Cardan shaft arrangement for a wheel carrier arrangement of a motor vehicle and corresponding wheel carrier arrangement

Abstract

A driveshaft assembly (1) for a wheel carrier assembly (2) of a motor vehicle, comprising a shaft (3) and an angularly movable joint (4), which has a first joint element (5) rotationally fixed to the shaft (3) and a second joint element (6) angularly movably connected to the first joint element (5) and driven by the latter, wherein a driveshaft boot (9) is attached on one side to a first attachment point (10) on the shaft (3) and on the other side to a second attachment point (11) on the second joint element (6), characterized in that the driveshaft boot (9) has a sealing projection (14) extending in the direction away from the shaft (3) beyond the second attachment point (11) and at least partially spaced in a radial direction with respect to an axis of rotation (15) of the second joint element (6).

Description

[0001] The invention relates to a drive shaft assembly for a wheel carrier assembly of a motor vehicle, comprising a shaft and an angularly movable joint having a first joint element coupled to the shaft in a rotationally fixed manner, and a second joint element connected to the first joint element in an angularly movable manner and coupled to the shaft via the first joint element. A drive shaft sleeve is attached to the shaft at a first attachment point and to the second attachment point. The invention further relates to a wheel carrier assembly for a motor vehicle.

[0002] EP 2 505 862 A1 is known from the prior art. This document describes a constant velocity joint with an inner hub, an outer hub, a pin connectable to the outer hub for connecting the joint, and a reinforcing ring that can be positively connected to the outer hub, engages the outer hub in a rotationally fixed manner, and has at least one stop region that defines the position of the outer hub in the reinforcing ring in a first axial direction.

[0003] It is an object of the invention to propose a cardan shaft arrangement for a wheel carrier arrangement of a motor vehicle, which has advantages over known cardan shaft arrangements, in particular achieving a particularly good fatigue strength of the wheel carrier arrangement by cost-effective and simple creation of a good seal against environmental influences.

[0004] This is achieved according to the invention with a propeller shaft arrangement for a wheel carrier arrangement of a motor vehicle having the features of claim 1. It is provided that the propeller shaft sleeve has a sealing projection which projects beyond the second fastening point in the direction facing away from the shaft and is at least partially spaced apart from the second joint element in the radial direction with respect to a rotational axis of the second joint element.

[0005] Advantageous embodiments with useful further developments of the invention are specified in the dependent claims. It should be noted that the exemplary embodiments explained in the description are not limiting; rather, any variations of the features disclosed in the description, the claims, and the figures are feasible.

[0006] The drive shaft assembly is preferably a component of the wheel carrier assembly, but can of course also be provided separately. The wheel carrier assembly serves to rotatably mount at least one wheel on a motor vehicle body. For this purpose, the wheel carrier assembly comprises a wheel carrier, which is connected to the body via one or more links. A wheel hub, to which the wheel is attached or at least attachable, is rotatably mounted on the wheel carrier by means of a wheel bearing. The wheel hub is rotationally fixedly coupled to the second joint element. For example, the second joint element has a toothing, and the wheel hub has a mating toothing. The toothing is preferably in the form of external toothing, and the mating toothing is correspondingly in the form of internal toothing. The wheel bearing is arranged in a wheel bearing receptacle of the wheel carrier, which is formed as an opening, preferably as a closed-edge opening, in the wheel carrier.

[0007] The cardan shaft assembly comprises at least the shaft and the angularly movable joint, which is connected to the shaft in a rotationally fixed manner. If the cardan shaft assembly is part of the wheel carrier assembly, the shaft is connected to a wheel hub via the angularly movable joint, which is rotatably mounted by the wheel carrier assembly. For this purpose, the angularly movable joint is connected to the shaft on the one hand and to the wheel hub on the other. The angularly movable joint is preferably a constant velocity joint. However, other configurations, such as a universal joint or the like, are also conceivable in principle, particularly for other applications of the cardan shaft assembly.

