DE102021104501A1 - Plain bearing assembly and shaft arrangement - Google Patents

Abstract

The invention relates to a slide bearing assembly (5) with a bearing bush (6) and a centering ring (7) which encompasses the bearing bush (6) and can be rotated about an axis of rotation (4) with respect to the bearing bush (6), a plurality of centering rings being formed in the bearing bush (6). first fluid passage channels (10) and a plurality of second fluid passage channels (11) formed in the centering ring (7) are in flow connection with one another independently of a rotational angle position of the bearing bush (6) and the centering ring (7). It is provided that the first fluid passage channels (10) form an outer circumferential surface (12) of the bearing bush (6), forming first fluid passage recesses (13) that are separate from one another, and the second fluid passage channels (11) form an inner circumferential surface (14) lying against the outer circumferential surface (12). of the centering ring (7) pass through, forming second fluid passage recesses (15) that are separate from one another, with the first fluid passage recesses (13) or the second fluid passage recesses (15) being evenly spaced, viewed in the circumferential direction with respect to the axis of rotation (4), and the other fluid passage recesses (13, 15 ) are arranged unevenly spaced. The invention also relates to a shaft arrangement (1).

Description

The invention relates to a plain bearing assembly with a bearing bush and a centering ring that encompasses the bearing bush and can be rotated about an axis of rotation with respect to the bearing bush, with a plurality of first fluid passage channels formed in the bearing bush and a plurality of second fluid passage channels formed in the centering ring being mutually independent of a rotational angle position of the bearing bush and the centering ring be in flow communication. The invention further relates to a shaft arrangement.

From the prior art, for example, the publication U.S. 10,794,425 B2 famous. This describes a mechanical assembly that includes a shaft, a mechanical device, a bearing mounted on the shaft, and at least one ring that can move in rotation about the shaft. Also provided is a lubrication system having a channel that allows for the flow of lubricant and is at an interface between the shaft and the bearing. In addition, distribution channels for lubricants are formed in the bearing and are fluidically connected to the channel. At least one constriction is designed in the channel to create a pressure loss of the lubricant flowing in the channel.

Furthermore, the reference discloses DE 102 18 201 C1 a camshaft adjuster for variable valve control of an internal combustion engine, which is connected to a valve-actuating camshaft, in such a way that a housing body of the camshaft adjuster is connected to a drive wheel which is combined with the camshaft and built into a timing drive by means of axial screws. It is provided that the axial screws are screwed into threaded holes of a retaining device formed by a retaining ring, which retaining ring is attached to the drive wheel, with a housing of the housing body of the camshaft adjuster and the retaining ring of the drive wheel working together by means of a centering device.

It is the object of the invention to propose a plain bearing assembly which has advantages over known plain bearing assemblies, in particular ensuring a uniform and reliable supply of lubricant to a bearing point.

According to the invention, this is achieved with a slide bearing assembly having the features of claim 1 . It is provided that the first fluid passage channels pass through an outer peripheral surface of the bearing bush, forming first fluid passage recesses that are separate from one another, and the second fluid passage channels pass through an inner peripheral surface of the centering ring that rests against the outer peripheral surface, forming second fluid passage recesses that are separate from one another, with the first fluid passage recesses being viewed in the circumferential direction with respect to the axis of rotation or the second fluid passage recesses are spaced evenly and the other fluid passage recesses are spaced non-uniformly.

Advantageous configurations with expedient developments of the invention are specified in the dependent claims.

The sliding bearing assembly is preferably part of the shaft arrangement, but can of course also be present separately from it. It is used to store a shaft. For this purpose it has the bearing bush and the centering ring. The shaft, which is initially not part of the plain bearing assembly, passes through the bearing bush, forming a plain bearing. For example, the shaft has a bearing area which bears against the bearing bush, namely on an inner peripheral surface of the bearing bush. The shaft is rotatably mounted in the bearing bush about the axis of rotation. The plain bearing is formed by the interaction of the shaft with the bearing bush.

The bearing bush is seated in the centering ring, which for this purpose surrounds it in the circumferential direction, namely in particular completely and continuously. The bearing bush is preferably held on a bearing element via the centering ring. This means that the bearing bush is mounted or fastened to the bearing element only indirectly, namely via the centering ring. The bearing element can be a bearing block or a housing, for example. Both the bearing block and the housing can each be present as part of the shaft arrangement. In this respect, the above-mentioned shaft is rotatably mounted about the axis of rotation with the aid of the slide bearing assembly on the bearing element, for example the bearing block or in the housing.

