Rotary bearing and bearing arrangement having a rotary bearing

Abstract

The invention relates to a rotary bearing (2), comprising a first bearing part (10) and a second bearing part (11), wherein the bearing parts are mounted rotatably relative to one another, wherein the rotary bearing has an integrated braking device (25) which comprises at least one adjusting screw (27) provided on the first bearing part and at least one friction element (26), wherein the friction element can be tensioned against the second bearing part via the adjusting screw in order to change the braking force.

Description

[0001] Rotating bearing and bearing arrangement with a rotating bearing

[0002] The present invention relates to a pivot bearing comprising a first bearing part and a second bearing part, wherein the bearing parts are mounted so as to be rotatable relative to one another.

[0003] Pivot bearings are used to connect components in such a way that they have a degree of freedom of movement with respect to relative rotation. Often, a certain braking or inhibiting effect is desired in order to stop any relative movement or rotation once handling, especially manual movement, of the components has been completed. Regarding the braking effect, there is a need to be able to specify the resulting braking force or its magnitude in an application-specific and permanent manner.

[0004] The invention has for its object to provide an improved concept with regard to a pivot bearing, in particular with regard to the aspect just mentioned concerning the braking effect.

[0005] According to the invention, the object is achieved in a pivot bearing of the type mentioned at the outset in that it has an integrated braking device which comprises at least one adjusting screw provided on the first bearing part and at least one friction element, wherein the friction element can be tensioned against the second bearing part via the adjusting screw in order to change the braking force.

[0006] The integrated braking device creates a frictional force between the friction element and the second bearing part, which counteracts any momentary relative movement or rotation between the bearing parts. With regard to the mobility between the bearing parts realized by means of the pivot bearing, the braking device thus creates rotational resistance. On the one hand, the frictional force means that the manually initiated generation of a relative movement between the components connected by the bearing parts requires a deliberate, manual force to overcome the frictional effect. In particular, unwanted movements of the components connected by the pivot bearing, which could occur, for example, due to unintentional impacts on the components, are avoided or at least reduced.On the other hand, the friction force causes the relative movement to be immediately slowed down when manual handling of the components is completed due to the inhibiting effect, without any conscious operating action being required, in particular manual action that counteracts the current movement of the components.

[0007] The adjusting screw represents a remarkably simple means, particularly compared to the use of electromechanical actuators or similar, of generating the frictional force on the one hand, and of being able to define and adjust its magnitude and thus the extent of the occurring rotational resistance as required by means of the specific screw position, on the other. Thus, the frictional force can be increased accordingly by tightening the adjusting screw further; in extreme cases, the frictional force is so high that the pivot bearing ultimately seizes up. In the other extreme case, the adjusting screw can be loosened or completely removed to such an extent that the frictional force generated by the friction element disappears completely, resulting in little or no braking effect on the pivot bearing.

[0008] According to the invention, the friction element can be a friction lining, in particular a plate- and / or strip-like one. The friction lining preferably has a planar extent that is significantly greater than the thickness or strength of the friction element. Within the scope of this embodiment, the friction element can be arranged in a gap, in particular in a gap formed between the first bearing part and the second bearing part.

[0009] The friction element is preferably made of a metal and / or a plastic. Typically, the bearing parts are made of a metal, such as steel. With regard to the material of the friction element, a material is provided which, in relation to the material pairing with the material of the second bearing part, has a sufficiently high coefficient of friction to generate an adequate braking effect. The material of the friction element preferably has a lower mechanical resistance compared to the second bearing part, so that the friction element is primarily worn due to the friction force. The friction element can therefore be replaceable. It is conceivable that the friction element is fiber-reinforced, i.e., comprises a fiber material, in particular a woven one. The pivot bearing particularly preferably forms a roller bearing.This means that the pivot bearing has an outer ring forming the first bearing part and an inner ring forming the second bearing part, wherein the inner ring and the outer ring are mounted so as to rotate relative to one another about a rotation axis. In the roller bearing, needles or rollers are provided, in particular, arranged in a bearing cage, which are arranged on bearing surfaces of the bearing parts that extend concentrically around the rotation axis along a circumferential direction. The bearing surface of the inner ring is provided on a radial outer side or surface of the inner ring, and the bearing surface of the outer ring is provided on a radial inner side or surface of the outer ring.

