Torsional vibration damper with two-part shaft

Abstract

Torsional vibration damper (1) comprising an input part (10) and an output part (2), and at least one spring element (30, 40), wherein the input part (10) and the output part (2) are mounted so as to be rotatable relative to one another about an axis of rotation (A) of the torsional vibration damper (1) against the action of the spring element (30, 40), a first shaft (50) extending coaxially to the axis of rotation (A) and connected in a rotationally fixed manner to the input part (10), and a second shaft (51) extending coaxially to the axis of rotation (A) and connected in a rotationally fixed manner to the output part (2), wherein at least one first bearing (60) is arranged between the first shaft (50) and the second shaft (51), with which bearing the first shaft (50) and the second shaft (51) are mounted so as to be rotatable relative to one another, characterized in that the second shaft (51) has a longitudinal bore (52) in the direction of the axis of rotation (A) on the the first shaft (50) facing side,wherein the first shaft (50) is rotatably mounted in the longitudinal bore (52) by the first bearing (60).

Description

[0001] The present invention relates to a torsional vibration damper with a two-part shaft for the best possible mounting of the torsional vibration damper with the lowest possible space requirements.

[0002] In reciprocating piston engines, the periodic sequence of accelerated piston movement and gas forces during intake, compression, compression, and exhaust, combined with the firing sequence of the individual cylinders, leads to rotational irregularities in the crankshaft and the connected flywheel. Since the drivetrain is a structure susceptible to torsional vibrations with characteristic natural frequencies due to the moment of inertia of the rotating components and their rigidities, the rotational irregularities induced by the engine inevitably lead to torsional vibrations, which, if left undamped, can result in unwanted side effects such as acoustic abnormalities or increased component wear. Torsional vibration dampers are used to mitigate these effects.

[0003] Torsional vibration dampers are known from the prior art. They are arranged to compensate, in particular, for torsional vibrations in a motor vehicle drivetrain in order to prevent the torsional vibrations generated by an internal combustion engine from being transmitted to a transmission, thus increasing its service life. A corresponding torsional vibration damper is known, for example, from US 2020 / 0032853 A1. To compensate for such 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 that they can rotate relative to one another about a rotational axis of the torsional vibration damper, limited by the action of a spring element. Together, the spring element and the flywheels form the core of the torsional vibration damper, which is designed as a dual-mass flywheel.According to the devices known from the prior art, one of the flywheels is non-rotatably connected to a corresponding hollow shaft, which in turn is non-rotatably mounted on another shaft passing through it. The other flywheel is non-rotatably connected to a gear and is mounted on the hollow shaft so that it can rotate relative to the other flywheel, limited by the action of the spring element.

[0004] Further devices for decoupling torsional vibrations in a drive train can be found in the publications DE 10 2015 208 232 A1, DE 10 2017 203 459 A1 and DE 40 26 204 A1.

[0005] Due to the split arrangement of two shafts connected in a rotationally fixed manner, the forces introduced into the gear wheel create both radial and axial forces, which can lead to tilting of the flywheel, which is connected in a rotationally fixed manner to the hollow shaft. This, in turn, places additional stress on the shaft, which is supported by two roller bearings. Furthermore, these forces can also lead to tilting of the flywheel connected in a rotationally fixed manner to the hollow shaft relative to the other flywheel.

[0006] It is desirable to introduce torque via a gear mounted between two housing-side bearings, filter out torsional vibrations introduced on the input side, and dissipate the introduced torque outside the housing-side bearings. Furthermore, the bearing of an input-side gear enclosed by the torsional vibration damper, used to introduce the torque, should be as precise as possible in order to minimize wear and the associated noise. This would require the gear to be mounted on two housing-side bearings. The output torque is to be transmitted via the output area located outside the housing and thus outside the bearings. Furthermore, for space reasons, the other components of the torsional vibration damper and the gear should be located inside, i.e., between, the housing-side bearings.Thus, the broadest possible support of the components conflicts with the desire for the smallest possible installation space for the torsional vibration damper.

