Hydrodynamic sliding bearings

Abstract

A hydrodynamic sliding bearing (1) for supporting a rotor (4) has a bearing body (2) with 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 portion (10a) which is eccentrically offset with respect to the center point (M0) of the bearing body, and the second sliding surface (20) having at least one second surface portion (20a), a) the second surface portion (20a) having an arc with radius (R2) in at least one axial cross section The center point (M2) is not offset with respect to the center point (M0) of the bearing shell, and / or, b) the second surface portion (20a) has at least b1) at least one opening (8) in the pocket (9) for supplying lubricant and / or coolant; b2) a keyway (23) having at least one portion (24) of the keyway (23) whose radial depth of the portion (24) decreases particularly continuously in the circumferential direction to the outflow edge (25) of the second sliding surface (20); b3) a connection portion (21) for supplying lubricant and / or coolant from the pocket (9) to the keyway (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 gear) having at least one rotor supported by at least one of the sliding bearings described herein, and the use of the sliding bearings described herein for supporting a rotor.

[0002] Patent documents 1, 2, and 3 are referenced.

Prior Art Documents

Patent Documents

[0003]

Patent Document 1

Patent Document 2

Patent Document 3

Summary of the Invention

Problems to be Solved by the Invention

[0004] The problem of the present invention is to improve the support of the rotor, or in particular the hydrodynamic sliding bearing provided and used therefor.

Means for Solving the Problems

[0005] This problem is solved by a hydrodynamic sliding bearing having the features of claim 1. Claims 11 and 12 protect a rotor assembly (in one embodiment, a gear) having one or more rotors supported by one or more of the sliding bearings described herein, and the use of the sliding bearings described herein for supporting a rotor. The dependent claims relate to advantageous further developments.

[0006] According to embodiments of the present invention, a hydrodynamic sliding bearing for supporting, or providing, setting, or using for, a rotor, preferably rotatably and / or at least radially, is a bearing shell comprising one or more parts, preferably having a bearing shell on its inner circumference having bearing surfaces for supporting, or providing, setting, or using for, a rotor, or having a plurality of, preferably one, (theoretical) bearing shells, the bearing shell, in particular, having bearing surfaces on its outer circumference, preferably having bearing surfaces for supporting, or providing, setting, or using for, a rotor, if the sliding bearing has or is configured as sliding bearing bolts.

[0007] In one embodiment, the rotor is a shaft, journal, etc., and in a particularly advantageous embodiment, it is a gear shaft, etc. In one embodiment, the rotor is a gear, in particular a planet of a planetary gear.

[0008] During operation, particularly during rated operation, the rotor rotates in the (main) rotational direction, around the (rotational) axis, or with respect to the (rotational) axis, preferably at a high rotational speed. Correspondingly, in one embodiment, the axial direction (of the sliding bearing) referred to herein is parallel to the longitudinal axis and / or rotational axis of the rotor to be supported or being supported, and the radial direction is perpendicular to the axial direction and the (main) rotational direction and / or circumferential direction.

[0009] In one embodiment, the sliding bearing is formed as a sliding bearing bush. In an alternative embodiment, the sliding bearing is formed as a sliding bearing bolt. Insofar as this specification relates to embodiments using sliding bearing bushes, it should be understood that this is not limiting generality and is particularly applicable to embodiments using sliding bearing bolts, and vice versa. Correspondingly, the term “bearing shell” as used herein should be understood in particular as a bearing shell having bearing surfaces preferably located radially inward when the sliding bearing is configured as a sliding bearing bush, or as a theoretical or hypothetical bearing shell having bearing surfaces located radially outward with respect to the sliding bearing bolt when the sliding bearing is configured particularly as a sliding bearing bolt, and in particular as a bearing shell relating to the axial portion provided, formed, or used for the sliding bearing when the sliding bearing is formed as a sliding bearing bolt. Correspondingly, the directions of grooves, openings, and connecting parts are understood to be such that, in embodiments in which the sliding bearing is formed in particular as a sliding bearing bush, they extend radially outward and penetrate deeply into the bearing shell or bearing surface, or are formed accordingly; or, in embodiments in which the sliding bearing is formed in particular as a sliding bearing bolt, they extend radially inward and penetrate deeply into the bearing shell or bearing surface, or are formed accordingly. With respect to sliding bearings formed as sliding bearing bolts, in particular in one embodiment, the term "bearing shell" as used herein should be understood as a shaft into which the features described herein are incorporated, or which are formed or created in particular by machining, or in particular an unmachined shaft.

[0010] According to embodiments of the present invention, the bearing surface has at least two sliding surfaces, which are referred to here as the first sliding surface and the second sliding surface, without limiting generality.

[0011] In one embodiment, the first and second sliding surfaces each have an extended portion or angle of 180°. In one embodiment, the first and second sliding surfaces do not overlap with each other, and are particularly adjacent on both sides or continuous in the circumferential direction, and together form a 360° bearing surface.

