DAMPERS FOR A ROTATING MOVEMENT, ESPECIALLY OF TOILET LIDS OR SEATS

Description

[0001] The present invention relates to a rotary damper, i.e., a device for damping rotary movements around a rotational axis. Such a damper can be used, in particular, to dampen the rotary movement of toilet lids or toilet seats mounted on a toilet. For example, it can prevent excessive impact at the end of a lowering movement.

[0002] Such dampers are generally known and in common use. They typically comprise a housing from which a pin-like part protrudes. The housing is coupled to one part of the device, and the pin is coupled to another part of the device for rotational movement. Relative movement leads to the displacement of a viscous damping medium in the housing, which is associated with a viscosity-related flow resistance that generates the actual damping effect.

[0003] The part protruding from the housing is referred to in the following description of the invention as the second part of a first damper element and is firmly connected to a first part of this first damper element, optionally designed as a single piece. The term "first part" refers to a part arranged in the housing. The rotation described leads to a relative movement of the first damper element with respect to a second damper element, which in turn is firmly coupled to the housing, in particular, can be designed as a single piece therewith.

[0004] It is generally known to change the volume of the damping medium and thus displace the damping medium by rotating the first and second damper elements relative to one another in the circumferential direction (with respect to the aforementioned axis of rotation). Furthermore, it is previously known to axially displace the second damper element (again with respect to the aforementioned axis of rotation) by means of the relative rotation between the two damper elements, thereby changing the volume of the damping medium and achieving the desired displacement of the damping medium. In the second case, the axial movement is generated in the prior art by helical shaped surfaces on the axial end faces of the first and second damper elements. For example, reference can be made to EP 2 587 089 of the present applicant.

[0005] Document US 2017 / 138433 A1, which is considered to be the closest prior art, discloses the features of the preamble of claim 1.

[0006] The object of the present invention is to create a rotary damper with a robust and yet not too complicated structure.

[0007] To this end, the invention is directed to a damper for a rotational movement, in particular of toilet lids or seats, about a rotational axis, comprising a housing, a viscous damping medium in the housing, a first damping element which has a first part in the housing and a second part outside the housing which is firmly connected to the first part in the direction of rotation and is rotatable with the first and second parts relative to the housing about the rotational axis, a second damping element which is firmly coupled to the housing with respect to rotations about the rotational axis and is coupled to the first damping element in such a way that a rotation of the first damping element relative to the housing leads to an axial displacement of the second damping element relative to the first damping element and a displacement of the damping medium along a flow path in the housing through the second damping element, characterized in thatthat the second damper element is coupled to the first damper element by means of a threaded engagement and is received radially in the first damper element at least to the extent that the threaded engagement is present in the first damper element, and that the threaded engagement and the resulting displacement of the damping medium by the second damper element act bidirectionally.

[0008] Preferred embodiments are specified in the dependent claims. The invention also relates to an advantageous use and to a toilet fitting equipped with a damper according to the invention.

[0009] The invention is based on the described prior art and is directed to a damper variant in which the rotation of the two damper elements relative to one another generates an axial displacement of the second damper element relative to the first. According to the invention, this is achieved via a threaded engagement between the two damper elements, specifically radially (in relation to the axis of rotation) between these two damper elements. In other words, the second damper element should be received radially in the first damper element at least to the extent that the threaded engagement is present in this received area and thus in the first damper element (i.e. in the area of ​​the overlap).

[0010] This is therefore not about the interaction between axially adjacent helical end faces, but about a radially outer region of the second damper element and an inner region of the first damper element, which are in threaded engagement with each other.

[0011] In this form, a robust and structurally not too complicated mechanical solution for generating the displacement of the damping medium can be realized.

[0012] In particular, a threaded engagement according to the invention can lead to axial displacement in two directions, whereas with the previously known axial end faces and their helical shapes, forces can only occur in one direction. If interaction in two directions is desired, the structures must be duplicated to a certain extent. Instead, the prior art also provides solutions in which an additional spring is provided, thus, in a sense, pre-loading the force in the second direction. In contrast, the invention is simpler in that the threaded engagement itself acts bidirectionally.

[0013] In addition, a solution with axial displacement creates possibilities for the realization of the flow path of the damping medium responsible for the actual damping, which are more diverse than the fundamentally different design type with movement in the circumferential direction and also simpler in relation to many solutions from this other field.

