Hydrodynamic sliding bearing assembly and hydrodynamic sliding bearing unit

Abstract

A hydrodynamic sliding bearing assembly and a hydrodynamic sliding bearing unit. The hydrodynamic sliding bearing assembly is adapted to be arranged radially between a first member (10) and a second member (20) that can rotate relative to each other, wherein the first member (10) has an inner peripheral surface for surrounding the second member (20), and a boss portion (101) is formed at the inner peripheral surface. The hydrodynamic sliding bearing assembly includes two hydrodynamic sliding bearings (40, 50; 70, 80), which can be fixed to the second member (20) concentrically and axially arranged such that the boss portion (101) is axially received between the two hydrodynamic sliding bearings (40, 50; 70, 80). The outer peripheral surfaces and the axially adjacent end faces of the respective hydrodynamic sliding bearings (40, 50; 70, 80) are connected and transitioned through arc surfaces (405, 505; 705, 805).

Description

Technical Field

[0001] The present application relates to the field of bearings. Specifically, the present application relates to a hydrodynamic sliding bearing assembly and a hydrodynamic sliding bearing unit. Background Art

[0002] With the development of offshore wind power, large-megawatt wind turbines are the future development trend. At the same time, in order to reduce the cost per kilowatt-hour, more stringent requirements are imposed on the cost and operating reliability of the gearboxes of wind turbines.

[0003] Bearings are key components in the gearboxes of wind turbines. In current wind turbine gearboxes, rolling bearings are mostly used. Due to the existence of occasional axial loads, in solutions using radial bearings such as needle bearings, thrust bearings also need to be additionally provided at the shaft. Especially due to installation and manufacturing errors and shaft deflection caused by working loads, rolling bearings with angle adjustment capabilities are preferably used. For example, Chinese Patent Application Document CN 102792018 B discloses a gearbox for a wind turbine, in which the gearbox has a housing, a gear carrier, a planetary gear shaft held on the gear carrier, planetary gears respectively supported on the planetary gear shaft, and an annular gear and a central gear meshing with the planetary gears. In this solution, each planetary gear is supported on the corresponding planetary gear shaft by a rolling bearing configured as a self-aligning roller bearing.

[0004] However, on the one hand, with the development of wind power technology, the requirements for the size and load-carrying capacity of bearings are getting higher and higher. On the other hand, as mentioned above, the operating reliability of bearings is also very important. If the rolling bearings in the gearbox of a wind turbine fail, it will result in a waste of a large amount of maintenance time and cost. Summary of the Invention

[0005] Therefore, the purpose of the present application is to provide a bearing assembly that has good load-carrying capacity and low cost.

[0006] The above object is achieved in one aspect by a hydrodynamic sliding bearing assembly. The hydrodynamic sliding bearing assembly is used to be arranged radially between a first member and a second member that can rotate relative to each other, so as to support between the first member and the second member in a relatively rotatable manner. Herein, the first member has an inner peripheral surface for surrounding the second member, and a boss portion is formed at the inner peripheral surface of the first member. The hydrodynamic sliding bearing assembly includes two hydrodynamic sliding bearings, and the hydrodynamic sliding bearings can be fixed to the first member concentrically and axially arranged such that the boss portion of the first member is axially received between the hydrodynamic sliding bearings, and the outer peripheral surfaces and the axially adjacent end faces of the respective hydrodynamic sliding bearings are connected and transitioned through arc surfaces.

[0007] Within the scope of this text, the first component and the second component are arranged to be sleeved with each other and can rotate relative to each other about the same axis of rotation. The central axis of the hydrodynamic sliding bearing assembly coincides with the same axis of rotation of the first component and the second component herein. Therefore, unless otherwise instructed, the terms "radial", "axial", and "circumferential" all refer to the central axis of the hydrodynamic sliding bearing assembly.

[0008] Herein, the first component has a substantially annular hole, preferably a central hole, for surrounding the second component. Within the scope of this text, unless otherwise instructed, the inner peripheral surface of the first component refers to the inner peripheral surface of this hole, preferably the central hole. Herein, the first component may have a hole in the form of a through hole. Alternatively, the first component may also have a hole in the form of a blind hole. For example, the first component is a gear or a housing, etc.

