Torsional vibration damper

Abstract

The invention relates to a torsional vibration damper (1) having a hub part (2) (primary mass) which can be fixed on an engine drive shaft and a flywheel ring (3) (secondary mass) which surrounds the hub part (2) in a radially outer region, a gap (4) being provided between the hub part (2) and the flywheel ring (3) which is filled with a fluid and sealing means (5) by means of which fluid outflow is to be avoided, the sealing means (5) each having a first ring (6) which is sealingly connected to the hub part (2) and a second ring (7) which is sealingly connected to the flywheel ring (3) and each having a sealing element (12) made of an elastomer which is sealingly connected to the first ring (6) on the one hand and to the second ring (7) on the other hand, the respective sealing element (12) being vulcanized to the respective axially outer side of the first and second rings (6, 7) by means of a fixing section.

Description

TECHNICAL FIELD

[0001] The invention relates to a torsional vibration damper having a hub part (primary mass) which can be fixed on a drive shaft of an engine and a flywheel ring (secondary mass) which surrounds the hub part in a radially outer region, a gap filled with a fluid and a sealing device being provided between the hub part and the flywheel ring, by means of which the fluid is to be prevented from flowing out. BACKGROUND

[0002] A torsional vibration damper of the same type is known from WO 2018 / 019729 A1.

[0003] The document US 5,140,868 A describes a viscous and rubber torsional damper having a hub part, a pulley part and a connecting element for elastically connecting the hub part and the pulley part.

[0004] Furthermore, GB 11 05 292 A also belongs to the background art.

[0005] The known torsional vibration dampers have an outwardly offset flywheel ring, which makes their structural form different from a design in which the flywheel ring is completely encapsulated in a separate housing.

[0006] The disadvantage of the latter design is that the mass of the housing is not relevant to the function of the damper and that the heat dissipation is limited by the encapsulation of the flywheel ring.

[0007] In the known torsional vibration dampers having an outwardly offset flywheel ring, it must be ensured that the fluid located between the hub part and the flywheel ring is prevented from flowing out.

[0008] In the design of the same type, each sealing device comprises a first ring in sealing connection with the hub part, a second ring in sealing connection with the flywheel ring and a ring made of elastomer, which is in sealing connection with the first ring on the one hand and with the second ring on the other hand.

[0009] Here, too, a design is described in which the ring made of elastomer is fixed or adhered on the radial surfaces and on the axial surfaces, in particular on the edge regions, of the rings at the same time. The respective elastomer ring here extends overall obliquely to the radial direction and the axial direction. SUMMARY

[0010] The task on which the invention is based is to propose a torsional vibration damper of this type which has a sealing device which is further advantageously improved with respect to the prior art.

[0011] The stated task is achieved in that the respective sealing element is vulcanized to the respective outer axial side of the first ring and the second ring by means of a fixing section.

[0012] By this design the disadvantages of the prior art are avoided, since no friction occurs between the sealing element and the rotating components of the torsional vibration damper. Furthermore, the sealing element is able to permanently compensate the relative movement between the flywheel ring and the hub component.

[0013] In contrast to the prior art, the sealing elements are fixed on the outer axial surfaces or axial sides and on the peripheral surfaces of the two rings, respectively, and not on the inner surfaces which are mounted on the flywheel ring or hub component, respectively.

[0014] The respective outer axial sides of the first and second ring are facing away from the flywheel ring (secondary mass).

[0015] In this way, the inner space between the rings is not affected or reduced by the sealing elements. Thereby, a further advantage is achieved, namely a greater moment of inertia of the flywheel ring. Furthermore, the flywheel ring does not need to be provided with recesses in the area of the sealing elements.

[0016] It is particularly advantageous if the respective sealing element is also vulcanized onto the respective radial side of the outer diameter of the first ring and of the inner diameter of the second ring, since in this way each fixing section of the respective sealing element encloses the outer edge region of the axial side and the peripheral surface of the respective ring, thereby achieving a better retention and a good sealing.

