Slide bearing bushing for slide bearing with improved load capacity

Abstract

The invention relates to a plain bearing bush (10) comprising a cylindrical body (11) having a first housing surface (12) and a second housing surface (14). The plain bearing bush (10) comprises a plurality of exchange holes (20) for a lubricant (30), wherein at least one exchange hole (20) has a first diameter (27) on the first housing surface (12) and a second diameter (29) on the second housing surface (14). The second diameter (29) is greater than the first diameter (27) to increase a load capacity (56) of the plain bearing bush (10). Two axially spaced exchange holes (20) are connected to each other on the second housing surface (14) by a pocket-like recess (28). The invention also relates to a plain bearing (40) provided with a plain bearing bush (10) of this type, and to a planetary transmission (50) having a plain bearing (40) of this type. The invention also relates to a wind farm (60) and an industrial application (70), respectively, having a planetary transmission (50) of this type. Furthermore, the invention relates to a computer program product (80) by means of which an operating behavior of a plain bearing bush (10) according to the invention can be simulated.

Description

Technical Field

[0001] This invention relates to a sliding bearing bushing that improves the load-bearing capacity of a sliding bearing. The invention also relates to a corresponding sliding bearing and a planetary gearbox equipped with this type of sliding bearing. Furthermore, the invention relates to a wind power plant and an industrial application, each featuring this type of planetary gearbox. Finally, the invention relates to a computer program product that can simulate the operational behavior of the corresponding sliding bearing bushing. Background Technology

[0002] Document DE 29 45 821 A1 discloses a bearing comprising a support body in which a floating bushing is rotatably disposed. A shaft is rotatably housed within the floating bushing. The floating bushing has a radially oriented channel through which oil can be supplied. The channel is widened on the side facing the oil supply.

[0003] Patent publication DE 35 37 449 A1 discloses a bearing system with a floating bushing having a radial bore through which oil can be supplied to a rotatably mounted shaft. Here, the radial bore is widened at the end facing the oil supply.

[0004] US4 371 219A discloses a cylindrical sliding bearing bushing having a lubricant exchange hole extending in a radial direction, wherein, in the case of the sliding bearing bushing, the exchange hole has a larger diameter on the radial outer shell surface of the sliding bearing bushing than on the radial inner shell surface of the sliding bearing bushing.

[0005] CN105 134 780A has disclosed a cylindrical sliding bearing bushing having a radially extending exchange hole for lubricant, wherein, in the case of the cylindrical sliding bearing bushing, the exchange hole has a larger diameter on the radial inner housing surface of the sliding bearing bushing than on the radial outer housing surface of the sliding bearing bushing.

[0006] DE 10 2017 216 192 A1 discloses a radial sliding bearing for mounting a shaft, wherein the radial sliding bearing has a cylindrical sliding bearing bushing having an exchange hole for lubricant extending radially.

[0007] DE 10 2017 223 390 A1 has disclosed a radial sliding bearing for a shaft used in mounting a gearbox in a wind farm, wherein the radial sliding bearing has a cylindrical sliding bearing bushing. Summary of the Invention

[0008] Sliding bearings are used in a variety of applications requiring high bearing load capacity, minimal bearing friction loss, and long bearing service life. There is also a need for simple and cost-effective production of this type of sliding bearing. An improved sliding bearing is required that provides at least one of the above objectives.

[0009] The stated objective is achieved by the sliding bearing bushing according to the invention. Preferred improvements are given in the following description, which may represent an aspect of the invention individually or in combination. If one feature is shown in combination with another feature, this is only for the purpose of simplifying the description of the invention and in no way implies that the feature cannot be an improvement of the invention even without the other feature.

[0010] The sliding bearing bushing according to the invention comprises a cylindrical body. The cylindrical body has a first housing surface and a second housing surface. The first and second housing surfaces are connected to each other via a plurality of supply holes, allowing lubricant to be transferred from the first housing surface to the second housing surface and vice versa. At least one of the exchange holes has a first diameter on the first housing surface and a second diameter on the second housing surface. Here, the diameter should be understood as a dimension substantially perpendicular to the flow direction of the lubricant. The second diameter is larger than the first diameter. Consequently, the flow velocity of the lubricant on the second housing surface is lower than that on the first housing surface. Furthermore, there is an increased flow drag force in the region of the exchange hole with the second diameter. Therefore, the lubricant has a higher drag effect on the sliding bearing bushing. This increased drag effect, in turn, allows for a higher lubrication clearance height. Thus, the increased load-carrying capacity of the sliding bearing, in which the sliding bearing bushing is used, is achieved by the second diameter, which is larger than the first diameter. Exchange holes of different diameters can be manufactured on the first and second housing surfaces in a simple manner. By changing the geometry, the drag effect is increased, enhancing the load-carrying capacity.

