Hydrodynamic sliding bearing

Abstract

The invention relates to a hydrodynamic plain bearing (1) for supporting a rotor (4), comprising a bearing shell (2) having a bearing surface (3) for supporting the rotor, the bearing surface having at least one first sliding surface (10) and at least one second sliding surface (20), the first sliding surface (10) having at least one first surface section (10a) which is offset eccentrically with respect to a center point (M0) of the bearing shell, and the second sliding surface (20) having at least one second surface section (10a) which is offset eccentrically with respect to the center point (M0) of the bearing shell. The second sliding surface (20) has at least one second surface section (20a), in which: a) in at least one axial cross-section, the second surface section (20a) has a circular arc section with a radius (R2), the center point (M2) of which is not offset with respect to the center point (M0) of the bearing shell; and / or b) the second surface section (20a) has at least: b1) at least one opening (8) in the recess (9) for supplying a lubricating medium and / or a cooling medium; b2) a wedge groove (23) having at least one section (24), the radial depth of which decreases in the circumferential direction as far as an outlet edge (25) on the second sliding surface (20), in particular continuously decreases; and b3) a connection (21) for supplying a lubricating medium and / or a cooling medium from the recess (9) to the wedge groove (23).

Description

Technical Field

[0001] The present invention relates to a hydrodynamic sliding bearing for supporting a rotor, a rotor assembly (in one embodiment a transmission device) having at least one rotor supported by at least one sliding bearing described herein, and the use of a sliding bearing described herein for supporting a rotor. Summary of the Invention

[0002] The objective of this invention is to improve the rotor support or, in particular, to design and use a hydrodynamic sliding bearing.

[0003] This task is solved by a hydrodynamic sliding bearing having the features of claim 1. Claims 11 and 12 respectively claim protection for a rotor assembly having one or more rotors (in one embodiment, a transmission device) (the rotor being supported by one or more sliding bearings described herein) or for the use of sliding bearings described herein to support a rotor. Dependent claims relate to advantageous improvements.

[0004] According to one embodiment of the invention, a hydrodynamic sliding bearing that supports a rotor (preferably rotatably and / or at least radially) or is pre-designed, established, or used for this purpose has a single-piece or preferably multi-piece bearing bush, which itself (preferably at the inner circumference of the bearing bush) has a bearing surface that supports the rotor or is pre-designed, established, or used for this purpose; or it has a multi-piece or preferably single-piece (theoretical) bearing bush, which itself (preferably at the outer circumference of the bearing bush) has a bearing surface that supports the rotor or is pre-designed, established, or used for this purpose, especially when the sliding bearing has a sliding bearing pin or is constructed as a sliding bearing pin.

[0005] In one embodiment, the rotor is a shaft, journal, or the like; in a particularly advantageous embodiment, it is a transmission shaft or the like. In one embodiment, the rotor is a gear, especially a planetary gear in a planetary transmission. During operation, especially during rated operation, it rotates about or relative to the (rotational) axis in the (primary) rotational direction, preferably at high speeds. Accordingly, in one embodiment, the axial or axial direction (of the sliding bearing) mentioned herein is parallel to the longitudinal axis and / or rotational axis of the rotor to be supported or already supported, and the radial or radial direction is perpendicular to the axial direction and the (primary) rotational direction and / or circumferential direction.

[0006] In one embodiment, the sliding bearing is constructed as a sliding bearing bushing. In an alternative embodiment, the sliding bearing is constructed as a sliding bearing pin. As long as this specification relates to embodiments with sliding bearing bushings, this should be understood as not limiting the generality, and in particular, it can be applied to embodiments with sliding bearing pins, and vice versa. Accordingly, as used herein, the term "bearing shell" should preferably be understood as a bearing shell having a radially inward bearing surface (especially when the sliding bearing is constructed as a sliding bearing bushing), or especially when the sliding bearing is constructed as a sliding bearing pin, it should be understood as a theoretical or hypothetical bearing shell having a bearing surface radially outward relative to the sliding bearing pin, particularly such that in sliding bearings constructed as sliding bearing pins, the bearing shell refers to an axial section provided or constructed for sliding support or for this purpose. Accordingly, the orientation of grooves, openings, connections, or the like should also be understood as follows: in embodiments of sliding bearings, particularly those configured as sliding bearing bushes, they are radially outwardly recessed into the bearing shell or bearing surface, or accordingly configured; or in embodiments of sliding bearings, particularly those configured as sliding bearing pins, they are radially inwardly recessed into the bearing shell or bearing surface, or accordingly configured. For sliding bearings configured as sliding bearing pins, particularly in one embodiment, as used herein, the term "bearing shell" should be understood as (particularly unmachined) a shaft into which / therein are machined or (particularly by cutting) the features described herein.

[0007] According to one embodiment of the invention, the bearing surface has at least two sliding surfaces, which are currently referred to as the first sliding surface or the second sliding surface without limitation.