[0017] The term "radial side" refers to a circumferential surface having the relevant diameter of the respective ring, which ring forms a cylindrical gasket having a circular cross-section comprising an outer diameter and an inner diameter.

[0018] Furthermore, it is advantageous here that the outer diameter of the first ring is smaller than the inner diameter of the second ring, since the running stretch is minimized and thus the durability is improved.

[0019] It is also advantageous in this regard that the sealing section of the respective ring-shaped sealing element extends at an angle oblique to the axial direction of the rotational axis of the torsional vibration damper and has a value of between 15° and 50°.

[0020] This sealing connection in both directions on the primary mass and / or secondary mass forms a particularly reliable and durable connection, respectively. Thereby, a particularly good defined state of the gap can also be ensured in continuous use.

[0021] The first or second ring of the sealing device, which is sealingly connected to the hub component or the flywheel ring, is preferably made of metal.

[0022] It is advantageous here that the outer diameter of the first ring is smaller than the inner diameter of the second ring, since the running stretch is minimized and thus the durability is improved.

[0023] The respective ring of the sealing device made of elastomer is preferably sealingly connected with the ring made of metal fixed on the hub part or the flywheel ring by a rubber-metal connection generated during the cross-linking of the elastomer.

[0024] Preferably, a high-temperature-resistant elastomer, such as EPDM or a silicone material, is used as the elastomer between the respective first and second ring of the sealing device. "Silicone material" in the scope of this document means a material which comprises or is a synthetic polymer in which silicon atoms are connected via oxygen atoms.

[0025] The sealing element can be made of inorganically filled silicone elastomer, wherein the proportion of inorganic material is at least 30%.

[0026] This is particularly advantageous, since the material is also suitable for the high-temperature range.

[0027] Furthermore, the material has only a small effect on the service life of the silicone oil. On the contrary, the material is resistant to silicone oil and only swells slightly.

[0028] It is particularly advantageous that not only the silicone oil in the torsional vibration damper but also the sealing device with the elastomer track (Elastomerspur) can be used continuously over the service life of the damper. On the contrary, other materials would lead to a strong degradation (Abbau) of the silicone oil, pure silicon would lead to an excessive swelling.

[0029] The respective sealing device according to the design does not involve a sliding sealing device, so that a reliable and durable complete sealing is achieved.

[0030] It is not necessary to press the sealing device in, whereby the advantage is created that the sealing device can be installed stress-free. Thus, especially when the flywheel ring is supported on a plain bearing relative to the hub part, it is possible to guarantee the defined state of the clearance in the torsional vibration damper.

[0031] In order to advantageously precisely maintain the clearance width, the flywheel ring can be defined supported on a plain bearing relative to the hub part in the radial and / or axial direction.

[0032] If the sealing element has one axial protrusion as a lip, particularly good support and installation properties are created. The shaping and styling of the outwardly extending lip is thereby advantageously achieved in a simple manner: the sealing element is not fixed on the outer axial surface or axial side of the first ring, but on the outer axial surface or axial side of the ring, i.e. on both outer axial sides, respectively.

[0033] It is furthermore advantageous that the sealing element has a cover as an additional mechanical protection against damage to the sealing device. Advantageously, the cover can be a metal plate which is mounted on the first ring, which metal plate is open radially outwards, one wall of the cover being arranged parallel to the sealing section of the sealing element spaced apart from the sealing section.