[0008] The angularly movable joint has at least the first joint element and the second joint element, which are connected to one another in an angularly movable manner. This means that the two joint elements, i.e. the first joint element and the second joint element, are connected to one another in a torque-transmitting manner, but their position relative to one another can be changed. For example, the first joint element is mounted for rotation about a first axis of rotation and the second joint element about a second axis of rotation. The axes of rotation usually intersect one another, but can have any angle from a drive shaft angle range during normal operation of the drive shaft arrangement. This angle can vary during operation of the drive shaft arrangement; in the context of the wheel carrier arrangement, for example, this compensates for any deflection of the wheel carrier.

[0009] The first joint element is coupled to the shaft in a rotationally fixed manner, while the second joint element is preferably coupled to the wheel hub or at least capable of being coupled. For example, the second joint element has a toothing that is connected to a counter-toothing of the wheel hub in a torque-transmitting manner. The toothing is preferably configured as external toothing; accordingly, the counter-toothing is configured as internal toothing.

[0010] To ensure reliable protection of the angular joint from environmental influences, the cardan shaft boot is a component of the cardan shaft assembly. It is attached to the shaft at the first attachment point. Starting at the first attachment point, it at least partially overlaps the angular joint and is attached to the second joint element at the second attachment point. The cardan shaft boot is arranged and attached in such a way that the angular joint is protected from environmental influences, in particular, that no dirt or moisture from the external environment of the cardan shaft assembly can penetrate into the angular joint.

[0011] Based on this, the protection provided by the drive shaft boot for the angularly movable joint is to be further improved and - optionally - also the wheel bearing and / or a sensor of the wheel carrier assembly are to be protected from environmental influences. For this purpose, the drive shaft boot protrudes beyond the second fastening point, namely in the direction facing away from the shaft. For this purpose, the drive shaft boot has the sealing projection. This is at least partially spaced from the second joint element in the radial direction with respect to the axis of rotation of the second joint element, i.e., the aforementioned second axis of rotation, in particular on its side facing away from the shaft.

[0012] In other words, the drive shaft sleeve has a free edge on the sealing projection on its side facing away from the shaft, which edge is arranged at a radial distance from the second joint element and is preferably annular. With this free edge, the sealing projection preferably confronts the wheel carrier and interacts with it in a sealing manner. In this case, for example, the sealing projection can be arranged with its free edge such that a remaining distance between the free edge and the wheel carrier is so small that the aforementioned sealing effect occurs. However, it is particularly preferred that the sealing projection engages with its free edge in a sealing recess formed on the wheel carrier. However, the sealing projection is preferably in any case continuously spaced from the wheel carrier, i.e., does not touch it, in order to avoid friction.The described arrangement creates a labyrinth seal that not only protects the angularly movable joint from environmental influences, but also the wheel bearing. This is preferably used to create a pre-seal for the wheel bearing.

[0013] The drive shaft boot, including its sealing projection, is preferably made of the same material and is continuous, i.e., in one piece. It is preferably made of an elastic plastic, in particular an elastomer. Alternatively, the drive shaft boot can also be made of rubber. The Shore A hardness of the material of the drive shaft boot, in particular according to DIN ISO 7619-1, is preferably at least 25 and at most 50 or at least 30 and at most 40. When the shaft, the angularly movable joint, and the drive shaft boot are arranged as intended, a fluid space exists between the shaft and the drive shaft boot, which fluid space is preferably at least partially or completely filled with air. The fluid space is delimited in the radially inward direction by the shaft and in the radially outward direction by the drive shaft boot.There is therefore no additional element between the shaft and the drive shaft sleeve in the radial direction.

[0014] Preferably, the drive shaft sleeve is fastened only at the first fastening point and at the second fastening point, in particular by means of corresponding fastening elements. For example, it is fastened at the first fastening point by means of a first fastening element and at the second fastening point by means of a second fastening element. The fastening elements are preferably in the form of hose clamps. These grip the drive shaft sleeve at the respective fastening point and press it against the shaft or the second joint element.

[0015] For example, the cardan shaft sleeve is composed of a base body and the sealing projection which extends from the base body. Preferably, only the base body is fastened to the shaft and the second joint element, while the sealing projection is fastened exclusively via the base body. Although it can be provided that the sealing projection rests partially against the second joint element, it is not itself fixed relative to it, in particular not in the axial direction relative to the axis of rotation of the second joint element. This fixing takes place exclusively via the base body. The base body therefore extends in the axial direction up to and including the second fastening point or the second fastening element. The sealing projection is immediately adjacent to the second fastening point or the second fastening element.