[0011] In the claimed sliding bearing bushing, at least one exchange hole is arranged axially offset relative to the lubricant inlet. Here, axial direction should be understood as a direction substantially parallel to the main rotation axis of the sliding bearing bushing. The lubricant inlet is constructed in the component of the sliding bearing opposite to the sliding bearing bushing. Therefore, the lubricant conducted through the at least one exchange hole flows along the surface of the first housing before reaching the at least one exchange hole. The exchange hole is correspondingly arranged such that the lubricant is output in a layered manner on the surface of the second housing. Specifically, the exchange hole may be axially offset relative to the main hole, which has a larger diameter than the exchange hole, and is arranged substantially opposite to the lubricant inlet.

[0012] Furthermore, at least two, and especially three or more, axially spaced exchange holes on the second housing surface, particularly the outer surface of the body, are connected to each other via pouch-like recesses. In the region of the pouch-like recesses, the flow velocity of the lubricant is further reduced, resulting in additional flow drag, which in turn leads to a further increase in drag force on the sliding bearing bush. The pouch-like recesses can be created by non-cutting or cutting machining methods and / or by mechanical and / or chemical action. Specifically, they can be created by milling, etching, or corrosion. The pouch-like recesses further enhance the load-bearing capacity of the claimed sliding bearing bush. Furthermore, multiple pouch-like recesses can be constructed on the second housing surface, arranged circumferentially to form an arrowhead pattern or an arcuate pattern. For example, the pouch-like recesses can be oriented in such a way that arrowheads pointing in the direction of circulation or opposite to the direction of circulation are indicated on the second housing surface in the central region of the sliding bearing bush. The arrowhead pattern can be configured along or opposite to the intended direction of rotation of the sliding bearing bush. Therefore, improved lubricant supply can be achieved on the second housing surface, and more uniform operation of the sliding bearing bushing can be ensured.

[0013] The pouch-like recesses can be configured as, for example, channels and / or grooves opening away from the surface of the first housing. The pouch-like recesses can have, for example, an inverted round (particularly substantially U-shaped) or rectangular flow cross-section in the direction of the exchange holes interconnected via the pouch-like recesses. For example, each pouch-like recess extends at an oblique angle relative to the axial and circumferential directions of the body, along a substantially constant radius relative to the axial centerline of the cylindrical body. Specifically, at least a portion, preferably all, of the pouch-like recesses located in the common axial region of the body extend parallel to each other in the unfolded view of the body. In one embodiment of the claimed sliding bearing bushing, at least two circumferentially successive pouch-like recesses are interconnected to exchange lubricant. The interconnected pouch-like recesses can extend at an angle to each other, wherein, in particular, one exchange hole opens into one pouch-like recess and the other. Preferably, the common exchange hole is located at the apex of an imaginary angle of the pouch-like recesses interconnected at an angle. As a result, the interconnected bag-shaped recesses can form a zigzag pattern, which is preferably a closed structure in the circumferential direction.

[0014] In one embodiment of the claimed sliding bearing bushing, the first housing surface is the side of the sliding bearing bushing facing the lubricant supply section. Therefore, the second housing surface is the side of the sliding bearing bushing away from the lubricant supply section. During normal operation, lubricant can be transferred from the first housing surface to the second housing surface through an exchange hole. During normal operation of the sliding bearing equipped with the claimed sliding bearing bushing, the lubrication clearance of the sliding bearing is disposed on the second housing surface. The second diameter of the lubricant on the second housing surface through at least one exchange hole increases the liquid drag force in the lubricant, and due to this liquid drag force, more lubricant is delivered to the lubrication clearance. The lubrication clearance can be configured as an internal lubrication clearance and / or an external lubrication clearance. Both internal and external lubrication clearances increase the lubricating film height. As a result, the effectiveness of the claimed sliding bearing bushing is improved.