[0009] In particular, a boss portion is formed at the inner peripheral surface of the hole of the first component, preferably the central hole, wherein the boss portion projects radially inward from the inner peripheral surface of the central hole. Preferably, the boss portion is formed as a continuous annular boss. Alternatively, the boss portion is formed discontinuously in the circumferential direction.

[0010] Herein, the second component at least partially has a substantially cylindrical outer peripheral surface and can be at least partially received in the hole of the first component, preferably the central hole, by means of this outer peripheral surface. The second component is, for example, an independent shaft member or a shaft portion formed on a component part.

[0011] Herein, the hydrodynamic sliding bearing assembly includes two hydrodynamic sliding bearings used in pairs, namely a first hydrodynamic sliding bearing and a second hydrodynamic sliding bearing. The hydrodynamic sliding bearings each have a substantially sleeve-like structure.

[0012] After assembly, the two hydrodynamic sliding bearings are fixed concentrically and axially arranged with their respective inner peripheral surfaces to the second component, preferably at the outer peripheral surface of the second component. Preferably, the two hydrodynamic sliding bearings respectively achieve a tight fit with the second component with their respective inner peripheral surfaces. Herein, the hydrodynamic sliding bearing assembly and the second component are jointly received in the hole of the first component in such a way that the boss portion of the first component can extend into the axial gap between the two hydrodynamic sliding bearings of the hydrodynamic sliding bearing assembly. In this case, the radial gap between the outer peripheral surfaces of the two hydrodynamic sliding bearings and the inner peripheral surface of the first component should be small enough to be able to generate a hydrodynamic pressure sufficient to radially support the first component in the hydraulic medium flowing through the radial gap. Similarly, the two axial gaps between the axially adjacent end faces of the two hydrodynamic sliding bearings and the axial end face of the boss portion of the first component should be small enough to be able to generate a hydrodynamic pressure sufficient to axially support the first component in the hydraulic medium flowing through the axial gap.

[0013] In this case, a hydraulic medium, preferably oil, can be conveyed into the hydrodynamic sliding bearing assembly, for example, under the action of a pump. The hydraulic medium can flow through the radial clearance between the outer peripheral surface of the hydrodynamic sliding bearing and the inner peripheral surface of the first member and through the axial clearance between the axially adjacent end faces of the two hydrodynamic sliding bearings and the axial end face of the boss portion of the first member. Thus, when the hydrodynamic sliding bearing assembly and the second member rotate relative to the first member together, a radial hydrodynamic bearing portion can be formed between the two hydrodynamic sliding bearings and the first member and an axial hydrodynamic bearing portion can be formed between the two hydrodynamic sliding bearings and the boss portion of the first member by means of the hydraulic medium. With this design, the hydrodynamic sliding bearing assembly can carry both radial loads and axial loads.

[0014] According to the solution proposed herein, the outer peripheral surface and the axially adjacent end faces of each hydrodynamic sliding bearing are respectively connected and transitioned by an arc surface. In other words, at the axial end of the first hydrodynamic sliding bearing close to the second hydrodynamic sliding bearing, the circumferential edge on the radially outer side of the first hydrodynamic sliding bearing is configured as an arc surface, for example, subjected to arc profiling, and at the axial end of the second hydrodynamic sliding bearing close to the first hydrodynamic sliding bearing, the circumferential edge on the radially outer side of the second hydrodynamic sliding bearing is configured as an arc surface, for example, subjected to arc profiling. Correspondingly, the inner peripheral surface of the first member and the two axial end faces of the boss portion are also preferably connected and transitioned by an arc surface. Thus, on the one hand, since the outer peripheral surface and the axially adjacent end faces of each hydrodynamic sliding bearing are respectively connected and transitioned by an arc surface, it is easy to form a hydraulic medium film axially between the hydrodynamic sliding bearing and the boss portion of the first member, which is beneficial for the hydrodynamic sliding bearing assembly to bear axial loads. On the other hand, when the first member, such as a gear, has an overturning moment, the hydrodynamic sliding bearing and the boss portion of the first member can achieve a self-aligning function by cooperating with each other through the arc surface, so as to adapt to the actual working conditions as much as possible.

[0015] According to a preferred embodiment, the respective outer peripheral surfaces and the axially adjacent end faces of the hydrodynamic sliding bearings are provided with a hardened coating. Here, by providing a hardened coating on the surface of the hydrodynamic sliding bearing for forming a hydraulic medium film, such as an oil film, the hydrodynamic sliding bearing, especially the above-mentioned surface, can be adapted to the dry friction and boundary friction between the hydrodynamic sliding bearing and the first member during the start-stop stage. Thereby, the wear resistance of the hydrodynamic sliding bearing can be improved.