[0007] Based on this, the present invention is based on the object of at least partially overcoming the problems known from the prior art.

[0008] This object is achieved by 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 expedient manner and can define further embodiments of the invention. Furthermore, the features specified in the claims are further specified and explained in the description, with further preferred embodiments of the invention being presented.

[0009] 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 rotatable relative to one another about an axis of rotation of the torsional vibration damper against the action of the spring element, a first shaft extending coaxially to the axis of rotation and connected in a rotationally fixed manner to the input part, and a second shaft extending coaxially to the axis of rotation and connected in a rotationally fixed manner to the output part, wherein 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 mounted so as to be rotatable relative to one another.

[0010] As a precaution, it should be noted that the numerals used here ("first", "second",...) primarily serve (only) to distinguish between several similar objects, quantities, or processes, and therefore do not necessarily specify any interdependence and / or sequence of these objects, quantities, or processes. Should a dependence and / or sequence be required, this is explicitly stated here or will be obvious to the person skilled in the art upon studying the specifically described embodiment.

[0011] The input part and the output part are a drive-side flywheel and an output-side flywheel, which are rotatable relative to each other about the common axis of rotation, counter to the spring force of the spring element. Preferably, the output part and / or the input part are designed as sheet metal elements, 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 methods. Preferably, the input part and the output part can each be produced using different production methods.

[0012] Preferably, a gear is coaxial with the first shaft and fastened to the first shaft in a rotationally fixed manner, the gear having a toothless region facing the second shaft on a circumferential section of its outer circumferential 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 in a disc shape 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 bores the gear and the input part are rotationally fixedly connected to the flange section and thus to the first shaft by means of screw connections. The gear is designed to absorb a corresponding torque and to introduce it into the torsional vibration damper or to discharge it from it.

[0013] The second shaft also has, on its end facing the first shaft, a corresponding further flange section with bores formed in the direction of the rotational axis A. The output part is formed coaxially to the second shaft with a radial and disc-shaped extension starting from the second shaft. Here, too, the further bores of the flange section of the second shaft are designed to create a rotationally fixed connection between the output part and the second shaft by means of rivets. However, other positive, frictional, and / or material-fit connection types between the input part and the first shaft and the output part and the second shaft are also preferably possible.

[0014] In order to create a space-saving bearing arrangement for the first shaft relative to the second shaft, the second shaft according to the invention has a longitudinal bore in the direction of the axis of rotation on the side facing the first shaft, wherein the first shaft is rotatably mounted in the longitudinal bore by the first bearing. Furthermore, the first shaft is preferably mounted radially relative to the second shaft by the first bearing and in the axial direction by a second bearing. The first and second shafts are thus supported on one another in both the radial and axial directions. The first and second bearings are preferably designed separately, wherein the first and second bearings are designed as needle bearings or a combination of plain and rolling bearings.

[0015] Preferably, however, the first and second bearings can also be combined, for example in the form of a plastic bushing with flange geometry.

[0016] Preferably, a first rolling bearing is arranged radially above the first bearing and coaxially to the second shaft on the outer circumferential surface of the second shaft, wherein the axial position of the first bearing and the first rolling bearing are preferably identical to one another. In contrast, a second rolling bearing is preferably arranged coaxially to the first shaft and on the outer circumferential surface of the first shaft, wherein the second rolling bearing is arranged on the side of the input part facing away from the output part. This arrangement of the first and second bearings and of the first and second rolling bearings relative to one another achieves optimal concentricity of the first and second shafts and mechanically impedes any possible tilting of the first shaft relative to the second shaft. Furthermore, installation space is saved.

[0017] Preferably, the output part has a radial extension relative to the rotational axis and is formed circumferentially and coaxially with the rotational axis with a cylindrical section oriented toward the spring element. Furthermore, a cover extending radially outward relative to the rotational axis is preferred, which cover has a circumferential fit complementary 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 channel between them that runs circumferentially relative to the rotational axis, wherein the channel at least partially encloses the spring element both radially and axially with respect to the rotational axis.