[0014] According to the invention, the second damper element is accommodated in the first damper element with respect to the threaded engagement, so that the first damper element lies radially outside the second damper element in this area. Since the first damper element has the second part outside the damper housing (usually a cylindrical pin with flattened portions on opposite sides), the forces are introduced into the threaded engagement via the radially outer part. This means that the lever lengths are relatively long, and the first damper element is particularly robust with regard to the transmission of these forces.

[0015] In principle, the threaded engagement can be achieved simply by providing a thread, i.e., a set of at least two helical surfaces, on only one of the two damping elements. The other damping element can then, for example, only have a simple projection (e.g., with a round base) or a recess, whereby the projection can engage between the two helical surfaces of the other damping element, or the two helical surfaces can engage into the recess.

[0016] However, it is preferred that both damper elements each have two helical surfaces and that there is a mutual engagement of threads with each other.

[0017] However, the thread lengths on both sides do not have to be the same and, for example, one of the damping elements may have only a short projection with two helical surfaces on its sides, while a groove is much longer in the circumferential direction than the counterpart of the other damping element.

[0018] Furthermore, the two helical surfaces of a damper element don't necessarily have to be different; they can be connected by a single circumferential path. In other words, the number 2 refers to the observation at a specific circumferential point.

[0019] The helical surfaces, i.e. threads, on both damper elements ensure that the forces are distributed over larger areas and thus provide a more robust solution.

[0020] Preferably, the second damper element is completely radially received in the first damper element at least in some of the positions resulting from the axial displacement. This reception then applies not only to an axial section of the second damper element. In this form, a particularly compact design can be achieved.

[0021] Furthermore, it is preferred that, in addition to the described threaded engagement, there is no further interaction between helical shaped surfaces on the axial end faces of the first and second damper elements. Thus, the mechanical interaction between the two damper elements is preferably limited to the described threaded engagement, although this can, of course, occur multiple times.

[0022] Preferably, the threaded sections formed by the helical surfaces extend over a rotation angle (relative to the rotation axis) that is not too small, preferably at least 50°. This results in improved stability and an overall robust design of the damper. Preferred lower limits are also 60°, 70°, and even 80°.

[0023] This angular extension does not have to be the same for the threaded sections of both damper elements. For example, in the exemplary embodiment described below, the threaded sections of the inner second damper element extend over a good 90°, but those of the outer first damper element extend over significantly more than 200°, because they cover the entire rotational movement of the damper and are also intended to completely or at least largely overlap with the inner threaded sections in all positions. In the case of the exemplary embodiment, this means a total angle of rotation of 120° plus a good 90° for the second damper element, and thus a good 210°. In this sense, the above minimum specifications refer to the respective shorter threaded sections of the damper elements.

[0024] Preferably, a rotatable adjustment element is also provided, which has an adjustment opening that can be moved by rotating the adjustment element. The part having the opening and the remaining adjustment element do not necessarily have to be designed as a single piece, but they can be coupled with respect to the rotational movement. The adjustment opening is arranged in the flow path and can change a flow cross-section through its moving movement. For this purpose, the adjustment opening overlaps with a covering edge. The covering edge therefore covers a varying portion of the adjustment opening depending on the setting, and this portion, i.e. the extent of the overlap, is adjusted by rotation.

[0025] For example, the cover edge may be a boundary edge (or the combination of a plurality of boundary edges) of another opening in the flow path that is immediately adjacent to the adjustment opening.

[0026] The rotatability can be provided relative to one damper element or the other damper element; the only decisive factor is that the rotatability affects the change in the described overlap.

[0027] Instead, solutions are known in the prior art in which a rotatable adjustment element undergoes an axial displacement during its rotation, namely by being guided in a thread and adjusted like a screw. Thus, instead of the described adjustment opening, an axial displacement of a front surface of the adjustment element affects a flow cross-section.

[0028] Advantageously, the adjustment opening can be spaced radially from the axis of rotation of the adjustment element, which in most cases coincides with the axis of rotation of the damper, thus providing greater design flexibility.

[0029] Furthermore, axial movement of the adjustment element can be avoided because it is not required for adjustment (although it is possible in the most general sense of the invention). In this case, the rotation is pure rotation without an axial component, i.e., no screw movement. Accordingly, the adjustment element does not change its axial position when viewed from the outside and, for example, remains axially in the same place with regard to operation. It does not, for example, protrude further into or out of a component of the damper in which it is housed. Furthermore, in the event of incorrect operation, the adjustment element can be prevented from falling out and thus causing the damper to leak, as is possible with thread-guided adjustment elements according to the state of the art.