[0034] The radially outwards opening of the metal plate enables dirt or particles which have accumulated on the elastomer track or the sealing element to be carried away. BRIEF DESCRIPTION OF DRAWINGS

[0035] Further features and advantages of the present application result from the following description of two embodiments of the present application. The drawings are as follows:

[0036] Fig. 1 shows a schematic partial sectional view of a torsional vibration damper according to the prior art;

[0037] Figure 2 shows a schematic partial sectional view of a torsional vibration damper according to the present application;

[0038] Figure 3 shows a schematic front view of a cover of a torsional vibration damper according to the present application according to Figure 2

[0039] Figure 4 shows a schematic sectional view of the cover according to Figure 3

[0040] Figures 5-9 shows an enlarged schematic sectional view of the area V of Figure 3 and Figure 4 DETAILED DESCRIPTION

[0041] Fig. 1 shows a torsional vibration damper 1' according to the prior art, which is described in detail with regard to structure and function in the document WO 2018 / 019729 A1, which is hereby incorporated by reference.

[0042] The torsional vibration damper 1' with a rotational axis 1a comprises a hub part 2 (primary mass) which can be fixed on a drive shaft of an engine, a flywheel ring 3 (secondary mass) which surrounds the hub part 2 in a radially outer region, a gap 4 which is provided between the hub part 2 and the flywheel ring 3 and which is filled with a fluid, preferably silicone oil, and a sealing device 5 for sealing the gap 4 to the outside. The flywheel ring 3 is referred to here as being located on the outside.

[0043] Each sealing device 5 has a first ring 6 which is sealingly connected to the hub part 2 and a second ring 7 which is likewise sealingly connected to the flywheel ring 3 and an elastomer ring 8 which is sealingly connected to the first ring 6 on the one hand and to the second ring 7 on the other hand.

[0044] ​​​The rings 6, 7 are preferably made of metal and are fixed and sealingly connected to the hub part 2 or to the flywheel ring 3 by suitable connection methods, in particular by screws, welding, adhesive bonding, brazing, etc.

[0045] The respective ring 8 made of an elastomer, preferably of a high-temperature-resistant elastomer, such as a silicone material, is sealingly connected in a composite part manner around both the first and the second ring 6, 7. This connection is achieved by a rubber-metal connection, which is produced, in particular, during crosslinking of the elastomer.

[0046] The rings 6, 7 and 8 form an assembly, which is also referred to as cover 100'. The torsional vibration damper 1' has two covers 100'.

[0047] In the prior art according to Fig. 1, the ring 8 made of an elastomer is vulcanized onto mutually opposite surfaces of the first and second rings 6, 7, which overlap one another in the radial direction.

[0048] The flywheel ring 3 is supported here on the plain bearing 9 with respect to the hub part 2, more precisely not only in the radial direction but also in the axial direction, thereby precisely defining the size of the gap 4.

[0049] The flywheel ring 3 comprises at least two components in order to be able to mount the flywheel ring 3 on the hub part 2. All hitherto known structural forms and other structural forms are conceivable here.

[0050] In the embodiment shown, the hub part 2 is provided with a radially outwardly projecting flange 10, which is terminated in the outer edge region by a bridge 11 extending in the axial direction, which can extend towards both sides of the flange 10, thereby forming a T-shaped cross section, but can also extend towards only one side of the flange 10, thereby forming an L-shaped cross section. By this geometry, the flywheel ring 3 is fixed both in the radial direction and in the axial direction with respect to the hub part 2, as already mentioned, the size of the encircling gap 4 always being defined by the plain bearing 9.

[0051] Figure 2 A partial sectional view of a torsional vibration damper 1 according to the application is shown.

[0052] The torsional vibration damper 1 according to the application differs from the above-described torsional vibration damper 1' according to Fig. 1 of the prior art in the sealing device 5.

[0053] The annular sealing element 12 made of an elastomer is instead vulcanized here onto the large-surfaced, outer axial and radial edge regions 6a, 7a of the rings 6 and 7, instead of the ring 8. The respective edge region 6a, 7a is thus a fixing surface for the sealing element 12. This will be further explained below.

[0054] Each sealing device 5 also comprises here a first ring 6 sealingly connected with the hub part 2, a second ring 7 sealingly connected with the flywheel ring 3 and a ring-shaped sealing element 12 made of an elastomer, which is sealingly connected on the one hand with the first ring 6 and on the other hand with the second ring 7.