[0010] The roller bearing can be a tapered roller bearing, in which the bearing surfaces are arranged at an angle relative to the rotational axis. It is conceivable that the inner ring has a set collar or a set nut and an inner cylinder, with the bearing surface of the inner ring being arranged on the radial outer side or surface of the set collar. The set collar has threads that are screwed to corresponding mating threads formed on the outer ring and the inner cylinder. The rollers of the tapered roller bearing can be mechanically preloaded by tightening the set collar, so that even large loads acting at an angle relative to the rotational axis can be transmitted via the pivot bearing.

[0011] Particularly preferably, the inner ring is arranged concentrically within the outer ring, with the friction element being arranged between an outer side of the inner ring and an adjacent inner side of the outer ring. The inner ring and the outer ring can have an at least substantially cylindrical or hollow-cylindrical shape, with the cylinder or hollow cylinder forming the inner ring being inserted into the radial interior of the hollow cylinder forming the outer ring. The rings can have an at least substantially equal axial extent with respect to, or along, the rotation axis.

[0012] Furthermore, it is conceivable for the adjusting screw to be screwed from the outside along the radial direction into a through-bore of the outer ring, wherein the friction element can be clamped against the inner ring by means of the adjusting screw for variable generation of the braking force. The through-bore represents a bore that completely penetrates the outer ring or the wall of the outer ring, in particular a hollow cylindrical one. A radially outer opening of the through-bore is preferably freely accessible, so that a screw head of the screw inserted into the through-bore can be reached from the outside using an appropriate tool, such as a screwdriver.In the case of the rotary bearing according to the invention according to this embodiment, the tightening of the screw and thus the adjustment of the braking effect can therefore only be carried out after the assembly of the other components and during the ongoing use of the rotary bearing, without any disassembly being necessary.

[0013] In the pivot bearing according to the invention, a groove running circumferentially along the inner side of the outer ring can be provided, wherein at least one depression is provided axially at the same height as the groove on the outer side of the inner ring, wherein a ball can be provided which is located on the one hand in the groove and on the other hand in the depression, wherein a threaded pin is screwed into a bore leading radially inward from an outer side of the outer ring and opening into the groove. According to this embodiment, the ball and the threaded pin form a movement stop with respect to the relative movement between the bearing parts.

[0014] With regard to the assembly or formation of this movement stop, the rings must be brought into a relative position to one another such that the bore 21 is aligned with or with one of the recesses. The ball is then inserted into this recess via the bore so that the ball is then located in the recess on the one hand and in the groove on the other. The position of the ball is fixed due to the local limitation of the recess, whereby the relative movement between the bearing parts is generally initially unaffected or limited due to the uninterrupted groove. If several recesses are provided, the insertion process just described can be repeated for another ball and another recess. The setscrew is then screwed into an internal thread of the bore until it protrudes into the groove. The ball then forms a one-sided end stop.If two balls are provided, these balls form end stops on both sides. It is conceivable that the friction element is attached to the first bearing part, particularly to the outer ring. Thus, the occurrence of the braking force can cause the respective bearing part, which is in contact with the friction element, to carry the friction element along and move it out of position.

[0015] According to an optional development, it is conceivable for the friction element to be attached to a holder, which in turn is attached to the first bearing part. Although, in principle, a direct attachment of the friction element to the first bearing part is also possible, in this embodiment, the holder functions as a connection interface between the friction element and the first bearing part. The friction element is preferably attached to the holder by means of an adhesive, in particular a high-strength adhesive.

[0016] Particularly when the pivot bearing forms the roller bearing, it is conceivable that the strip-shaped holder is arranged in a gap between the or an outer side of the first bearing part, i.e., the inner ring, and the or an inner side of the second bearing part, i.e., the outer ring. Particularly when not only the holder but also the friction element is plate- or strip-shaped, the components required to generate the braking force, i.e., the holder and the friction element, require as little installation space as possible, thus enabling a compact design for the pivot bearing according to the invention. In particular, these components only require the gap that already exists between the bearing parts or rings.