[0030] According to a preferred embodiment, the adjustment opening can be arranged in a reversal region of the flow path. This flow path connects two volumes, one of which is reduced and the other enlarged by the relative movement or displacement, wherein in this embodiment the flow path has a central axial part. The adjustment opening is then located between this axial part of the flow path and one of the two volumes which is located radially further outwards. The damping medium can therefore be supplied via the axial part of the adjustment opening (or vice versa). The two volumes are preferably located axially on either side of the displaced second damper element and accordingly one of the two is closer to the adjustment opening and is connected via this to the axial flow path part. For illustration, reference is made to the exemplary embodiment.

[0031] In this design, the radially offset position of the adjustment opening from the axis allows the use of the axis position for the axial part of the flow path.

[0032] A valve element can advantageously also be provided in the flow path of the damping medium to change the function of the damper depending on the direction. This valve element can be moved depending on the flow direction and can switch on or block a bypass opening in the flow path. The bypass opening significantly reduces the overall flow resistance of the flow path and thus reduces the degree of damping. For example, it may be desirable to be able to raise a toilet seat or lid against a relatively low damping resistance while simultaneously ensuring sufficient damping of the lowering movement.

[0033] If the bypass opening is not completely closed in one flow direction, but merely significantly narrowed, this leads to analogous technical consequences and is therefore included.

[0034] Conversely, the valve element does not necessarily have to be moved to a precisely defined position in the other flow direction. An elastomer valve element is particularly preferred, in which the flowing damping medium moves part of the valve element or the entire valve element against a restoring force of the elastomer material, so that a varying degree of deflection of the valve element can occur depending on the flow velocity. The main aim is to significantly change the flow resistance at the corresponding point depending on the flow direction, or even to completely prevent the flow of the damping medium in the blocking direction.

[0035] In a particularly simple embodiment, the valve element is a one-way valve that opens or closes depending on the flow direction and is provided in the part of the flow path leading through the bypass opening.

[0036] Advantageously, the bypass opening is connected in parallel to the adjustment opening of the adjustment element when open. When the bypass opening or the portion of the flow path passing through it is open, the adjustment opening is largely disabled, so that adjustment via the adjustment element affects the more strongly damped direction of rotation of the damper.

[0037] In a further preferred embodiment, a storage chamber for damping medium follows the previously described adjustment opening. "Following" here means that the storage chamber directly adjoins the adjustment opening, or that there is no constriction in between that is relevant to the flow resistance of the damping medium. Furthermore, this refers to the flow direction in which the damping effect adjustable through the adjustment opening occurs (and not the direction, for example, provided with a significantly lower flow resistance by the previously discussed bypass opening).

[0038] This storage chamber serves to store a certain amount of damping medium so that the damping medium forced through the adjustment opening in its damping function meets the damping medium stored in the storage chamber. Typically, the damping medium exhibits the property of temporarily having a lower viscosity than before after passing through narrow spaces, particularly the adjustment opening, forced by a corresponding pressure gradient. Then, during a movement over a certain distance, particularly a movement subjected to a greater force, the flow resistance in those parts of the flow path downstream of the adjustment opening could decrease. The described storage chamber counteracts this by mixing the damping medium that has passed through the adjustment opening with other damping medium.

[0039] In particular, the storage chamber can be, for example, a funnel-like widening of an approximately radially extending channel in the flow path, as the exemplary embodiment shows.

[0040] The adjustment opening itself can be located at a recess in an outer surface of the damper component containing the channel (or of a directly adjacent component), adjoining this channel, in particular its widening. Preferably, it is a recess in a cylindrical outer surface of a damper component. The exemplary embodiment also illustrates this. Such a recess can be easily manufactured in small dimensions and has the advantage that, by reworking, for example, an injection molding tool or replacing a small part of a multi-part injection molding tool, the dimensions of such a recess can be slightly changed after testing or to adapt to a new application situation. This allows the damping properties to be adjusted (at least in the direction relevant here) during production in addition to the adjustment option according to the invention.

[0041] In a further embodiment, this recess has a tapered shape in at least one direction, narrowing from the channel. The direction in which the term "narrow" applies is perpendicular to the direction of relative movement of the damper elements (and, of course, perpendicular to the radial direction). Starting from the channel in the direction of relative movement, the narrowness increases. Preferably, the recess also becomes shallower (relative to the radial direction).