In order to achieve low-friction and long-lasting storage with the help of the slide bearing assembly, the bearing point should at least be temporarily exposed to lubricant. In addition, this can be done to cool the bearing point. The lubricant is particularly preferably discharged through outlet openings which are formed in the inner peripheral surface of the bearing bush. The lubricant is supplied to the outlet openings via the fluid passage channels, namely the first fluid passage channels formed in the bearing bush and the second fluid passage channels formed in the centering ring. Also a vice reversed flow guidance can alternatively be provided.

The outlet openings are preferably formed by the inner peripheral surface of the bearing bush reaching through the first fluid passage channels. In other words, the first fluid passage channels pass through the inner peripheral surface of the bearing bush, forming the outlet openings. In this case, the outlet openings are arranged at a distance from one another in the circumferential direction with respect to the axis of rotation. Provision can be made for each of the outlet openings to be delimited by a continuous edge which is present on the inner peripheral surface of the bearing bush. For example, this edge is in continuous contact with an outer peripheral surface of the shaft if it is arranged in the bearing bush.

However, it can also be provided that the outlet openings open into an outlet channel, which runs in the circumferential direction and is formed in the bearing bush, reaching through the inner circumferential surface of the bearing bush. Particularly preferably, the outlet channel surrounds the shaft completely and uninterruptedly in the circumferential direction. In this respect, all outlet openings of the bearing bush open into the outlet channel. This achieves a particularly efficient distribution of the lubricant.

As already mentioned, the lubricant is supplied to the outlet openings via the first fluid passage channels and the second fluid passage channels. Here, the lubricant is fed to the second fluid passage channels and conveyed in the direction of the first fluid passage channels. The second fluid passage channels run in the centering ring in the radial direction with respect to the axis of rotation from the outside to the inside. There they are in flow connection with the first fluid passage channels, which in turn are designed to run in the radial direction in the bearing bush. The second fluid passage channels are fluidically connected to the first fluid passage channels on the side of the first fluid passage channels opposite the outlet openings.

The bearing bush is rotatable about the axis of rotation with respect to the centering ring. This is to be understood in particular as meaning that the bearing bushings are arranged in any rotational angle relative to one another with respect to the axis of rotation with respect to the centering ring at least before and/or during assembly. On the other hand, after the assembly is complete, the angular position set before and/or during assembly is constant, so that the bearing bush and the centering ring are fixed in the circumferential direction with respect to the axis of rotation. The angle of rotation present after assembly is random and is not specifically set to a specific value. Alternatively, it can of course be provided that the bearing bushing and the centering ring can also be rotated in relation to one another after assembly, so that the rotational angle position changes or at least can change at least temporarily during operation of the plain bearing assembly.

Since the bearing bush can be rotated about the axis of rotation with respect to the centering ring, the first fluid passage channels should be fluidically connected to the second fluid passage channels in such a way that the flow connection between them is independent of the angular position of the bearing bush relative to the centering ring. In other words, the flow connection should be present for all angular positions that occur during proper assembly and/or proper operation of the bearing bush or plain bearing assembly. These rotary angle positions lie, for example, in a specific rotary angle range, which preferably comprises at least 90°, at least 180°, at least 270° or 360°.

Of course, for the values of at least 90°, at least 180°, at least 270° it can be provided that the angle of rotation range is less than 360° and is for example at most 270°, at most 180° or at most 90°. The rotation angle range therefore preferably comprises at least 90° and at most 360°, at most 270° or at most 180°. Alternatively, the angle of rotation range comprises at least 180° and at most 360° or at most 270°. Further alternatively, it can cover at least 270° and at most 360°.

The first fluid passage channels pass through the outer peripheral surface of the bearing bush, forming the first fluid passage recesses. The second fluid passage channels, on the other hand, pass through the inner peripheral surface of the centering ring, forming the second fluid passage recesses.

In order to establish the flow connection independently of the rotational angle position of the bearing bush and the centering ring, it can be provided, for example and not according to the invention, to design the first fluid passage recesses or the second fluid passage recesses as oblong holes. This is particularly preferably done in such a way that in each of the rotational angle positions occurring during normal operation of the plain bearing assembly, one of the slot-like fluid passage recesses is arranged to overlap at least one of the other fluid passage recesses.