[0017] The holder is preferably formed from a spring steel sheet. The holder can be bent in a circular shape with respect to its longitudinal direction, with a bending radius that corresponds to the radius of the gap between the bearing parts. The bearing can form a closed ring that extends completely around the circumferential direction. Several friction elements, in particular equidistantly distributed, can be attached to the holder, or in particular to the previously explained ring running around it. Only a single friction element can be attached to the holder, in which case it is particularly provided that several holders are arranged along the circumferential direction. A gap can be provided between each of the holders. Three holders, each with a friction element, can be provided along the circumferential direction, each of the holders extending at an angle of, in particular, just under 120° around the axis of rotation.Generally speaking, a plurality of evenly distributed holders, in particular each with a friction element attached thereto, can be arranged along the circumferential direction, each of the holders extending around the axis of rotation by an angle which results from 360° divided by the number of holders provided.

[0018] It is conceivable that the pivot bearing according to the invention has a receiving groove extending along a circumferential direction of the pivot bearing and provided on the outside of the inner ring and / or the inside of the outer ring, wherein the holder is inserted into the receiving groove. A cross-sectional area of ​​the holder that is perpendicular to the longitudinal direction of the holder and the cross-sectional area of ​​the receiving groove can correspond to one another or be equal to one another. For example, a rectangular cross-sectional area is conceivable in this regard. The receiving groove synergistically realizes several advantages. For example, the receiving groove ensures that the holder is recessed in the respective receiving groove. This creates a larger contact area between the bearing part having the receiving groove and the holder, whereby the holder is further stabilized with respect to undesired displacement along its longitudinal direction.Further stabilization is achieved in the transverse direction of the holder due to the positive locking between the holder and the receiving groove. Furthermore, the recessed position of the holder in the receiving groove enables an even more compact design for the pivot bearing according to the invention. For example, the gap between the rings can be made even narrower.

[0019] It is conceivable that the pivot bearing according to the invention has at least one radial bore extending radially through the outer ring and the holder, into which a screw is screwed from the inside to fasten the holder to the outer ring. The screw thus prevents displacement of the holder when the braking force occurs. For the purposes of simpler production, it can be provided that the radial bore extends completely through the outer ring or through a wall of the outer ring. Since a head of the screw is arranged on the inside of the outer ring and thus in the gap between the rings, it should not come into contact with the outside of the inner ring. For this purpose, the height of the head of the screw can be smaller than the width or thickness of the friction element, which in this case is also arranged in this gap.Additionally or alternatively, the head can be at least partially received in a counterbore of the holder and / or the outer ring, which is provided radially on the inside of the radial bore.

[0020] Particularly preferably, at least one spring element is arranged between the friction element and the adjusting screw, wherein the extent of elastic deformation of the spring element, on which in turn the braking force depends, can be changed by changing the screw position of the adjusting screw. A front or radially inner end face of the adjusting screw can be in contact with the spring element. The spring element can thus be supported on the one hand on the adjusting screw and on the other hand on the friction element. Tightening the adjusting screw causes the elastic deformation of the spring element, which in turn causes a corresponding elastic restoring force. This elastic restoring force then presses the friction element against the second bearing part, wherein the strength of this restoring force determines the strength of the resulting braking effect.The spring element allows for the adjustability of the braking force by extending the total distance available for the adjusting screw to generate the braking force, depending on the screw position. This allows for more precise adjustment of the braking force, since the screw does not reach its end position immediately after contact with the friction element is established. Instead, the spring element gradually deforms over a longer displacement range of the adjusting screw.

[0021] Particularly preferably, the spring element is at least one compression spring or comprises at least one compression spring. A radially inner end of the compression spring is preferably supported on the friction element, and a radially outer end of the compression spring is supported on the adjusting screw, in particular on its end face. Screwing in the adjusting screw thus causes an elastic compression of the compression spring, with a steady increase in the elastic restoring force and thus a braking effect. It is conceivable that several compression springs are provided stacked one above the other along the radial direction. The compression spring can be a helical spring or a disc spring.