[0016] According to a preferred embodiment, an axially extending hydraulic medium chamber is formed at the outer peripheral surface of the hydrodynamic sliding bearing. Optionally, particularly according to the radial dimension of the hydrodynamic sliding bearing, one, two, three or more hydraulic medium chambers may be formed at the outer peripheral surface of the hydrodynamic sliding bearing. Advantageously, the hydraulic medium chamber is arranged offset from the main load-bearing region of the hydrodynamic sliding bearing. Preferably, two hydraulic medium chambers are provided at the outer peripheral surface of the hydrodynamic sliding bearing. Particularly preferably, two radially opposed hydraulic medium chambers are provided at the outer peripheral surface of the hydrodynamic sliding bearing. This is advantageous for forming a hydraulic medium film axially over the entire outer peripheral surface of the hydrodynamic sliding bearing. In addition, since the radial clearance between the outer peripheral surface of the hydrodynamic sliding bearing and the inner peripheral surface of the first member is small, forming the hydraulic medium chamber at the outer peripheral surface of the hydrodynamic sliding bearing is advantageous for the rapid filling of the hydraulic medium into this radial clearance, so that when the first member and the second member start to rotate relative to each other, the dry friction and boundary friction between the hydrodynamic sliding bearing and the first member can be ended as quickly as possible.

[0017] Advantageously, the hydrodynamic sliding bearing is provided with a hydraulic medium inlet, and the hydraulic medium inlet communicates from the inner peripheral surface of the hydrodynamic sliding bearing to the hydraulic medium chamber. Preferably, the hydraulic medium inlet is formed as a through hole here, and the through hole penetrates the hydraulic medium chamber on the outer surface of the hydrodynamic sliding bearing and the inner surface of the hydrodynamic sliding bearing. Thus, the structure of the hydraulic medium inlet itself is simple and easy to manufacture. Correspondingly, the internal structure of the second member can be utilized to realize the input passage for supplying the hydraulic medium to the hydrodynamic sliding bearing assembly, specifically the hydraulic medium inlet. Thus, the hydraulic medium passage is simple and reliable, and the hydrodynamic sliding bearing assembly or the hydrodynamic sliding bearing unit can be realized with a simple structure and at a low cost.

[0018] Advantageously, the hydrodynamic sliding bearing is provided with a hydraulic medium outlet, and the hydraulic medium outlet communicates from the hydraulic medium chamber to the axially adjacent end faces of the hydrodynamic sliding bearing. Preferably, the hydraulic medium outlet is formed as a pressure relief groove here. Thus, the hydraulic medium can flow from the hydraulic medium chamber to between the axially adjacent end faces of the hydrodynamic sliding bearing and the axially end face of the boss portion of the first member through the hydraulic medium outlet, thereby forming an axial hydrodynamic support portion.

[0019] Here, in one embodiment, a spacer ring is arranged axially between the hydrodynamic sliding bearings, and the spacer ring is provided with an annular groove at its outer peripheral surface and a through hole communicating the annular groove and the inner peripheral surface of the spacer ring. Thus, the hydraulic medium flowing into the axial clearance between the two hydrodynamic sliding bearings through the hydraulic medium outlet can be collected in the annular groove of the spacer ring, and can be further discharged through the through hole to, for example, a hydraulic medium output passage located inside the second member.

[0020] Here, in another embodiment, annular axial protrusions are formed at the ends of the hydrodynamic journal bearing that are close to each other. The axial protrusions are arranged in the radially inner region of the hydrodynamic journal bearing and are provided with axially recessed notches. Here, the axial protrusions belonging to two paired hydrodynamic journal bearings are combined with each other to functionally basically replace the spacer ring in the previous embodiment. In this case, the notches belonging to the two axial protrusions can be combined into through holes that communicate with the hydraulic medium output passage inside the second member. Thus, the hydraulic medium from the hydraulic medium output part can flow along the surface of the hydrodynamic journal bearing to the outer peripheral surface of the axial protrusion. The hydraulic medium at the axial protrusion can further be discharged through the through holes formed by combining the notches to, for example, the hydraulic medium output passage located inside the second member.

