DE29824531U1 - Gasket for torsional vibration damper - Google Patents

Description

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Seal for torsional vibration damper

The invention relates to a torsional vibration damper with two components arranged such that they can rotate relative to one another and a spring chamber. In such a spring chamber, at least one spring acting tangentially between the two components, for example a spiral spring, is generally arranged.

In the following, the terms "axial" mean a direction parallel to the main axis of rotation of the torsional vibration damper, "radial" means a direction pointing away from the main axis of rotation in a plane perpendicular to the main axis of rotation, and "tangential" means a direction perpendicular to the two aforementioned directions.

Such a torsional vibration damper is known, for example, from DE 42 29 638 C2.

It is the object of the present invention to provide a generic torsional vibration damper in which the spring chamber is sealed without influencing the other properties of the torsional vibration damper.

As a solution, the invention proposes a generic torsional vibration damper with the features of claim 1.

Here, the T-surface follows a centrifugal force that moves the fat radially outwards. In this way, fat that hits the T-surfaces also experiences a radial

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of the guide surfaces, it is ensured that the grease on a guide surface is transported radially outwards due to the centrifugal force CTt*? ⁿ g the surface.

The second guide surface ensures that grease flying around ubiquitously cannot pass through the gap between the first and second assembly, as it is intercepted by this second guide surface. This means that the second guide surface is on the side of the gap and therefore also on the side of the

at least one area of the first guide surface, grease which should radially leave the second guide surface is intercepted by the first guide surface. The centrifugal force prevents this grease from being accelerated radially inwards again towards the gap between the first guide surface and the second assembly.

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Due to the gap between the first guide surface and the second assembly, the present invention makes it possible to seal the spring chamber without contact. This arrangement therefore advantageously does not affect the other properties of the torsional vibration damper, particularly when it is used for clutches.

The first guide surface can be designed as a guide plate which is firmly connected to the first assembly. This design has the advantage over a one-piece design of the first assembly and the first guide surface that it can be manufactured more easily. In particular, difficult-to-create undercuts can be avoided in this way. All suitable types of connection, such as soldering, welding, riveting and the like, can be used to connect the guide plate and the first assembly.

The manufacture of a torsional vibration damper according to the invention is simplified in particular if this connection between the first assembly and the guide plate is designed as a clip connection. For example, the guide plate can be bent as a clamp which, due to the inherent elasticity of the material, easily opens and grips a projection of the first assembly.

In particular, the guide plate can be designed in the shape of a ring disk. As a rule, a generic torsional vibration damper,

namely, several tangentially arranged springs or spring chambers. With such a ring-shaped arrangement, a ring-shaped design of the guide plate means that assembly is particularly simple, since a corresponding guide plate can be assembled for all spring chambers in one operation. With this design, the radial symmetry of a ring disk also makes it particularly easy to create a clamp for connecting the guide plate to the first assembly.

Furthermore, the second guide surface can be designed as a guide disk. Such a guide disk can be arranged in an uncomplicated manner on the spring chamber side above the gap between the first guide surface and the second assembly. In particular, for the reasons mentioned above, it is advantageous to design the guide disk serving as the second guide surface in the shape of an annular disk.

The guide disc can also be firmly connected to the first guide surface or to the guide plate. This firm connection can be provided, for example, by a clip connection, a rivet connection, or a Torx rivet connection. This firm connection increases the stability of the arrangement of the guide disc and the first guide surface or guide plate. In particular, it is possible to manufacture the guide disc from a light and low-friction material, such as plastic, since the first guide surface or guide plate provides stabilization

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the guide plate. This arrangement also enables pre-assembly of the guide plate and guide plate, which simplifies the manufacture of a torsional vibration damper according to the invention.

At least one opening pointing towards the spring chamber can be provided between the first guide surface and the second guide surface. Through this opening, lubricant or grease which has somehow got behind the second guide surface, for example due to creeping processes, can be guided back into the spring chamber. In particular, it is advantageous if the opening is arranged in such a way that a particle with a radial movement component can pass through. In this case, particles behind the second guide surface are guided back into the spring chamber.

A calmed space can be provided between the first and second guide surfaces in the vicinity of the gap which is arranged between the first guide surface and the second assembly. Lubricant which has got behind the second guide surface can collect in this space and is thus prevented from passing through the gap. Such a calmed space is particularly advantageous in conjunction with an opening provided on the radial outside of the space through which the accumulated grease can be returned to the spring chamber.

