limiter 8th shown in different views and sectional views. The version shown is in the 1 to 4th with screwed in screws 48 shown with the screws 48 are not included in the end product and will only be screwed in in the workshop. The moment limiter 8th is located between a torsion damper, for example 5 , connected to a combustion engine, not shown, via the screw 28 , and a transmission input shaft. The moment limiter 8th includes two side panels 10 , 18th and a centrifugal pendulum absorber 9 . A disc spring 38 pushes over a pressure plate 39 the toppings 24a , 24b . The moment is via a flange (receiving element 30th ) into the friction plate (carrier 29 ) and then into the slip clutch 8th directed. The slip clutch linings 24a , 24b transfer the slipping torque into the side plates 10 , 18th . The side panels 10 , 18th are with a hub flange 25th connected. The part 15th contains an internal toothing with which the torque is passed on.

List of reference symbols

1

Vibration damping unit

2

Primary part

3

Axis of rotation

4th

Abutment

5

Spring damper

6th

first friction partner

7th

second friction partner

8th

Torque limiter

9

Centrifugal pendulum

10

first side panel

11

Pendulum mass

12

casing

13a

first point of contact

13b

second contact point

14th

Helical compression spring

15th

attack

16

Collar area

17th

Side face

18th

second side panel

19th

Spacer plate

20th

first spacer bolt

21st

second spacer bolt

22nd

Caulking area

23

Friction element

24a

first covering

24b

second topping

25th

hub

26th

first riveted connection

27

second through hole

28

screw

29

carrier

30th

Receiving element

31

window

32

Fasteners

33

second riveted connection

34

Recording room

35

Bowl

36

rivet

37

Attachment area

38

Disc spring

39

printing plate

40

Tab

41a

first guide pin

41b

second guide pin

42a

first backdrop

42b

second backdrop

43

Bowl area

44

Tooth contour

45

Recess

46

head Start

47

Release device

48

Release agent

49

inner thread

50

first through hole

51

first sub-segment

52

second sub-segment

53

Support point

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

• WO 2007/124709 A1 [0039]

Claims (10)

Vibration damping unit (1) for a motor vehicle drive train, with a spring damper (5) having a primary part (2) and a secondary part (4) which is resiliently supported relative to the primary part (2) about a central axis of rotation (3) in one direction of rotation, and a two permanent spring damper Up to a certain torque threshold in one operation, friction partners (6, 7) having torque limiter (8) that are non-rotatably connected to one another, a first friction partner (6) in an axial direction of the axis of rotation (3) between two sub-segments (51, 52) of a second friction partner (7) is clamped with a certain contact pressure, characterized in that a centrifugal pendulum (9) is present, from which centrifugal pendulum (9) several pendulum masses (11) radially within a contact point (13a, 13b) formed between the friction partners (6, 7) ) and are arranged at least partially axially at the same height as the first friction partner (6), with a release device (47), which for Au A release means (48) which spreads the two subsegments (51, 52) with a reduction in the contact pressure is formed is present. Vibration damping unit (1) according to Claim 1 , characterized in that the first friction partner (6) is connected to the secondary part (4) and the second friction partner (7) is part of a housing (12) of the centrifugal pendulum (9) which accommodates the pendulum masses (11). Vibration damping unit (1) according to Claim 1 or 2 , characterized in that the pendulum masses (11) are arranged radially inside and / or axially offset to a plurality of helical compression springs (14) of the spring damper (5) distributed in a circumferential direction. Vibration damping unit (1) according to one of the Claims 1 to 3 , characterized in that the release device (47) has at least one through hole (50) which is made in a first sub-segment (51) and provided with an internal thread (49). Vibration damping unit (1) according to Claim 4 , characterized in that a plurality of through holes (50) distributed in a circumferential direction are provided in the first partial segment (51). Vibration damping unit (1) according to Claim 4 or 5 , characterized in that the at least one through hole (50) is attached radially inside the first friction partner (6). Vibration damping unit (1) according to one of the Claims 4 to 6 , characterized in that the at least one through hole (50) is arranged so as to overlap radially to form a second partial segment (52) which is pressed against the first friction partner (6) by means of a plate spring (38). Vibration damping unit (1) according to Claim 7 , characterized in that the at least one through hole (50) is arranged so as to overlap radially to form a radially inwardly protruding tab (40) of the second subsegment (52). Vibration damping unit (1) according to one of the Claims 4 to 8th , characterized in that the internal thread (49) of the at least one through hole (50) is implemented as a standard thread. Vibration damping unit (1) according to one of the Claims 1 to 8th , characterized in that the first subsegment (51) directly forms a first side plate (10) of the housing (12) and / or the second subsegment (52) directly forms the pressure plate (39).

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