[0008] In one embodiment, the first sliding surface and the second sliding surface each have an extension range or angle of 180°. In another embodiment, the first sliding surface and the second sliding surface do not overlap each other, and they may be adjacent to each other on both sides or successively in the circumferential direction and together form 360° of the bearing surface.

[0009] In one embodiment, the (rated load) vector of the bearing force (resultant force and / or radial force) applied to the bearing by the rotating rotor during operation at maximum speed or rated speed and / or maximum load or rated load is located in the first sliding surface. In a stationary state, the gravity load vector or gravity vector applied to the bearing by the stationary rotor may be located in either the first or second sliding surface. In one embodiment, the first sliding surface is a loaded sliding surface or a so-called "load segment," while the second sliding surface is an unloaded sliding surface or a so-called "non-load segment."

[0010] In a preferred embodiment, the bearing bush has a first bearing portion (which has a first sliding surface at its inner circumference) and at least one second bearing portion (which has a second sliding surface at its inner circumference) connected thereto (in an improved embodiment, non-destructively detachable). Particularly preferably, the first and second sliding surfaces are abutted against each other at the seam between these bearing portions, especially when the sliding bearing is constructed as a sliding bearing bush. This simplifies manufacturing in one embodiment. However, the invention is not limited thereto. In particular, in an equally advantageous embodiment, the bearing bush may have a first bearing portion and at least one second bearing portion connected thereto (in an improved embodiment, non-destructively detachable), wherein the first bearing portion has a section of the first sliding surface and a section of the second sliding surface at its inner circumference, and / or the second bearing portion has a section of the first sliding surface and a section of the second sliding surface at its inner circumference.

[0011] According to one embodiment of the invention, the first sliding surface has at least one surface segment, referred to herein as the first surface segment without limitation, and is offset relative to a center point (preferably the bearing axis, particularly formed by the preferred cylindrical outer surface of the bearing bush). Preferably, this offset is achieved such that, in the case of a (rotationally symmetric) shaft (or its circular axial section) arranged (conceptually) relative to the center point or the bearing axis, a convergent gap in the (main) rotational direction is formed between the shaft and the first surface segment, particularly when the sliding bearing is constructed as a sliding bearing bush, and especially when the first sliding surface can be identical to the first surface segment. In an improved embodiment, the first surface segment has a radius-bearing arcuate portion in one or more axial sections, the center point of which (preferably as described above) is eccentrically offset relative to the center point of the bearing bush (preferably the bearing axis). Preferably, the first surface segment is described by the arcuate portion in one or more axial sections.

[0012] Thus, in one embodiment, the supply of lubricating and / or cooling media can be improved in the first section during operation, and / or the risk of (undesired) subsynchronous vibrations (especially half-frequency vortices / so-called "oil whirls") associated with higher speeds and lower bearing forces can be reduced, which is known per se in so-called "multi-wedge bearings" (e.g., lemon-shaped bearings).

[0013] According to one embodiment of the invention, the first sliding surface has at least one surface segment, referred to herein as the first surface segment without limitation, and is eccentrically offset relative to a center point (preferably the bearing axis). Preferably, this offset is achieved such that, when the shaft (or its circular axial section) is centrally arranged (ideally) with respect to the center point or the bearing axis (pivot-symmetric), a converging gap is formed between the rotor and the first surface segment in the (main) rotational direction, particularly when the sliding bearing is constructed as a sliding bearing pin. In particular, the first sliding surface may be identical to the first surface segment. In an improved embodiment, the first surface segment has a radius-bearing arc segment in one or more axial sections, the center point of which (preferably as described above) is eccentrically offset relative to the center point of the bearing bush (preferably the bearing axis). Preferably, the first surface segment is described by this arc segment in one or more axial sections.

[0014] Therefore, in one embodiment, the supply of lubricating and / or cooling media can be improved within the first sliding surface section during operation, and / or the risk of (undesired) subsynchronous vibrations (especially half-frequency vortices / so-called "oil whirls") associated with higher speeds and lower bearing forces can be reduced. According to one embodiment of the invention, the second sliding surface has at least one surface section, referred to as the second surface section without limitation, and in particular, the second sliding surface may be identical to the second surface section.

[0015] According to one aspect of the invention, particularly when the sliding bearing is constructed as a sliding bearing bushing, the second face section has a radius-bearing arcuate segment in one or more axial sections (preferably the one or more axial sections mentioned above with respect to the first face section), the center point of which is centrally arranged (implemented) relative to the center point of the bearing bush (preferably the bearing axis, which is particularly formed by a preferably cylindrical outer surface) or is not offset relative to the center point of the bearing bush (preferably the bearing axis). Preferably, the second face section is described by the arcuate segment in one or more axial sections.

[0016] According to one aspect of the invention, particularly when the sliding bearing is constructed as a sliding bearing pin, the second face section has a circular arc segment with a radius in one or more axial sections (preferably the one or more axial sections mentioned above with respect to the first face section), the center point of which is not offset relative to the center point of the bearing axis (especially in the case of the center point relative to the center point of the theoretical bearing) or relative to the center point of the bearing axis (especially relative to the center point of the theoretical bearing), preferably, the second face section is described by the circular arc segment in one or more axial sections.