[0022] The invention further relates to a bearing arrangement comprising at least one pivot bearing according to the preceding description. According to the invention, the bearing arrangement can be rotatably mounted on a holding section via the pivot bearing or via one of the pivot bearings. It is conceivable that the holding section forms a ceiling of a room, in particular a medical treatment room such as an operating room, or is a ceiling support. Additionally or alternatively, according to the invention, it can be provided that two components of the bearing arrangement are mounted rotatably relative to one another via the pivot bearing or via one of the pivot bearings. With regard to the components, it can be provided that tripod arms are provided as components, or that one of the components is a tripod arm and the other of the components is a support element, for example for a medical device.

[0023] Preferably, the support arrangement according to the invention is a ceiling mount, for example, for medical-technical applications in a hospital. The ceiling mount can be a support device for the medical device, wherein the medical device can be, for example, a display device, such as a screen, a power outlet, a component of a medical imaging device, such as an X-ray source, or a resuscitation device.

[0024] All features, advantages and aspects explained in connection with the rotary bearing according to the invention are equally transferable to the bearing arrangement according to the invention and vice versa.

[0025] The invention is explained below using exemplary embodiments with reference to the drawings. The drawings are schematic representations and show:

[0026] Figure 1: a view of a bearing arrangement according to the invention according to a

[0027] Embodiment comprising several pivot bearings according to the invention according to an embodiment, Figure 2: a perspective view of one of the pivot bearings of the bearing arrangement of Figure 1 obliquely from above,

[0028] Figure 3: a perspective view of the pivot bearing of Figure 2 from below,

[0029] Figure 4: a sectional view through the pivot bearing of Figures 2 and 3, the section line in Figure 2 being indicated by IV-IV,

[0030] Figure 5: a sectional view through the pivot bearing of Figures 2 and 3, the section line in Figure 2 being indicated by VV,

[0031] Figure 6: a horizontal section through the pivot bearing of Figures 2 and 3, and

[0032] Figure 7: a view of friction elements arranged on a holder of the

[0033] Pivot bearing of Figure 2.

[0034] Figure 1 shows a bearing assembly 1 according to the invention according to one exemplary embodiment, which is, for example, a ceiling mount for medical use in a hospital. The bearing assembly 1 comprises three pivot bearings 2, 3, and 4 according to the invention, each according to one exemplary embodiment. Specifically, an upper pivot bearing 2, a middle pivot bearing 3, and a lower pivot bearing 4 are provided, which, with regard to the aspects explained below, are fundamentally identical in design.

[0035] The bearing arrangement 1 further comprises a plurality of components 5, namely an upper pivot arm 6, a lower pivot arm 7 and a support device 8 for a medical device (not shown in detail), which may be, for example, a display device such as a screen, a power outlet, a medical imaging device or a resuscitation device.

[0036] The bearing assembly 1 is rotatably mounted on a support section 9, which in this case is a ceiling support, via the upper pivot bearing 2. Furthermore, the upper pivot arm 6 and the lower pivot arm 7 are mounted for relative rotation via the middle pivot bearing 3. Finally, the lower pivot arm 7 and the support device 8 are mounted for relative rotation via the lower pivot bearing 4. The respective rotation axes 14 are arranged vertically in space, for example.

[0037] Below, details regarding the upper pivot bearing 2 are explained, which in principle also apply equally to the other pivot bearings 3, 4. For simplicity, we will briefly refer to the pivot bearing 2 below. Figure 2 shows a perspective view of the pivot bearing 2 from an angled top, and Figure 3 shows a perspective view from an angled bottom.

[0038] The pivot bearing 2 forms a rolling bearing and comprises a first bearing part 11 and a second bearing part 10, wherein the first bearing part 11 is an outer ring 13 and the second bearing part 10 is an inner ring 12. The bearing parts 10, 11 are mounted so as to be rotatable relative to one another about the rotation axis 14. The outer ring 13 and an adjusting ring 16 or an adjusting nut of the inner ring 12 each have threaded bores 15, via which the components 5 or the holding section 9 are or are connected to the pivot bearing 2.