[0042] The overlap with the cover edge increases (when the adjustment element is rotated) in the direction of relative movement of the damper elements, so that due to the increasing overlap, only narrower and flatter parts of the recess remain exposed. Accordingly, the shape of the recess, despite the preferably uniform pitch of the helical shape of the cover edge, achieves a non-linear response of the adjustment option. In particular, the response behavior can also be adjusted in the sense described above by changing the recess.

[0043] A further or alternative preferred control option for the damper according to the invention is not direction-dependent, but rather rotation-angle-dependent, thus affecting a portion of the damper's total rotational travel. In an end region of this total rotational travel, the damping effect is to be increased accordingly by narrowing another opening in the flow path, thus adding another significant flow resistance to the damping effect of the adjustment opening.

[0044] This is advantageously achieved by the second damper element, during its axial displacement movement, narrowing or possibly even completely closing a passage opening of the damping medium through increasing overlap in one end region of this movement. In the latter case, this could force the damping medium through a parallel flow path section with a correspondingly high flow resistance.

[0045] In any case, this approach can be used to ensure, for example, that a toilet lid or seat lifting movement that is already relatively dampened or damped-free can be increased or increased in the final phase just before impact. In this case, this second control option would be added to the direction-dependent one described above.

[0046] In an advantageous embodiment, the passage opening just described can be connected to the previously mentioned axial part of the flow path of the damping medium. Thus, with respect to this axial part of the flow path, it is located, so to speak, opposite the adjustment opening (but is by no means symmetrical to it). The exemplary embodiment illustrates this aspect.

[0047] For example, the final phase of a closing movement could be dampened more strongly in order to achieve a particularly gentle impact in the final position of the closing movement, while at the same time not slowing down the closing movement itself too much. Accordingly, there is then a corresponding through opening (two in the exemplary embodiment) in the other end area of ​​the movement of the second damper element. This through opening significantly reduces the damping in the initial phase of the closing movement, but is then closed in the final phase, so that the actual damping comes into effect through the adjustment opening. The above basic idea of ​​a through opening, which is covered by the second damper element in the final phase of its movement, can therefore also be implemented twice.

[0048] The previously described adjustment option with the rotatable adjustment element is structurally particularly flexible, and it can also be implemented very sensitively (particularly due to the aforementioned helical shape of the cover edge). In a preferred use of this aspect of the invention, a certain number of preferably identical dampers are adapted to individual situations using the adjustment option. This particularly applies to different masses of toilet seats or lids (or parts whose movement is otherwise dampened). Thus, a larger number of different such masses can be effectively covered with one or a small number of damper types by using the adjustment option for individualization.

[0049] This particularly applies to multiple dampers of identical construction with the same damping medium, e.g., the same type of grease. Conventionally, a distinction is made between different damping media to account for the different masses of the parts to be damped. However, it is much easier to fill a small number of damper types, or even just a single damper type, with a small number of different damping media types, or even just a single type of damping medium, and use only the adjustment option for adaptation.

[0050] Finally, the invention also relates to a toilet fitting with at least one damper according to the invention. A toilet fitting refers to at least one toilet lid or one toilet seat, preferably both in combination, for mounting (or mounted) on a toilet. A damper according to the invention is used to dampen the rotational movements of the fitting parts, with one damper preferably being provided for each of the toilet seat and the toilet lid.

[0051] In the following, the invention is explained in more detail using exemplary embodiments, whereby the individual features within the scope of the independent claims can also be essential to the invention in other combinations and no distinction is made in detail between the different claim categories.

[0052] In detail: Figure 1 shows a perspective view of a toilet equipped with a toilet seat according to the invention, with a toilet lid shown in a vertical and additionally half-lowered position; Figure 2 shows an exploded view of a damper according to the invention in the toilet seat from Figure 1 , the individual parts being pulled apart along the axis of rotation; Figure 3 is a sectioned and simultaneously perspective view of the essential part of the rotary damper from Figure 2 ; Figure 4 a section of the illustration in Figure 3 enlarged; Figure 5a Figure 3 corresponding representation, but in side view perpendicular to the section plane and the rotation axis; Figures 6, 7 and 8Views analogous to Figure 5 , but with changed positions of the components; Figure 9 a representation analogous to Figure 3 , but with the component positions according to Figure 8; Figure 10 an enlarged view of the adjusting element 12 from Figure 2 with slightly changed rotation position compared to Figure 2 and Figure 11 is an enlarged view of the axle part 7 from Figure 2 .