[0012] In one embodiment, the (rated load) vector of the bearing reaction force (resulting in the radial) applied to the bearing by a rotating rotor operating at maximum rotational speed or rated rotational speed and / or maximum load or rated load lies within the first sliding surface. In a stationary state, the weight load vector or weight vector applied to the bearing by a stationary rotor may lie within the first or second sliding surface. In one embodiment, the first sliding surface is a loaded sliding surface, so-called "loaded segment," and the second sliding surface is an unloaded sliding surface, so-called "unloaded segment."

[0013] In a preferred embodiment, the bearing shell has a first shell portion having a first sliding surface on its inner circumference, and at least one second shell portion having a second sliding surface on its inner circumference, and in a further developed embodiment, nondestructively separable from the first shell portion, particularly preferably, especially when the sliding bearing is formed as a sliding bearing bush, the first and second sliding surfaces are adjacent to each other at a joint between these shell portions. This can simplify manufacturing in one embodiment. However, the present invention is not limited thereto, and in a particularly equally advantageous embodiment, the bearing shell has a first shell portion and at least one second shell portion having a first sliding surface (face) portion and in a further developed embodiment, nondestructively separable from the first shell portion, wherein the first shell portion has a (face) portion of a first sliding surface and a (face) portion of a second sliding surface on its inner circumference, and / or the second shell portion has a (face) portion of a first sliding surface and a (face) portion of a second sliding surface on its inner circumference.

[0014] According to embodiments of the present invention, the first sliding surface has at least one surface portion called the first surface portion, which is offset eccentrically from a center point, preferably the center point of the bearing axis, formed by a preferably cylindrical surface on the outside of the bearing shell, thereby forming a converging gap between the shaft and the first surface portion, preferably when the (rotationally symmetric) shaft (or its circular axial cross section) is assumed to be centered with respect to the center point or the bearing axis, and particularly when the sliding bearing is formed as a sliding bearing bush, the first sliding surface may be identical to the first surface portion. In a further development, the first surface portion has a radiused arc in one or more axial cross-sections (each), whose center point is preferably offset eccentrically from the center point of the bearing shell, preferably the bearing axis, as described above, and preferably the first surface portion is represented by an arc in one or more axial cross-sections (each).

[0015] In one embodiment, this improves the supply of lubricant and / or coolant to the first surface portion during operation and / or reduces the risk of (undesirable) subsynchronous vibrations (particularly half-frequency vortices, so-called "oil whirls") associated with relatively high rotational speeds and low bearing reaction forces, which are well known in so-called multi-key bearings (Mehrkeillager), such as lemon-shaped bearings.

[0016] According to one embodiment of the present invention, the first sliding surface has at least one surface portion called the first surface portion, without limiting generality, which is offset eccentrically from a center point, preferably from the center point of the bearing axis, thereby forming a converging gap between the rotor and the first surface portion, preferably when the (rotationally symmetric) shaft (or its circular axial cross section) is assumed to be centered with respect to the center point or bearing axis, and in particular when the sliding bearing is formed as a sliding bearing bolt, the first sliding surface may be identical to the first surface portion. In a further development, the first surface portion has a radiused arc in one or more axial cross-sections (each), which is preferably offset eccentrically from the center point of the bearing shell, preferably from the center point of the bearing axis, preferably as described above, and preferably the first surface portion is represented by an arc in one or more axial cross-sections (each).

[0017] In one embodiment, this improves the supply of lubricant and / or coolant to the first surface portion during operation and / or reduces the risk of (undesirable) subsynchronous vibrations (particularly half-frequency vortices, so-called "oil whirls") associated with relatively high rotational speeds and low bearing reaction forces. According to embodiments of the present invention, the second sliding surface has at least one surface portion called the second surface portion, without limiting generality, and in particular, the second sliding surface may be identical to the second surface portion.

[0018] According to an aspect of the present invention, the second surface portion has a radius arc in one or more axial cross-sections, preferably in the axial cross-sections described above with respect to the first surface portion, and its center point is not offset from the center point of the bearing shaft, preferably formed by the outer, preferably cylindrical surface of the bearing body, or the center point of the bearing shaft, preferably of the bearing body, preferably in relation to the center point of the bearing shaft, and preferably, in particular when the sliding bearing is formed as a sliding bearing bush, the second surface portion is represented by an arc in one or more axial cross-sections (each).

[0019] According to an aspect of the present invention, the second surface portion has a radius arc in one or more axial cross-sections, preferably in the axial cross-sections described above with respect to the first surface portion, and its center point is located centered with respect to the center point of the bearing axis, in particular the center point of the theoretical bearing shell, or is not offset with respect to the center point of the bearing axis, in particular the center point of the theoretical bearing shell, and in particular when the sliding bearing is formed as a sliding bearing bolt, preferably the second surface portion is represented by an arc in one or more axial cross-sections (each).

