DE102022111141A1 - Torsional vibration damper with two-part shaft - Google Patents

Abstract

The invention relates to a torsional vibration damper (1) with an input part (10) and an output part (2), which can be rotated to a limited extent relative to one another about an axis of rotation (A) against the action of spring elements (30, 40). The torsional vibration damper (1) has a first shaft (50) which extends coaxially to the axis of rotation (A) and is connected in a rotationally fixed manner to the input part (10) and a first shaft (50) which extends coaxially to the axis of rotation (A) and is connected in a rotationally fixed manner to the output part (2). second wave (51). To rotatably support the torsional vibration damper (1) about the axis of rotation (A), a first bearing (60) is arranged between the first shaft (50) and the second shaft (51), with which the first shaft (50) and the second shaft (51) are mounted rotatably relative to each other.

Description

The present invention relates to a torsional vibration damper with a two-part shaft, for the best possible storage of the torsional vibration damper, with the lowest possible demand on installation space.

In reciprocating piston engines, the periodic sequence of the accelerated piston movement and the gas forces during suction, compression, work and ejection in combination with the firing sequence of the individual cylinders leads to rotational irregularities in the crankshaft and the connected flywheel in the form of a flywheel. Since the drive train is a structure capable of torsional vibrations with characteristic natural frequencies due to the moment of inertia of the rotating components and the rigidity, the rotational irregularities introduced by the motor inevitably lead to torsional vibrations, which, if left undamped, can result in unwanted side effects such as acoustic abnormalities or increased wear of components. To reduce these effects, torsional vibration dampers are used.

Torsional vibration dampers are known from the prior art, which are arranged to compensate for, in particular, torsional vibrations in a drive train of a motor vehicle in order not to pass on the torsional vibrations generated by an internal combustion engine to a transmission and thus increase its service life. A corresponding torsional vibration damper is, for example, from US 2020/0032853 A1 known. In order to compensate for corresponding torsional vibrations, a rotating flywheel is installed on both the engine side and the transmission side. These are arranged coaxially and rotatably relative to one another and are mounted so as to be limited to each other about an axis of rotation of the torsional vibration damper against the action of a spring element. Together, the spring element and the flywheel masses form the core of the torsional vibration damper designed as a dual-mass flywheel. According to the devices known from the prior art, one of the flywheels is connected in a rotationally fixed manner to a corresponding hollow shaft, which in turn is mounted in a rotationally fixed manner on another shaft passing through it. The other flywheel is connected to a gear in a rotationally fixed manner and is mounted on the hollow shaft so that it can rotate relative to the other flywheel against the action of the spring element.

The two-part arrangement of two shafts that are connected to each other in a rotationally fixed manner creates both radial and axial forces due to the forces introduced into the gear, which can lead to a tilting of the flywheel, which is connected to the hollow shaft in a rotationally fixed manner. This in turn places additional stress on the shaft, which is supported by two roller bearings. Furthermore, these forces can also lead to a tilting of the flywheel, which is connected to the hollow shaft in a rotationally fixed manner, relative to the other flywheel.

It is desirable to introduce a torque via a gear mounted between two bearing points on the housing side, to filter out torsional vibrations introduced on the drive side and to divert the introduced torque outside the bearing points on the housing side. In addition, the storage of an input-side gear included in the torsional vibration damper for introducing the torque should be as precise as possible in order to minimize its wear and the associated noise. This would require the gear to be stored at two bearing points on the housing side. The output torque is to be delivered via the output area arranged outside the housing and therefore outside the bearing points. Furthermore, the other components of the torsional vibration damper and the gear should be located within, i.e. between the bearing points on the housing side, for reasons of installation space. The broadest possible support for the components therefore contradicts the desire for the smallest possible installation space for the torsional vibration damper.

Proceeding from this, the present invention is based on the object of at least partially overcoming the problems known from the prior art.

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

The torsional vibration damper according to the invention comprises an input part and an output part, and at least one spring element, wherein the input part and the output part are mounted so as to be limited to each other about an axis of rotation of the torsional vibration damper against the action of the spring element, which extends coaxially to the axis of rotation and is connected in a rotationally fixed manner to the input part first shaft and a second shaft which extends coaxially to the axis of rotation and is non-rotatably connected to the output part, with between At least one first bearing is arranged between the first shaft and the second shaft, with which the first shaft and the second shaft are rotatably mounted relative to one another.