An element, preferably a ring, made of absorbent material can also be provided between the first and second guide surfaces, which at least when the torsional vibration damper is at a standstill covers the gap between the first guide surface and the second assembly. Such an absorbent material can be any material that can absorb and release the lubricant or similar in the spring chamber. In particular, this material can be made of felt-like sponge or foam. The material should have a higher capillary force than the gap. The fact that this absorbent material covers the gap between the first guide surface and the second assembly prevents grease or similar from creeping through this gap. When the torsional vibration damper rotates, such creeping processes can be ignored due to the centrifugal forces. Consequently, this sealing ring can be designed in such a way that when the torsional vibration damper rotates, it lifts off the second assembly or the first guide surface due to the centrifugal force, so that a contactless seal is present when the torsional vibration damper rotates. In particular, this sealing ring can be provided in a calm space between the first and second guide surface.

Furthermore, it is advantageous if openings are provided radially on the outside between the first guide surface and the second guide surface towards the spring chamber, so that lubricant accumulated in the sealing ring is transported into the spring chamber by centrifugal force.

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It is particularly possible to pre-assemble an arrangement of sealing ring, guide plate and guide disk. For this purpose, for example, the guide plate and guide disk can be firmly connected as described above, so that the sealing ring is fixed in a suitable manner between the guide disk and the guide plate.

The sealing ring can be held under radially inwardly directed prestress of a guide disk that surrounds the second guide surface and is designed in such a way that when the torsional vibration damper rotates, this prestress is reduced, preferably to zero. For this purpose, the guide disk can, for example, have axial projections that grip the sealing ring and press it radially inward against the second assembly. These axial projections are dimensioned in such a way that when the torsional vibration damper rotates, they are moved outwards by the centrifugal force and thus release the sealing ring.

The second assembly of the torsional vibration damper according to the invention can comprise a third, essentially radial guide surface, which covers an axial gap between the second guide surface and the second assembly on a side facing away from the spring chamber. In this way, lubricant particles which pass through a gap, possibly present and open in the axial direction, between the second guide surface and the second assembly can be caught by the third guide surface and transported radially outwards on it.

Advantageously, the gap between the first guide surface and the second assembly is further away from the spring chamber in the axial direction than this third guide surface. If a particle transported on the third guide surface reaches the radially outer end of the third guide surface and, due to centrifugal force, detaches itself from its end in the radial direction, it cannot leave the spring chamber because the actual opening of the spring chamber, namely the gap between the first guide surface and the second assembly, is further away from the spring chamber in the axial direction.

In order to influence the return transport of the lubricant or grease into the spring chamber in a suitable manner, further guide surfaces can be arranged in the spring chamber, in particular in the vicinity of the first guide surface, and/or in a calm space between the first and second guide surfaces, in such a way that particles striking the guide surfaces are deflected in a desired direction, preferably in the direction of the spring chamber or the spring, when the torsional vibration damper rotates.

The torsional vibration damper can further comprise means which close a gap between the first assembly and the second assembly depending on a twist angle between these assemblies. These means can be designed in such a way that the spring chamber is completely closed when a certain

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angle of rotation between the two assemblies is reached and the risk of grease splashing around is therefore greatest. If the angle of rotation is small or non-existent, however, the gap can be left open so that - at least at this point - a contactless seal of the spring chamber and thus low friction is ensured.

The closing means preferably comprise at least one nose which is moved in the axial direction at a certain angle of rotation. This nose can be connected to a locking plate which bridges the gap between the first assembly and the second assembly when the nose moves axially. It is particularly possible to use an existing guide plate as a locking plate.

Any structural unit of the torsional vibration damper that indicates a twist between the first assembly and the second assembly can be used as the intended drive for the nose. In particular, these can be projections on the first or second assembly. However, spring wedges between which the springs are arranged are particularly suitable.

It is understood that the aforementioned closing means can also be used independently of the other features of the inventive

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Torsional vibration damper advantageous" can be used to seal a spring chamber.

In addition, the torsional vibration damper can have a grease transport system caused by centrifugal forces. During operation, the grease is sprayed or distributed in various directions in the spring chamber. As a rule, however, the grease is only required in certain areas in the spring chamber. By providing a grease transport system according to the invention, the grease distributed in the spring chamber can be returned to the desired positions.