[0020] In one embodiment, this makes it possible to reduce the consumption of lubricant and / or coolant, and / or power loss, within the second surface portion during operation.

[0021] Therefore, in one embodiment, in particular when the sliding bearing is formed as a sliding bearing bush, the so-called keyhole of the first surface portion is combined with the round hole of the second surface portion, or in one embodiment, in particular when the sliding bearing is configured as a sliding bearing bolt, the wedge-shaped portion of the first surface portion is combined with the arc of the second surface portion. ru.

[0022] This configuration involves a combination of a surface portion with grooves to which a load is applied and a surface portion without grooves to which no load is applied. Add te , the The two face portions have at least the following: - One or more openings within a pocket through which lubricant and / or coolant is supplied during operation, or which are provided, set up, or used for this purpose; - A keyway having at least a portion, particularly a face portion, the radial depth of which decreases downstream in the circumferential direction, preferably in the (main) rotation direction, preferably in the (main) rotation direction of the shaft and / or in the outflow direction from the pockets of the lubricant and / or coolant, and / or up to the outflow edge of the second sliding surface adjacent to the first sliding surface, and in a preferred further development continuously decreases, and in one embodiment, the portion of the keyway has an arc with a radius in one or more axial cross-sections, preferably in the axial cross-section described above with respect to the first or second face portion, the center point of which is eccentric or eccentrically offset with respect to the center point of the bearing body, particularly the theoretical bearing body, preferably the bearing shaft, and the radial depth (of the keyway or its portion) decreases continuously up to the outflow edge in the circumferential direction, and in a preferred development is represented by an arc; - A connection consisting of one or more channels, which enables the supply of lubricant and / or coolant to the keyway, particularly from the pockets, or supplies it, or is provided, or set, or used for this purpose.

[0023] In one embodiment, by this method, at least a part, preferably most, of the lubricant and / or coolant flowing in through the opening passes from the pocket through the connection part and is guided to the keyway, and can receive hydrodynamic dynamic pressure inside the wedge-shaped part of the keyway. As a result, in one embodiment, advantageously, during operation, especially at a low bearing load, a lift force is provided, whereby the dynamic stability is advantageously enhanced in an effective manner, especially as a result of the small radial play of the rotor with respect to the second surface part without grooves, and / or especially when the rotational speed is relatively high, the displacement of the rotor to the second surface part or the unloaded part is reduced, preferably prevented. Compared with the known and widely used "pressure dam" grooves (generally having a constant axial width and a constant depth and having a sudden depth change at the end of the groove or immediately before the outlet of the groove by the tool outlet in the rotational direction), the structure of the keyway provides, in particular, a lift force, (more) advantageous pressure characteristics, and thus a (more) advantageous (especially dynamic) effect on the shaft or rotor.

[0024] In one embodiment, a keyway or a part thereof whose radial depth decreases in the circumferential direction to the outflow edge, in a further development form, has an arc with a radius whose center point is eccentric with respect to the center point of the bearing housing or the bearing axis of the bearing housing, and the distance or angular offset from the pocket smaller than the outflow edge in the circumferential direction, and has a starting end from which the radial depth preferably continuously decreases to the outflow edge.

[0025] In one embodiment, the connection between the pocket and the keyway has one or more supply grooves connected to the pocket (each), and in a further development, one or more supply grooves (each) have a width, particularly a maximum, intermediate, or minimum width, at least partially axially, such that the width is smaller than the width of the pocket in the axial direction, particularly the maximum, intermediate, or minimum width, and / or smaller than the width of the keyway in the axial direction, particularly the maximum, intermediate, or minimum width. This can, in one embodiment, improve the flow of lubricant and / or coolant from the pocket to the keyway. By limiting the axial width of one or more supply grooves, in one embodiment, advantageously, the hydrodynamic action of the sliding surface located laterally to the supply groove in the axial direction is maintained within the angular length or perimeter length of the supply groove.

[0026] Additionally or alternatively, in one embodiment, the connection between the pocket and the keyway has, in a further development, at least one distribution groove connected to the keyway and / or supply groove, the distribution groove having an axial width, particularly a maximum, intermediate, or minimum width, which is greater than the width of the supply groove, particularly the maximum, intermediate, or minimum width. This improves, in one embodiment, the flow of lubricant and / or coolant into or within the keyway, particularly the distribution, and more particularly the axial distribution. In a further development, the distribution groove has an axial width, particularly a maximum, intermediate, or minimum width, which is greater than or equal to the width of the supply groove, particularly the maximum, intermediate, or minimum width. This further improves, in one embodiment, the flow of lubricant and / or coolant into or within the keyway, particularly the distribution, and more particularly the axial distribution.