[0015] Furthermore, the second diameter can be constructed using countersunk recesses and / or stepped bores. Since countersunk recesses are essentially conical in shape, the lubricant flow rate can be reduced substantially continuously. Countersunk recesses can be manufactured precisely and economically in a simple manner using countersunk tools. Stepped bores (i.e., interchangeable bores with different diameters in different sections) can also be manufactured quickly and cost-effectively. Boreholes of different diameters can be manufactured with greater precision, allowing the reduction in lubricant flow rate to be set accordingly precisely based on the ratio between the first and second diameters. Therefore, the sliding bearing bushing to be protected can be easily adapted to different applications. Countersunk recesses or stepped bores can also be combined to achieve their respective advantages in a combined manner.

[0016] In another embodiment of the claimed sliding bearing bushing, the second diameter of the exchange bore can correspond to 1.05 to 6.00 times the first diameter. As a result, a favorable reduction in lubricant flow velocity is achieved on the second housing surface, generating a flow drag force. Consequently, the drag effect of the lubricant on the sliding bearing bushing is correspondingly increased. Simultaneously, the corresponding second diameter provides smooth operation for the claimed sliding bearing bushing.

[0017] Furthermore, the claimed sliding bearing bushing can be configured as a floating bushing. The floating bushing is positioned between the stationary and rotating parts of the sliding bearing, creating internal and external lubrication clearances between them. Because the sliding bearing bushing is subjected to increased drag during normal operation, it follows the rotational movement of the rotating part more quickly. Therefore, the height of the lubrication clearance in the internal and / or external lubrication clearances is increased, thereby also increasing the load-carrying capacity of the sliding bearing. Due to the presence of both internal and external lubrication clearances in the case of a floating bushing, a particularly increased load-carrying capacity is achieved by the claimed sliding bearing bushing. In particular, the damping effect in the lubrication clearances is improved, and improved load distribution is achieved in the case of axial distance deviation. Improved start-up behavior after shutdown is also achieved, and the temperature is reduced during operation.

[0018] In another embodiment of the claimed sliding bearing bushing, at least one exchange orifice includes an outlet portion having a second diameter, at least segmented. The outlet portion opens onto a second housing surface. The length of the outlet portion is 10% to 100% of the orifice length of the exchange orifice. Correspondingly, at least one exchange orifice includes an inlet portion extending from a first housing surface through the sliding bearing bushing and merging into or adjacent to the outlet portion. The at least one exchange orifice has a first diameter at the inlet portion. The longer the outlet portion, the greater the reduction in lubricant flow velocity that can be achieved, while avoiding the formation of turbulence in the lubricant. Therefore, uniform discharge of lubricant onto the second housing surface can be achieved. This applies both to outlet portions with a second diameter constructed by countersunk recesses and to outlet portions with a second diameter constructed by stepped bores.

[0019] Furthermore, the countersunk recess, which forms a second diameter for at least one exchange hole, can have an opening angle ranging from 45° to 135°. This results in a particularly advantageous reduction in lubricant flow velocity. This type of opening angle can be quickly and economically produced in a simple manner using a correspondingly shaped countersunk tool.

[0020] The objective of this invention is also achieved by a sliding bearing according to the invention. This sliding bearing includes a rotating component rotatably mounted on a sliding bearing bushing. The sliding bearing also includes a stationary component. According to the invention, the sliding bearing bushing is constructed according to one of the above embodiments. Due to the use of this type of sliding bearing bushing, the sliding bearing has an increased load-carrying capacity. In particular, the claimed bearing can have a Sommerfeld number from 0.10 to 10.00. Therefore, the claimed sliding bearing provides load-carrying capacity, and thus also provides a load-carrying capacity reserve, thereby opening up challenging application areas, such as in planetary gearboxes of rock crushers or cement mills.

[0021] Furthermore, the objectives outlined at the beginning of this document are achieved by means of a planetary transmission according to the invention. The planetary transmission includes a planet carrier to which a plurality of planetary gears are rotatably attached. Here, in each case, the planetary gears are rotatably mounted on the planet carrier via sliding bearings. According to the invention, at least one of the sliding bearings is configured according to the embodiment shown above.