The grease transport advantageously has a grease intake arranged radially on the inside and a grease discharge arranged radially further outwards, with means being provided between the grease discharge and the grease intake which displace the grease in the circumferential direction on its way from the grease discharge to the grease intake. While the centrifugal forces automatically cause the grease to move radially, the displacement means according to the invention also enable the grease to be transported in a targeted manner in the circumferential direction.

Any surface of the torsional vibration damper can serve as the grease receptacle according to the invention. In particular, the grease can also be absorbed through gaps or openings, e.g. through a gap leading behind a guide surface.

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The displacement means according to the invention can be, for example, structures formed on a surface with a radial component, such as deflection surfaces, by means of which a particle, such as a fat particle, is deflected in the circumferential direction when it is moved radially outward by centrifugal forces.

It is understood that the grease transport described above can be used advantageously, regardless of the other features, in a torsional vibration damper in which grease is only required at certain locations.

Further advantages, properties and objectives of the present invention can be found in the following description of the accompanying drawing, in which ten embodiments of torsional vibration dampers according to the invention are shown by way of example. In the drawing:

Figure 1 shows a first embodiment of a torsional vibration damper according to the invention in section;

Figure 2 shows a detail from Figure 1;

Figure 3 shows a second embodiment of a torsional vibration damper according to the invention, sectioned at a nose of a first assembly;

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Figure 4 shows the torsional vibration damper according to Figure 3 in a similar representation to Figure 2;

Figure 5 shows a third embodiment of a torsional vibration damper according to the invention in a similar representation to Figure 2;

Figure 6a shows a fourth embodiment of a torsional vibration damper according to the invention in a similar representation to Figure 3;

Figure 6b shows the torsional vibration damper according to Figure 6 in a similar representation to Figure 2;

Figure 7a shows a variant of the fourth torsional vibration damper in a similar representation to Figure 3;

Figure 7b shows the variant according to Figure 7a in a similar representation to Figure 2;

Figure 8a shows another variant of the fourth

Torsional vibration damper in section;

Figure 8b shows the further variant according to Figure 8a in a similar representation as Figure 1;

Figure 8c shows the further variant according to Figures 8a and 8a in a similar representation as Figure 2;

Figure 9a shows a fifth embodiment of a torsional vibration damper according to the invention in a similar representation to Figure 1;

Figure 9b shows the torsional vibration damper according to Figure 8 in a similar representation to Figure 2;

Figure 10 shows a sixth embodiment of an inventive

Torsional vibration damper in a similar representation as Figure 3;

Figure 11 shows the torsional vibration damper according to Figure 10 in a similar representation to Figure 2;

Figure 12 shows a seventh embodiment of an inventive

Torsional vibration damper in a similar representation as Figure 2;

Figure 13 shows an eighth embodiment of a torsional vibration damper according to the invention in a similar representation to Figure 2;

Figure 14 shows the torsional vibration damper according to Figure 13 in a different operating position;

Figure 15 shows a ninth embodiment of a torsional vibration damper according to the invention in a similar representation to Figure 2 and

Figure 16 shows a tenth embodiment of a vibration damper according to the invention in a similar representation to Figure 2.

The torsional vibration damper according to the invention of the first embodiment (Figures 1 and 2) has a first assembly 1 and a second assembly 2, which are arranged to rotate relative to one another. The two assemblies 1 and 2 enclose a spring chamber 7 in which a spring arrangement 70 is provided. This spring arrangement 70 acts tangentially between the two assemblies 1 and 2, the first assembly 1 having lugs 72 which interact with spring wedges 71 of the spring arrangement 70.

A disc-shaped guide plate 3 is clipped onto the first assembly 1 (clip connection 10), which has a first guide surface 30 and is spaced from the second assembly 2 via a gap 31.

Furthermore, this torsional vibration damper has an annular disk-shaped guide disk 5 which is fastened to the guide plate 3. This guide disk 5 is spaced from the second assembly 2 via a gap 51 and has a second guide surface 50.

Behind the guide disk 5 or the second guide surface 50 there is a calmed space 40 which is partially filled by a sealing ring 4. The sealing ring 4 rests against the second assembly 2 and in this way covers the axially aligned gap 31 between the first guide surface 30 and the second assembly 2. In the present embodiment, the sealing ring 4 is made of felt.