[0055] In contrast to the prior art according to Figure 1, the first ring 6 and the second ring 7 of the respective sealing device 5 do not overlap in the radial direction. Here, the outer diameter of the first ring 6 is smaller than the inner diameter of the second ring 7.

[0056] The first and second rings 6, 7 of the respective sealing device 5 are here arranged in planes which are spaced apart from one another in the axial direction.

[0057] The first and second rings 6, 7 of the respective sealing device 5 are here also preferably made of metal and are connected, in particular sealingly connected, to the hub part 2 or to the flywheel ring 3 in a ring-shaped manner by suitable connecting methods.

[0058] The respective ring-shaped sealing element 12 made of an elastomer, preferably of a high-temperature-resistant elastomer, such as a silicone material, is sealingly connected, in particular in a ring-shaped manner, to the two first and second rings 6, 7 in the manner of a composite part. The ring-shaped sealing element 12 made of an elastomer of the respective sealing device 5 is preferably sealingly connected to the rings 6, 7 made of metal, which are fixed to the hub part 2 or to the flywheel ring 3, by a rubber-metal connection, in particular produced during cross-linking of the elastomer.

[0059] This achieves a defect-free and durable sealing of the gap region, if a high-temperature-resistant elastomer, such as a silicone material, is used for the respective ring-shaped sealing element 12, the advantage arises that these ring-shaped sealing elements are also suitable for the high-temperature range.

[0060] It is particularly advantageous if the ring-shaped sealing element 12 made of an elastomer, preferably of silicone, is vulcanized onto the edge regions 6a, 7a of the axially outer lying axial faces of the first and second rings 6, 7, which are arranged offset to one another, and onto the radially opposite lying radial faces. This will be described further below.

[0061] The term "offset" is to be understood in the sense that the axially outer lying axial faces or the edge regions 6a, 7a thereof are arranged overlapping in the radial direction and both face in the same direction, namely outwards, and that the inner diameter of the edge region 7a of the second ring 7 is greater than the outer diameter of the first ring 6.

[0062] The flywheel ring 3 is here advantageously also supported on a plain bearing 9 with respect to the hub part 2, more precisely not only in the radial direction but also in the axial direction, thereby precisely defining the size of the gap 4.

[0063] In this manner, the covers 100 of the torsional vibration damper 1 according to the present invention are formed, and these covers have a first ring 6, a second ring 7 and a sealing element 12 respectively.

[0064] Figure 3 This is shown according to Figure 2 A schematic front view of the cover 100 of the torsional vibration damper 1 according to the present invention. Figure 4 Showing according to Figure 3 A schematic cross-sectional view of the cover 100. Figure 5 Showing according to Figure 3 The area covered by the 100 VV and Figure 4 A magnified view of region V in the image.

[0065] The outer diameter edge of the first ring 6 and the inner diameter edge of the second ring 7 are radially and axially spaced apart.

[0066] The sealing section 13 of the corresponding annular sealing element 12 extends generally in the radial and axial directions and adheres to the outer axial and radial sides of the corresponding rings 6 and 7.

[0067] The term “inclined in the radial and axial directions” should be understood as the sealing section 13 extending in the radial direction at an angle α relative to the axial direction perpendicular to the axis of rotation 1a and in the axial direction at an angle β relative to the axis of rotation 1a.

[0068] The corresponding rings 6 and 7 have edge regions 6a and 7a on their outer axial sides.

[0069] The term "outer axial side" refers to the respective side or side surface of the rings 6 and 7 of the two sealing devices 5, which face outwards and are therefore away from the flywheel ring 3 and, unlike the inner side, are neither connected to the flywheel ring 3 nor to the hub component 2.

[0070] The term "radial side" refers to the radial circumferential surface of the corresponding rings 6 and 7 with their respective diameters. Rings 6 and 7 form cylindrical washers with circular cross-sections including both outer and inner diameters.