[0016] The described design of the drive shaft arrangement enables particularly reliable protection of the angularly movable joint from environmental influences. It also optionally allows for protection of the wheel bearing and / or the sensor.

[0017] A further development of the invention provides that the sealing projection has an axial extension that corresponds to at least 3%, at least 5%, or at least 10% of the total extension of the drive shaft sleeve in this direction, and / or that the axial extension of the sealing projection corresponds to at least the extension of a fastening element used to fasten the drive shaft sleeve to the second fastening point in the same direction. Thus, the sealing projection does not merely protrude slightly beyond the second fastening point, but rather the projection is considerable. It is selected in particular such that it cooperates with the wheel carrier in a sealing manner.

[0018] In principle, the sealing projection has a length in the axial direction relative to the rotational axis of the second joint element that corresponds to at least one of the aforementioned portions of the total axial extension of the drive shaft sleeve. Additionally or alternatively, the length of the sealing projection corresponds at least to the greatest extension of the fastening element, in particular the hose clamp, in the axial direction over its circumference. For example, the length of the sealing projection is greater than the extension of the fastening element by a factor of at least 1.5, at least 2, at least 2.5, or at least 3. A length of the sealing projection selected in this way enables a particularly good sealing effect, in particular due to the sealing interaction of the sealing projection with the wheel carrier.

[0019] A further development of the invention provides that the sealing projection has a contact area adjacent to the second joint element and a sealing area spaced radially from the second joint element relative to the rotational axis of the second joint element. The sealing projection is thus conceptually divided into several areas, namely the contact area and the sealing area. However, it is constructed from the same material and in one piece; the contact area and the sealing area preferably merge directly into one another.

[0020] The contact area is understood to be an area of ​​the sealing projection in which it rests at least partially against the second joint element in the circumferential direction, preferably continuously over the entire circumference of the second joint element. The contact area preferably extends from the second fastening point or the second fastening element in the direction away from the shaft, namely as far as the sealing area which is spaced from the second joint element. In longitudinal section, the contact area is understood to be the entire area of ​​the sealing projection which rests against the second joint element. The sealing area, on the other hand, is understood to be the entire area of ​​the sealing projection which is spaced from the second joint element. The contact area which rests against the second joint element ensures stiffening or stabilization of the sealing projection.The sealing effect and thus protection against environmental influences is finally achieved by means of the sealing area.

[0021] A further development of the invention provides that the distance of the sealing projection from the second joint element in the radial direction with respect to the axis of rotation is greater by a factor of at least 3, at least 5, or at least 10 than a material thickness of the sealing projection in the sealing area. The distance of the sealing projection from the second joint element is to be understood as the smallest distance between the sealing projection and the second joint element in the radial direction, viewed in the circumferential direction. This means that the minimum distance of the sealing projection has the stated size, i.e. is at least five times greater than the material thickness of the sealing projection in the sealing area. This distance ensures high flexibility of the sealing projection in its sealing area and thus enables a good sealing effect.

[0022] A further development of the invention provides that the contact area and the sealing area are aligned with one another in the radial direction with respect to the axis of rotation, the sealing area being arranged in the axial direction in overlap with a taper of the second joint element, or that the contact area and the sealing area are arranged offset from one another in the radial direction with respect to the axis of rotation, in that the contact area and the sealing area are connected via a connecting ring formed by the sealing projection.

[0023] Basically, the drive shaft sleeve can be available in two different versions. According to a first version, the contact area and the sealing area overlap with each other in the radial direction. For example, the sealing area represents an extension of the contact area, so that in cross-section, a straight line intersecting the contact area in the middle also intersects the sealing area in the middle. For example, the contact area is completely accommodated in an imaginary hollow circular cylinder, and the sealing area lies completely in an imaginary extension of this hollow circular cylinder. The distance between the sealing area and the second joint element is achieved by tapering the second joint element, which is achieved by reducing the dimensions in the radial direction.

[0024] The taper overlaps the sealing area in the axial direction, so that the distance between the sealing area and the second joint element increases starting from the contact area, for example, continuously or—in the case of a step or recessed taper—abruptly. The distance between the sealing area and the second joint element is achieved by a corresponding design of the second joint element.