[0022] Similarly, the objective upon which this invention is based is achieved through a wind power plant according to the invention. This wind power plant includes a nacelle on which a multi-bladed rotor is rotatably mounted. A drive system comprising a planetary gearbox is disposed within the nacelle, the planetary gearbox being connected to the multi-bladed rotor and the generator in a torque-transmitting manner. According to the invention, the planetary gearbox is configured according to one of the above embodiments.

[0023] The stated objective is also achieved through an industrial application according to the invention, comprising a drive unit and an output unit. The drive unit and output unit are connected to each other via a planetary gearbox in a torque-transmitting manner. The drive unit is configured as, for example, an electric motor, an internal combustion engine, or a hydraulic motor, and provides the drive power to be transmitted to the output unit via the planetary gearbox. The output unit can be configured as, for example, a mill, vertical mill, sugar mill, cement mill, crusher, conveyor belt, pump, roller press, plate conveyor, tube mill, rotary kiln, rotary device, mixing unit, lifting equipment, waste compactor, or vehicle crusher. For this purpose, the output unit is connected to the drive unit via the planetary gearbox. According to the invention, the gearbox is configured according to one of the above embodiments. Due to the claimed sliding bearing bushing, the planetary gearbox according to the invention has increased load-bearing capacity and reliability. As a result, the maintenance complexity of the planetary gearbox is reduced, thereby improving the economic efficiency of the industrial application according to the invention.

[0024] The objective described at the beginning of this document is also achieved by a computer program product according to the invention, which can simulate the operational behavior of a sliding bearing bushing in a sliding bearing. Here, at least one lubrication clearance, such as an internal lubrication clearance and / or an external lubrication clearance, is simulated, which is configured on the sliding bearing due to rotational motion. Specifically, the current lubrication clearance height can be simulated in a manner dependent on the current operating state. For this purpose, the computer program product may include runnable simulation routines for hydrodynamic mechanisms and data interfaces (via which operating parameters such as rotational speed, lubricant temperature, or radial load of the sliding bearing can be specified), or may output simulation results. The computer program product includes a dataset through which at least the sliding bearing bushing is modeled. According to the invention, the sliding bearing bushing is configured according to one of the above embodiments. By means of the computer program product according to the invention, the load-carrying capacity present in a sliding bearing having a sliding bearing bushing can be predicted, or at least its feasibility can be tested. Furthermore, the sliding bearing bushing according to the invention can be adjusted in design by the computer program product according to the invention, thereby easily optimizing the sliding bearing. For this purpose, the computer program product can be configured, for example, as a so-called digital twin. For example, this type of digital twin is illustrated in patent publication US2017 / 286572A1. The disclosure of US2017 / 286572A1 is incorporated herein by reference. Attached Figure Description

[0025] In the following text, the invention will be explained in more detail with reference to the various embodiments shown in the accompanying drawings. These drawings should be considered complementary, such that the same reference numerals have the same technical meaning in different drawings. Features of the various embodiments can also be combined with each other. Furthermore, the embodiments shown in the drawings can be combined with the features outlined above. The drawings are shown in detail below:

[0026] Figure 1 A first embodiment of the claimed sliding bearing bushing is shown in oblique view;

[0027] Figure 2 A first embodiment of the sliding bearing bushing requiring protection is shown in longitudinal section.

[0028] Figure 3 A first embodiment of the sliding bearing bushing requiring protection is shown in cross-sectional detail;

[0029] Figure 4 A second embodiment of the sliding bearing bushing requiring protection is shown in sectional detail;

[0030] Figure 5The structure of one embodiment of the claimed sliding bearing is schematically shown, wherein the sliding bearing has the sliding bearing bushing of the third embodiment;

[0031] Figure 6 The structure of one embodiment of the claimed wind farm is shown in a sectional oblique view, and...