[0071] This will be combined below Figure 5 To explain in more detail.

[0072] Advantageously, the two rings 6 and 7 of the sealing device 5, i.e., the two metal rings, have different diameters (inner diameter and outer diameter), and the sealing element 12, constructed as an elastomeric ring, extends relative to the axial direction at an angle β, the value of which is between 15° and 50°. The angle α related to the radial direction then has the value α = 90° - β.

[0073] This leads to a very good durability of the sealing element 12 under strong mechanical loads. The material of the sealing element 12 has little influence on the service life of the silicone oil in the gap 4. Furthermore, the material of the sealing element 12 is low in resistance to silicone oil over the service life of the damper (low swelling).

[0074] The sealing element 12 comprises a ring-shaped sealing section 13 which has transition sections 14, 15 and fixing sections 16, 17. This can be seen clearly in the Figure 5 enlarged view.

[0075] The sealing section 13 is connected at its lower end to the first fixing section 16 by a concave transition section 14 (relative to the outside). The fixing section 16 has a ring-shaped recess 21 facing away from the second ring 7, which is delimited in the axial direction by a ring-shaped protrusion 20 extending in the radial direction and in the radial direction by a further ring-shaped protrusion 20a extending in the axial direction.

[0076] The sealing element 12 is vulcanized to the axial and radial side of the outer diameter of the first ring 6 by means of the first fixing section 16 such that the recess 21 surrounds the outer edge of the first ring 6. Here the fixing section 17 is connected to the edge region 6a of the first ring 6 by means of the radial protrusion 20 and to the peripheral surface 6d of the outer diameter of the first ring 6 by means of the axial protrusion 20a.

[0077] The edge rounding 6c between the edge region 6a and the peripheral surface 6d of the first ring 6 is sealingly surrounded by the corresponding section of the recess 21 of the sealing element 12 in the form of a crescent 21a.

[0078] Similarly, the sealing section 13 is connected at its upper end to the second fixing section 17 by a convex transition section 15. The fixing section 17 has a recess 22 facing towards the second ring 7, which is delimited in the axial direction by a protrusion 18 extending in the radial direction and in the radial direction by a ring-shaped crescent 22a.

[0079] The sealing element 12 is vulcanized to the axial and radial side of the inner diameter of the second ring 7 by means of the second fixing section 17 such that the recess 22 surrounds the inner edge of the second ring 7. Here the fixing section 17 is connected to the edge region 7a of the second ring 7 by means of the radial protrusion 18 and to the peripheral surface 7d of the inner diameter of the second ring 7 by means of the crescent 22a. The edge rounding 7b between the edge region 7a and the peripheral surface 7d of the second ring 7 is sealingly surrounded by the corresponding crescent 22a of the recess 22 of the sealing element 12.

[0080] The fixing section 17 here has an axial protrusion which protrudes outward from the fixing section 17. This protrusion is referred to here as a lip 19 and is rectangular in cross section and has rounded edges. This integrated lip 19 prevents damage to the sealing element 12 during manufacture, transport and installation of the torsional vibration damper 1.

[0081] The shaping and design of the outwardly extending lip 19 is particularly simple and thus can be realized in a simple manner: The sealing element 12 is not fixed on the axially outer surface or axially outer side of the first ring 6, but on the axially outer surface or axially outer side of the ring 7.

[0082] Figures 6 to 8 A further enlarged schematic sectional view of the region V is shown in Figure 3 and Figure 4 , in which the design of the flywheel ring 3 in the region of the sealing element 12 has three exemplary variants. The plain bearing 9 is not shown here, but is conceivable.

[0083] Since the sealing element 12 is fixed on the axially outer surface or axially outer side and the peripheral surface 6d, 7c of the rings 6, 7 and not on the axially inner surface, the space between the second rings 7 is not affected or reduced by the sealing element 12. A further advantage thus arises, namely that a greater moment of inertia of the flywheel ring 3 is achieved. Furthermore, the flywheel ring 3 does not need to be provided with recesses in the region of the sealing element 12.