[0018] 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 understood to mean a positive and / or frictional connection between the two elements. For example, the cover can also have, preferably on its radially outward-facing side, a cylindrical section that is positively connected to the cylindrical section of the output part, with which the cover at least partially rests circumferentially on the inner circumference or on the outer circumference of the cylindrical section of the output part. Alternatively, however, other designs of the connection between the cylindrical section of the output part and the cover are also preferred. The cover is preferably designed as a sheet metal element, alternatively preferably designed as a cast or forged part. Furthermore, the production of the cover is preferably not limited to these production methods.Preferably, the lid can also be manufactured using different manufacturing processes.

[0019] As already explained, the output part and the cover form a channel between them that extends around the axis of rotation, with the channel at least partially enclosing the spring element both radially and axially 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 slippage 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, with this area being designed as a friction surface for the spring element displacing within the channel. Preferably, additional stops are also formed on the cover to support the spring element. Preferably, instead of one spring element, several spring elements are distributed around the circumference.

[0020] Preferably, the cover is arranged coaxially to the toothless region of the gear on its radially inner side with respect to the axis of rotation 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 axial position as the connection of the output part to 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 provides additional guidance for the output part extending beyond the cover and ensures a corresponding counter-torque. Preferably, the third bearing is designed for the radial bearing between the cover and the toothless area of ​​the gear and / or the axial bearing between the cover and the toothless area of ​​the gear. Like the first and second bearings, the third bearing is preferably designed as a needle bearing or a combination of a plain and roller bearing. Preferably, however, the third bearing can also be designed in a combined manner, for example, in the form of a plastic bushing with a flange geometry.

[0021] The invention and the technical environment are explained in more detail below with reference to 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 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 illustrated proportions are only schematic. The same reference numerals denote the same objects, so that explanations from other figures can be used as a supplement if necessary. They show: Fig. 1: a highly abstract representation of an input part of a torsional vibration damper according to the invention; Fig. 2: a highly abstract representation of an output part of the torsional vibration damper according to the invention; Fig. 3: a highly abstract representation of the torsional vibration damper according to the invention; Fig. 4: a schematic longitudinal section of the torsional vibration damper according to the invention;

[0022] Fig. 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 designed as a sheet metal element, alternatively preferably as a cast or forged part. The input part 10 is designed as a wing flange 20, wherein the wing flange 20 has two wings 22 formed symmetrically to one another and extending 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. Furthermore, the wing flange body 21 has a recess 24 formed on its outer peripheral surface and coaxial with a rotational axis A. The wing flange 20 is formed point-symmetrically to the rotational axis 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 with reference to the axis of rotation A, unless explicitly stated otherwise.

[0023] Fig. 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 mass with a recess 3 formed coaxially to the circumferential 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, on the circumferential side and opposite one another, a first channel region 4 and a second channel region 5, which extend over part of the circumference of the output part 2. Furthermore, the output part 2 has, on the radially outer side, a first stop 6 and a second stop 8, which are also designed point-symmetrically 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 one another.The first stop 6 has a first stop surface 7, which faces circumferentially toward the first channel region 4. A second stop surface 18, which is formed circumferentially opposite to the first stop surface 7 on the first stop 6, faces toward the second channel region 5. The second stop 8 has a first stop surface 17, which faces circumferentially toward the first channel region 4, while an opposite second stop surface 9 faces toward the second channel region 5.

[0024] Fig. Figure 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 a rotational axis A, so that the recesses 3, 24 of the output part 2 and the input part 10 are aligned with each other. Fig. 3, the torsional vibration damper 1 comprises, in addition to the input part 10 and the output part 2, a first spring element 30 and a second spring element 40, each 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 mounted in the second channel region 5 for movement in the circumferential direction, with the first and second channel regions 4, 5 serving as guides for the spring elements 30, 40. In the uncompressed state, the spring elements 30, 40 have an extension that 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 support a first end 31 of the first spring element 30, while a second stop surface 9 of the second stop 8 is designed to support 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 opposite the stop surfaces 7, 9 are designed to circumferentially limit the respective 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 serve as a support for the second end 32, 42 of the first and second spring elements 30, 40, respectively.