[0027] Accordingly, in a preferred embodiment, the supply groove may be adjacent to the pocket and keyway and connected to supply lubricant and / or coolant, or, particularly preferably, the supply groove may be adjacent to the pocket and distribution groove, and the distribution groove may be adjacent to the supply groove and keyway.

[0028] In one embodiment, the pocket and / or supply groove and / or distribution groove and / or keyway are (each) separated by a second surface portion on both axial sides of the sliding bearing, thereby directing at least a portion, preferably a large portion, of the lubricant and / or coolant flowing in through the opening into the keyway, or generating hydrodynamic dynamic pressure or uplift pressure, particularly during partial load operation.

[0029] In one embodiment, the sliding bearing has a continuous transition between an arc having a radius for the first surface portion and an arc having a radius for the second surface portion. Here, "continuous" is understood to mean "continuous or without steps, either within the range of manufacturing tolerances or with regard to manufacturing tolerances."

[0030] Such a continuous or stepless transition allows, in one embodiment, a more advantageous, particularly smooth, wave transfer to the unloaded shell. Furthermore, in one embodiment, this can reduce the risk of instability and cavitation formation or damage to the sliding surface. In a further development, in an offset plane formed on the one hand by the axis of the bearing shell or theoretical bearing shell and on the other hand by the center point of the arc having the radius of the first face portion and / or the center point of the arc having the radius of the second face portion, there is exactly one radial offset in the circumferential direction at the transition from the second face portion to the first face portion, and in at least one axial cross section of the bearing shell, a continuous transition is formed on the opposite side as a result of the radius and eccentricity of the first face portion. In one embodiment, the radial offset extends in the circumferential direction, particularly over several degrees, particularly at least 2° and / or up to 5°. In one embodiment, the radial offset is formed to be at least generally continuous and not particularly abrupt, and in one embodiment, it extends circumferentially, particularly over several degrees, particularly at least 2° and / or up to 5°.

[0031] This makes the aforementioned advantageous continuous transition particularly advantageous from a manufacturing perspective in one embodiment, especially when the sliding bearing is formed as a sliding bearing bush.

[0032] In one embodiment, the first surface portion has one or more openings in a further pocket for supplying a lubricant and / or coolant, and in a further development, the starting end of this further pocket, which is circumferentially adjacent to the second surface portion, is pivoted at an angle of at least 5° and / or up to 35° circumferentially with respect to the radial offset between the first and second surface portions, preferably as described above.

[0033] Such a first, loaded sliding surface, or a portion thereof, preferably a pocket orbiting from the joint of the bearing shell, makes it possible in one embodiment to reduce the undesirable flow of thermal lubricant and / or coolant from the unloaded sliding surface to the loaded sliding surface, and as a result, particularly advantageous in one embodiment, by supplying a larger proportion of cold lubricant and / or coolant from the pocket, a reduction in the maximum pressure and / or maximum temperature at the loaded sliding surface can be achieved, with a higher average viscosity.

[0034] In one embodiment, the inner bearing surface is set back radially and axially by two or more radial recesses, preferably on two edges, or on both axial ends of the bearing shell; in a further development, one or more recesses extend circumferentially over at least the entire circumference of the second sliding surface. Additionally or alternatively, in a further development, one or more recesses extend circumferentially over the radial offset between the first and second surface portions, preferably as described above, or in a further development, one or more recesses cover the offset circumferentially.

[0035] This allows, in one embodiment, to advantageously discharge or remove thermal lubricant and / or coolant from the bearing, particularly at the axial edges of the end of the sliding surface under load, thereby reducing power loss in addition to the average clearance temperature.

[0036] In a further development, one or more recesses in the first sliding surface extend from the radial offset in the circumferential direction, extend across the radial offset, or cover the radial offset at an angle that is less than or equal to the angle at which the starting end of the further pocket is pivoted relative to the radial offset.

[0037] This makes it possible to further reduce power loss, in addition to the advantages mentioned above, in one embodiment.

[0038] In a further development, one or more recesses in the first sliding surface extend from the radial offset in the circumferential direction, extend across the radial offset, or cover the radial offset at an angle greater than the angle at which the starting end of the further pocket is pivoted relative to the radial offset.

[0039] This, in one embodiment, improves the supply of lubricant and / or coolant in additional pockets, in addition to the advantages described above.

[0040] Particularly preferably, the difference between the radial offset on the first sliding surface, the angle between the end of one or more recesses, and the angle at which the starting end of a further pocket is pivoted relative to this radial offset is a maximum of 40°.

[0041] In one embodiment, this limitation of the recessed surface can reduce the maximum pressure and / or bearing temperature at the sliding surface under load.

[0042] In one embodiment, the sliding bearing is mounted or used such that, particularly within a bearing assembly, an angle of 50° to 70° is formed between the rated load vector and the starting end of the pocket on the unloaded sliding surface in the circumferential direction.