On the radially outer side of the calmed space 40, openings 6 are provided between the first guide surface 30 and the second guide surface 50 or between the guide plate 3 and the guide disk 5.

On the side of the gap 51 facing away from the spring chamber 7 between the second assembly 2 and the second guide surface 50, a third guide surface 20 is arranged.

Each of the three guide surfaces 30, 50 and 20 has an axial surface component that points towards the spring chamber. When the torsional vibration damper rotates, particles located on the guide surfaces 30, 50 and 20 are thus moved radially outwards and thus remain in the spring chamber 7. Particles that have entered through the gap 51 are transported on the third guide surface 20 into the calmed space 40 and from there, due to the centrifugal force, reach the first guide surface 30 with the particles in the sealing ring and through the opening 6 back into the spring chamber 7. Likewise, particles on the second guide surface 50 are transported radially outwards and reach the first guide surface 30 due to the centrifugal force.

The sealing ring 4 is selected such that it lifts off the second assembly at a desired speed of the torsional vibration damper. In this way, contactless sealing of the spring chamber 7 is ensured at these and higher speeds.

The torsional vibration damper according to the second embodiment (Figures 3 and 4) corresponds essentially to that according to the first embodiment. However, the second embodiment has an essentially planar guide disk 5 which is positively connected to the guide plate 3 by means of several depressions (connections 52).

Between the connection points 52, radial, elongated recesses of the guide plate 3 are provided, which form the openings 6.

The third embodiment (Figure 5) is almost identical in construction and differs from the second embodiment only in that a welding point is provided at the connection point 52. Alternatively, a lens-shaped recess can be provided in the guide plate 3 at the connection point 52, into which a corresponding projection of the guide plate 5 engages in a form-fitting manner.

The fourth embodiment (Figures 6a and 6b) also corresponds essentially to the second embodiment. However, in this case a sealing ring has been dispensed with entirely. Instead, the second assembly 2 has a concave guide surface 41 which extends from the gap 31 between the second assembly 2 and the first guide surface 30 into the calmed space 40 and meets the third guide surface 20 in an extension. When this torsional vibration damper rotates, particles located on the third guide surface 20 or the concave guide surface 41 are transported to the extension in order to be pushed radially into the calmed space 40 towards the first guide surface when the adhesion forces are overcome accordingly.

In the circumferential direction, in this embodiment, an inclined discharge surface 61 is provided on both sides of each opening 6, through which

an accumulation of grease in the calmed space 40 on surfaces parallel to the axis of rotation is avoided or reduced. These discharge surfaces 61 have an axially directed surface component and in this way discharge grease in the circumferential direction.

A first variant of the fourth embodiment is shown in Figures 7a and 7b. While in the fourth embodiment the openings 6 are arranged at the height of the lugs 72 of the first assembly 1, in this variant the openings 6 are at the height of the springs 70. In this way, depending on the existing requirements, transport of the grease to the desired position is ensured.

In this first variant, the guide disk 5 is designed to be planar and has an outer radius that approximately corresponds to the outer radius of the guide plate 3. In this way, the guide disk 5 can be attached together with the guide plate 3 to the first assembly 1 by means of the clip connection 10, and this embodiment is particularly easy to assemble. Holes 60 are provided in the guide disk 5 at the level of the radially outer side of the calmed space 40, which form the openings 6 and through which the grease is removed.

A second variant shown in Figures 8a to 8c has an enlarged, annular calmed space 40 compared to the first variant.

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Furthermore, three holes 60 are provided in the guide disk 5 at the level of the spring arrangement 70, instead of the one hole 60 in the first variant. In this second variant, discharge surfaces have been dispensed with and the grease is transported simply by a suitable arrangement of the holes 60. In this variant, the displacement means for grease displacement comprise the holes 60 and the first guide surface 30, on which the grease accumulates until it is discharged through the holes 60.

The fifth embodiment (Figures 9a and 9b) of a torsional vibration damper according to the invention also corresponds essentially to the aforementioned embodiments. In this fifth embodiment, however, a sealing ring 4 is provided.