[0025] In a second variant of the cardan shaft sleeve, however, the distance is achieved by a corresponding design of the cardan shaft sleeve or its sealing projection. For this purpose, the contact area and the sealing area are arranged offset from one another in the radial direction and are connected to one another via the connecting ring. The connecting ring preferably overlaps the contact area in the axial direction and extends from there in the radial direction outwards to the sealing area. The tapering of the second joint element can of course also be provided in order to increase the distance between the sealing area and the second joint element. The described design of the cardan shaft arrangement enables the advantages already explained in a structurally simple manner.

[0026] A further development of the invention provides for the sealing area to be shaped like a hollow circular cylinder. The sealing projection is thus rotationally symmetrical in the sealing area, particularly with respect to the second axis of rotation. This achieves a particularly good sealing effect.

[0027] A further development of the invention provides that the sealing projection has a base body, preferably in the shape of a hollow circular cylinder, in the contact area, from which at least one stiffening rib extends outward in the radial direction relative to the rotation axis. The base body rests on the one hand against the second joint element, in particular completely and continuously. On its side facing away from the second joint element in the radial direction, the at least one stiffening rib extends from the base body, so that the material thickness of the sealing projection is locally increased in this area.

[0028] The at least one stiffening rib increases the rigidity of the sealing projection, so that the sealing effect provided by the sealing projection is reliably provided. The base body is preferably hollow-circular-cylindrical in shape. The at least one stiffening rib extends outward from it. Of course, any number of stiffening ribs can be provided, in particular, several stiffening ribs extend from the base body. For example, these stiffening ribs are arranged on the base body evenly distributed in the circumferential direction. The at least one stiffening rib is preferably made in one piece and from the same material as the base body.

[0029] A further development of the invention provides that the at least one stiffening rib extends as far as the sealing area and / or the connecting ring, in particular merges into the sealing area and / or the connecting ring. The stiffening rib serves to stabilize the sealing area. For this purpose, it extends in the axial direction as far as the sealing area or at least as far as the connecting ring. Preferably, it merges into the sealing area or the connecting ring, i.e., it directly borders on it. The stiffening rib preferably runs in the axial direction, i.e., its longitudinal center axis is parallel to the axis of rotation of the second joint element. The described configuration results in particularly high stiffness of the sealing projection and thus a good sealing effect.

[0030] A further development of the invention provides for the drive shaft sleeve to be designed as a bellows. The bellows allows for simple length compensation in the axial direction.

[0031] The invention further relates to a wheel carrier arrangement for a motor vehicle, comprising a wheel carrier and a cardan shaft arrangement, in particular a cardan shaft arrangement according to the embodiments in the context of this description, wherein the cardan shaft arrangement has a shaft and an angularly movable joint which has a first joint element which is coupled in a rotationally fixed manner to the shaft and a second joint element which is connected in an angularly movable manner to the second joint element and is drive-coupled to the shaft via this, wherein a cardan shaft sleeve is fastened on the one hand to a first fastening point on the shaft and on the other hand to a second fastening point on the second joint element.It is provided that the cardan shaft sleeve has a sealing projection which projects beyond the second fastening point in the direction facing away from the shaft and is at least partially spaced apart from the second joint element in the radial direction with respect to a rotational axis of the latter.

[0032] The advantages of such a design of the wheel carrier assembly and the propeller shaft assembly have already been pointed out. Both the wheel carrier assembly and the propeller shaft assembly can be further developed according to the explanations in this description, so reference is made to these in this regard.

[0033] A further development of the invention provides that the sealing projection is spaced from a sealing surface of the wheel carrier in the axial direction and / or in the radial direction by a factor of at most 2, at most 4, or at most 6 greater than a material thickness of the sealing projection in a sealing region spaced from the second joint element in the radial direction with respect to the axis of rotation of the second joint element. The sealing surface and the sealing projection or its sealing region are designed and arranged relative to one another in such a way that they jointly effect the aforementioned sealing effect. For this purpose, they are spaced slightly apart from one another, namely in the axial direction and / or in the radial direction. Relative to the material thickness of the sealing projection in the sealing region, in particular the material thickness of the sealing region on its side facing the sealing surface, the distance is at most 2, at most 4, or at most 6.This achieves a good sealing effect.