[0025] The input part 10 in the form of the vane 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 rotational axis A. The output part 2, which is indirectly connected to the vane flange 20 via the spring elements 30, 40, is considered below to be 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 transmitting the torque to a transmission attached to it, in particular to a transmission input shaft (not shown).

[0026] 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 applied to the input part 10 is reduced, or if the applied torque does not fluctuate but is applied evenly, the spring elements 30, 40 can at least partially relax and release their stored energy to reverse the rotation of the input part 10 relative to the output part 2.

[0027] The Fig. 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 likewise arranged coaxially to the axis of rotation A. The first shaft 50 is rotatably mounted relative to the second shaft 51 via a first bearing 60 in a longitudinal bore 52 of the second shaft 51. Furthermore, 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. in the direction of the axis of rotation A.

[0028] Starting from the rotational axis 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, the first shaft 50 is rotatably mounted with a second bearing seat 81 offset along the rotational axis A by a second roller bearing 80 at its end facing away from the second shaft 51 on the housing (not shown).

[0029] On the circumferential side, the first shaft 50 has a flange section 53 which is designed to create a rotationally fixed connection between the input part 10, which extends radially and disc-shaped from the first shaft 50, and a gear 110 by means of screw connections 54. For this purpose, the flange section 53 is designed with bores 55 extending in the direction of the axis of rotation A, through which the gear 110 and the input part 10 are rotationally fixedly connected 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 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 that combines the functions of a starter motor and an alternator.

[0030] 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 rotation axis A. Coaxial with the second shaft 51, the output part 2 is formed with a radial and disc-shaped extension extending 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 rotationally fixed connection between the output part 2 and the second shaft 51, for example by means of rivets 58.

[0031] The output part 2 has first channel regions 4 and second channel regions 5, which are opposite one another with respect to the axis of rotation A and extend over part of the circumference of the output part 2, wherein the outer circumferential region of the output part 2 is cup-shaped and beveled in the direction of the axis of rotation A and forms a cylindrical section 100 coaxial with the axis of rotation A. In addition, the output part 2 has a first stop 6 and a second stop 8 on the radially outer side, 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.

[0032] 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, wherein the channel areas 4, 5 serve as a guide for the spring elements 30, 40. Since the spring elements 30, 40 are arranged according to Fig. 3 supported with a first end 31, 41 on the stops 6, 8 of the output part 2 and with their second ends 32, 42 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.

[0033] 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 flank of the spring elements 30, 40 facing away from the output part 2 or the channel regions 4, 5 is held in the channel regions 4, 5 by a cover 90. The cover 90 is arranged coaxially to the output part 2 and the input part 10 and is also disc-shaped in the radial direction starting from the axis of rotation A. In order to ensure uniform loading of the spring elements 30, 40 in their direction of extension and to avoid possible torsion, a first stop 91 and a second stop 92 are formed on the cover 90 to support the stops 6, 8 of the output part 2, also acting in the same direction.

[0034] Furthermore, the cover 90 also has, on its radially outward-facing side, a beveled and cylindrical section 101 complementary to the cylindrical section 100 of the output part 2, with which the cover 90 rests circumferentially against the inner circumference of the cylindrical section 100 of the output part 2. In order to connect the output part 2 and the cover 90 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 inner side of the cylindrical section of the cover 101 and in the axial direction by the channel regions 4, 5 and the radially outward-facing sides of the cover 90.

[0035] On its radially inward-facing side, the cover 90 is formed with a further beveled and cylindrical section 102, which is formed opposite 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 arranged between the cylindrical section 102 and the toothless region 111 of the gear 110, which supports the further cylindrical section 102 relative to the toothless region 111 of the gear 110 both in the radial and axial directions, i.e. in the direction of the rotation axis A.