[0017] Therefore, in one embodiment, during operation, the consumption of lubricating and / or cooling media and / or power loss can be reduced in the second face section.

[0018] Therefore, in one embodiment, particularly when the sliding bearing is constructed as a sliding bearing bushing, it can be said that a wedge-shaped bore having a first face section is combined with a circular bore having a second face section; or, in one embodiment, particularly when the sliding bearing is constructed as a sliding bearing pin, a wedge-shaped segment having a first face section is combined with an arcuate segment having a second face section. Thus, in one embodiment, it can be said that a single-wedge bore bearing is constructed, which is particularly not a multi-wedge bore bearing.

[0019] As an alternative to, or independently of, or particularly preferably as a supplement to, the combination of the aforementioned contoured load-bearing surface segment and the non-contoured non-load-bearing surface segment, according to one aspect of the invention, the second surface segment has at least: - One or more openings located within the recess, through which lubricating and / or cooling media are supplied during operation, or which are pre-set, established, or used for this purpose; - A wedge-shaped groove having at least one section (particularly a face section) whose radial depth decreases in the circumferential direction (preferably in the (main) rotational direction) up to the outlet edge (which is preferably in the (main) rotational direction or the direction of shaft rotation and / or downstream and / or adjacent to the first sliding surface in the direction of flow of lubricating and / or cooling media from the recess) at the second sliding surface (continuously in a preferred improvement), wherein in one embodiment, this section of the wedge-shaped groove has a radius-bound arcuate segment in one or more axial sections (preferably one or more axial sections mentioned above with respect to the first or second face section) whose center point is eccentric with respect to the center point of the (particularly theoretical) bearing bush (preferably the bearing axis), or is so eccentrically offset that the radial depth (of the wedge-shaped groove or section) decreases in the circumferential direction up to the outlet edge (continuously in a preferred improvement), and is preferably described by the arcuate segment; and - A single-channel or multi-channel connection through which lubricating and / or cooling media can be supplied from (especially from) the recess to the wedge groove, or for this purpose may be pre-set, established, or used.

[0020] In this way, in one embodiment, at least a portion (preferably the majority) of the lubricating and / or cooling medium entering through the openings can be guided from the recess through the connection to the wedge groove, where it experiences hydrodynamic back pressure within the wedge-shaped section of the groove. Thus, in one embodiment, advantageously, it can promote jacking pressure during operation with (particularly small) bearing loads, thereby significantly enhancing dynamic stability in a highly efficient and effective manner (particularly due to the smaller radial clearance of the non-profiled second face section towards the rotor), and / or reducing (preferably preventing) rotor movement towards the second face section or unloaded section (particularly at higher speeds). Compared to the known and widely adopted "pressure dam" groove—which typically has a constant axial width, a constant depth, and a sudden depth change near the groove end or outlet in the rotor rotation direction due to tool retraction—the wedge groove embodiment (particularly jacking pressure) achieves a (more) advantageous pressure distribution, thereby achieving a (more) advantageous (particularly dynamic) effect on the shaft or rotor.

[0021] In one embodiment, the wedge groove or the section of its radial depth that decreases in the circumferential direction up to the exit edge (in an improved embodiment, an arc segment with a radius, the center point of which has an eccentricity relative to the center point of the bearing bush or the bearing axis, such that the radial depth decreases in the circumferential direction up to the exit edge) has a starting point, the distance or angular offset of this starting point from the concave portion in the circumferential direction being less than the distance or angular offset of the exit edge from the concave portion, and from this starting point, the radial depth (preferably continuously) decreases up to the exit edge.

[0022] In one embodiment, the connection between the recess and the wedge groove, or the connection between them, has one or more supply grooves (each) connected to the recess. In an improved embodiment, the supply grooves (each) have at least partially a (particularly maximum, average, or minimum) width in the axial direction, which is smaller than the (particularly maximum, average, or minimum) width of the recess in the axial direction, and / or smaller than the (particularly maximum, average, or minimum) width of the wedge groove in the axial direction. Thus, in one embodiment, the flow of lubricating and / or cooling media from the recess to the wedge groove can be improved. By limiting the axial width of one or more supply grooves, in one embodiment, the hydrodynamic effect of the sliding surfaces located on the sides of the supply grooves (multiple supply grooves) in the axial direction can be advantageously retained within the angular length or circumference of the supply grooves (multiple supply grooves).

[0023] Furthermore, or alternatively, in one embodiment, the connection between the recess and the wedge groove has at least one distribution groove (in an improved embodiment, connected to the wedge groove and / or the supply groove), which has a width (particularly maximum, average, or minimum) in the axial direction, greater than the width (particularly maximum, average, or minimum) of the supply groove. Thus, in one embodiment, the distribution of lubricating and / or cooling media flowing into or within the wedge groove can be particularly improved (especially axially). In an improved embodiment, the distribution groove has a width (particularly maximum, average, or minimum) in the axial direction, greater than or equal to the width (particularly maximum, average, or minimum) of the supply groove. Thus, in one embodiment, the distribution of lubricating and / or cooling media flowing into or within the wedge groove can be further improved (especially axially).