In contrast to the fifth embodiment, the sixth embodiment (Figures 10 and 11) does not have a sealing ring. Furthermore, in the sixth embodiment, the calmed space 40 is not designed as a continuous ring, but is divided into chambers. Between these chambers there are webs to which the guide plate 3 and the guide disk 5 are additionally connected. Holes 60 are used for these connections, which serve as openings 6 between the guide plate 3 and the second guide surface 50 at the level of the calmed space 40. In this embodiment, a high level of stability of the guide disk 5 is thus ensured.

ensured, so that in this embodiment in particular a less stable material can be used as the guide disk 5.

In the seventh embodiment (Figure 12), the guide disk 5 is not connected to the guide plate 3, but is placed on the second assembly 2. In this embodiment, the guide disk 5 rotates together with the second assembly 2. In this embodiment, the opening 6 is formed by an axial gap between the guide plate 3 and the guide disk 5.

In the eighth embodiment (Figures 13 and 14) the guide disk 5 is also placed on the second assembly 2 and is spaced from the guide plate 3 via the opening 6. In this embodiment, the guide plate 3 has lugs 32 which interact with spring wedges 71 provided at the ends of the springs 70 in such a way that the lugs 32 are moved by a spring wedge 71 towards the second assembly 2 when the spring 70 is compressed, i.e. the second assembly 2 moves relative to the first assembly 1. This movement presses the guide plate 3 against a sealing body 42 provided on the second assembly 2. In this way, the spring chamber 7 is completely closed when the spring 70 is compressed and the risk of grease splashing around is thus greatest. When the spring is not compressed or only slightly compressed, however, the spring chamber 7 is sealed without contact.

In the ninth and tenth embodiments (Figures 15 and 16), however, the guide plate 3 is constantly pressed against the sealing body 42. The force required for this is applied by fingers 53 of the guide plate 5. In order to ensure that the guide plate 5 is firmly seated despite these axially effective forces, the guide plate 5 is attached to the second assembly 2 by means of a clip connection 54. In this respect, in the ninth and tenth embodiments, the guide plate 3 constantly slides over the sealing body 42. In the event of a relative movement between the two assemblies 1 and 2, the spring wedge 71 also acts on the guide plate 3 via the nose 32 and increases the sealing force of the guide plate 3 on the sealing body 42. The ninth and tenth embodiments differ in the radial distance of the point of attack of the fingers 53 on the guide plate 3. In this way, the resulting force, in particular on the second assembly 2, can be regulated. This means that the structural design of the fingers 53 when using the second assembly 2 as a coupling flange of a clutch can ensure that the resulting force acts in the direction of the actuating force of the clutch.

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1. Torsional vibration damper with two assemblies (1, 2) arranged such that they can rotate relative to one another and with a spring chamber (7), characterized in that the first assembly (1) has a first guide surface (30) and seals the spring chamber (7) radially on the outside, the first guide surface being spaced from the second assembly (2) by a gap (31) and arranged essentially radially, and an essentially radially arranged second guide surface (50) being provided which covers the gap (31) on the spring chamber side.

2. Torsional vibration damper according to claim 1, characterized in that the first guide surface (30) is designed as a guide plate (3) which is firmly connected to the first assembly (1).

3. Torsional vibration damper according to claim 2, characterized in that the guide plate (3) is designed in the shape of an annular disk.

4. Torsional vibration damper according to one of the preceding claims, characterized in that the second guide surface (50) is designed as a guide disk (5).

Claims (23)