[0032] Figure 7 The structure of one embodiment of the claimed industrial application is shown. Detailed Implementation

[0033] Figure 1 A first embodiment of the claimed sliding bearing bushing 10 is shown. The sliding bearing bushing 10 includes a generally cylindrical body 11 having a first housing surface 12 configured as an inner surface 17. Correspondingly, the sliding bearing bushing 10 also has a second housing surface 14 configured as an outer surface 19. The sliding bearing bushing 10 can be used in a sliding bearing 40, which, in its operation, rotates 25 about a main axis of rotation 15. The main axis of rotation 15 is also the axis of symmetry of the sliding bearing bushing 10. In operation of the sliding bearing 40, the sliding bearing bushing 10 is supplied with lubricant 30. The lubricant 30 is provided via a lubricant supply section 33 on the side of the first housing surface 12 (i.e., the inner side 17) and delivered via a main bore 16 to the second housing surface 14 (i.e., the outer surface 19). The main bores 16 are configured to be substantially uniformly and circumferentially spaced in an axial intermediate region 23 on the sliding bearing bushing 10. The sliding bearing bushing 10 has a plurality of exchange holes 20 spaced axially 32 apart, the diameter of which is generally smaller than that of the main bore 16. The exchange holes 20 are also configured to be substantially uniformly spaced in the circumferential direction 24. Furthermore, the exchange holes 16 are arranged in such a way that they interact with one main bore 16 in each case to form an arrow pattern 26. Corresponding to the arrow pattern 26, two exchange holes 20 on the second housing surface 14 are paired and connected to each other by a pouch-shaped recess 28. During operation of the sliding bearing 40, the exchange holes 20 are configured to allow lubricant 30 to pass radially 34, thereby wetting the second housing surface 14 with lubricant 30. Wetting of the second housing surface 14 is aided by the pouch-shaped recess 28.

[0034] Apart from Figure 1 , Figure 2A first embodiment of the claimed sliding bearing bushing 10 is also shown in a longitudinal sectional view. On the first housing surface 12, i.e., the inner side 17, at least one of the exchange holes 20 has a first diameter 27 into which lubricant 30 enters during normal operation of the sliding bearing 40. On the second housing surface 14, i.e., the outer surface 19, the at least one exchange hole 20 has a second diameter 29 larger than the first diameter 27. The flow velocity 31 of the lubricant 30 decreases as it passes through the at least one exchange hole 20. The difference in the flow velocity 31 of the lubricant 30... Figure 2 The image is illustrated by arrows of varying lengths. In the region of the second housing surface 14, at least one exchange hole 20 has a countersunk recess 36, which increases the flow cross-section in the exchange hole 20, thereby reducing the flow velocity 31.

[0035] according to Figure 1 and Figure 2 The first embodiment of the claimed sliding bearing bushing 10 is in Figure 3 The detailed view shown in the cross-sectional view is as follows. The exchange hole 20 is configured as a countersunk recess 36 having an inlet portion 35 and an outlet portion 39, wherein the inlet portion 35 has a first diameter 27, and the outlet portion 39 is adjacent to or incorporated into the inlet portion 35 and has a second diameter 29 in the region of the second housing surface 14. The length 43 of the outlet portion 39 is equivalent to 10% to 100% of the orifice length 41 of the exchange hole 20. The length 43 of the outlet portion 39 is essentially the radial dimension 34 of the countersunk recess 36. This type of length 43 of the outlet portion 39 will sufficiently reduce the flow velocity 31 of the lubricant 30, thereby causing a drag force 45 to be generated on the sliding bearing bush 10 on the second housing surface 14. The drag force 45 produces a dragging effect, by which the sliding bearing bush 10 follows the rotational movement 25 of the sliding bearing 40. The increased drag force 45 is generated by the second diameter 39, the opening angle 37, and the length 43 of the outlet portion 39. The countersunk recess 36 can be made in a cost-effective manner using a countersunk tool.

[0036] The second embodiment of the claimed sliding bearing bushing 10 is in Figure 4 The detailed view is shown in the cross-sectional view. According to... Figure 4 The embodiments can also be based on Figure 1 , Figure 2 and Figure 3The embodiments are combined. The exchange orifice 20 is essentially constructed as a stepped orifice 38 and has an inlet portion 35 and an outlet portion 39, wherein the inlet portion 35 has a first diameter 27, and the outlet portion 39 is adjacent to or incorporated into the inlet portion 35 and has a second diameter 29. The length 43 of the outlet portion 39 corresponds to 10% to 100% of the orifice length 47 of the exchange orifice 20. The length 43 of the outlet portion 39 is essentially the radial dimension 34 of the stepped orifice 38. This type of length 43 of the outlet portion 39 will sufficiently reduce the flow velocity 31 of the lubricant 30, thereby causing a drag force 45 to be generated on the sliding bearing bushing 10 on the second housing surface 14. The drag force 45 generates a dragging action, through which the sliding bearing bushing 10 follows the rotational movement 25 of the sliding bearing 40. The increased drag force 45 is generated by the second diameter 39 and length 43 of the outlet portion 39.