[0053] Figure 1 shows a perspective view of a toilet from the top left front. A toilet fitting is mounted on a toilet body 1. This fitting includes a toilet lid 2 and a toilet seat 3, each of which can be opened and closed about a transverse pivot axis at the rear. For illustrative purposes, the toilet lid 2 is shown in a semi-lowered position in addition to its upright position.

[0054] The toilet fitting is equipped with two dampers according to the invention in slightly thickened areas 4 of the toilet seat 3, which will be discussed in more detail in the following figures and which serve to dampen the rotational movement of the toilet lid 2 and the toilet seat 3. A corresponding rotatable or rotationally locked guide / connection ensures that one rotary damper only dampens the rotational movement of the toilet lid 2 and is rotatable relative to the toilet seat 3, while the other rotary damper does the opposite.

[0055] In Figure 2 you can see one of the dampers with a series of individual components along the axis of rotation, whereby here the left of the two positions 4 in Figure 1 is parked. On the far right, a housing 5 of the damper can be seen, which is open on the left side and provides an essentially cylindrical cavity for accommodating the remaining parts.

[0056] The right part of the damper housing 5, also shown, is used for fastening to a vertical mounting mandrel, which is mounted on the toilet body 1 made of Figure 1 is fixed in a conventional manner and that in Figure 2 6. For the details of this fastening, reference is made to the present applicant's earlier application EP 20 152 653.0 for illustration purposes. These details are not essential to the present invention.

[0057] In the sequence from right to left, one can also see an axle part 7, the right end of which has a star-like disc with rounded tips for a rotationally locked, positive-locking assembly in a corresponding recess in the invisible front end surface of the cavity in the housing 5. In addition, the axle part 7 has two outer longitudinal ribs parallel to the axis of rotation, one of which is shown, and which serve for positive engagement (with regard to rotation) in corresponding grooves of the element 8 shown to the left. This is the so-called second damping element 8 and, as shown in the figure, has an outer threaded section 9, another is in Figure 2 not visible and lies behind element 8.

[0058] Further to the left there are two elastomer O-rings 10 and 11, which will be discussed in more detail, as well as a sleeve pin-like adjusting element 12.

[0059] This is followed by the so-called first damper element 13, which according to Figure 2 a right-hand cylindrical first part for receiving in the housing 5 and a left-hand second part, which are formed integrally with one another. The second part of the first damper element serves to transmit torque to the fitting part 2 or 3 damped by the damper, for which purpose the two lateral flattened portions serve. In this respect, the damper is constructed similarly to conventional dampers.

[0060] Further to the left you can see a seal 14, another disc 15 and a cover 16.

[0061] Parts 12 and 7 show the Figures 10 and 11 individually and enlarged.

[0062] In the Figures 3 and 4-9 these elements are shown in assembled state, with only the right part of the damper housing 5 being omitted.

[0063] The Figures 3 and 9on the one hand in a plane containing the axis of rotation and in relation to Figure 2 vertical plane, on the other hand perspective and thus comparable with Figure 2 . The Figures 5-8 are cut in the same section plane, but shown in a vertical plan view of the section plane, whereby this Figures 5-8 in comparison with each other show different positions of the first damping element 13 and the second damping element 8 on the one hand and of the adjusting element 12 on the other hand. With regard to these positions, the Figures 3 and 5 on the one hand and 8 and 9 on the other.

[0064] First, the interplay between the first damper element 13, the second damper element 8, and the axle part 7 will be explained. In the figures, the housing 5 is stationary with respect to rotation (just as it is on the toilet body 1), which also applies to the axle part 7 due to the previously described rotational locking through the positive engagement. Due to the engagement of its ribs in the grooves of the second damper element 8, also described above, the second damper element 8 is also stationary with respect to rotation and can only be moved axially. The first damper element 13, in turn, is rotatable.

[0065] The outer threaded portion 9 of the second damper element 8 engages in an internal thread in the first damper element 13, specifically in its first part. The correspondingly inwardly projecting threaded portion is designated 17 in the figures, whereby due to the sectional plane, the threaded portion 9 is Figure 2 in the Figures 3 to 9cannot be seen (it is located behind or in front of the cutting plane). Through this interaction, a rotary movement of the first damper element 13 is translated into an axial sliding movement of the second damper element 8, which can be seen from the comparison of the Figures 5-8 (or 3 and 9). In the order of the figure numbers, this represents a lifting movement of a fitting part, with the second damper element 8 moving from left to right, reducing the volume 20 axially to the right of it, clearly visible in the figures, and increasing the volume of another volume 21 axially to the left of it. In a conventional manner, these cavities are filled with a damping medium (a special grease) of high viscosity, which is accordingly displaced from the right-hand cavity and forced through a flow path to the left-hand cavity.