Alternatively, it cannot be provided according to the invention that the first fluid passage recesses or the second fluid passage recesses are arranged in a connecting channel which encompasses the axis of rotation, in particular reaches through it completely and uninterruptedly. In this case, the fluid passage recesses that are not present in the connecting channel are in the flow order via the connecting channel with the fluid passage recesses that are present in the connecting channel. For example, the first fluid passage recesses are arranged in the connecting channel, while the second fluid passage recesses are present outside of the connecting channel and are fluidically connected to the first fluid passage recesses only indirectly via it. A reverse configuration can also be implemented.

However, the configurations described have the disadvantage that the material of the bearing bush and/or the centering ring is weakened, so that they either have to be made more solid or a shorter service life has to be accepted. It is therefore provided according to the invention that the fluid passage recesses are formed in surfaces of the bearing bush and of the centering ring that abut one another and are arranged at a distance from one another in the circumferential direction. In order to realize the flow connection between the first fluid passage channels and the second fluid passage channels that is independent of the rotational angle position, either the first fluid passage recesses or the second fluid passage recesses are arranged at equal distances from one another in the circumferential direction. In addition, the respective other fluid passage recesses, that is to say either the second fluid passage recesses or the first fluid passage recesses, are unevenly spaced from one another in the circumferential direction.

To put it another way, in one embodiment of the plain bearing assembly, the first fluid passage recesses are arranged at a uniform spacing and the second fluid passage recesses are spaced unevenly in the circumferential direction. In a second embodiment of the slide bearing assembly, on the other hand, the second fluid passage recesses are arranged at an equal distance and the first fluid passage recesses are arranged at an uneven distance. The evenly spaced arrangement of the first fluid passage recesses or the second fluid passage recesses means that the fluid passage recesses have identical spacings from one another in the circumferential direction. The fluid passage recesses are preferably distributed uniformly around the axis of rotation in the circumferential direction.

In the case of the unevenly spaced arrangement, the distances between the fluid passage recesses are different from one another in the circumferential direction. This means that at least one distance is different from the other distances (which can be identical to one another). However, several distances preferably differ from one another, so that the distances between the fluid passage recesses in the circumferential direction comprise at least three, at least four, at least five or at least six different distances. The distances are particularly preferably completely different from one another, so that the distances do not contain identical distances.

The number of fluid passage recesses and their distances from one another are selected such that in each angular position of the bearing bush relative to the centering ring, at least one of the first fluid passage recesses is in flow communication with at least one of the second fluid passage recesses. It is therefore not necessary for a plurality of first fluid passage recesses to be in flow connection with at least one of the second fluid passage recesses or vice versa in each of the angular positions. The design of the slide bearing assembly described avoids an excessive weakening of the material of the bearing bush and the centering ring, but at the same time ensures a reliable and permanent supply of lubricant to the bearing point.

A development of the invention provides that the first fluid passage recesses each have the same dimensions and/or that the second fluid passage recesses each have the same dimensions. The dimensions are to be understood in particular as the dimensions in the circumferential direction. Additionally or alternatively, the dimensions can be in the axial direction. Provision is particularly preferably made for the first fluid passage recesses to be designed to be identical to one another and/or for the second fluid passage recesses to be designed to be identical to one another. For example, the fluid passage recesses are each oval, in particular round.

It is preferably provided that the first fluid passage recesses have the same dimensions as the second fluid passage recesses or vice versa. This means that each of the second fluid passage recesses is congruent with each of the first fluid passage recesses or vice versa. For example, the first fluid passage channels and the second fluid passage channels are each present as bores, in particular as bores with an identical diameter. Alternatively, the first fluid passage channels and the second fluid passage channels are each in the form of oblong holes. On the other hand, a configuration is particularly preferred in which the first fluid passage channels or the second fluid passage channels are designed as oblong holes and the other ones as bores. For example, the first fluid passage channels are designed as oblong holes and the second fluid passage channels as bores, or vice versa. In this case, the first fluid passage channels and the second fluid passage channels particularly preferably have the same dimensions in at least a first direction, for example in the axial direction with respect to the axis of rotation, while their dimensions differ from one another in another direction, in particular perpendicular to the first direction. This enables the slide bearing assembly to be manufactured simply and inexpensively.

A development of the invention provides that the geometric focal points of the first fluid passage recesses lie on a first imaginary circular path and/or that the geometric focal points of the second fluid passage recesses lie on a second imaginary circular path. This means that the first fluid passage recesses overlap one another as viewed in the axial direction, that is to say are arranged at the same axial position. The first circular path and the second circular path preferably lie completely and continuously in a plane which is perpendicular to the axis of rotation.