As a precaution, it should be noted that the number words used here (“first”, “second”,...) primarily serve (only) to distinguish between several similar objects, sizes or processes, i.e. in particular no dependency and/or order of these objects , sizes or processes to each other. If a dependency and/or sequence is required, this is explicitly stated here or it will be obvious to the person skilled in the art when studying the specifically described embodiment.

The input part and the output part are a drive-side flywheel and an output-side flywheel, which can be rotated to a limited extent relative to one another about the common axis of rotation against the spring force of the spring element. The output part and/or the input part are preferably designed as a sheet metal element, alternatively preferably as cast or forged parts. Furthermore, the production of the output part and the input part is preferably not limited to these production processes. Preferably, the input part and the output part can each be manufactured using different manufacturing processes.

Preferably, a gear wheel is coaxial with the first shaft and fastened in a rotationally fixed manner on the first shaft, the gear wheel having a toothless region formed towards the second shaft on a circumferential section of its outer peripheral surface. On the circumferential side, the first shaft has a flange section which is designed to create a rotationally fixed connection between the input part, which extends radially and discus-shaped from the first shaft, and a gear. For this purpose, the flange section is designed with bores in the direction of the axis of rotation, through which the gear and the input part are connected in a rotationally fixed manner by means of screw connections to the flange section and thus to the first shaft. The gear is designed to absorb a corresponding torque and to introduce it into or out of the torsional vibration damper.

The second shaft also has a corresponding further flange section with bores formed in the direction of the axis of rotation A on its end facing the first shaft. Coaxial to the second shaft, the output part is designed with a radial and disc-shaped extension starting from the second shaft. Here too, the further bores in the flange section of the second shaft are designed to create a non-rotatable connection between the output part and the second shaft by means of rivets. However, other positive, frictional and/or cohesive types of connection between the input part and the first shaft and the output part and the second shaft are also preferably possible.

In order to create a space-saving storage of the first shaft relative to the second shaft, the second shaft preferably has a longitudinal bore in the direction of the axis of rotation on the side facing the first shaft, the first shaft being rotatably mounted in the longitudinal bore by the first bearing. Furthermore, the first shaft is preferably supported relative to the second shaft radially by the first bearing and in the axial direction by a second bearing. The first and second shafts are thus supported against one another in both the radial and axial directions. The first and second bearings are preferably designed separately, with the first and second bearings being designed as needle bearings or a combination of plain and roller bearings. Preferably, the first and second bearings can also be designed in combination, for example in the form of a plastic bushing with a flange geometry.

Preferably, a first roller bearing is arranged radially above the first bearing and coaxially to the second shaft on the outer circumferential surface of the second shaft, wherein preferably the axial position of the first bearing and the first roller bearing are identical to one another. In contrast, a second rolling bearing is preferably arranged coaxially with the first shaft and on the outer peripheral surface of the first shaft, the second rolling bearing being arranged on the side of the input part facing away from the output part. This arrangement of the first and second bearings and the first and second roller bearings relative to one another achieves optimal concentricity of the first and second shafts and makes possible mechanical tilting of the first shaft relative to the second shaft more difficult. In addition, this saves installation space.

Preferably, the output part has a radial extension relative to the axis of rotation and is formed on the circumference and coaxially to the axis of rotation with a cylindrical section oriented towards the spring element, with a cover extending radially outwards relative to the axis of rotation being preferred, which has a cover on the circumference has a complementary fit to the cylindrical section and is connected in a rotationally fixed manner to the cylindrical section of the output part or the input part. Furthermore, the output part and the cover preferably form a circumferential element between them relative to the axis of rotation Channel, wherein the channel at least partially encloses the spring element both in the radial direction and in the axial direction with respect to the axis of rotation.

A complementary connection between the cylindrical section of the output part and the radially outer end of the cover with respect to the axis of rotation is to be understood as a positive and/or frictional connection between the two elements. For example, the cover can preferably also have, on its radially outward-facing side, a cylindrical section which is positively connected to the cylindrical section of the output part and with which the cover lies at least partially on the circumference of the inner circumference or on the outer circumference of the cylindrical section of the output part. Alternatively, other versions of the connection between the cylindrical section of the output part and the lid are also preferred. The cover is preferably designed as a sheet metal element, alternatively preferably as a cast or forged part. Furthermore, the production of the lid is preferably not limited to these production processes. Preferably, the lid can also be manufactured using various manufacturing processes.