[0024] Accordingly, in a preferred embodiment, the supply channels may be adjacent to the recess and the wedge-shaped channel, or connected to supply a lubricating medium and / or a cooling medium, or particularly preferably, the supply channels are adjacent to the recess and the dispensing channel, and the dispensing channel is adjacent to the supply channels and the wedge-shaped channel.

[0025] In one embodiment, recesses and / or (multiple) supply grooves and / or distribution grooves and / or wedge grooves (respectively) are defined by second face sections on both axial sides of the sliding bearing to guide at least a portion (preferably a majority) of the lubricating medium and / or cooling medium entering through (multiple) openings to the wedge groove, or to induce hydrodynamic back pressure or jacking pressure therein (especially during partial load operation).

[0026] In one embodiment, the sliding bearing has a continuous transition between the radius-bearing arc segment of the first face section and the radius-bearing arc segment of the second face section. Currently, "continuous" is particularly understood to mean "continuous or stepless within or taking into account manufacturing tolerances."

[0027] In one embodiment, this continuous or stepless transition makes axial movement toward the unloaded bearing more advantageous (especially smoother). Furthermore, this can reduce instability at the sliding surface and the risk of cavitation formation or cavitation damage in one embodiment. In an improved embodiment, in the offset plane (which is parted on one hand by the axis of the bearing or theoretical bearing and on the other hand by the center point of the radius-bearing arcuate section of the first face section and / or the center point of the radius-bearing arcuate section of the second face section), there is only one radial offset in the circumferential direction at the transition from the second face section to the first face section, wherein in at least one axial section of the bearing, a continuous transition is formed on opposite sides due to the radius and eccentricity of the first face section. In one embodiment, the radial offset extends in the circumferential direction (especially beyond a few degrees, especially at least 2° and / or at most 5°). In one embodiment, the radial offset is configured to be (at least substantially) continuous (especially non-abrupt or jumpy) and in another embodiment extends in the circumferential direction (especially more than a few degrees, especially at least 2° and / or at most 5°).

[0028] Thus, particularly in sliding bearings constructed as sliding bearing bushings, the aforementioned advantageous continuous transition can be achieved in one embodiment with particular advantage in manufacturing technology.

[0029] In one embodiment, the first face section has one or more openings for supplying lubricating and / or cooling media in another recess, wherein in an improved embodiment, the starting point of the other recess closer to the second face section in the circumferential direction is pivoted in the circumferential direction relative to the (preferably the aforementioned) radial offset between the first face section and the second face section by an angle of at least 5° and / or at most 35°.

[0030] By pivoting from the bearing seam to a recess in the first loaded sliding surface or its first section, in one embodiment, unwanted hot lubricating and / or hot cooling media carryover from the unloaded sliding surface to the loaded sliding surface can be reduced. In particular, in one embodiment, due to the increased proportion of cold lubricating and / or cold cooling media supplied from the recess, a higher average viscosity leads to a reduction in the maximum pressure and / or maximum temperature in the loaded sliding surface.

[0031] In one embodiment, the inner bearing surface is recessed radially and axially by two or more radial recesses (preferably on the two edge sides or at the two axial end faces of the bearing bush), wherein, in an improved embodiment, one or more of these recesses extend at least beyond the entire circumference of the second sliding surface in the circumferential direction. Furthermore, or alternatively, in an improved embodiment, one or more of these recesses extend circumferentially across the (preferably the aforementioned) radial offset between the first and second surface segments, or in an improved embodiment, one or more of these recesses overlap circumferentially.

[0032] Thus, in one embodiment, particularly at the axial edge of the end of the loaded sliding surface, the hot lubricating medium and / or hot cooling medium can be advantageously discharged or discharged from the bearing; thereby, in particular, in addition to the average clearance temperature, power loss can also be reduced.

[0033] In one improved embodiment, one or more of these recesses extend in the first sliding surface in the circumferential direction from a radial offset that they extend across or cover by an angle less than or equal to the angle by which the starting point of another recess is pivoted relative to the radial offset.

[0034] Therefore, in one implementation scheme, in particular, power loss can be further reduced in addition to the advantages mentioned above.

[0035] In one improved embodiment, one or more of the recesses extend in the first sliding surface in the circumferential direction from a radial offset that it extends across or covers by an angle greater than the angle by which the starting point of the other recess pivots relative to the radial offset.

[0036] Thus, in one embodiment, in particular, in addition to the advantages described above, the supply of lubricating and / or cooling media in another recess can be improved.

[0037] Particularly preferably, the difference between the angle between the radial offset in the first sliding surface and the end of one or more of the recesses, and the angle by which the starting point of the other recess pivots relative to the radial offset, is at most 40°.

[0038] By limiting the area of ​​the recess, in one embodiment, the maximum pressure in the loaded sliding surface and / or the bearing temperature can be reduced.