[0034] A further development of the invention provides that the wheel carrier has a sealing recess into which the sealing projection engages, viewed in the axial direction relative to the axis of rotation, to form a labyrinth seal. The sealing recess is preferably circularly cylindrical. It is located on the side of the wheel carrier facing the drive shaft sleeve. The wheel carrier and the drive shaft sleeve are arranged relative to one another in such a way that the sealing projection engages in the sealing recess. The aforementioned sealing surface preferably delimits the sealing recess, for example, it represents a base of the sealing recess.

[0035] The sealing recess is preferably delimited both by the base and by walls which extend from the base at a distance from one another and are each formed by the wheel carrier. The two walls are each annular. The sealing recess is delimited in the radially inward direction by a first of the walls, in the radially outward direction by a second of the walls, and in the axial direction by the base. Viewed in the axial direction, the sealing projection is preferably arranged so as to overlap both walls and is a sufficiently small distance from both walls. For example, the distance from each of the walls, again based on the material thickness of the sealing projection, is at most 6, at most 4, or at most 2. This particularly preferably also applies to the base.

[0036] The features and feature combinations described in the description, in particular the features and feature combinations described in the following description of the figures and / or shown in the figures, can be used not only in the respective combination specified, but also in other combinations or on their own, without departing from the scope of the invention. Thus, embodiments are also considered to be encompassed by the invention that are not explicitly shown or explained in the description and / or the figures, but which follow from or can be derived from the explained embodiments.

[0037] The invention will be explained in more detail below with reference to the exemplary embodiments shown in the drawings, without limiting the invention. In the drawings: Fig. 1 a schematic representation of a cardan shaft arrangement for a wheel carrier arrangement of a motor vehicle, Fig. 2 a schematic representation of the cardan shaft arrangement in a first embodiment, Fig. 3 a schematic representation of the cardan shaft arrangement in a second embodiment, Fig. 4 a schematic representation of the wheel carrier arrangement, as well as Fig. 5 a further schematic representation of the wheel carrier arrangement.

[0038] The Fig. 1 shows a schematic representation of a drive shaft assembly 1, such as is used for a wheel carrier assembly 2 of a motor vehicle. The drive shaft assembly 1 has a shaft 3 and an angularly movable joint 4, which has a first joint element 5 (not visible here) and a second joint element 6. The second joint element 6 comprises a toothed extension 7, on which a toothing is formed. The angularly movable joint 4 is at least partially overlapped by a drive shaft sleeve 9, which is fastened at a first fastening point 10 to the shaft 3 and at a second fastening point 11 to the second joint element 6. The fastening at the first fastening point 10 is effected by means of a first fastening element 12 and at the second fastening point by means of a second fastening element 13, each of which is designed as a hose clamp.

[0039] The drive shaft sleeve 9 is designed as a bellows, at least in some regions, namely in particular between the first fastening point 10 and the second fastening point 11. On the side of the second fastening point 11 facing away from the shaft 3, the drive shaft sleeve 9 has a sealing projection 14, which is at least partially spaced apart from the second joint element 6 in the radial direction with respect to a rotational axis 15 of the latter. This means that between the sealing projection 14 of the drive shaft sleeve 9 and the second joint element 6 there is an annular space 16, which is delimited in the radially inward direction directly by the second joint element 6 and in the radially outward direction directly by the sealing projection 14.

[0040] Viewed in the axial direction, the sealing projection has a contact area 17 and a sealing area 18. In the contact area 17, it rests against the second joint element 6, in particular continuously in the circumferential direction. In the sealing area 18, however, it is spaced from the joint element 6 to create the annular space 16. In the exemplary embodiment illustrated here, the contact area 17 and the sealing area 18 are connected to one another by means of a connecting ring 19, which extends from the contact area 17 in the radial outward direction to the sealing area 18.

[0041] The contact area 17 has a base body 20, which is essentially hollow-cylindrical. One or more stiffening ribs 21 extend from this base body 20 and, viewed in the axial direction, extend from the second fastening point 11 to the sealing area 18 or at least the connecting ring 19 and merge into it. The stiffening ribs 21 have an outer diameter that corresponds to, or at least substantially corresponds to, an outer diameter of the sealing area 18. This at least partially prevents deformation of the sealing area 18, for example, due to the centrifugal force occurring when the shaft 3 rotates.