[0036] The invention relates to a torsional vibration damper 1 with an input part 10 and an output part 2, which are rotatable 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 extending coaxially to the axis of rotation A and connected in a rotationally fixed manner to the input part 10, and a second shaft 51 extending coaxially to the axis of rotation A and 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 mounted so as to be rotatable relative to one another. List of reference symbols 1 torsional vibration damper 2 Output part 3 recess 4 first channel area 5 second channel area 6 first attack 7 first stop surface 8 second stop 9 first stop surface 10 Entrance part 17 first stop surface 18 second stop surface 20 wing flange 21 wing flange body 22 wings 23 stop 24 recess 30 first spring element 31 first end 32 second end 40 second spring element 41 first end 42 second end 50 first well 51 second wave 52 Longitudinal bore 53 Flange section 54 screw connection 55 bore 56 additional flange section 57 additional boreholes 58 rivet 60 first camp 61 second camp 62 third camp 70 first rolling bearing 71 first camp site 80 second rolling bearing 81 second bearing seat 90 lids 91 first attack 92 second attack 100 cylindrical section output part 101 cylindrical section cover 102 further cylindrical section cover 110 gear 111 toothless area 120 channel A axis of rotation

Claims

[1] Torsional vibration damper (1) comprising an input part (10) and an output part (2), and at least one spring element (30, 40), wherein the input part (10) and the output part (2) are mounted to rotate relative to each other about an axis of rotation (A) of the torsional vibration damper (1) with limited resistance to the action of the spring element (30, 40), a first shaft (50) extending coaxially to the axis of rotation (A) and non-rotatably connected to the input part (10) and a second shaft (51) extending coaxially to the axis of rotation (A) and non-rotatably connected to the output part (2), wherein at least one 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 to rotate relative to each other, characterized by, 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), wherein the first shaft (50) is rotatably mounted in the longitudinal bore (52) by the first bearing (60). [2] Torsional vibration damper (1) according to claim 1, characterized by , that the first shaft (50) is supported radially relative to the second shaft (51) by the first bearing (60) and axially by a second bearing (61). [3] Torsional vibration damper (1) according to claim 1, characterized by , that a first rolling bearing (70) is arranged radially above the first bearing (60) and coaxially to the second shaft (51) on the outer circumferential surface of the second shaft (51). [4] Torsional vibration damper (1) according to any one of the preceding claims, characterized bya second rolling bearing (80) arranged coaxially to the first shaft (50) and on the outer circumferential surface of the first shaft (50), wherein the second rolling bearing (80) is arranged on the side of the input part (10) facing away from the output part (2). [5] Torsional vibration damper (1) according to any one of the preceding claims, characterized by a gear (110) which is coaxial to the first shaft (50) and rotationally fixed to the first shaft (50), wherein the gear (110) has a toothless area (111) on a circumferential section of its outer circumferential surface which is formed towards the second shaft (51). [6] Torsional vibration damper (1) according to any one of the preceding claims, characterized by , that the output part (2) has a radial extension relative to the axis of rotation (A) and is formed circumferentially and coaxially to the axis of rotation (A) with a cylindrical section (100) oriented towards the spring element (30, 40). [7] Torsional vibration damper (1) according to claim 6, characterized by a cover (90) extending radially outwards relative to the axis of rotation (A), which has a circumferential fit complementary to the cylindrical section (100) and is connected to the cylindrical section (100) of the outlet part (2) or the inlet part (10) in a rotationally fixed manner. [8] Torsional vibration damper (1) according to claim 7, characterized by , that the output part (2) and the cover (90) form a channel (120) between them which rotates around the axis of rotation (A), wherein the channel (120) at least partially encloses the spring element (30, 40) both radially and axially with reference to the axis of rotation (A). [9] Torsional vibration damper (1) according to claim 7 or 8, characterized by, that the cover is arranged coaxially to the toothless area (111) of the gear (110) on its radially inner side with respect to the axis of rotation (A) and is rotatably mounted on the toothless area (111) by means of a third bearing (62).

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