[0021] Advantageously, a circumferentially extending hydraulic medium channel is further formed at the outer peripheral surface of the hydrodynamic journal bearing, and the hydraulic medium channel communicates with the hydraulic medium chamber. This is beneficial for forming a hydraulic medium film circumferentially on the entire outer peripheral surface of the hydrodynamic journal bearing. Optionally, according to the axial dimension of the hydrodynamic journal bearing, one, two, three or more hydraulic medium channels can be provided at the outer peripheral surface of the hydrodynamic journal bearing. Preferably, one hydraulic medium channel is provided at the outer peripheral surface of the hydrodynamic journal bearing.

[0022] According to a preferred embodiment, the two hydrodynamic journal bearings of the hydrodynamic journal bearing assembly are constructed identically. Here, the first hydrodynamic journal bearing and the second hydrodynamic journal bearing are designed and manufactured completely identically and are oppositely installed with respect to each other in subsequent steps. In this case, the two hydrodynamic journal bearings can be interchanged with each other, which is beneficial for saving design costs as well as manufacturing and maintenance costs.

[0023] The above object can also be achieved by a hydrodynamic journal bearing unit in another aspect. The hydrodynamic journal bearing includes: a first member and a second member that can rotate relative to each other, wherein the first member has an inner peripheral surface for surrounding the second member, and a boss portion is formed at the inner peripheral surface of the second member; and a hydrodynamic journal bearing assembly constructed according to the above embodiment and arranged radially between the first member and the second member. Here, the hydrodynamic journal bearings of the hydrodynamic journal bearing assembly are fixed to the second member, preferably at its outer peripheral surface, concentrically and axially arranged such that the boss portion of the first member is axially received between the hydrodynamic journal bearings, wherein the inner peripheral surface of the first member and the two axial end faces of the boss portion are respectively connected and transitioned through arc surfaces, and the outer peripheral surface of each hydrodynamic journal bearing and the axially adjacent end faces are respectively connected and transitioned through arc surfaces.

[0024] Thereby, a radial hydrodynamic bearing portion can be formed between the outer peripheral surface of the hydrodynamic sliding bearing and the inner peripheral surface of the first member, and an axial hydrodynamic bearing portion can be formed between the axially end faces of the hydrodynamic sliding bearing that are close to each other and the axial end face of the boss portion of the first member. In addition, thereby, when there is an overturning moment in the first member, such as a gear, the arc surfaces of the hydrodynamic sliding bearing and the boss portion of the first member can achieve a self-aligning function in a matching manner.

[0025] In an advantageous embodiment, the boss portion of the first member is constructed at the axial middle position of the inner peripheral surface of the first member. Thereby, the first member, such as a gear, can be constructed symmetrically in the axial direction, which is beneficial to enhancing the support stability. In addition, in this embodiment, the two hydrodynamic sliding bearings of the hydrodynamic sliding bearing assembly are allowed to be constructed exactly the same. The two hydrodynamic sliding bearings can be interchanged with each other, which is beneficial to saving design costs as well as manufacturing and maintenance costs.

[0026] In a preferred embodiment, the second member is constructed with an input passage for supplying the hydraulic medium to the hydrodynamic sliding bearing assembly. Thereby, there is no need to provide an additional input passage for the hydraulic medium. The hydrodynamic sliding bearing unit can be implemented compactly and at low cost.

[0027] In a preferred embodiment, the second member is constructed with an output passage for discharging the hydraulic medium from the hydrodynamic sliding bearing assembly. Thereby, there is no need to provide an additional output passage for the hydraulic medium. The hydrodynamic sliding bearing unit can be implemented compactly and at low cost.

[0028] The hydrodynamic sliding bearing assembly and the hydrodynamic sliding bearing unit according to the present application can be applied to various fields, especially can be used in the wind power field. Specifically, the hydrodynamic sliding bearing assembly can, for example, rotatably support a planetary gear on a corresponding planetary gear shaft in a gearbox of a wind turbine.