[0042] The Fig. Figure 2 shows a schematic design of the cardan shaft assembly 1 in a first embodiment. This corresponds to the one explained above, so reference is made to the corresponding embodiments. The radial distance between the second joint element 6 and the sealing area 18 is indicated by the double arrow 22.

[0043] The Fig. Figure 3 schematically shows the propeller shaft assembly 1 in a second embodiment. This is fundamentally similar to the first embodiment, so reference is made to the above explanations, and only the differences will be discussed below. These are that there is no offset in the radial direction between the contact area 17 and the sealing area 18, but rather that they are radially aligned with each other. The distance, again indicated by the double arrow 22, is achieved by a taper 23 of the second joint element 6. Thus, the connecting ring 19 is omitted.

[0044] The Fig. Figure 4 shows a schematic representation of the wheel carrier assembly 2, which, in addition to the drive shaft assembly 1, has a wheel carrier 24 on which a wheel flange 26 is rotatably mounted by means of a wheel bearing 25. The wheel flange 26 has a mating toothing 27 that engages with the toothing 8 of the toothing attachment 7. It can be seen that the sealing area 18 extends almost to a sealing surface 28 of the wheel carrier 24. It cooperates with this sealing surface to protect not only the joint 4 but also the wheel bearing 25 from environmental influences. This can also apply to a sensor arranged in the area of ​​the wheel bearing 24. The second embodiment of the drive shaft assembly 1 is shown here.

[0045] The wheel bearing 25 preferably has its own seals, not shown here. By means of the seals, a rolling element chamber, in which rolling elements of the wheel bearing 25 are arranged, is sealed from the surroundings of the wheel bearing 25. Preferably - viewed in longitudinal section - one of the seals is arranged on the one hand for the rolling elements and another of the seals is arranged on the other hand for the rolling elements, so that they accommodate the rolling element chamber between them. The sealing interaction of the sealing area 18 with the wheel carrier 24 creates a pre-seal for one of the wheel bearing seals. This significantly reduces the amount of dirt and / or moisture that could reach the wheel bearing seal from the shaft 3 without the pre-seal. Accordingly, a smaller dimensioning of the wheel bearing is possible. This is possible without increased friction because the sealing area 18 is spaced apart from the wheel carrier 24, thus creating a gap seal.

[0046] The Fig. 5 shows a further schematic representation of the wheel carrier assembly 2, wherein the drive shaft assembly 1 is in its first embodiment. Reference is made in full to the above explanations, and only the differences are discussed below. These consist in the fact that the sealing surface 28 is now located in a sealing recess 29, which is delimited by the sealing surface 28 and additionally by walls 30 and 31. The sealing region 18 of the sealing projection 14 protrudes into this sealing recess 29, so that it is ultimately located between the walls 30 and 31. This forms a labyrinth seal 32, which in turn preferably forms the pre-seal for the wheel bearing. LIST OF REFERENCE SYMBOLS: 1 Cardan shaft arrangement 2 wheel carrier arrangement 3 Wave 4 joint 5 1. Joint element 6 2. Joint element 7 Serration process 8 Gearing 9 Drive shaft boot 10 1. Attachment point 11 2. Attachment point 12 1. Fastening element 13 2. Fastening element 14 Sealing projection 15 axis of rotation 16 Annular space 17 Investment area 18 Sealing area 19 Connecting ring 20 basic bodies 21 Stiffening rib 22 Arrow 23 Rejuvenation 24 wheel carriers 25 wheel bearings 26 Wheel flange 27 Counter-toothing 28 Sealing surface 29 Sealing recess 30 wall 31 Wall 32 Labyrinth seal QUOTES CONTAINED IN THE DESCRIPTION

[0000] This list of documents submitted by the applicant was generated automatically and is included solely for the convenience of the reader. This list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions. Cited patent literature

[0000] EP 2505862 A1

[0002]