[0043] In one embodiment, the depth of the connection is at least twice, and / or up to eight times, the minimum radial clearance within the sliding bearing when the rotor is centered on the bearing.

[0044] In one embodiment, the maximum depth of the keyway is preferably at least 0.3 times and / or up to 2.5 times the minimum radial clearance within the sliding bearing when the rotor is centered in the bearing.

[0045] In one embodiment, the circumferential angle of the keyway is at least 15° and / or up to 50°, and in particular, is at least the same as the circumferential angle of the distribution groove. 。

[0046] In one embodiment, the circumferential angle of the supply groove is at least 40° and / or up to 100°.

[0047] In one embodiment, the axial width of the supply groove on the unloaded sliding surface, particularly the axial width of the entire supply groove, is at least 15% and / or up to 45% of the axial width of the loaded sliding surface, particularly in total.

[0048] In one embodiment, the sliding bearings according to the present invention can reduce the consumption of lubricant and / or coolant, as well as power loss and / or maximum temperature. One or more sliding bearings described herein can be used particularly advantageously to support at least one rotor of a gear, preferably a high-speed gear; one or more sliding bearings described herein, preferably to support a first rotor; and one or more sliding bearings described herein, preferably to support at least one further rotor. The lubricants and / or coolants mentioned herein can, in particular, include oil, and are preferably oil. However, the present invention is not limited to such uses or oil.

[0049] Further advantages and features are evident from the dependent claims and embodiments, which are partially summarized below. [Brief explanation of the drawing]

[0050] [Figure 1] This is a side view showing a sliding bearing of a rotor assembly according to an embodiment of the present invention. [Figure 2] This is an exploded view of the inner circumference of the bearing shell of a sliding bearing, or an exploded view of the outer circumference of the sliding bearing bolt shown in Figure 3. [Figure 3] This is a side view of the sliding bearing of a rotor assembly according to an embodiment of the present invention. [Modes for carrying out the invention]

[0051] Figure 1 is a side view showing a sliding bearing 1, particularly a sliding bearing bush, for supporting a rotor 4 of a rotor assembly having a (main) rotation direction 5 of the rotor, according to an embodiment of the present invention, and Figure 2 is an exploded view showing the inner circumference of the bearing body 2 of the sliding bearing.

[0052] Here, the bearing shell has two bearing shell portions (upper and lower in Figure 1), which are adjacent to each other at a joint (horizontal dashed line in Figure 1, L1 and L2 in Figure 2) and connected to each other in a manner not shown. The upper bearing shell in Figure 1 has a first sliding surface 10 at 180° on its inner circumference, and the lower bearing shell in Figure 1 has a second sliding surface 20 at 180° on its inner circumference. These two sliding surfaces 10 and 20 together form the inner bearing surface 3 of the sliding bearing 1 or bearing shell 2. In this case, when the rotating rotor is operating at maximum or rated rotational speed and / or maximum or rated load, the (rated) vector of the bearing reaction force F (resulting in and / or radial) exerted on the bearing lies within the first sliding surface. Therefore, this, or the upper bearing shell portion in Figure 1, forms a loaded sliding surface, i.e., a loaded segment ("loaded segment"), and the second sliding surface, i.e., the lower bearing shell portion in Figure 1, forms an unloaded sliding surface, i.e., an unloaded segment ("unloaded segment"). While this is particularly advantageous from a manufacturing perspective, the present invention is not limited to the identity of the sliding surface and the bearing shell portion (adjacent at the joint).

[0053] The first, load-bearing sliding surface 10 has a first surface portion 10a or a keyhole, which in the side view of Figure 1 is represented by a circular arc with radius R1, and its center point M1 is eccentric (degree of eccentricity e1) with respect to the center point M0 formed by the radius R0 of the circle of the outer cylindrical surface of the bearing shell.

[0054] The second, unloaded sliding surface 20 has a second surface portion 20a or a round hole, which in the side view is represented by a circular arc with radius R2, and its center point M2 is centered relative to the center point M0 formed by the radius R0 of the circle of the outer cylindrical surface of the bearing body.

[0055] In particular, as can be seen by looking at the side view in Figure 1 and the unfolded view in Figure 2 together, the second surface portion 20a of the sliding surface 20 to which no load is applied has the following elements: - Openings 8 (for example, two) in the lubrication pocket 9 for supplying lubricant and / or coolant, - A supply groove 21 extending circumferentially (horizontally in Figure 2) connects to or reaches the lubrication pocket 9, - A distribution groove 22 extending in the circumferential direction, which connects to or reaches the supply groove 21, - A keyway 23 extending in the circumferential direction, which connects to or reaches the distribution groove 22, The keyway 23 has a (surface) portion 24 represented by an arc with radius Rk in the side view of Figure 1, the center point Mk of which has an eccentricity ek with respect to the center point M0 of the bearing body, thereby the radial depth of the keyway 23 decreases continuously in the circumferential direction to its outflow edge 25 of the unloaded sliding surface 20.