[0029] The hydrodynamic sliding bearing assembly provided herein is configured as a multi-functional bearing assembly that can simultaneously bear radial loads, axial loads, and overturning moments. However, the hydrodynamic sliding bearing assembly has a simple structure, is easy to install, and has a low cost. In particular, the hydrodynamic sliding bearing assembly can bear accidental axial loads, so no additional thrust bearing is required, which can reduce costs. In particular, the mating surfaces of the hydrodynamic sliding bearing and the first member, such as the boss portion of the planetary gear, are both configured as arc surfaces. Thus, it is easy to form a hydraulic medium film, such as an oil film, axially between the hydrodynamic sliding bearing and the boss portion, which is beneficial for the hydrodynamic sliding bearing to bear axial loads; at the same time, the arc-shaped mating surface can achieve a self-aligning function when the first member, such as the planetary gear, overturns, and the hydrodynamic sliding bearing can bear the overturning moment. In particular, the outer peripheral surface of the hydrodynamic sliding bearing and the axial end face facing another hydrodynamic sliding bearing, especially the surface with arc-shaped modification, are hardened coated, that is, the surface of the hydrodynamic sliding bearing for forming the hydraulic medium film, preferably the oil film, is hardened coated. Thus, the hydrodynamic sliding bearing assembly can adapt to the dry friction and boundary friction between the hydrodynamic sliding bearing and the first member, such as the planetary gear, during the start-stop stage. Description of the Drawings

[0030] The features, advantages, and technical effects of the exemplary embodiments of the present application will be described below with reference to the drawings.

[0031] Figure 1 is a schematic axial cross-sectional view of a hydrodynamic sliding bearing unit according to the first embodiment,

[0032] Figure 2 is according to Figure 1 a schematic perspective view of the hydrodynamic sliding bearing in the hydrodynamic sliding bearing unit of

[0033] Figure 3 is according to Figure 1 a schematic perspective view of the spacer in the hydrodynamic sliding bearing unit of

[0034] Figure 4 is a schematic axial cross-sectional view of a hydrodynamic sliding bearing unit according to the second embodiment, and

[0035] Figure 5 is according to Figure 4 a schematic perspective view of the hydrodynamic sliding bearing in the hydrodynamic sliding bearing unit of Detailed Description of the Embodiments

[0036] Figure 1 shows a schematic axial cross-sectional view of a hydrodynamic sliding bearing unit according to the first embodiment. In this embodiment, the hydrodynamic sliding bearing unit is applied in the gearbox of a wind turbine.

[0037] Here, the hydrodynamic journal bearing unit includes a first member implemented as a planetary gear 10 and a second member implemented as a planetary gear shaft 20. The planetary gear shaft 20 is fixed to the planet carrier 30 here.

[0038] The hydrodynamic journal bearing unit further includes a hydrodynamic journal bearing assembly. The hydrodynamic journal bearing assembly is arranged radially between the planetary gear 10 and the planetary gear shaft 20 to rotatably support the planetary gear 10 relative to the planetary gear shaft 20.

[0039] As Figure 1 shown, the hydrodynamic journal bearing assembly includes two hydrodynamic journal bearings, namely a first hydrodynamic journal bearing 40 and a second hydrodynamic journal bearing 50. The two hydrodynamic journal bearings 40, 50 have a substantially sleeve-like structure. In the present embodiment, the first hydrodynamic journal bearing 40 and the second hydrodynamic journal bearing 50 are designed and manufactured identically, whereby they can be interchanged with each other, which is conducive to saving design costs as well as manufacturing and maintenance costs. After assembly, as Figure 1 shown, the first hydrodynamic journal bearing 40 and the second hydrodynamic journal bearing 50 are arranged opposite to each other.

[0040] The first hydrodynamic journal bearing 40 and the second hydrodynamic journal bearing 50 are concentrically and axially arranged and fixed at the outer peripheral surface of the planetary gear shaft 20. Here, the first hydrodynamic journal bearing 40 and the second hydrodynamic journal bearing 50 are in interference fit with the planetary gear shaft 20.

[0041] The hydrodynamic journal bearing assembly further includes a spacer 60, which is arranged axially between the first hydrodynamic journal bearing 40 and the second hydrodynamic journal bearing 50. In this case, the flange 203 of the planetary gear shaft 20, the second hydrodynamic journal bearing 50, the spacer 60, the first hydrodynamic journal bearing 40, and the planet carrier 30 arranged axially in sequence abut against each other.

[0042] The planetary gear 10 has a central hole for surrounding the hydrodynamic journal bearing assembly and the planetary gear shaft 20, and an annular boss portion 101 is formed on the inner peripheral surface of the central hole. In the present embodiment, the boss portion 101 is arranged at the axial middle of the inner peripheral surface of the central hole.