[0039] In the following, particular reference is also made to Figures 4 and 5, which each show sectional views of the pivot bearing 2, wherein the sectional plane of Figure 4 is indicated by the line IV-IV in Figure 2, and the sectional plane of Figure 5 is indicated by the line VV in Figure 2. The bearing parts 10, 11 are mechanically coupled to one another via components forming a double-acting bearing, namely an axial angular contact needle bearing or angular contact roller bearing. Needles or rollers 18 arranged in a bearing cage 17 are arranged concentrically around the rotation axis 14 on inclined bearing surfaces of the bearing parts 10, 11. The bearing surface of the inner ring 12 is located on a radial outer side or surface of the adjusting ring 16, and the bearing surface of the outer ring 13 is located on a radial inner side or surface of the outer ring 13.The adjusting ring 16 has threads that are screwed to corresponding mating threads formed on the outer ring 13 and an inner cylinder 19 of the inner ring 12. The rollers 18 of the angular contact roller bearing can be mechanically preloaded by tightening the adjusting ring 16. This allows the pivot bearing 2 to transmit large loads that act obliquely with respect to the rotational axis 14.

[0040] It is often desired that the relative movement between the bearing parts 10, 11 is limited or at least that a corresponding movement stop is provided. For this purpose, a groove 20 with a curved groove base is provided on the radial inner side of the outer ring 13, running along the circumferential direction. A bore 21 leading radially inward from a radial outer side of the outer ring 13 opens into the groove 20. Axially at the same height as the groove 20, several local depressions 22 are provided on the radial outer side or lateral surface of the inner ring 12 along the circumferential direction. In order to limit the relative movement between the bearing parts 10, 11, the rings 12, 13 are to be brought into a relative position to one another such that the bore 21 is aligned with one of the depressions 22, with a ball 23 being introduced into the depression 22 via the bore 21.This ball 23 is then located on the one hand in the depression 22 and on the other hand in the groove 20. The position of the ball is fixed due to the local limitation of the depression 22, whereby the relative movement between the bearing parts 10, 11 is generally not initially impaired due to the uninterrupted groove 20. The insertion process can be repeated with regard to another ball 23 in a different depression 22. A threaded pin 24 can then be screwed into an internal thread of the bore 21 until it protrudes into the groove 20. The two balls 23 then represent end stops with regard to the relative movement between the bearing parts 10, 11, onto which the threaded pin 24 runs accordingly. Optionally, the use of only a single ball 23 is also conceivable.

[0041] A further aspect concerning the pivot bearing 2 relates to a braking device 25, comprising friction elements 26 and adjusting screws 27 provided as threaded pins or grub screws. In this regard, particular reference is made to Figure 6, which shows a horizontal section through the pivot bearing 2, with the section plane passing through the adjusting screws 27. Figure 7 shows some components of the braking device 25 detached from the other components of the pivot bearing 2.

[0042] By means of the braking device 25, a braking force can be generated that decelerates the relative movement between the bearing parts 10, 11 and thus the respective components 5. For this purpose, the friction elements 26 are in contact with the outer side of the inner ring 12. The friction elements 26 each form a flat, plate-like, or strip-like friction lining arranged between the outer side of the inner ring 12 and the inner side of the outer ring 13. The friction elements 26 can generally be made of a metal and / or a plastic. A fiber material, in particular a woven one, is conceivable in this regard. One specific possibility regarding the material from which the friction elements 26 are made is the so-called Orkot® C380 from Trelleborg.

[0043] Each of the two friction elements 26 is assigned one of the adjusting screws 27 or is mechanically operatively connected to one of such an element, wherein the adjusting screws 27 are each screwed from the outside along the radial direction into a through-bore 28 of the outer ring 13. In particular, Figure 6 shows that each of the friction elements 26 can be tensioned against the second bearing part 10 or the inner ring 12 by means of the respective adjusting screw 27 in order to generate the braking force. In principle, the braking force is greater the further the adjusting screw 27 is screwed into the through-bore 28. Thus, the specific screw position of the adjusting screw 27 enables the generation of a defined rotational resistance, for example by applying a correspondingly defined torque to the respective adjusting screw 27 to screw in this adjusting screw 27.In particular, the extreme case is conceivable in which, if the adjusting screw 27 is screwed in sufficiently far, the braking force is so high that the pivot bearing 2 is virtually fixed. On the other hand, if the adjusting screw 27 is unscrewed or located sufficiently far radially outwards, the braking force generated thereby can become zero. In principle, the torque required for a specific braking effect on the pivot bearing 2 when tightening the adjusting screws 27 can be specified using an analytical relationship or a lookup table. In this regard, a procedure based on the trial-and-error principle is also conceivable, i.e., a concrete measurement of the braking effect occurring and a corresponding adjustment of the screw position, with this process being repeated iteratively.