As already explained, the output part and the cover form a channel between them that runs around the axis of rotation, the channel at least partially enclosing the spring element both in the radial direction and in the axial direction with respect to the axis of rotation. The sections of the output part and the cover that extend radially from the axis of rotation are designed to prevent axial slipping of the spring element in the direction of the axis of rotation and to fix it axially. In contrast, the cylindrical section of the output part and the complementary part of the cover serve to guide the spring element in the radial direction, this area being designed as a friction surface for the spring element displacing within the channel. Further stops are preferably also formed on the cover to support the spring element. Instead of one spring element, several spring elements are preferably designed to be distributed over the circumference.

Preferably, the cover is arranged on its radially inner side with respect to the axis of rotation coaxially with the toothless region of the gear and is rotatably mounted on the toothless region by means of a third bearing. If the spring element of the torsional vibration damper is compressed, it presses against the stops of the output part and the cover as well as against the stop of the input part. Since the stops of the cover and the output part are not in exactly the same position in the axial direction as the connection of the output part and the second shaft, but are axially offset, a moment acts on the connection area between the output part and the second shaft. This can lead to the cover and the output part tilting relative to the second shaft. The additional bearing between the cover and the toothless area of the gear ensures additional guidance of the output part extended over the cover and ensures a corresponding counter-torque. Preferably, the third bearing is designed for radial mounting between the cover and the toothless region of the gear and/or axial mounting between the cover and the toothless region of the gear. Like the first and second bearings, the third bearing is preferably designed as a needle bearing or a combination of plain and roller bearings. Preferably, the third bearing can also be designed in combination, for example in the form of a plastic bushing with a flange geometry.

• 1: eine stark abstrahierte Darstellung eines Eingangsteils eines erfindungsgemäßen Drehschwingungsdämpfers;
• 2: eine stark abstrahierte Darstellung eines Ausgangsteils des erfindungsgemäßen Drehschwingungsdämpfers;
• 3: eine stark abstrahierte Darstellung des erfindungsgemäßen Drehschwingungsdämpfers;
• 4: einen schematischen Längsschnitt des erfindungsgemäßen Drehschwingungsdämpfers;

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

• 1 : a highly abstracted representation of an input part of a torsional vibration damper according to the invention;
• 2 : a highly abstracted representation of an output part of the torsional vibration damper according to the invention;
• 3 : a highly abstracted representation of the torsional vibration damper according to the invention;
• 4 : a schematic longitudinal section of the torsional vibration damper according to the invention;

1 shows a highly abstracted representation of an input part 10 of a torsional vibration damper according to the invention. The input part 10 represents a flywheel and is preferably as a sheet metal element, alternatively preferably as a Cast or forged part formed. The input part 10 is designed as a wing flange 20, the wing flange 20 having two wings 22 which are symmetrical to one another and extend radially away from a wing flange body 21. In principle, the input part 10 is not limited to the embodiment of a wing flange 20. In addition, the wing flange body 21 has a recess 24 formed on its outer peripheral surface and coaxial with an axis of rotation A. The wing flange 20 is point-symmetrical to the axis of rotation A. The wings 22 are thus formed opposite one another. The terms radial or radial direction, axial or axial direction and circumferential direction used in this document are always understood in relation to the axis of rotation A, unless explicitly stated otherwise.

2 shows a highly abstracted representation of an output part 2 of the torsional vibration damper according to the invention. The output part 2 is designed as a disc-shaped flywheel, with a recess 3 formed coaxially to the peripheral side. Like the wing flange 20, the output part 2 is preferably designed as a sheet metal element, alternatively preferably as a cast or forged part. The output part 2 has a first channel region 4 and a second channel region 5 on the circumference and opposite one another, which extend over part of the circumference of the output part 2. In addition, the output part 2 has a first stop 6 and a second stop 8 on the radial outside, which are also point-symmetrical to one another, which also extend over part of the circumference of the output part 2 and separate the first and second channel regions 4, 5 from each other . The first stop 6 has a first stop surface 7, which points in the circumferential direction in the direction of the first channel region 4. A second stop surface 18, which is formed on the first stop 6 in the circumferential direction opposite to the first stop surface 7, points in the direction of the second channel region 5. The second stop 8 has a first stop surface 17, which points in the circumferential direction in the direction of the first channel region 4, while an opposite second stop surface 9 points in the direction of the second channel area 5.