[0039] In one embodiment, the sliding bearing is installed or used (especially in bearing assemblies) such that, in the circumferential direction, an angle between 50° and 70° is formed between the rated load vector and the starting point of the recess in the unloaded sliding surface.

[0040] In one embodiment, the depth of the connection is at least 2 times and / or at most 8 times greater than the minimum radial clearance within the sliding bearing when the rotor is located at the center of the bearing.

[0041] In one embodiment, the maximum depth of the wedge groove is preferably at least 0.3 times and / or at most 2.5 times the minimum radial clearance within the sliding bearing when the rotor is located at the center of the bearing.

[0042] In one embodiment, the circumferential angle of the wedge groove is at least 15° and / or at most 50°, and in particular at least as large as the circumferential angle of the dispensing groove.

[0043] As used herein, the term "wedge groove" in one embodiment should be understood as a wedge-shaped recess, particularly internal, of a surface segment (as described herein). In one embodiment, the wedge groove may be axially defined by one / the surface segment. As used herein, the term "wedge groove" should preferably not be understood as wedge clearance and / or wedge bore, particularly wedge bore, and further particularly wedge clearance of (multiple) wedge bore bearings, or these terms should preferably not be understood as synonyms for "wedge groove".

[0044] In one embodiment, the circumferential angle of the supply slot is at least 40° and / or at most 100°.

[0045] In one embodiment, the axial width (especially the sum) of the supply grooves in the unloaded sliding surface is at least 15% and / or at most 45% of the axial width of the loaded sliding surface.

[0046] In one embodiment, the sliding bearing according to the invention can reduce the consumption of lubricating and / or cooling media and / or power loss and / or maximum temperature. Particularly advantageously, one or more sliding bearings described herein are used to support at least one rotor, preferably one or more sliding bearings described herein are used to support a first rotor of a transmission (preferably operating at high speed), and one or more sliding bearings described herein are used to support at least one additional rotor. The lubricating and / or cooling media mentioned herein can in particular be oil, preferably oil. Nevertheless, the invention is not limited to such applications or oil. Attached Figure Description

[0047] Further advantages and features arise from the dependent claims and embodiments. For this purpose, they are illustrated in part: Figure 1 A side view of the sliding bearing of a rotor assembly according to an embodiment of the present invention is shown; and Figure 2 This shows the unfolding of the inner circumference of the bearing bush of a sliding bearing, or... Figure 3 The outer periphery of the sliding bearing pin shown is unfolded; Figure 3The image shows a side view of a sliding bearing of a rotor assembly according to one embodiment of the present invention. Detailed Implementation

[0048] Figure 1 A side view of a sliding bearing 1, particularly a sliding bearing bushing, for supporting a rotor 4 of a rotor assembly having a rotor (main) rotation direction 5 according to an embodiment of the present invention is shown. Figure 2 The inner circumference of the bearing bush 2 of the sliding bearing is shown in the diagram.

[0049] Here, the bearing has two bearing parts ( Figure 1 Above and below (in the middle), they are at the dividing seam ( Figure 1 The horizontal dotted line in the middle; Figure 2 The L1 and L2 points are adjacent to each other and connected to each other in a manner not shown. Figure 1 The upper and middle bearing bush has a first sliding surface 10 at 180° on its inner circumference. Figure 1 The lower bearing bush has a second sliding surface 20 at the same 180° angle on its inner circumference. These two sliding surfaces 10 and 20 together constitute the inner bearing surface 3 of the sliding bearing 1 or bearing bush 2. Here, the (rated load) vector of the bearing force F (resultant force and / or radial force) applied to the bearing by the rotating rotor at maximum speed or rated speed and / or maximum load or rated load lies in the first sliding surface, such that the first sliding surface or... Figure 1 The upper middle bearing portion forms one or more load-bearing sliding surfaces or one or more load-bearing segments (“load segment”), and the second sliding surface or Figure 1 The lower middle portion of the bearing forms either a non-load sliding surface or a non-load segment. This is particularly suitable for manufacturing techniques, but the invention is not limited to the sliding surface being completely aligned with the bearing portions (adjacent to each other in the dividing seam).

[0050] The first loaded sliding surface 10 has a first surface section 10a or a wedge-shaped hole, which in Figure 1 The side view is described by an arc segment with radius R1, the center point M1 of which is eccentric (eccentricity e1) relative to the center point M0 (which is implemented by the radius R0 of the circle of the outer cylindrical surface of the bearing).

[0051] The second unloaded sliding surface 20 has a second surface section 20a or a circular hole, which is described in the side view by an arc segment with radius R2, the center point M2 of which is centered relative to the center point M0 (which is implemented by the radius R0 of the circle of the outer cylindrical surface of the bearing).