1. Torsional vibration damper with two assemblies ( 1 , 2 ) arranged such that they can rotate relative to one another and with a spring chamber ( 7 ), characterized in that the first assembly ( 1 ) has a first guide surface ( 30 ) and seals the spring chamber ( 7 ) radially on the outside, the first guide surface being spaced from the second assembly ( 2 ) by a gap ( 31 ) and being arranged essentially radially, and an essentially radially arranged second guide surface ( 50 ) being provided which covers the gap ( 31 ) on the spring chamber side. 2. Torsional vibration damper according to claim 1, characterized in that the first guide surface ( 30 ) is designed as a guide plate ( 3 ) which is firmly connected to the first assembly ( 1 ). 3. Torsional vibration damper according to claim 2, characterized in that the guide plate ( 3 ) is designed in the shape of an annular disk. 4. Torsional vibration damper according to one of the preceding claims, characterized in that the second guide surface ( 50 ) is designed as a guide disk ( 5 ). 5. Torsional vibration damper according to claim 4, characterized in that the guide disk ( 5 ) is designed in the shape of an annular disk. 6. Torsional vibration damper according to claim 4 or 5, characterized in that the guide disk ( 5 ) is firmly connected to the first guide surface ( 50 ). 7. Torsional vibration damper according to one of claims 1 to 6, characterized in that between the first guide surface ( 30 ) and the second guide surface ( 50 ) at least one opening ( 6 ) pointing towards the spring chamber ( 7 ) is provided. 8. Torsional vibration damper according to claim 7, characterized in that the opening ( 6 ) is arranged such that a particle with a radial movement component can pass through. 9. Torsional vibration damper according to one of claims 1 to 8, characterized in that a calmed space (40) is provided between the first and second guide surface ( 30 , 50 ) in the vicinity of the gap ( 31 ) which is arranged between the first guide surface ( 30 ) and the second assembly ( 29 ). 10. Torsional vibration damper according to claim 9, characterized in that the calmed space ( 40 ) has an opening ( 6 ) radially on the outside which leads to the spring chamber. 11. Torsional vibration damper according to one of claims 1 to 10, characterized in that a sealing material ( 4 ) made of absorbent material is provided between the first and second guide surface ( 30 , 50 ), which at least when the torsional vibration damper is at a standstill covers the gap between the first guide surface ( 30 ) and the second assembly ( 2 ). 12. Torsional vibration damper according to claim 11, characterized in that the sealing ring ( 4 ) is held under radially inwardly directed prestress of a guide disk ( 5 ) which surrounds the second guide surface ( 50 ) and is designed such that when the torsional vibration damper rotates, this prestress is reduced, preferably to zero. 13. Torsional vibration damper according to one of claims 1 to 12, characterized in that the second assembly ( 2 ) comprises a third substantially radial guide surface ( 20 ) which covers an axial gap ( 51 ) between the second guide surface ( 50 ) and the second assembly ( 2 ) on a side facing away from the spring chamber ( 7 ). 14. Torsional vibration damper according to claim 13, characterized in that the gap ( 31 ) between the first guide surface ( 30 ) and the second assembly ( 2 ) is further away from the spring chamber ( 7 ) in the axial direction than the third guide surface ( 20 ). 15. Torsional vibration damper according to one of claims 1 to 14, characterized by means ( 3 , 32 , 42 ) which close a gap between the first assembly ( 1 ) and the second assembly ( 2 ) as a function of a twist angle between these assemblies ( 1 , 2 ). 16. Torsional vibration damper according to claim 15, characterized in that the closing means ( 3 , 32 , 42 ) comprise at least one nose ( 32 ) which is moved in the axial direction at a certain angle of rotation. 17. Torsional vibration damper according to one of claims 1 to 16, characterized by a grease transport caused by centrifugal forces. 18. Torsional vibration damper according to claim 17, characterized in that the grease transport has a grease receptacle arranged radially on the inside, in particular a gap ( 51 ) leading behind a guide surface ( 5 ), and a grease discharge arranged radially further outward, in particular at least one opening ( 6 ) or a hole ( 60 ), wherein means are provided between the grease discharge and the grease receptacle which displace the grease in the circumferential direction on its way from the grease discharge to the grease receptacle. 19. Torsional vibration damper with two assemblies ( 1 , 2 ) arranged such that they can rotate relative to one another and with a spring chamber ( 7 ), characterized in that the first assembly ( 1 ) has a first guide surface ( 30 ) and seals the spring chamber ( 7 ) radially on the outside, wherein the first guide surface is spaced from the second assembly ( 2 ) by a gap ( 31 ) and is arranged essentially radially, and wherein an essentially radially arranged second guide surface ( 50 ) is provided which covers the gap ( 31 ) without contact and which is placed on the second assembly ( 2 ). 20. Torsional vibration damper according to claim 1, characterized in that the first guide surface ( 30 ) is designed as a guide plate ( 3 ) which is firmly connected to the first assembly ( 1 ). 21. Torsional vibration damper according to claim 2, characterized in that the guide plate ( 3 ) is designed in the shape of an annular disk. 22. Torsional vibration damper according to one of the preceding claims, characterized in that the second guide surface ( 50 ) is designed as a guide disk ( 5 ). 23. Torsional vibration damper according to one of the preceding claims, characterized in that the two assemblies ( 1 , 2 ) are arranged to be rotatable relative to one another via a plain bearing.