[0056] Since the grooves 21 and 22 connecting the pocket 9 to the keyway 23, and the keyway 23 itself are separated by the second surface portion 20a on both axial sides of the sliding bearing, most of the lubricant or coolant flowing in through the opening 8 is guided from the pocket 9 through the grooves 21 and 22 to the keyway 23.

[0057] In the sliding surface 20 where no load is applied, the supply groove 21 is configured to have a shorter axial length than the keyway 23.

[0058] The distribution groove 22 of the sliding surface 20, to which no load is applied, has a greater axial length than the supply groove 21.

[0059] L1 indicates the boundary (line) between the end of the second, unloaded sliding surface 20 and the start of the first, loaded sliding surface, and L2 indicates the boundary (line) between the end of the first, loaded sliding surface and the start of the second, unloaded sliding surface.

[0060] On the offset surface 30 formed by the center points M1, M2 and the rotation axis of the bearing shell, there is exactly one radial offset 31 in the circumferential direction at the transition L1 between the second surface portion 20a of the second, unloaded sliding surface 20 and the first surface portion 10a of the first, loaded sliding surface 10. In the side view of the bearing shell described above, as a result of the radii R1, R2 and the eccentricity e1 of the first surface portion 10a, a continuous transition portion 32, L2 without a radial offset is formed on the opposite side.

[0061] A further lubrication pocket 7, having an opening 6 in the first surface portion 10a, pivots outward from the offset surface 30, and the circumferential angle θ from the offset surface 30 to the starting end of the lubrication pocket 7, having a radial offset 31, is between 5° and 35°.

[0062] The inner bearing surface 3 is set back radially and axially from the edge of the end face of the second sliding surface 20 by two radial recesses 35. Both recesses extend circumferentially around the shaft over the entire circumference of the second, unloaded sliding surface 20 (part 35a), and at their angular extensions 35b, they extend circumferentially beyond the radial offset 31, forming an angle α. In this embodiment, this angle α is smaller than the angle θ between the offset surface and the starting end of the lubrication pocket 7 in the circumferential direction. In modified examples, angle α may be equal to or greater than angle θ.

[0063] Figure 3 is a side view showing a sliding bearing 1, particularly a sliding bearing bolt, for supporting a rotor 4 of a rotor assembly having a (main) rotation direction 5 of the rotor, according to an embodiment of the present invention. For simplification, only the portion of the shaft formed as a sliding bearing bolt that has the sliding bearing is shown in the side view. Figure 2 is an exploded view of the outer circumference of the sliding bearing 1, particularly a sliding bearing bolt.

[0064] Here, the sliding bearing bolt has two (theoretical) bearing body portions (upper and lower in Figure 3), which are adjacent to each other at a joint (horizontal dashed line in Figure 3, L1 and L2 in Figure 2). The upper theoretical bearing body in Figure 3 has a first sliding surface 10 with a 180° angle on its outer circumference, and the lower theoretical bearing body in Figure 3 has a second sliding surface 20 with a 180° angle on its outer circumference. These two sliding surfaces 10 and 20 together form the outer bearing surface 3 of the sliding bearing (bolt) 1. In this case, when the rotating rotor is operating at maximum or rated rotational speed and / or maximum or rated load, the (rated load) vector of the bearing reaction force F (resulting in and / or radial) exerted on the bearing or sliding bearing bolts lies within the first sliding surface. Therefore, this, or the upper theoretical bearing shell portion in Figure 3, forms a loaded sliding surface, i.e., a loaded segment ("loaded segment"), and the second sliding surface, i.e., the lower theoretical bearing shell portion in Figure 3, forms an unloaded sliding surface, i.e., an unloaded segment ("unloaded segment"). While this is particularly advantageous from a manufacturing perspective, the present invention is not limited to the identity of the sliding surface and the (theoretical) bearing shell portion.

[0065] The first sliding surface 10 to which a load is applied has a first surface portion 10a represented by a circular arc with radius R1 in the side view of Figure 1, and its center point M1 is eccentric (degree of eccentricity e1) with respect to the center point M0 formed by the radius R0 of the circle of the outer cylindrical surface of the theoretical bearing shell.

[0066] The second, unloaded sliding surface 20 has a second surface portion 20a represented in the side view by an arc with radius R2, the center point M2 of which is centered relative to the center point M0 formed by the radius R0 of the circle of the outer cylindrical surface of the theoretical bearing shell.