[0052] Such as combination Figure 1 Side view and Figure 2 As can be particularly identified by the unfolding, the second surface segment 20a of the unloaded sliding surface 20 has the following elements: - Openings 8 located within the lubrication recess 9 (e.g., two) for supplying lubricating and / or cooling media; - In the circumferential direction ( Figure 2 The supply groove 21 extends horizontally and is connected to or reaches the lubrication recess 9; - A dispensing groove 22 extending in the circumferential direction, which is connected to or reaches the supply groove 21; - A wedge-shaped groove 23 extending in the circumferential direction, which connects to or reaches the dispensing groove 22, wherein the wedge-shaped groove 23 has a (surface) section 24, the section being in Figure 1 The side view is described by an arc segment with radius Rk, whose center point Mk has an eccentricity ek relative to the center point M0 of the bearing, such that the radial depth of the wedge groove 23 decreases continuously in the circumferential direction until its exit edge 25 at the unloaded sliding surface 20.

[0053] The grooves 21 and 22 connecting the recess 9 and the wedge groove 23, as well as the wedge groove 23 itself, are defined by the second surface section 20a relative to the two axial sides of the sliding bearing, so that most of the lubricating or cooling medium entering through the opening 8 is guided from the recess 9 through the grooves 21 and 22 to the wedge groove 23.

[0054] The supply groove 21 in the unloaded sliding surface 20 is made smaller than the wedge groove 23 in its axial length.

[0055] The distribution groove 22 in the unloaded sliding surface 20 is larger than the supply groove 21 in its axial length.

[0056] Use L1 to mark the boundary (line) between the end of the second unloaded sliding surface 20 and the starting point of the first loaded sliding surface, and use L2 to mark the corresponding boundary (line) between the end of the first loaded sliding surface and the starting point of the second unloaded sliding surface.

[0057] In the offset plane 30, which is separated by the center points M1, M2 and the axis of rotation of the bearing, there is only one radial offset 31 in the circumferential direction at the transition L1 from the second surface section 20a of the second unloaded sliding surface 20 to the first surface section 10a of the first loaded sliding surface 10. In the above-described side view of the bearing, on the opposite side, due to the radii R1, R2 and the eccentricity e1 of the first surface section 10a, a continuous transition section 32, L2 without radial offset is constructed.

[0058] Another lubrication recess 7 with an opening 6 in the first surface section 10a pivots out from the offset plane 30, wherein, in the circumferential direction, the angle from the offset plane 30 with radial offset 31 to the starting point of the lubrication recess 7 is... The angle is between 5° and 35°.

[0059] The inner bearing surface 3 is recessed radially and axially at the end face edge of the second sliding surface 20 by two radial recesses 35, wherein both recesses extend beyond the entire circumference (segment 35a) of the second unloaded sliding surface 20 in the circumferential direction of the shaft, and each occupies an angle α in its angular extension 35b across the radial offset 31 in the circumferential direction, wherein in the embodiment, this angle α is less than the circumferential angle between the offset plane and the beginning of the lubrication recess 7. In one variant scheme, angle α can also be related to angle... The same size or larger.

[0060] Figure 3 A side view of a sliding bearing 1 (particularly a sliding bearing 1 constructed as a sliding bearing pin) for supporting a rotor 4 with a rotor (main) rotation direction 5 according to an embodiment of the present invention is shown, wherein, for simplicity, only the portion of the shaft with the sliding bearing constructed as a sliding bearing pin is shown as a side view. Figure 2 The outer periphery of the sliding bearing 1 (especially the sliding bearing 1 constructed as a sliding bearing pin) is shown in the diagram.

[0061] Here, the sliding bearing pin has two (theoretical) bearing bush parts. Figure 3 Above and below, they are at the dividing seam ( Figure 3 The horizontal dotted line in the middle; Figure 2 In the L1 and L2 range, the elements are adjacent to each other. Figure 3 The theoretical bearing in the upper middle section has a first sliding surface 10 at 180° on its outer periphery. Figure 3 The theoretical bearing bush at the lower center has a second sliding surface 20 at the same 180° angle on its outer periphery. These two sliding surfaces 10 and 20 together constitute the outer bearing surface 3 of the sliding bearing (pin) 1. Here, the bearing force (rated load) vector (resultant force and / or radial force) applied to the bearing or sliding bearing pin by the rotating rotor during operation at maximum speed or rated speed and / or maximum load or rated load lies in the first sliding surface, such that the first sliding surface or... Figure 3 The upper part of the theoretical bearing shell forms one or the load-bearing sliding surface or one or the load-bearing segment (“loadsegment”), and the second sliding surface or Figure 3 The lower central portion of the theoretical bearing shell forms either a non-load sliding surface or a non-load segment. This is particularly suitable for manufacturing techniques, but the invention is not limited to the sliding surface being completely aligned with the (theoretical) bearing shell portion.

[0062] The first loaded sliding surface 10 has a first surface segment 10a, which in Figure 1 The side view is described by an arc segment with radius R1, the center point of which is eccentric (eccentricity e1) relative to the center point M0 (which is implemented by the radius of the circle of the outer cylindrical surface of the theoretical bearing).