The plane accommodating the first imaginary circular path can be arranged at a distance from the plane accommodating the second imaginary circular path. However, the planes particularly preferably coincide, so that the first fluid passage recesses and the second fluid passage recesses are arranged at the same position as viewed in the axial direction. As a result, the flow connection between the first fluid passage channels and the second fluid passage channels is produced particularly efficiently.

A development of the invention provides that there are different numbers of first fluid passage recesses than second fluid passage recesses. The number of first fluid passage openings is therefore different from the number of second fluid passage openings. For example, there is a ratio of 7:8, 6:8 or 5:8 between the numbers. There is preferably a difference of at least one, at least two or at least three and/or at most five, at most four or at most three between the number of first fluid passage openings and the number of second fluid passage openings. The difference is preferably between one and three, in particular exactly one, exactly two or exactly three. The number of first fluid passage openings is particularly preferably greater than the number of second fluid passage openings, in particular by exactly one, exactly two or exactly three. As a result, a particularly high fluid throughput, that is to say a particularly high mass flow or volume flow per unit of time, can be achieved.

Alternatively, however, it can also be provided that there are as many first fluid passage recesses as there are second fluid passage recesses. This enables the lubricant to be fed efficiently to the bearing point while at the same time reducing the material weakening of the bearing bush and the centering ring. For example, at least six, at least eight or at least ten first fluid passage recesses are formed in the bearing bush and just as many second fluid passage recesses are formed in the centering ring.

A development of the invention provides that distances between the first fluid passage recesses in the circumferential direction correspond at least to their respective dimensions in the same direction, and/or that distances between the second fluid passage recesses in the circumferential direction correspond at least to their respective dimensions in the same direction. The dimensions and distances are preferably to be understood as meaning angles or angular dimensions. The distances each describe distances between immediately adjacent fluid passage recesses.

Thus, no further fluid passage recesses are arranged between the fluid passage recesses between which there is the respective distance. The smallest permissible distance between two fluid passage recesses corresponds to the dimensions of each of the two fluid passage recesses in the same direction, ie also in the circumferential direction. The distance between the fluid passage recesses is therefore at least as large as their dimensions. This avoids an excessive weakening of the material of the bearing bush or the centering ring.

A development of the invention provides that for each angular position of the bearing bush and the centering ring relative to one another between each of the first fluid passage recesses and the second fluid passage recess that is closest to it in the circumferential direction certain degree of coverage is present, the degrees of coverage being at least partially different from one another. For each angular position of the bearing bush relative to the centering ring, the second fluid passage recess lying closest to it in the circumferential direction is determined for each of the first fluid passage recesses.

The respective degree of overlap is then determined for the first fluid passage recess and the corresponding second fluid passage recess. The degree of overlap means the proportion of the first fluid passage recess that is overlapped by the second fluid passage recess in the circumferential direction. The degree of coverage is specified as a percentage, for example. With a degree of overlap of 0%, there is no overlap whatsoever between the first fluid passage recess and the second fluid passage recess. A degree of overlap of 100% preferably means that the first fluid passage recess is completely overlapped by the second fluid passage recess. For example, the two fluid passage recesses are aligned with one another in this case.

Due to the uniform spacing of the first fluid passage recesses or the second fluid passage recesses and the non-uniform spacing of the respective other fluid passage recesses, the degrees of overlap for the fluid passage recesses are at least partially different from one another. For example, in at least one rotational angle position, one of the first fluid passage recesses can have a degree of overlap of 100% with one of the second fluid passage recesses, whereas another of the first fluid passage recesses has a degree of overlap that is smaller with the second fluid passage recess that is closest to it in the circumferential direction in the same rotational angle position than 100% or even 0%.

It follows from this that a flow connection is not always established to the same extent via all first fluid passage channels and second fluid passage channels, since this depends on the respective degree of overlap between the corresponding first fluid passage recesses and the corresponding second fluid passage recesses and thus on the rotational angle position between the bearing bush and centering ring. The first fluid passage recesses and the second fluid passage recesses are preferably designed and arranged such that the sum of the degrees of overlap for all first fluid passage recesses is greater than 0% in every rotational angle position occurring during normal operation of the plain bearing assembly. This ensures a reliable supply of lubricant to the plain bearing.