[0084] The underside of the flywheel ring 3 with the inner section 3a is shown in Figure 6 . The inner section 3a here is arranged only with a small spacing from the edge 2a of the hub part 2. The obliquely running edge 3b of the inner section 3a of the flywheel ring 3 runs approximately parallel to the likewise obliquely running sealing section 13 of the sealing element 13.

[0085] Between the sealing section 13 of the sealing element 13 and the edge 3b of the inner section 3a of the flywheel ring 3 a small gap 23 is determined which communicates with a further likewise small gap 24 between the inner section 3a of the flywheel ring 3 and the edge of the hub part 2.

[0086] In Figure 7 , the edge 3b of the inner section 3a of the flywheel ring 3 runs axially in the continuation of the inner diameter edge of the second rings 7 and parallel to the edge 2b of the hub part 2 and parallel to the axis of rotation 1a. Here a common large gap 23, 24 is formed between the edges 3b and 2b which is closed outwardly by the obliquely running sealing section 13 of the sealing element 12 (likewise on the other side by a further sealing element 12).

[0087] Figure 8A further increase of the clearances 23, 24 is shown. Here, the edge 3b of the inner section 3a of the flywheel ring 3 extends radially upward at an angle γ with respect to the parallel of the rotation axis 1a.

[0088] In Figures 6 to 8 the variant of the flywheel ring 3 shown in

[0089] Figure 9 A further enlarged schematic sectional view of the region V in Figure 3 and Figure 4 with the cover 25 as additional mechanical protection of the sealing device 5 against damage.

[0090] The cover 25 can be realized, for example, by means of a welded-on metal plate which is open radially outward in order to be able to carry away dirt or particles which have accumulated on the elastomer track of the sealing device 5.

[0091] In the exemplary illustration, the cover 25 is configured in the form of a metal plate ring having a Z-shaped cross section. It has one radially extending fixing section 25a, one obliquely extending wall 25b and one substantially again radially extending edge section 25c.

[0092] By means of the fixing section 25a, the cover is fixedly and sealingly mounted, for example welded, to the fixing surface 6b under the edge region 6a of the first ring 6. Here, the wall 25b extends substantially parallel to the sealing section 13 of the sealing element 12 spaced apart therefrom. The edge section 25c of the cover 25 here extends in correspondence with the course of the protruding transition section 15 of the sealing element 12 and together with this transition section determines a radial opening between the wall 25b and the sealing section 13. Of course, other designs are also possible, for example the wall 25b can be shorter or even longer or have a different angle.

[0093] It is to be noted that the flywheel ring 3 here comprises at least two components in order to be able to mount the flywheel ring 3 on the hub part 2. All presently known construction forms are conceivable here.

[0094] The application is not limited to the embodiments given above, but can be modified within the scope of the application.