3 shows a highly abstracted representation of the torsional vibration damper 1 according to the invention, wherein the previously described output part 2 and the input part 10 are arranged one above the other or coaxially to an axis of rotation A, so that the recesses 3, 24 of the output part 2 and the input part 10 are aligned with one another. According to 3 In addition to the input part 10 and the output part 2, the torsional vibration damper 1 includes a first spring element 30 and a second spring element 40, each of which is designed as a compression spring. The input part 10 in the form of the wing flange 20 is designed to be rotatable relative to the output part 2. The first spring element 30 is mounted in the first channel region 4 of the output part 2 and the second spring element 40 is movably mounted in the circumferential direction in the second channel region 5, the first and second channel regions 4, 5 serving as a guide for the spring elements 30, 40. In the unstressed state, the spring elements 30, 40 have an extension which corresponds to the extension of the channel regions 4, 5 over the circumference of the output part 2. A first stop surface 7 of the first stop 6 is designed to serve as a support for a first end 31 of the first spring element 30, with a second stop surface 9 of the second stop 8 being designed to serve as a support for a first end 41 of the second spring element 40 . The second stop 8 has a first stop surface 17 for supporting the first spring element 30. Furthermore, the first stop 6 has a second stop surface 18 for supporting the second spring element 40. The stop surfaces 17, 18 of the first and second stops 6, 8, which are opposite the stop surfaces 7, 9, are designed to limit the circumference of the other spring element 30, 40, but can also absorb forces if an angular momentum occurs in the opposite direction. Opposite the stop surfaces 7, 9, 17, 18 of the first and second stops 6, 8, the wing flange 20 also has stop surfaces 23 which are designed to provide support for the second end 32, 42 of the first and second spring elements 30, 40, respectively to serve.

The input part 10 in the form of the wing flange 20 represents the driven primary side of the torsional vibration damper 1 and is directly subjected to an external torque and rotated about the axis of rotation A. The output part 2, which is operatively connected to the wing flange 20 via the spring elements 30, 40, is considered below as the secondary side of the torsional vibration damper 1 driven by the primary side. Although not shown, the primary side can preferably be driven by an internal combustion engine, with the secondary side preferably passing on the torque to a transmission attached to it, in particular to a transmission input shaft, not shown.

If the input part 10 is rotated relative to the output part 2, the first and second spring elements 30, 40 are compressed or apply a counter torque that counteracts the rotation. If the drive-side torque on the input part 10 is reduced or the applied torque does not experience any fluctuations, son If it lies evenly, the spring elements 30, 40 can at least partially relax and release their stored energy in order to reverse the rotation of the input part 10 relative to the output part 2.

The 4 shows a schematic longitudinal section of a torsional vibration damper 1 according to the invention, to illustrate further components of the torsional vibration damper 1. The torsional vibration damper 1 comprises a first shaft 50 arranged coaxially to the axis of rotation A and a second shaft 51 also arranged coaxially to the axis of rotation A. The first shaft 50 is relative to the second shaft 51 via a first bearing 60 in a longitudinal bore 52 of the second shaft 51 rotatably mounted. In addition, a second bearing 61 is provided between the first shaft 50 and the second shaft 51, which is designed as a spacer between the first shaft 50 and the second shaft 51 and which supports the first shaft 50 and the second shaft 51 in the axial direction. i.e. supported against each other in the direction of the axis of rotation A.

Starting from the axis of rotation A, the second shaft 51 is rotatably mounted in the radial direction with a first bearing seat 71 by a first roller bearing 70 on a housing, not shown. Accordingly, along the axis of rotation A, the first shaft 50 is rotatably mounted with a second bearing seat 81 by a second roller bearing 80 at its end facing away from the second shaft 51 on the housing, not shown.