[0066] According to the figures, the second damper element 8 is accommodated entirely radially within the first damper element 13, specifically within its first part. It can also be seen that the torque is transmitted from the second part of the first damper element 13 (left in the figures) to the first part (right in the figures) and from this first part of the first damper element 13 to the second damper element 8 (i.e., radially inward) at relatively large radii, thus taking into account the leverage effect with limited forces and stable structures.

[0067] One can also see, for example, in the Figures 3 and 5 that the first damper element with its internal thread, for example, in Figure 5 can also be seen again in the bottom right corner of the first damper element or in Figure 8once again at the top left, and therefore engages the outer threaded element 9 of the second damper element 8 on both sides with corresponding helical surfaces. In this respect, the thread engagement is bidirectional.

[0068] In the movement shown in the figures, initially, i.e. in the stage of Figure 5 to Figure 6 , the damping medium is pressed from the right-hand volume 20 through the radial passage opening designated 22 into a central and axial part 23 of the flow path, namely centrally in the axle part 7. From there, it flows axially further to the left and then, on the one hand, into a central channel section 24 at the right end of the adjusting element 12 and from there, after approximately one-third of its length, radially outward toward the elastomer O-ring 10.

[0069] Its location is in Figure 4Enlarged as a section, the figures show a closed position, contrary to the operating state described here. The O-ring 10 is a valve element similar to a one-way valve and can be slightly deformed radially outward by the flow just described. It sits in a roughly V-shaped recess and is soft enough so that the damping medium can lift it outward, thus creating a sufficient flow cross-section.

[0070] In addition, there is another passage for the flow medium between the right end of the adjustment element 12 and the inner edge of the left end of the axle part 7, which also leads to the valve element or O-ring 10 and is similarly fluidically connected to the volume 21 radially further outward by deformation of this valve element 10. This is the volume 21 to the left of the second damper element 8.

[0071] The path that also still exists through a longer section of channel section 24 to the left and then radially upwards plays no significant role in this direction of movement because the flow cross-sections there are too small, and will be described in more detail below. In the opposite direction of movement, the valve element 10 closes off the radially outward path just described because it is pressed into the position shown in the figures or, depending on the pressure, even further inward. In this respect, the valve element 10 is located in what was previously described as a bypass opening.

[0072] At this point, it should be briefly noted that the two further O-rings or sealing rings 11 and 14 serve conventional sealing functions, namely on the one hand between the first damper element 13 and the housing 5 and on the other hand between the former and the adjusting element 12, compare the figures.

[0073] The comparison of the Figures 5-7 shows that the second damper element 8 is increasingly pushed over the passage opening 22 and the available flow cross section for the damping medium of Figure 5 to Figure 6 has already been significantly restricted and Figure 6 to Figure 7 will be even more restricted. In the state according to Figure 8 the flow cross-section is at its smallest, and this is also where the end of the rotational movement path is reached.

[0074] This connection results in the movement of the fitting part 2 or 3 being increasingly damped in its final phase. The user can thus tilt the toilet seat 3 or the toilet lid 2 backward from the horizontal position without significant resistance and release it at the end, where it is then braked to make the impact as gentle as possible.

[0075] In this context, Figure 11and the short explanation below, according to which the opening 22 is adjoined to the right by a small depression, which Figure 5-8 is not easy to see.

[0076] In this case, the maximum total range of rotation in the damper is approximately 120°. This consists of 90° for the movement from horizontal to vertical, a further typical 10° for the rearward tilt of the fitting into a stable position (e.g., resting against a wall or the seat against the lid), plus 10° buffers at both ends.

[0077] The reverse process can be explained using the same figures, but in descending order of their numbering. The movement of the second damper element 8 now displaces damping medium in the volume 21 and forces it along a flow path towards the volume 20. After some distance of the rotary movement, Figure 6the passage openings 25 are increasingly covered by the second damping element 8 and finally according to Figure 5 blocked.