Claims

[1] A cardan shaft arrangement (1) for a wheel carrier arrangement (2) of a motor vehicle, comprising a shaft (3) and an angularly movable joint (4) which has a first joint element (5) which is coupled in a rotationally fixed manner to the shaft (3) and a second joint element (6) which is connected in an angularly movable manner to the first joint element (5) and is coupled via this to the shaft (3) in a drive-related manner, wherein a cardan shaft sleeve (9) is fastened on the one hand to a first fastening point (10) on the shaft (3) and on the other hand to a second fastening point (11) on the second joint element (6), characterized by in that the cardan shaft sleeve (9) has a sealing projection (14) which projects beyond the second fastening point (11) in the direction facing away from the shaft (3) and is at least partially spaced apart from the second joint element (6) in the radial direction with respect to a rotational axis (15) of the latter. [2] Cardan shaft arrangement according to claim 1, characterized bythat the sealing projection (14) has an extension in the axial direction which corresponds to at least 3%, at least 5% or at least 10% of a total extension of the cardan shaft sleeve (9) in this direction, and / or that the extension of the sealing projection (14) in the axial direction corresponds to at least one extension in the same direction of a hose clamp used to fasten the cardan shaft sleeve (9) to the second fastening point (11). [3] Cardan shaft arrangement according to one of the preceding claims, characterized by that the sealing projection (14) has a contact area (17) lying against the second joint element (6) and a sealing area (18) spaced apart from the second joint element (6) in the radial direction with respect to the axis of rotation (15) of the second joint element (6). [4] Cardan shaft arrangement according to one of the preceding claims, characterized bythat the distance of the sealing projection (14) from the second joint element (6) in the radial direction with respect to the axis of rotation (15) is greater by a factor of at least 3, at least 5 or at least 10 than a material thickness of the sealing projection (14) in the sealing region (18). [5] Cardan shaft arrangement according to one of the preceding claims, characterized by that the contact area (17) and the sealing area (18) are aligned with one another in the radial direction with respect to the axis of rotation (15), the sealing area (18) being arranged in the axial direction in overlap with a taper (23) of the second joint element (6), or that the contact area (17) and the sealing area (18) are arranged offset from one another in the radial direction with respect to the axis of rotation (15), in that the contact area (17) and the sealing area (18) are connected via a connecting ring (19) formed by the sealing projection (14). [6] Cardan shaft arrangement according to one of the preceding claims, characterized by that the sealing area (18) is hollow circular cylindrical. [7] Cardan shaft arrangement according to one of the preceding claims, characterized by that the sealing projection (14) in the contact area (17) has a base body (20) from which at least one stiffening rib (21) extends outwards in the radial direction with respect to the axis of rotation (15). [8] Wheel carrier arrangement (2) for a motor vehicle, comprising a wheel carrier (24) and a propeller shaft arrangement (1), in particular a propeller shaft arrangement (1) according to one or more of the preceding claims, wherein the propeller shaft arrangement (1) has a shaft (3) and an angularly movable joint (4) which has a first joint element (5) coupled in a rotationally fixed manner to the shaft (3) and a second joint element (6) connected in an angularly movable manner to the first joint element (5) and coupled via the latter to the shaft (3) in a drive-related manner, wherein a propeller shaft sleeve (9) is fastened on the one hand to a first fastening point (10) on the shaft (3) and on the other hand to a second fastening point (11) on the second joint element (6), characterized byin that the cardan shaft sleeve (9) has a sealing projection (14) which projects beyond the second fastening point (11) in the direction facing away from the shaft (3) and is at least partially spaced apart from the second joint element (6) in the radial direction with respect to a rotational axis (15) of the latter. [9] Wheel carrier arrangement according to claim 8, characterized by in that the sealing projection (14) has a distance from a sealing surface (28) of the wheel carrier (24) in the axial direction and / or in the radial direction, which distance is greater by a factor of at most 2, at most 4 or at most 6 than a material thickness of the sealing projection (14) in a sealing region (18) spaced from the second joint element (6) in the radial direction with respect to the axis of rotation (15) of the second joint element (6). [10] Wheel carrier arrangement according to one of the preceding claims, characterized bythat the wheel carrier (24) has a sealing recess (29) into which the sealing projection (14) engages in the axial direction with respect to the axis of rotation (15) to form a labyrinth seal (32).

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