Alternatively, a hydraulic diameter or fluid flow rate is used instead of the degree of coverage. The hydraulic diameter describes the diameter that is effective in terms of flow for the fluid when flowing between the first fluid passage recess and the second fluid passage recess and/or when flowing through the first fluid passage channel and the second fluid passage channel. The fluid throughput is the throughput of the fluid that results from the overlap or the hydraulic diameter under given flow conditions, i.e. in particular a pressure difference across the first fluid passage channel and the second fluid passage channel, and/or opposite fluid properties, in particular a viscosity of the fluid. The arrangement and the dimensions of the first fluid passage recesses and the second fluid passage recesses are optimized with regard to the largest possible hydraulic diameter and/or the highest possible fluid throughput.

A development of the invention provides that a sum of the degrees of overlap for all possible rotary angle positions based on a theoretical maximum value corresponds to at least a minimum value. This means that for each of the possible rotary angle positions, the sum of the degrees of overlap, based on the maximum value, is greater than or equal to the minimum value. The theoretical maximum value is calculated, for example—in the case of identical configurations of the first fluid passage recesses—from the number of first fluid passage recesses multiplied by 100%. The degrees of coverage and their total are also given as a percentage.

The minimum value is preferably at least 20%, at least 30% or at least 40%. The first fluid passage recesses and the second fluid passage recesses are preferably designed and arranged in such a way that the desired minimum value is achieved for each of the possible rotational angle positions. In addition or as an alternative, it can be provided that the sum of the degrees of overlap for all possible rotary angle positions in relation to the theoretical maximum value corresponds to at most 50%, at most 40% or at most 35%. This means in particular that the sum of the degrees of coverage, based on the maximum value, is in a range from 20% to 50%, in particular from 30% to 40 % or from 30% to 35%. This ensures a reliable and, in particular, uniform supply of lubricant to the plain bearing.

Instead of the degrees of overlap, the hydraulic diameters or the fluid throughputs for all possible angles of rotation can be used. The basic procedure and the minimum value according to the above explanations can also be used here.

A further development of the invention provides that each of the first fluid passage recesses is delimited by a continuous edge, which in at least one rotational angle position bears continuously and uninterruptedly against the inner peripheral surface, and/or that each of the second fluid passage recesses is delimited by a continuous edge, which in at least a rotational angle position continuously and uninterruptedly applied to the outer peripheral surface. The edge delimits the respective fluid passage recesses continuously, ie without interruption. Accordingly, it completely encompasses the respective fluid passage recesses. The edge is present in the outer peripheral surface of the bearing bush in the case of the first fluid passage recesses and in the inner peripheral surface of the centering ring in the case of the second fluid passage recesses.

The edge is in continuous and uninterrupted contact with the other peripheral surface. This means that the edge or the edges of the first fluid passage recesses rest against the inner peripheral surface of the centering ring in every rotational angle position, and/or in the case of the second fluid passage recesses continuously and uninterruptedly contact the outer peripheral surface of the bearing bush in every rotational angle position.

If the respective first fluid passage recesses are not at least partially overlapping one of the second fluid passage recesses or, conversely, the corresponding second fluid passage recesses are not at least partially overlapping one of the first fluid passage recesses, the flow connection between them and thus between the fluid passage channels assigned to them is interrupted. Such a design of the slide bearing assembly only requires the production of bores and/or elongated holes for forming the fluid passage channels and the fluid passage recesses. Accordingly, a simple and inexpensive manufacture of the plain bearing assembly is ensured.

A further development of the invention provides that, seen in the circumferential direction, each of the fluid passage recesses arranged unevenly distributed is at a rotational angle distance from the fluid passage recesses that are closest in a specific circumferential direction, with some of the rotational angle distances being in a first rotational angle interval and the respective other of the rotational angle distances being in a second rotational angle interval , wherein the second rotation angle interval is greater than the first rotation angle interval by a factor of at least 5. The rotational angle distance between two fluid passage recesses arranged directly spaced apart from one another in the circumferential direction refers in particular to the rotational angle distance between their respective geometric focal points. In other words, each of the fluid passage recesses has a longitudinal central axis, which is preferably perpendicular to the axis of rotation.

The angle of rotation distance is now the angle between two longitudinal center axes that are adjacent in the circumferential direction. The angular distances are at least partially different from one another. Particularly preferably, the angular distances are completely different from one another, so that the angular distances do not contain a multiple angular distance. The rotation angle distances are assigned either to the first rotation angle interval or to the second rotation angle interval, which are different from one another. The two rotation angle intervals therefore have no overlap whatsoever. For example, smaller of the angular distances are assigned to the first angular interval and larger of the angular distances are assigned to the second angular interval. Particularly preferably, the rotation angle intervals include the same number of rotation angle distances, so that the rotation angle distances are evenly distributed over the rotation angle intervals.