[0067] In particular, as can be seen by looking at the side view in Figure 3 and the unfolded view in Figure 2 together, the second surface portion 20a of the sliding surface 20, to which no load is applied, has the following elements: - An opening (e.g., two) in a lubrication pocket 9 for supplying lubricant and / or coolant, the opening having an axial, particularly coaxial hole, to which a sliding bearing bolt is fluidly connected in one embodiment and configured to supply in particular to the opening (e.g., two) 8; - A supply groove 21 that connects to or reaches the lubrication pocket 9 and extends circumferentially (horizontally in Figure 2); - A distribution groove 22 that connects to or reaches the supply groove 21 and extends in the circumferential direction; - A keyway 23 having a (surface) portion 24 that connects to or reaches a distribution groove 22, extends circumferentially, and is represented in the side view of Figure 1 by an arc having radius Rk, wherein the center point Mk of the (surface) portion 24 has an eccentricity ek with respect to the center point M0 of the theoretical bearing shell, thereby the radial depth of the keyway 23 decreases continuously in the circumferential direction to its outflow edge 25 of the unloaded sliding surface 20.

[0068] The grooves 21 and 22 connecting the pocket 9 to the keyway 23, and the keyway 23 itself, are each separated on both axial sides of the sliding bearing by a second surface portion 20a, so that most of the lubricant or coolant flowing in through the opening 8 is guided from the pocket 9 through the grooves 21 and 22 to the keyway 23.

[0069] The supply groove 21 of the sliding surface 20, to which no load is applied, is formed such that its axial length is shorter than that of the keyway 23.

[0070] The distribution groove 22 of the sliding surface 20, to which no load is applied, is formed such that its axial length is longer than that of the supply groove 21.

[0071] L1 indicates the boundary (line) between the end of the second, unloaded sliding surface 20 and the start of the first, loaded sliding surface, and L2 indicates the boundary (line) between the end of the first, loaded sliding surface and the start of the second, unloaded sliding surface.

[0072] On the offset surface 30 formed by the center points M1, M2 and the rotation axis of the bearing shell, there is exactly one radial offset 31 in the circumferential direction at the transition L1 between the second surface portion 20a of the second, unloaded sliding surface 20 and the first surface portion 10a of the first, loaded sliding surface 10. In the side view of the bearing shell described above, as a result of the radii R1, R2 and the eccentricity e1 of the first surface portion 10a, a continuous transition portion 32, L2 without a radial offset is formed on the opposite side.

[0073] A further lubrication pocket 7 having an opening 6 in the first surface portion 10a is pivoted outward from the offset surface 30, and the circumferential angle θ from the offset surface 30 having a radial offset 31 to the starting end of the lubrication pocket 7 is between 5° and 35°.

[0074] The inner bearing surface 3 is set back radially and axially from the edge of the end face of the second sliding surface 20 by two radial recesses 35, both of which extend circumferentially around the shaft over the entire circumference of the second, unloaded sliding surface 20 (part 35a), and at their angular extensions 35b, they each form an angle α beyond the radial offset 31 in the circumferential direction, and in this embodiment, this angle α is smaller than the angle θ between the offset surface and the starting end of the lubrication pocket 7 in the circumferential direction. In modified examples, angle α may be the same as or greater than angle θ.

[0075] In this disclosure, "having X" generally does not mean an exclusive enumeration, but is an abbreviation of "having at least one X," and also includes "having two or more Xs" and "having Y in addition to X." While the above description refers to exemplary embodiments, it should be noted that many variations are possible. Furthermore, it should be noted that the embodiments are merely examples and do not limit the scope of protection, uses, or configurations. Rather, the above description provides guidance on the implementation of at least one exemplary embodiment, and in particular, various modifications can be made with respect to the function and arrangement of the described components without departing from the scope of protection obtained from the claims and combinations of features equivalent to the claims. [Explanation of symbols]

[0076] 1. Hydrodynamic sliding bearings 2 Bearing shell 3. Bearing surfaces (inner and outer) 4 rotors 5. Rotor rotation direction 6 openings 7 pockets 8 openings 9 pockets 10 The first sliding surface to which a load is applied 10a First (loaded) surface portion 20. Second, the sliding surface to which no load is applied. 20a Second (unloaded) surface portion 21 Supply groove 22 Distribution groove 23 keyways 24 sides 25 Outflow edge 30 Offset surface 31 Radial offset 32 Continuous transitions 35 Radial recess 35a The second, radially recessed portion of the sliding surface to which no load is applied. 35b The first portion of the radial recess in the sliding surface to which the load is applied. F Rated load vector L1 boundary line: End of the second, unloaded sliding surface / Start of the first, loaded sliding surface L2 boundary line: End of the first, loaded sliding surface / Start of the second, unloaded sliding surface R0 is the radius of the circle on the outer cylindrical surface of the bearing shell or theoretical bearing shell. R1 Radius of the arc of the first face portion R2 Radius of the arc of the second face portion Rk radius of the keyway arc M0 Bearing shell, especially the center point of the circle on the outer cylindrical surface of the theoretical bearing shell. M1 Center point of the arc of the first surface portion M2 Center point of the arc of the second face portion Center point of the arc of the Mk keyway e1 Eccentricity of the arc of the first surface portion ek Keyway eccentricity α is the angle between the offset plane and the end of the recess. θ is the angle between the offset plane and the start of the further pocket.