[0044] In particular, in order to be able to adjust the braking force with sufficient precision specifically for the respective application, a spring element 29 is arranged between each of the friction elements 26 and the associated adjusting screw 27, which spring element 29 is supported on the one hand on the respective friction element 26 and on the other hand on the end face of the respective adjusting screw 27. The braking force therefore depends on the extent of compression of the spring element, so that a precise adjustment of the braking force is possible by means of the screw position of the adjusting screw 27. The spring element 29 can be a compression spring. Specifically, the spring element 29 can comprise or be a helical spring and / or a disc spring. In the present case and by way of example, the spring element 29 is realized from a package of several disc springs stacked one above the other.

[0045] To ensure that the friction elements 26 remain in their respective positions while the braking force is generated, each of the friction elements 26 is fastened to the inside of the outer ring 13. For this purpose, each of the friction elements 26 is attached to a holder 30, in particular by means of a high-strength adhesive. The holder 30, in turn, is fastened to the inside of the outer ring 13, in particular by means of a screw connection. It is also conceivable for several, in particular all, friction elements 26 to be provided on a common holder 30.

[0046] In this case, the holder 30 is a strip-shaped spring steel sheet arranged in the gap or area between the outer side of the inner ring 12 and the inner side of the outer ring 13. The spring steel sheet forming the holder 30 is bent into a circle, specifically with a bending radius corresponding to the radius of the aforementioned gap. A receiving groove 31 extending along the circumferential direction, into which the holder 30 is inserted, can be provided on the outer side of the inner ring 12 and / or the inner side of the outer ring 13, in this case, for example, exclusively on the inner side of the outer ring 13.

[0047] Although two holders 30 are provided in the present case, each extending at an angle of almost 120° around the rotation axis 14, the number of holders and their dimensions can vary. Thus, the holder 30 can also form a closed ring on which friction elements 26 can be arranged, for example, evenly distributed along the circumference. The number of friction elements 26 and adjusting screws 27 can also differ from the present embodiment. The holders 30 and the friction elements 26 arranged thereon collectively form a kind of open or closed brake ring.

[0048] For fastening the holders 30 to the outer ring 13, radial bores 32 are provided, extending through the outer ring 13 and the holder 30, specifically through one end of the holder 30. A screw 33 is screwed into each of the radial bores 32 from the inside to secure one of the holders 30. The height of the head of the screw 33 is smaller than the width or thickness of the friction elements 26.

[0049] List of reference symbols

[0050] 1 bearing arrangement

[0051] 2 upper pivot bearing

[0052] 3 middle pivot bearing

[0053] 4 lower pivot bearing

[0054] 5 component

[0055] 6 upper swivel arm

[0056] 7 lower swivel arm

[0057] 8 Carrier device

[0058] 9 Holding section

[0059] 10 bearing part

[0060] 11 Bearing part

[0061] 12 inner ring

[0062] 13 Outer ring

[0063] 14 Rotation axis

[0064] 15 threaded hole

[0065] 16 Adjusting ring

[0066] 17 Bearing cage

[0067] 18 rollers

[0068] 19 inner cylinders

[0069] 20 grooves

[0070] 21 Hole

[0071] 22 depression

[0072] 23 ball

[0073] 24 threaded pin

[0074] 25 Braking device

[0075] 26 Friction element

[0076] 27 Adjusting screw

[0077] 28 through hole

[0078] 29 Spring element

[0079] 30 holders

[0080] 31 mounting groove

[0081] 32 radial bore

[0082] 33 Screw

Claims

Patent claims 1 . Pivot bearing (2, 3, 4), comprising a first bearing part (10) and a second bearing part (11), wherein the bearing parts (10, 11) are mounted so as to be rotatable relative to one another, wherein the pivot bearing (2, 3, 4) has an integrated braking device (25) which comprises at least one adjusting screw (27) provided on the first bearing part (10) and at least one friction element (26), wherein the friction element (26) can be tensioned against the second bearing part (11) via the adjusting screw (27) in order to change the braking force.