The rotation angle intervals are defined by the rotation angle distances assigned to them. Each of the rotation angle intervals is limited on the one hand by the smallest rotation angle distance assigned to it and on the other hand by the largest rotation angle distance assigned to it. Each of the rotation angle intervals therefore includes a specific rotation angle range, which is defined on the one hand by the smallest rotation angle distance assigned to it and on the other hand by the largest rotation angle distance assigned to it and is calculated as the difference between the largest rotation angle distance assigned to it and the smallest rotation angle distance assigned to it. This rotation angle range is larger for the second rotation angle interval than for the first rotation angle interval, preferably by a factor of at least five.

If—for example—the fluid passage recesses are at 0°, 51.7°, 85.4°, 119.2°, 167.9°, 202.6°, 242.3° and 327°, then the angular distances are 51.7 °, 33.7°, 33.8°, 48.7°, 34.7°, 39.7°, 84.7° and 33°. The smallest of these rotation angle distances are 33°, 33.7° and 33.8°, these define the first rotation angle interval. The largest rotation angle distances are 39.7°, 48.7°, 51.7° and 84.7° and define the second rotation angle interval. The rotation angle range of the first rotation angle interval is 0.8°, that of the second rotation angle interval is 45°. If the rotation angle distances are allocated differently (33°, 33.7°, 33.8° and 39.7° on the one hand and 48.7°, 51.7° and 84.7° on the other hand), rotation angle intervals of 6.7° and 36° In any case, there is a factor of at least five or more between the angle of rotation ranges of the two angle of rotation intervals.

The angle of rotation range of the first angle of rotation interval comprises, for example, at most 7.5°, at most 5°, at most 4°, at most 3° or at most 2°. In contrast, the angle of rotation range of the second angle of rotation interval comprises at least 10°, at least 15°, at least 20° or at least 25°. However, it is preferably larger and is in particular at least 30°, at least 35°, at least 40° or at least 45°. This achieves an arrangement of the fluid passage recesses which, on the one hand, ensures a permanent and, on the other hand, a uniform supply of lubricant to the plain bearing.

The invention also relates to a shaft arrangement, with at least one shaft and a plain bearing assembly that supports the shaft in a rotatable manner, in particular a plain bearing assembly according to the statements made within the scope of this description, the plain bearing assembly having a bearing bush and a centering ring that surrounds the bearing bush and is rotatable about an axis of rotation with respect to the bearing bush is provided, wherein a plurality of first fluid passage channels formed in the bearing bush and a plurality of second fluid passage channels formed in the centering ring are in fluid communication with one another independently of a rotational angular position of the bearing bush and the centering ring.

It is provided that the first fluid passage channels pass through an outer peripheral surface of the bearing bush, forming first fluid passage recesses that are separate from one another, and the second fluid passage channels pass through an inner peripheral surface of the centering ring that rests against the outer peripheral surface, forming second fluid passage recesses that are separate from one another, with the first fluid passage recesses viewed in the circumferential direction with respect to the axis of rotation or the second fluid passage recesses are spaced evenly and the other fluid passage recesses are spaced non-uniformly.

Reference has already been made to the advantages of such a configuration of the shaft arrangement or of the slide bearing assembly. Both the shaft arrangement and the slide bearing assembly can be further developed in accordance with the explanations within the scope of this description, so that reference is made to them.

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 combination specified in each case, but also in other combinations or on their own, without going beyond the scope of the leave invention. The invention is therefore also to be regarded as encompassing embodiments which are not explicitly shown or explained in the description and/or the figures, but emerge from the explained forms of expression or can be derived from them.

• 1 eine schematische Darstellung einer Wellenanordnung mit einer eine Lagerbuchse und einen Zentrierring aufweisenden Gleitlagerbaugruppe.

The invention is explained in more detail below with reference to the exemplary embodiments illustrated in the drawing, without the invention being restricted. It shows the only

• 1 a schematic representation of a shaft arrangement with a plain bearing assembly having a bearing bush and a centering ring.

the 1 shows a schematic representation of a shaft arrangement 1, which has a shaft 2 and a bearing element 3, on and/or in which the shaft 2 is rotatably mounted about an axis of rotation 4. The bearing element 3 is present, for example, as a housing of the shaft arrangement 1 . Alternatively, it can also be designed as a bearing block or the like. For the rotatable mounting of the shaft 2 on the bearing element 3 , the shaft arrangement 1 has a slide bearing assembly 5 . This has a bearing bush 6 and a centering ring 7 . The shaft 2 passes through the bearing bush 6 and in this case lies slidingly with an outer peripheral surface 8 on an inner peripheral surface 9 of the bearing bush 6 . The outer circumferential surface 8 of the shaft 2 is, for example, part of a bearing area of the shaft 2. The shaft 2 and the bearing bush 6 together form a sliding bearing for the rotatable mounting of the shaft 2 and therefore a bearing point.