[0063] The second unloaded sliding surface 20 has a second surface section 20a, which is described in the side view by an arc segment with radius R2, the center point of which is centered relative to the center point M0 (which is implemented by the radius of the circle of the outer cylindrical surface of the theoretical bearing).

[0064] Such as combination Figure 3 Side view and Figure 2 As can be particularly identified by the unfolding, the second surface segment 20a of the unloaded sliding surface 20 has the following elements: - Two openings 8 located within the lubrication recess 9 for supplying lubricating and / or cooling media, wherein in one embodiment, the sliding bearing pin has an axial, particularly coaxial, bore that is fluidly connected to two openings 8, and is particularly configured to supply two openings 8. - In the circumferential direction ( Figure 2 The supply groove 21 extends horizontally and is connected to or reaches the lubrication recess 9; - A dispensing groove 22 extending in the circumferential direction, which is connected to or reaches the supply groove 21; - A wedge-shaped groove 23 extending in the circumferential direction, which connects to or reaches the dispensing groove 22, wherein the wedge-shaped groove 23 has a (surface) section 24, the section being in Figure 1 The side view is described by an arc segment with radius Rk, whose center point Mk has an eccentricity ek relative to the center point M0 of the theoretical bearing, such that the radial depth of the wedge groove 23 decreases continuously in the circumferential direction until its exit edge 25 at the unloaded sliding surface 20.

[0065] The grooves 21 and 22 connecting the recess 9 and the wedge groove 23, as well as the wedge groove 23 itself, are defined by the second surface section 20a relative to the two axial sides of the sliding bearing, so that most of the lubricating or cooling medium entering through the opening 8 can be guided from the recess 9 through the grooves 21 and 22 to the wedge groove 23.

[0066] The supply groove 21 in the unloaded sliding surface 20 is made smaller than the wedge groove 23 in its axial length.

[0067] The distribution groove 22 in the unloaded sliding surface 20 is larger than the supply groove 21 in its axial length.

[0068] Use L1 to mark the boundary (line) between the end of the second unloaded sliding surface 20 and the starting point of the first loaded sliding surface, and use L2 to mark the corresponding boundary (line) between the end of the first loaded sliding surface and the starting point of the second unloaded sliding surface.

[0069] In the offset plane 30, which is separated by the center points M1, M2 and the rotation axis of the bearing, there is only one radial offset 31 in the circumferential direction at the transition from the second surface section 20a of the second unloaded sliding surface 20 to the first surface section 10a of the first loaded sliding surface 10. On the opposite side of the bearing side view, due to the radius and the eccentricity of the first surface section 10a, a continuous transition section 32, L2 without radial offset is constructed.

[0070] Another lubrication recess 7 with an opening 6 in the first surface section 10a pivots out from the offset plane 30, wherein, in the circumferential direction, the angle from the offset plane 30 with radial offset 31 to the starting point of the lubrication recess 7 is... The angle is between 5° and 35°.

[0071] The inner bearing surface 3 is recessed radially and axially at the edge of the end face of the second sliding surface 20 by two radial recesses 35, wherein both recesses extend beyond the entire circumference (segment 35a) of the second unloaded sliding surface 20 in the circumferential direction of the shaft, and each occupies an angle α in its angular extension 35b across the radial offset 31 in the circumferential direction, wherein in the embodiment, this angle α is smaller than the circumferential angle between the offset plane and the lubrication recess 7. In one variant scheme, angle α can also be related to angle... The same size or larger.

[0072] In this disclosure, "having X" generally does not imply an exhaustive enumeration, but is a shorthand for "having at least one X," and also encompasses "having two or more Xs" and "having Y in addition to X." Although exemplary embodiments have been illustrated in the foregoing description, it should be noted that various variations are possible. Furthermore, it should be noted that the exemplary embodiments are merely examples and are by no means intended to limit the scope of protection, application, or construction. Rather, the foregoing description provides guidance for those skilled in the art to implement at least one exemplary embodiment, wherein various modifications, particularly in terms of the function and arrangement of the components, can be made without departing from the scope of protection derived from the claims and their equivalent combinations.

[0073] List of reference numerals 1. Hydrodynamic sliding bearing 2 Bearings 3. Bearing surface (internal or external) 4 rotors 5. Rotor rotation direction 6 Openings 7. Recess 8 Opening 9. Concave area 10 First Loaded Sliding Surface 10a First (load-bearing) section 20 Second unloaded sliding surface 20a Second (Unloaded) Surface Section 21 Supply Tank 22 Distributor slots 23 Wedge-shaped groove 24-section 25 Exit edge 30 Offset Plane 31 Radial offset 32 Continuous transition section 35 Radial recess 35a Section of radial concave portion in the second unloaded sliding surface 35b Section of radial recess in the first loaded sliding surface F Rated load vector L1 dividing line: the end of the second unloaded sliding surface / the beginning of the first loaded sliding surface L2 dividing line: the end of the first loaded sliding surface / the beginning of the second unloaded sliding surface R0 is the radius of the circle on the outer cylindrical surface of the bearing or theoretical bearing. The radius of the arc segment of the first face section R1 The radius of the arc segment of the second surface section R2 Rk is the radius of the arc segment of the wedge groove. The center point of the circle on the outer cylindrical surface of the M0 (especially theoretical) bearing. The center point of the arc section of the first face of M1 The center point of the arc section of the second section of M2 The center point of the arc section of the Mk wedge groove. Eccentricity of the arc segment of the first surface section e1 Eccentricity of the wedge groove (ek) α is the angle between the offset plane and the end of the recess. The angle between the offset plane and the starting point of another concave area