On the circumference, the first shaft 50 has a flange section 53, which is designed to create a non-rotatable connection by means of screw connections 54 between the input part 10, which extends radially and discus-shaped from the first shaft 50, and a gear 110. For this purpose, the flange section 53 is formed with bores 55 extending in the direction of the axis of rotation A, through which the gear 110 and the input part 10 are connected in a rotationally fixed manner to the flange section 53 and thus to the first shaft 50 by means of the screw connections 54. The gear 110 is designed to absorb a corresponding torque and to introduce it into the torsional vibration damper 1 or to discharge a torque from the torsional vibration damper 1. The torsional vibration damper 1 is preferably used in a drive train of a motor vehicle, which preferably has at least one internal combustion engine as a torque source. The torsional vibration damper 1 is preferably connected directly or indirectly to the crankshaft of the internal combustion engine via the gear 110. The torsional vibration damper 1 is preferably connected to a starter generator, which combines the functions of a starter and an alternator.

The second shaft 51 also has, on its end facing the first shaft 50, a corresponding further flange section 56 with further bores 57 formed in the direction of the axis of rotation A. Coaxial to the second shaft 51, the output part 2 is formed with a radial and disc-shaped extension starting from the second shaft 51. Here too, the further bores 57 of the further flange section 56 of the second shaft 51 are designed to create a rotation-proof connection between the output part 2 and the second shaft 51, for example by means of rivets 58.

The output part 2 has first channel regions 4 and second channel regions 5 opposite one another with respect to the axis of rotation A, which extend over part of the circumference of the output part 2, the outer peripheral region of the output part 2 being bent in a cup shape in the direction of the axis of rotation A and closed the axis of rotation A forms a coaxial cylindrical section 100. In addition, the output part 2 has a first stop 6 and a second stop 8 on the radial outside, which also extend over part of the circumference of the output part 2 and separate the first and second channel regions 4, 5 from one another.

The input part 10 has stops 23 opposite the stops 6, 8 of the output part 2. In the channel areas 4, 5 and between the stops 6, 8, 23, a spring element 30, 40 is mounted in the circumferential direction, with the channel areas 4, 5 serving as a guide for the spring elements 30, 40. Since the spring elements 30, 40 according to 3 with a first ends 31, 41 supported on the stops 6, 8 of the output part 2 and with their second ends 32, 42 supported on the stops 23 of the input part 10, the spring elements 30, 40 counteract a rotation of the input part 10 relative to the output part 2.

In order to prevent movement of the spring elements 30, 40 in the axial direction, i.e. in the direction of the axis of rotation A and thus out of the guide channels 4, 5, the edge of the spring elements 30, 40 facing away from the output part 2 or the channel regions 4, 5 is through a cover 90 is held in the channel areas 4, 5. The cover 90 is arranged coaxially to the output part 2 and the input part 10 and is also designed to be discus-shaped in the radial direction starting from the axis of rotation A. In order to ensure an even load on the spring elements 30, 40 in their direction of extension and to avoid possible torsion, a first stop 91 and a second stop on the cover 90 also act in the same direction to support the stops 6, 8 of the output part 2 92 trained.

In addition, the cover 90 also has, on its radially outward-facing side, a bent and cylindrical section 101 which is complementary to the cylindrical section 100 of the output part 2 and with which the cover 90 abuts the inner circumference of the cylindrical section 100 of the output part 2 on the circumferential side. In order to connect the output part 2 and the cover 90 to one another in a rotationally fixed manner, the cylindrical sections 100, 101 of the output part 2 and the cover 90 are pressed together and together form a circumferential channel 120 between them. Thus, the spring elements 30, 40 are held both in the radial direction by the inside of the cylindrical section of the cover 101 and also in the axial direction by the channel regions 4, 5 and the radially outward-facing sides of the cover 90.

On its radially inward-facing side, the cover 90 is formed with a further folded and cylindrical section 102, which is formed opposite to the radially outer cylindrical section 101. In the radial direction, a toothless region 111 of the gear 110 and the further cylindrical section 102 overlap, with a third bearing 62 being arranged between the cylindrical section 102 and the toothless region 111 of the gear 110, that the further cylindrical section 102 opposite the toothless region 111 of the gear 110 is supported in both the radial and axial directions, i.e. in the direction of the axis of rotation A.

The invention relates to a torsional vibration damper 1 with an input part 10 and an output part 2, which can be rotated to a limited extent relative to one another about an axis of rotation A against the action of spring elements 30, 40. The torsional vibration damper 1 has a first shaft 50 which extends coaxially to the axis of rotation A and is connected in a rotationally fixed manner to the input part 10 and a second shaft 51 which extends coaxially to the axis of rotation A and is connected in a rotationally fixed manner to the output part 2. For the rotatable mounting of the torsional vibration damper 1 about the axis of rotation A, a first bearing 60 is arranged between the first shaft 50 and the second shaft 51, with which the first shaft 50 and the second shaft 51 are rotatably mounted relative to one another.