The bearing bush 6 is connected to the bearing element 3 via the centering ring 7, preferably exclusively. In particular, the centering ring 7 is fixed or rigidly attached to the bearing element 3. The bearing bushing 6 , on the other hand, is arranged or mounted in the centering ring 7 such that it can rotate about the axis of rotation 4 . This means that the bearing bushing 6 and the centering ring 7 can be displaced in relation to one another in the circumferential direction until the assembly of the plain bearing assembly 5 is complete, in particular only until the assembly is complete. The bearing bushing 6 and the centering ring 7 are preferably fixed against one another after the assembly is complete, in particular in the circumferential direction. Alternatively, it can of course also be provided that the angular position of the bearing bush 6 and the centering ring 7 relative to one another also changes during operation of the bearing assembly 5, for example due to a rotary movement of the shaft 2.

A plurality of first fluid passage channels 10 are formed in the bearing bush 6 and a plurality of second fluid passage channels 11 are formed in the centering ring 7 . Lubricant is to be supplied to the bearing point or the shaft 2 via this, in particular for lubricating and/or cooling the sliding bearing. However, since the bearing bush 6 can be rotated with respect to the centering ring 7, special measures must be taken in order to establish a flow connection between the fluid passage channels 10 and 11 or via the fluid passage channels 10 and 11. For this purpose, the first fluid passage channels 11 pass through an outer peripheral surface 12 of the bearing bush 6, forming first fluid passage recesses 13, and the second fluid passage channels 11 an inner peripheral surface 14, forming second fluid passage recesses 15. From the first fluid passage channels 10, the second fluid passage channels 11, the first fluid passage recesses 13 and the second fluid passage recesses 15 is only one / marked.

The first fluid passage recesses 13 and the second fluid passage recesses 15 are each delimited by a continuous edge. The edges delimiting the first fluid passage recesses 13 are in continuous contact with the inner peripheral surface of the centering ring 7 . The edges delimiting the second fluid passage recesses 15 bear continuously against the outer peripheral surface 12 of the bearing bush 6 .

The first fluid passage recesses 13 are spaced evenly apart in the circumferential direction with respect to the axis of rotation 4, in particular they are arranged distributed evenly in the circumferential direction. The second fluid passage recesses 15, on the other hand, are arranged at uneven intervals in the circumferential direction. Of course, the reverse configuration can also be realized, in which the first fluid passage recesses 13 are arranged at an uneven distance and the second fluid passage recesses 15 are arranged at an even distance. Such a design and arrangement of the first fluid passage recesses 13 and the second fluid passage recesses 15 ensures that the bearing point is acted upon with lubricant evenly and independently of a rotational angle position of the bearing bush 6 with respect to the centering ring 7 .

The first fluid passage recesses 13 or their longitudinal center axes are preferably arranged at the following angular positions: 0°, 45°, 90°, 135°, 180°, 225°, 270° and 315°. The second fluid passage recesses 15 or their longitudinal center axes, on the other hand, are arranged at the following angular positions: 0°, 51.7°, 85.4°, 119.2°, 167.9°, 202.6°, 242.3° and 327°. In this case, the first fluid passage recesses 13 have the same dimensions as one another. The second fluid passage recesses 15 also have the same dimensions as one another. In addition, the first fluid passage recesses 13 and the second fluid passage recesses 15 particularly preferably have the same dimensions. The fluid passage channels 10 and 11 are in the form of bores and/or oblong holes and are correspondingly simple and inexpensive to produce.

The described configuration of the plain bearing assembly 5 or the shaft arrangement 1 enables a reliable and continuous application of lubricant to the bearing point regardless of the angular position of the bearing bush 6 with respect to the centering ring 7. At the same time, simple and cost-effective production is realized.