Claims

1. A hydrodynamic sliding bearing (1) for supporting a rotor (4), having a bush (2) with a bearing surface (3) for supporting the rotor, wherein the bearing surface has at least one first sliding surface (10) and at least one second sliding surface (20), in, The first sliding surface (10) has at least one first surface segment (10a), which is offset off-center relative to the center point (M0) of the bearing bush, and The second sliding surface (20) has at least one second surface segment (20a), wherein a) In at least one axial section, the second face section (20a) has an arcuate section with a radius (R2) whose center point (M2) is not offset relative to the center point (M0) of the bearing bush; and / or b) The second face section (20a) has at least: b1) At least one opening (8) located within the recess (9) for supplying lubricating medium and / or cooling medium; b2) A wedge groove (23) having at least one section (24) whose radial depth decreases in the circumferential direction up to the outlet edge (25) at the second sliding surface (20), and decreases continuously in particular; as well as b3) Connecting part (21) for supplying lubricating medium and / or cooling medium from the recess (9) to the wedge groove (23).

2. The sliding bearing (1) according to the preceding claim, characterized in that, The connecting part has - At least one supply groove (21) is connected to the recess (8) and has a width in the axial direction at least partially, the width of which is smaller than the width of the recess (8) and / or the wedge groove (23) in the axial direction; and / or - At least one dispensing groove (22), which is particularly connected to the wedge groove (23) and / or the supply groove (21), the dispensing groove having a width in the axial direction that is greater than the width of the supply groove (21).

3. The sliding bearing (1) according to any one of the preceding claims, characterized in that, - In at least one axial section, the first face section (10a) has an arcuate section with a radius (R1) whose center point (M1) is offset relative to the center point (M0) of the bearing bush; and / or - The section (24) of the wedge groove (23) whose radial depth decreases up to the outlet edge (25) has an arc section with radius (Rk) in at least one axial section, the center point (Mk) of which has an eccentricity (ek) relative to the center point (M0) of the bearing, such that the radial depth decreases in the circumferential direction up to the outlet edge, and decreases continuously.

4. The sliding bearing (1) according to the preceding claim, characterized in that, There is a continuous transition section (32) between the arc segment with radius (R1) of the first surface section (10a) and the arc segment with radius (R2) of the second surface section (20a).

5. The sliding bearing (1) according to the two preceding claims, characterized in that, In the offset plane (30) opened up by the axis of the bearing and the center point (M1) of the arc segment with radius (R1) of the first surface section (10a) and / or the center point (M2) of the arc segment with radius (R2) of the second surface section (20a), there is only one radial offset (31) in the circumferential direction at the transition from the second surface section (20a) to the first surface section (10a).

6. The sliding bearing (1) according to any one of the preceding claims, characterized in that, The first surface section (10a) has at least one opening (6) in another recess (7) for supplying lubricating medium and / or cooling medium.

7. The sliding bearing (1) according to the preceding claim, characterized in that, The starting point of the other recess (7) closer to the second surface segment (20a) in the circumferential direction is pivoted by an angle in the circumferential direction relative to the radial offset (31) between the first surface segment (10a) and the second surface segment (20a). The angle is at least 5° and / or at most 35°.

8. The sliding bearing (1) according to any one of the preceding claims, characterized in that, The inner bearing surface (3) is recessed in the radial and axial directions by at least two radial recesses (35), wherein at least one of the recesses extends in the circumferential direction beyond the entire circumference of the second sliding surface (20) and / or extends beyond at least one radial offset (31) between the first surface segment (10a) and the second surface segment (20a).

9. The sliding bearing (1) according to claims 7 and 8, characterized in that, The at least one recess extends in the first sliding surface (10) in the circumferential direction from the radial offset (31) between the first surface segment (10a) and the second surface segment (20a) by an angle (α), which is less than or equal to the angle by which the starting point of the other recess (7) is pivoted relative to the radial offset (31). ).

10. The sliding bearing (1) according to claims 7 and 8, characterized in that, The recess extends in the first sliding surface (10) in the circumferential direction from the radial offset (31) between the first surface segment (10a) and the second surface segment (20a) by an angle (α), which is greater than the angle by which the starting point of the other recess (7) pivots relative to the radial offset (31). ).

11. A rotor assembly, particularly a transmission device, having at least one sliding bearing (1) according to any one of the preceding claims and a rotor supported thereon.

12. Use of a sliding bearing (1) according to any one of the preceding claims for supporting a rotor (4).

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