Reference symbol list

1

Torsional vibration damper

2

Output part

3

recess

4

first channel area

5

second channel area

6

first attack

7

first stop surface

8th

second attack

9

first stop surface

10

Entrance part

17

first stop surface

18

second stop surface

20

wing flange

21

Wing flange body

22

wing

23

attack

24

recess

30

first spring element

31

first ending

32

second ending

40

second spring element

41

first ending

42

second ending

50

first well

51

second wave

52

Longitudinal bore

53

flange section

54

Screw connection

55

drilling

56

another flange section

57

further drilling

58

rivet

60

first camp

61

second camp

62

third camp

70

first rolling bearing

71

first warehouse location

80

second rolling bearing

81

second bearing seat

90

Lid

91

first attack

92

second attack

100

cylindrical section output part

101

cylindrical section lid

102

another cylindrical section lid

110

gear

111

edentulous area

120

channel

A

Axis of rotation

QUOTES INCLUDED IN THE DESCRIPTION

This list of 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.

Cited patent literature

• US 20200032853 A1 [0003]

Claims (10)

Torsional vibration damper (1) comprising an input part (10) and an output part (2), and at least one spring element (30, 40), the input part (10) and the output part (2) being limited against the action of the spring element (30, 40). are rotatably mounted relative to each other about an axis of rotation (A) of the torsional vibration damper (1), a first shaft (50) which extends coaxially to the axis of rotation (A) and is non-rotatably connected to the input part (10), and a first shaft (50) which is coaxial to the axis of rotation (A). extending second shaft (51) which is non-rotatably connected to the output part (2), at least one first bearing (60) being arranged between the first shaft (50) and the second shaft (51), with which the first shaft (50) and the second shaft (51) is rotatably mounted relative to one another. Torsional vibration damper (1). Claim 1 , characterized in that the second shaft (51) has a longitudinal bore (52) in the direction of the axis of rotation (A) on the side facing the first shaft (50), the first shaft (50) passing through the first bearing (60). is rotatably mounted in the longitudinal bore (52). Torsional vibration damper (1). Claim 1 or 2 , characterized in that the first shaft (50) is supported radially relative to the second shaft (51) by the first bearing (60) and in the axial direction by a second bearing (61). Torsional vibration damper (1). Claim 2 , characterized in that a first roller bearing (70) is arranged radially above the first bearing (60) and coaxially to the second shaft (51) on the outer peripheral surface of the second shaft (51). Torsional vibration damper (1) according to one of the preceding claims, characterized by a second roller bearing (80) arranged coaxially to the first shaft (50) and on the outer circumferential surface of the first shaft (50), the second roller bearing (80) being on the output part (2) facing away from the input part (10). Torsional vibration damper (1) according to one of the preceding claims, characterized by a gear (110) which is coaxial with the first shaft (50) and non-rotatably fastened to the first shaft (50), the gear (110) being on a circumferential section of its outer peripheral surface has a toothless area (111) formed towards the second shaft (51). Torsional vibration damper (1) according to one of the preceding claims, characterized in that the output part (2) has a radial extension relative to the axis of rotation (A) and on the circumference and coaxially to the axis of rotation (A) with one towards the spring element (30, 40). oriented cylindrical section (100) is formed. Torsional vibration damper (1). Claim 7 , characterized by a cover (90) which extends radially outwards relative to the axis of rotation (A), which has a circumferential fit that is complementary to the cylindrical section (100) and is non-rotatably connected to the cylindrical section (100) of the output part (2) or the Input part (10) is connected. Torsional vibration damper (1). Claim 8 , characterized in that the output part (2) and the cover (90) form a channel (120) between them which runs around the axis of rotation (A), the channel (120) supporting the spring element (30, 40) both in the radial direction also at least partially encloses in the axial direction with respect to the axis of rotation (A). Torsional vibration damper (1). Claim 8 or 9 , characterized in that the cover is arranged on its radially inner side with respect to the axis of rotation (A) coaxially with the toothless region (111) of the gear (110) and by means of a third bearing (62) on the toothless region (111) is rotatably mounted

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