[0095] List of reference signs

[0096] 1, 1' torsional vibration damper

[0097] 1a rotation axis

[0098] 2 hub part

[0099] 2a fixing surface

[0100] 2b edge

[0101] 3 flywheel ring

[0102] 3a inner section

[0103] 3b edge

[0104] 3c fixing face

[0105] 4 gap

[0106] 5 sealing device

[0107] 6 ring

[0108] 6a edge region

[0109] 6b fixing face

[0110] 6c rounding

[0111] 6d peripheral face

[0112] 7 ring

[0113] 7a edge region

[0114] 7b rounding

[0115] 7c peripheral face

[0116] 8 ring

[0117] 9 plain bearing

[0118] 10 flange

[0119] 11 bridge

[0120] 12 sealing element

[0121] 13 sealing section

[0122] 14, 15 transition section

[0123] 16, 17 fixing section

[0124] 18 protrusion

[0125] 19 lip

[0126] 20 protrusion

[0127] 21, 22 recess

[0128] 21a, 22a crescent recess

[0129] 23, 24 interspace

[0130] 25 cover

[0131] 25a fixing section

[0132] 25b wall

[0133] 25c edge section

[0134] 100, 100' cover

[0135] α, β, γ angle

Claims

1. Torsional vibration damper (1) comprising a hub part (2) as primary mass, which can be fixed on a drive shaft of an engine, and a flywheel ring (3) as secondary mass, which surrounds the hub part (2) in a radially outer region, between which hub part (2) and flywheel ring (3) a gap (4) is provided, which is filled with a fluid, and sealing means (5), by means of which an outflow of the fluid shall be avoided, each of the sealing means (5) having a first ring (6) sealingly connected to the hub part (2) and a second ring (7) sealingly connected to the flywheel ring (3) and each having a sealing element (12) made of an elastomer, which is sealingly connected to the first ring (6) on the one hand and to the second ring (7) on the other hand, respectively, characterized in that the respective sealing element (12) being vulcanized to the respective outer axial side of the first ring (6) and the second ring (7) by means of a fixing section (16, 17).

2. Torsional vibration damper according to claim 1, characterized in that The respective outer axial side of the first ring (6) and the second ring (7) faces away from the flywheel ring (3).

3. The torsional vibration damper according to claim 1, characterized in that The respective sealing element (12) is also vulcanized to the respective radial side of the outer diameter of the first ring (6) and to the respective radial side of the inner diameter of the second ring (7).

4. Torsional vibration damper according to any one of claims 1 to 3, characterized in that The outer diameter of the first ring (6) is smaller than the inner diameter of the second ring (7).

5. Torsional vibration damper according to any one of claims 1 to 3, characterized in that A sealing section (13) of the annular respective sealing element (12) extends at an angle (β) to the axial direction of the rotational axis (la) of the torsional vibration damper (1) and has a value of between 15° and 50°.

6. Torsional vibration damper according to any one of claims 1 to 3, characterized in that The first ring (6) connected to the hub part (2) and the second ring (7) connected to the flywheel ring (3) of the sealing means (5) are made of metal.

7. Torsional vibration damper according to any one of claims 1 to 3, characterized in that The sealing element (12) made of elastomer of the sealing means (5) is sealingly connected to the rings made of metal fixed on the hub part (2) and the flywheel ring (3) by means of a rubber-metal connection generated during the crosslinking process of the elastomer.

8. Torsional vibration damper according to any one of claims 1 to 3, characterized in that The sealing element (12) made of elastomer between the respective first ring (6) and the second ring (7) of the sealing means (5) is made of a high-temperature-resistant elastomer.

9. Torsional vibration damper according to claim 8, characterized in that The sealing element (12) is made of a silicone material.

10. The torsional vibration damper according to claim 8, characterized in that The sealing element (12) is made of an inorganically filled silicone elastomer, wherein the proportion of inorganic material is at least 30%.

11. Torsional vibration damper according to any one of claims 1 to 3, characterized in that The flywheel ring (3) is supported in a defined manner with respect to the hub part (2) on a plain bearing (9) in the radial and / or axial direction.

12. Torsional vibration damper according to any one of claims 1 to 3, characterized in that The sealing element (12) has a protrusion projecting axially outward as a lip (19).

13. Torsional vibration damper according to claim 12, characterized in that The lip (19) is integrally formed on a fixing section (17) of the sealing element (12) by means of which the sealing element (12) is fixed on the outer axial side of the second ring (7).

14. Torsional vibration damper according to any one of claims 1 to 3, characterized in that The sealing element (12) has a cover (25) as a mechanical protection against damage to the sealing means (5).

15. Torsional vibration damper according to claim 14, characterized in that The cover (25) is a metal plate mounted on the first ring (6) which is open radially outwards, one wall (25b) of the cover (25) being arranged parallel to the sealing section (13) of the sealing element (12) spaced apart from the sealing section (13).

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