[0078] As already mentioned, the elastomer O-ring 10, which is pressed inwards by the damping medium, also blocks the bypass opening as a valve element, so that the damping medium must flow past it axially further to the left, whereby the upper area of ​​the sectional views must be observed.

[0079] Here, there is a space extending over a certain angle of rotation due to a small edge 26 on the otherwise cylindrical inner surface of the first damper element. According to the Figures 8 and 9With regard to the axial direction, this space is located almost entirely above a small depression 27 in the outer surface of the rightmost region of the adjusting element 12, the depth of which increases towards the left. Through this gap, the damping medium is pressed into a funnel-like widening 28 in the adjusting element 12, from which the damping medium flows radially inwards into the channel section 24 already described.

[0080] From this channel section 24, the damping medium then flows into the axial part 23 of the flow path within the axle part 7. From the central flow path part 23 in the axle part 7, the flow medium can pass between the second damper element 8 and the axle part 7 with the opposite flow direction, but otherwise as previously described, after it has passed through the passage opening 22, wherein the corresponding damping there becomes increasingly weaker with the movement of the second damper element 8 to the left.

[0081] This direction of movement corresponds to a lowering movement, and in the final phase, this is more dampened. In this context, it is also important to consider that the effectiveness of the weight force increases during the lowering movement. Due to the weight of the fittings, adjustability (see below) is particularly important.

[0082] During the lifting movement, the final part in particular is strongly dampened, as just described, in order to make the impact of the toilet lid 2 against the wall or a cistern as gentle as possible. This is because an elastomer buffer is no longer provided here, as is evident from Figure 1 the toilet lid 2 rests on the toilet seat 3 at the end of the lowering movement (and analogously the toilet seat 3 rests on its underside on the toilet body 1).

[0083] In the above explanation, contrary to Figures 3-9, a constant relationship between the first damping element 13 and the adjusting element 12 was assumed, which also corresponds to the actual operation. The adjusting element 12 is namely Figure 2The damper element 13 can be rotated relative to the damper element 13 via a clearly visible frontal engagement for a tool and a corresponding opening in the front of the damper element 13. This rotation is somewhat stiff due to the contact surfaces between them and, above all, the sealing ring 11, so that no adjustment is possible without tool engagement.

[0084] In comparison of the Figures 3-9 , particularly 5-8, the adjusting element 12 is shown in different positions relative to the first damping element 13. This is simply because the adjusting element 12 is always shown in the same sectional plane in the figures, as are elements 5-8, whereas the first damping element 13 is rotated as described above.

[0085] Comparing the relative positioning of the edge 26 on the left at the end of the space relative to the adjusting element 12 and in particular the recess 27 therein between the Figures 5-8 , we can see that this edge 26 of Figure 5 to Figure 8 gradually to the left or vice versa. Accordingly, with an analogous rotation of the adjusting element 12 relative to the first damping element 13, the axial overlap between the space and the recess 27 can be adjusted between practically completely in Figure 8 and very low in Figure 5 Accordingly, the flow resistance at this point changes, which becomes crucial during the final phase of the lowering movement. In contrast to the lifting movement, the valve in the form of valve body 10 is closed in its seat, and the damping medium must therefore pass through this constriction.

[0086] In this case, the adjusting element 12 is exclusively rotatable, i.e., it cannot be simultaneously axially adjusted as with a screw movement. In particular, it is captive for the reason described above and due to its plug-in assembly from the inside, as can be seen in the figures.

[0087] The adjustment opening, in turn, is clearly the opening formed by the recess 27 in the otherwise cylindrical outer surface in this right-hand section of the adjustment element 12. Depending on the angle of rotation, it overlaps more or less with the step at the left end of the space 26, which accordingly forms a helical covering edge.

[0088] Finally, the adjusting element 12 has, in the form of the funnel-shaped widening 18 of the radially inwardly leading channel, a storage chamber for damping medium underneath, which has the advantageous effects described above and (in the direction of movement relevant with regard to the adjustable damping effect) immediately follows the adjusting opening.

[0089] The depression 27 is particularly clearly visible in the Figure 10 top right, in which the adjustment element 12 is shown in isolation. Figure 11with an isolated axle section 7 shows that there are similar recesses adjacent to the passage openings 22 and 25. There, too, they serve to refine the adjustment options with an already greatly reduced flow cross-section.