[0037] Figure 5 An embodiment of the claimed sliding bearing 40 used in a planetary transmission 50 (not shown in more detail) is schematically shown in cross-section. The sliding bearing 40 includes a planetary gear 46 as a rotating component 42, rotatably arranged on a planet carrier 55 of the planetary transmission 50. Furthermore, the sliding bearing 40 includes a shaft 48 as a stationary component 44, which is fixedly connected to the planet carrier 55 for mutual rotation. Lubricant 30 is supplied to the sliding bearing 40 via the stationary component 44 through a lubricant supply section 33. The lubricant supply section 44 is configured as a lubricant channel (not shown in detail). The sliding bearing 40 also includes a sliding bearing bushing 10 configured as a floating bushing 53. The sliding bearing bushing 10 is disposed between the stationary component 44 and the rotating component 42, thereby forming a lubricant gap 49 between them in each case. Lubricant 30 is delivered into the external lubrication gap 54 between the sliding bearing bushing 10 and the rotating component 42 by the rotational movement 25 of the rotating component 42. A lubrication gap height 51 is created at the external lubrication gap 54 according to the speed of the rotational motion 25. The sliding bearing bush 10 is provided with an exchange hole 20 through which lubricant 30 exits in the region of the external lubrication gap 54. As a result, a dragging force 45 (i.e., a dragging effect) is applied to the sliding bearing bush 10, thereby causing the sliding bearing bush 10 to more closely follow the rotational motion 25 of the rotating component 42. The rotational speed 18 of the sliding bearing bush generated in this way is lower than the rotational speed 21 of the rotating component 42. An internal lubrication gap 52 is formed between the stationary component 44 and the sliding bearing bush 10, and this internal lubrication gap 52 has a lubrication gap height 51 according to the rotational speed 21 of the sliding bearing bush. The sliding bearing bush 10 is provided with an exchange hole 20, such as... Figure 3 or Figure 4As shown, the result is that during normal operation of the sliding bearing 40, an increased drag force 45 is applied to the sliding bearing bush 10 in the external lubrication gap 54. Consequently, the lubrication film height 51 is increased at the external lubrication gap 54 and / or the internal lubrication gap 52. The higher the lubrication gap height 51 at the internal lubrication gap 52 and / or the external lubrication gap 54, the higher the load-carrying capacity 56 of the sliding bearing 40. The load-carrying capacity 56 is a measure of the magnitude of the radial load 58 that the sliding bearing 40 can load during normal use. The claimed protected sliding bearing bush 10, constructed as a floating bushing 53, increases the load-carrying capacity 56 of the sliding bearing 40. If the flow direction of the lubricant 30 is temporarily reversed, the same effect can be achieved in the case of the internal lubrication gap 52 as in the case of the external lubrication gap 54. Furthermore, the sliding bearing bush 10 is modeled in a computer program product 80 configured to simulate the operating behavior of the sliding bearing bush 10 during the operation of the sliding bearing 40.

[0038] Figure 6 A cross-sectional perspective view of an exemplary embodiment of the claimed wind farm 60 is shown, including a nacelle 61 to which a multi-bladed rotor 62 is rotatably attached. A drivetrain 66 of the wind farm 60 is housed within the nacelle 61, the drivetrain 66 including a main shaft 63 connected to the multi-bladed rotor 62 in a torque-transmitting manner. The drivetrain 66 also includes a generator 64, which is connected to the main shaft 63 via a gearbox 65 in a torque-transmitting manner. Here, the gearbox 65 is configured as a planetary gearbox 50 according to one of the embodiments described above.