2. Pivot bearing (2, 3, 4) according to claim 1, characterized in that the friction element (26) is a plate- and / or strip-like friction lining.

3. Pivot bearing (2, 3, 4) according to claim 1 or 2, characterized in that the friction element (26), in particular comprising a woven fiber material, consists of a metal and / or a plastic 4. Pivot bearing (2, 3, 4) according to one of the preceding claims, characterized in that the pivot bearing (2, 3, 4) forms a roller bearing, in particular a skew roller bearing, in which an inner ring (12) forming the first bearing part (10) and an outer ring (13) forming the second bearing part (11) are mounted so as to be rotatable relative to one another about a rotation axis (14).

5. Pivot bearing (2, 3, 4) according to claim 4, characterized in that the inner ring (12) is arranged concentrically within the outer ring (13), wherein the friction element (26) is arranged between an outer side of the inner ring (12) and an inner side of the outer ring (13) adjacent thereto.

6. Pivot bearing (2, 3, 4) according to claim 5, characterized in that the adjusting screw (27) is screwed from the outside along the radial direction into a through hole (28) of the outer ring (13), wherein the friction element (26) can be tensioned against the inner ring (12) by means of the adjusting screw (27) for variable generation of the braking force.

7. Pivot bearing (2, 3, 4) according to one of claims 4 to 6, characterized in that a groove (20) running along the circumferential direction is provided on the or an inner side of the outer ring (13), wherein at least one depression (22) is provided axially at the same height as the groove (20) on the outer side of the inner ring (12), wherein a ball (23) is located on the one hand in the groove (20) and on the other hand in the depression (22), wherein a threaded pin (24) is screwed into a bore (21) leading radially inwards from an outer side of the outer ring (13) and opening into the groove (20), wherein the ball (23) and the threaded pin (24) form a movement stop with respect to the relative movement between the bearing parts (10, 11).

8. Pivot bearing (2, 3, 4) according to one of the preceding claims, characterized in that the friction element (26) is fastened to the first bearing part (10).

9. Pivot bearing (2, 3, 4) according to claim 8, characterized in that the friction element (26) is fastened to a holder (30), in particular by means of a high-strength adhesive, and the holder (30) is fastened to the first bearing part (10).

10. Pivot bearing (2, 3, 4) according to one of claims 4 to 7 and according to claim 9, characterized in that the strip-shaped holder (30) is arranged in a gap between the or an outer side of the inner ring (12) and the or an inner side of the outer ring (13).

11. Pivot bearing (2, 3, 4) according to claim 10, characterized by a receiving groove (31) extending along a circumferential direction of the pivot bearing (2, 3, 4) and provided on the outside of the inner ring (12) and / or the inside of the outer ring (13), wherein the holder (30) is inserted into the receiving groove (31).

12. Pivot bearing (2, 3, 4) according to claim 10 or 11, characterized by at least one radial bore (32) extending radially through the outer ring (13) and the holder (30), into which a screw (33) screwed in from the inside is provided for fastening the holder (30) to the outer ring (13), wherein it is provided in particular that a height of a head of the screw (33) is smaller than the width or thickness of the friction element (26).

13. Pivot bearing (2, 3, 4) according to one of the preceding claims, characterized in that at least one spring element (29) is arranged between the friction element (26) and the adjusting screw (27), wherein an extent of elastic deformation of the spring element (29), on which in turn the braking force depends, is determined by means of a Changing the screw position of the adjusting screw (27) can be changed.

14. Pivot bearing (2, 3, 4) according to claim 5, characterized in that the spring element (29) is at least one compression spring or comprises at least one compression spring, wherein the compression spring is in particular a helical spring or a disc spring.

15. Bearing arrangement (1), in particular ceiling mount, comprising at least one pivot bearing (2, 3, 4) according to one of the preceding claims, wherein - the bearing arrangement (1) can be rotatably mounted on a holding section (9) via the pivot bearing (2) or via one of the pivot bearings (2), and / or - two components (5) of the bearing arrangement (1) are mounted so as to be rotatable relative to one another via the pivot bearing (3, 4) or via one of the pivot bearings (3, 4).

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