[0090] The damping adjustability according to the invention is not only particularly simple, robust, and reliable. It can also be adjusted particularly precisely and over a wide range. According to the invention, extensive adaptation to different damping tasks, e.g., different weights of the fitting parts 2 and 3, can be achieved, whereby a smaller number of different damping media or even one and the same damping medium can advantageously be used.

[0091] In this context, there are also production-side adjustment options, namely through minor interventions to change the shape, particularly the axial length and radial depth, of the various recesses. For example, minor reworking of injection molds or other parts, or the replacement of corresponding parts of injection molds, can be used here.

Claims

1. Damper for a rotary movement, in particular of toilet lids (2) or seats (3), about an axis of rotation, having a housing (5), a viscous damping medium in the housing (5), a first damper element (13), which has a first part in the housing (5) and a second part, firmly connected to the first part in a rotational sense, outside the housing (5) and which is rotatable with the first and the second part relative to the housing (5) about the axis of rotation, a second damper element (8), which is firmly coupled to the housing (5) with respect to rotations about the axis of rotation, and which is coupled to the first damper element (13) such that a rotation of the first damper element (13) relative to the housing (5) leads to an axial displacement of the second damper element (8) relative to the first damper element (13) and a displacement of the damping medium in the housing (5) by the second damper element (8), characterized in that the second damper element (8) is coupled to the first damper element (13) by means of a thread engagement and is received radially in the first damper element (13) at least to the extent that the thread engagement is present in the first damper element (13), and that the thread engagement and the resulting displacement of the damping medium by the second damping element (8) have a bidirectional effect.

2. Damper according to claim 1, wherein a shaped element (9) of the second damper element (8) provided for the thread engagement and a shaped element (17) of the first damper element (13) provided for the thread engagement are each threaded portions which are in engagement with one another.

3. Damper according to claim 1 or 2, in which the second damper element (8) is accommodated completely radially in the first damper element (13) for at least some of its possible positions with respect to its axial displacement.

4. Damper according to claim 2, also in combination with claim 3, in which the threaded portions (9, 17) each cover an angle of rotation of at least 50° about the axis of rotation.

5. Damper according to one of the preceding claims with an adjusting element (12) which is accessible from outside the damper and is designed to change a flow cross-section of a part of a flow path of the damping medium in its displacement by the second damper element (8).

6. Damper according to claim 5, in which the adjusting element (12) is a central axial pin in the second part of the first damper element (13) and has an adjustment opening which can be moved by rotating the pin and has a radial flow direction for changing the flow cross-section.

7. Damper according to claim 6, in which the adjustment opening overlaps with a cover edge (26) in at least part of a travel path of the rotatability, the extent of the overlap being adjusted by the rotation and thus the flow cross-section being adjusted.

8. Damper according to claim 6 or 7, in which the rotation of the adjusting element (12) has no axial component.

9. Damper according to claim 6, optionally in combination with claim 7 or 8, in which the movable opening is in a reversal region of the flow path of the damping medium between a volume (21) occupied by the damping medium and changed by the displacement of the second damper element (8) and an axial centric part (23) of the flow path between this volume (21) and a volume (20) changed in the opposite sense to this volume (21) by the displacement of the second damper element (8) and occupied by the damping medium, wherein the two changed volumes (20, 21) lie axially on both sides of the second damper element (8).

10. Damper according to one of the preceding claims with a valve element (10) provided in a flow path of the damping medium, which can be moved back and forth between two positions depending on the flow direction by the damping medium and in one of the positions closes or narrows a bypass opening provided for reducing the overall flow resistance of the damping medium in one of the flow directions of the damping medium and not in the other position.

11. Damper according to claim 5 and claim 10, in which the bypass opening in the open state is connected in parallel to the adjustment opening of the adjusting element (12) with respect to the flow of the damping medium.

12. Damper according to one of the preceding claims, in which the second damper element (8) narrows or closes a passage opening (22, 25) for the damping medium in an end region of its axial displacement by overlapping with the passage opening (22, 25) and thus causes greater damping in this end region.

13. Damper according to claim 9 and claim 12, wherein the passage opening (22, 25) is adjacent to the axial part (23) of the flow path.

14. Use of a plurality of preferably structurally identical dampers according to claim 6, also in combination with another of the preceding claims, in which the dampers of the plurality are filled with the same type of damping medium, for different applications with regard to the forces to be damped, in particular for toilet lids (2) or seats (3) of different weights.

15. Toilet set with a toilet lid (2) and / or a toilet seat (3) for mounting on a toilet and with at least one damper according to one of claims 1 to 13.