[0039] Figure 7 An embodiment of the claimed industrial application 70 is schematically illustrated. The industrial application 70 includes an output unit 72, which can be configured as, for example, an electric motor, a wind turbine, an internal combustion engine, or a hydraulic motor. Drive power (i.e., rotational motion 25) is provided via the drive unit 72, and the drive power is fed to a transmission 75. The drive power is fed to the output unit 74 via a conversion between the current speed and the current torque. The output unit 74 can be configured as, for example, a mechanical application, resulting in the industrial application 70 being configured as a mill, vertical mill, sugar mill, cement mill, crusher, conveyor belt, pump, roller press, plate conveyor, tube mill, rotary kiln, rotary device, mixing unit, mixing crusher, lifting equipment, waste compactor, or vehicle crusher. According to the invention, the drive unit 72, connected thereto to the transmission 75 of the output unit 74, is configured as a planetary transmission 50 according to one of the above embodiments. Therefore, the transmission 75 is provided with at least one sliding bearing 40 according to one of the above embodiments, and has a sliding bearing bushing 10 according to at least one of the above embodiments.

Claims

1. A sliding bearing bushing (10) comprising a cylindrical body (11) having a first housing surface (12) and a second housing surface (14), the cylindrical body (11) having a plurality of exchange holes (20) for lubricant (30), at least one of the exchange holes (20) having a first diameter (27) on the first housing surface (12) and a second diameter (29) on the second housing surface (14), the second diameter (29) being larger than the first diameter (27) to improve the load-bearing capacity (56) of the sliding bearing bushing (10), characterized in that, Two exchange holes (20) spaced apart axially on the second housing surface (14) are connected to each other by a bag-shaped recess (28).

2. The sliding bearing bushing (10) as described in claim 1, characterized in that, The first housing surface (12) is the side of the sliding bearing bush (10) facing the lubricant supply section (33).

3. The sliding bearing bushing (10) as described in claim 1 or 2, characterized in that, The second diameter (29) is constructed by countersunk recess (36) or stepped hole (38).

4. The sliding bearing bushing (10) as described in claim 3, characterized in that, The countersunk recess (36) has an opening angle (37) of 45° to 135°.

5. The sliding bearing bushing (10) as described in claim 1 or 2, characterized in that, The corresponding bag-shaped recess (28) extends at a radius that is substantially constant relative to the axial centerline of the body (11) in an axial and circumferential manner relative to the body (11).

6. The sliding bearing bushing (10) as described in claim 1 or 2, characterized in that, The structure has multiple bag-shaped recesses (28), which are arranged in a circumferential arrow pattern (26) or a zigzag pattern.

7. The sliding bearing bushing (10) as described in claim 1 or 2, characterized in that, The second diameter (29) is 1.05 to 6.00 times the first diameter (27).

8. The sliding bearing bushing (10) as described in claim 1 or 2, characterized in that, The sliding bearing bushing (10) is configured as a floating bushing (53).

9. The sliding bearing bushing (10) as described in claim 1 or 2, characterized in that, The outlet portion (39) of at least one of the exchange holes (20) having a second diameter (29) is configured to be 10% to 100% of the hole length (41) of at least one of the exchange holes (20).

10. A sliding bearing (40) comprising a stationary component (44) and a rotating component (42), wherein the stationary component (44) is provided with a sliding bearing bushing (10) as claimed in any one of claims 1 to 9, and the rotating component (42) is rotatably attached to the sliding bearing bushing (10).

11. The sliding bearing (40) as claimed in claim 10, characterized in that, The sliding bearing (40) has a Somerfield number ranging from 0.10 to 10.

00.

12. A planetary transmission (50) comprising a planet carrier (55) in which a plurality of planetary gears (46) are rotatably arranged using a sliding bearing (40) as claimed in claim 10 or 11 in each case.

13. A wind power plant (60) includes a nacelle (61) in which a transmission (65) is connected to a generator (64) in a torque-transmitting manner, the transmission (65) being configured as a planetary transmission (50) as claimed in claim 12.

14. An industrial application device comprising a drive unit (72) and an output unit (74) connected to each other via a transmission (75), the transmission (75) being configured as a planetary transmission (50) as claimed in claim 12.

15. A computer program product (80) for simulating the operational behavior of a sliding bearing bushing (10) disposed in a sliding bearing (40) as described in any one of claims 1 to 9.

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