Reference List

1

shaft arrangement

2

wave

3

bearing element

4

axis of rotation

5

plain bearing assembly

6

bearing bush

7

centering ring

8th

outer peripheral surface

9

inner peripheral surface

10

first fluid passage channel

11

second fluid passage channel

12

outer peripheral surface

13

first fluid passageway

14

inner peripheral surface

15

second fluid passageway

QUOTES INCLUDED IN DESCRIPTION

This list of documents cited by the applicant was generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Patent Literature Cited

• US10794425B2 [0002]
• DE 10218201 C1 [0003]

Claims (10)

Plain bearing assembly (5) with a bearing bush (6) and a centering ring (7) which encompasses the bearing bush (6) and can be rotated about an axis of rotation (4) with respect to the bearing bush (6), wherein a plurality of first fluid passage channels (10 ) and a plurality of second fluid passage channels (11) formed in the centering ring (7) are in flow connection with one another independently of a rotational angular position of the bearing bush (6) and the centering ring (7), characterized in that the first fluid passage channels (10) have an outer peripheral surface (12 ) the bearing bush (6) forming first fluid passage recesses (13) and the second fluid passage channels (11) that are separate from one another pass through, seen in the circumferential direction with respect to the axis of rotation (4) the first fluid passage recesses (13) or the second fluid passage recesses (15) are arranged uniformly and the respective other fluid passage recesses (13, 15) are arranged unevenly spaced. plain bearing assembly claim 1 , characterized in that the first fluid passage recesses (13) each have the same dimensions and / or the second fluid passage recesses (15) each have the same dimensions. Plain bearing assembly according to one of the preceding claims, characterized in that the geometric focal points of the first fluid passage recesses (13) lie on a first imaginary circular path and/or the geometric focal points of the second fluid passage recesses (15) lie on a second imaginary circular path. Plain bearing assembly according to one of the preceding claims, characterized in that there are different numbers of first fluid passage recesses (13) than second fluid passage recesses (15). Plain bearing assembly according to one of the preceding claims, characterized in that in the circumferential direction distances between the first fluid passage recesses (13) correspond at least to their respective dimensions in the same direction, and/or in that in the circumferential direction distances between the second fluid passage recesses (15) correspond at least to their respective dimensions in the same match direction. Plain bearing assembly according to one of the preceding claims, characterized in that for each angular position of the bearing bush (6) and the centering ring (7) relative to one another between each of the first fluid passage recesses (13) and the second fluid passage recesses (15) lying closest to it in the circumferential direction certain degree of coverage is present, the degrees of coverage being at least partially different from one another. Plain bearing assembly according to one of the preceding claims, characterized in that a sum of the degrees of overlap for all possible rotational angle positions based on a theoretical maximum value corresponds to at least a minimum value. Plain bearing assembly according to one of the preceding claims, characterized in that each of the first fluid passage recesses (13) is delimited by a continuous edge which in at least one angular position bears continuously and uninterruptedly against the inner peripheral surface (14), and/or that each of the second fluid passage recesses ( 15) is delimited by a continuous edge which bears continuously and uninterruptedly against the outer peripheral surface (12) in at least one rotational angular position. Plain bearing assembly according to one of the preceding claims, characterized in that viewed in the circumferential direction each of the unevenly distributed arranged fluid passage recesses (13, 15) has a rotational angular distance from the respective closest of these fluid passage recesses (13, 15) in a specific circumferential direction, with some of the rotational angular distances in one first rotation angle interval and the respective other of the rotation angle distances lie in a second rotation angle interval, the second rotation angle interval being greater by a factor of at least five than the first rotation angle interval. Shaft arrangement (1), with at least one shaft (2) and a plain bearing assembly (5) rotatably supporting the shaft (2), in particular a plain bearing assembly (5) according to one or more of the preceding claims, wherein the plain bearing assembly (5) has a bearing bush ( 6) and a centering ring (7) which surrounds the bearing bush (6) and can be rotated about an axis of rotation (4) with respect to the bearing bush (6), a plurality of first fluid passage channels (10) formed in the bearing bush (6) and a plurality of first fluid passage channels (10) being formed in the centering ring ( 7) formed second fluid passage channels (11) independent of a rotational angle position of the bearing bush (6) and the centering ring (7) relative to one another in flow communication with one another stand, characterized in that the first fluid passage channels (10) have an outer peripheral surface (12) of the bearing bush (6), forming first fluid passage recesses (13) that are separate from one another, and the second fluid passage channels (11) have an inner peripheral surface (14 ) of the centering ring (7) pass through to form second fluid passage recesses (15) that are separate from one another, with the first fluid passage recesses (13) or the second fluid passage recesses (15) being uniform and the other fluid passage recesses (13, 15) are arranged unevenly spaced.

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