Claims

1. A hydrodynamic sliding bearing (1) for supporting a rotor (4), comprising a bearing body (2) having 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), The first sliding surface (10) has at least one first surface portion (10a), the first surface portion is offset eccentrically with respect to the center point (M0) of the bearing body. The second sliding surface (20) has at least one second surface portion (20a), a) The second surface portion (20a) has an arc with radius (R2) in at least one axial cross-section, the center point (M2) of the arc is not offset with respect to the center point (M0) of the bearing body, and / or b) The second surface portion (20a) comprises at least, b1) At least one opening (8) in the pocket (9) for supplying lubricant and / or coolant; b2) A keyway (23) having at least one portion (24), wherein the radial depth of the portion decreases particularly continuously in the circumferential direction to the outflow edge (25) of the second sliding surface (20); b3) Having a connecting portion (21) for supplying lubricant and / or coolant from the pocket (9) to the keyway (23), Hydrodynamic sliding bearing (1).

2. The aforementioned connection part, - At least one supply groove (21) connected to the pocket (8) and having a width at least partially in the axial direction smaller than the width of the pocket (8) and / or the keyway (23) in the axial direction; and / or - At least one distribution groove (22) having a width in the axial direction greater than the width of the supply groove (21), particularly connected to the keyway (23) and / or the supply groove (21); A sliding bearing (1) according to claim 1, characterized by having the following features.

3. - The first surface portion (10a) has an arc with radius (R1) in at least one axial cross-section, and the center point (M1) of the arc is eccentrically offset with respect to the center point (M0) of the bearing body; and / or, - A sliding bearing (1) according to claim 1 or 2, wherein the portion (24) of the keyway (23) in which the radial depth decreases to the outflow edge (25) has an arc with radius (Rk) in at least one axial cross section, and the center point (Mk) of the arc has an eccentricity (ek) with respect to the center point (M0) of the bearing body, thereby the radial depth decreases particularly continuously in the circumferential direction to the outflow edge.

4. A sliding bearing (1) according to any one of claims 1 to 3, characterized by a continuous transition portion (32) between an arc having the radius (R1) of the first surface portion (10a) and an arc having the radius (R2) of the second surface portion (20a).

5. A sliding bearing (1) according to any one of claims 1 to 4, characterized in that, in the offset surface (30) formed by the shaft of the bearing body and the center point (M1) of an arc having radius (R1) of the first surface portion (10a) and / or the center point (M2) of an arc having radius (R2) of the second surface portion (20a), there is exactly one radial offset (31) in the circumferential direction at the transition from the second surface portion (20a) to the first surface portion (10a).

6. The sliding bearing (1) according to any one of claims 1 to 5, characterized in that the first surface portion (10a) has at least one opening (6) in a further pocket (7) for supplying a lubricant and / or coolant.

7. A sliding bearing (1) according to any one of claims 1 to 6, characterized in that the starting end of a further pocket (7) located closer to the second surface portion (20a) in the circumferential direction is pivoted at an angle (θ) of at least 5° and / or up to 35° in the circumferential direction with respect to the radial offset (31) between the first surface portion (10a) and the second surface portion (20a).

8. A sliding bearing (1) according to any one of claims 1 to 7, characterized in that the inner bearing surface (3) is set back radially and axially by at least two radial recesses (35), and at least one of the recesses extends in the circumferential direction over at least the entire circumference of the second sliding surface (20) and / or over at least one radial offset (31) between the first surface portion (10a) and the second surface portion (20a).

9. The sliding bearing (1) according to claims 7 and 8, characterized in that at least one recess extends within the first sliding surface (10) over an angle (α) in the circumferential direction from a radial offset (31) between the first surface portion (10a) and the second surface portion (20a) such that the starting end of the further pocket (7) is less than or equal to the angle (θ) at which it pivots with respect to the radial offset (31).

10. The sliding bearing (1) according to claims 7 and 8, characterized in that the recess extends within the first sliding surface (10) in the circumferential direction from a radial offset (31) between the first surface portion (10a) and the second surface portion (20a) by an angle (α) greater than the angle (θ) at which the starting end of the further pocket (7) is pivoted with respect to the radial offset (31).

11. A rotor assembly, particularly a gear, comprising at least one sliding bearing (1) according to any one of claims 1 to 10, and a rotor supported by the sliding bearing.

12. Use of a sliding bearing (1) according to any one of claims 1 to 10 for supporting the rotor (4).

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