[0043] The first hydrodynamic journal bearing 40 and the second hydrodynamic journal bearing 50 are accommodated in the central hole of the planetary gear 10 such that the boss portion 101 of the planetary gear 10 extends into the axial gap between the first hydrodynamic journal bearing 40 and the second hydrodynamic journal bearing 50. In this case, the spacer 60 is located radially inside the boss portion 101 of the planetary gear 10.

[0044] In the present embodiment, the hydraulic medium is lubricating oil for lubricating each component in the gearbox. Here, the oil can flow into the radial clearance between the outer peripheral surfaces of the two hydrodynamic journal bearings 40 and 50 and the inner peripheral surface of the central hole of the planetary gear 10 and form an oil film serving as a hydraulic medium film. Thereby, a radial hydrodynamic support portion can be formed between the outer peripheral surfaces of the two hydrodynamic journal bearings 40 and 50 and the inner peripheral surface of the central hole of the planetary gear 10. The oil can also flow into the two axial clearances between the axially adjacent end faces of the two hydrodynamic journal bearings 40 and 50 and the axially end face of the boss portion 101 of the planetary gear 10 and form an oil film serving as a hydraulic medium film. Thereby, an axial hydrodynamic support portion can be formed between the axially adjacent end faces of the hydrodynamic journal bearings 40 and 50 and the axially end face of the boss portion 101 of the planetary gear 10.

[0045] As Figure 1 shown, the outer peripheral surface of the first hydrodynamic journal bearing 40 and the axially end face adjacent to the second hydrodynamic journal bearing 50 are respectively connected and transitioned through an arc surface 405, and the outer peripheral surface of the second hydrodynamic journal bearing 50 and the axially end face adjacent to the first hydrodynamic journal bearing 40 are respectively connected and transitioned through an arc surface 505. At the same time, the inner peripheral surface of the planetary gear 10 and the two axially end faces of the boss portion 101 are respectively connected and transitioned through arc surfaces. When there is an overturning moment on the planetary gear 10, the arc-shaped mating surfaces of the two hydrodynamic journal bearings 40 and 50 and the boss portion 101 of the planetary gear 10 can coordinately achieve a self-aligning function, so as to adapt to various actual working conditions.

[0046] In the present embodiment, the outer peripheral surface of the first hydrodynamic journal bearing 40 and the axially end face adjacent to the second hydrodynamic journal bearing 50 are provided with a hardened coating, and the outer peripheral surface of the second hydrodynamic journal bearing 50 and the axially end face adjacent to the first hydrodynamic journal bearing 40 are provided with a hardened coating. Thereby, the above-mentioned surfaces of the hydrodynamic journal bearings 40 and 50 can be adapted to the dry friction and boundary friction between the hydrodynamic journal bearings 40 and 50 and the planetary gear 10 during the starting and stopping stages.

[0047] Figure 2 and Figure 3 respectively show schematic perspective views of the first hydrodynamic journal bearing 40 and the spacer 60 in the hydrodynamic journal bearing unit according to the first embodiment. In particular, in combination with Figures 1 to 3 it can be seen the flow path of the oil serving as the hydraulic medium.

[0048] As Figure 1 and Figure 2As shown, hydraulic medium chambers extending axially, namely hydraulic oil chambers 401 and 501, and hydraulic medium channels extending circumferentially, namely oil channels 404, are formed on the outer peripheral surfaces of the respective hydrodynamic journal bearings 40 and 50. Here, the hydraulic oil chambers 401 and 501 communicate with the oil channels 404. In the present embodiment, two radially opposed hydraulic oil chambers 401 and 501 are respectively provided on the outer peripheral surfaces of the hydrodynamic journal bearings 40 and 50, and the oil channels 404 are arranged at the axial intermediate positions on the outer peripheral surfaces of the hydrodynamic journal bearings 40 and 50. This is conducive to the formation of an oil film along the axial direction and the circumferential direction on the outer peripheral surface of the entire hydrodynamic journal bearing. In addition, each of the hydrodynamic journal bearings 40 and 50 is provided with a hydraulic medium input portion in the form of an oil inlet hole 402 and 502. The oil inlet holes 402 and 502 communicate from the inner peripheral surface of the central hole of the hydrodynamic journal bearings 40 and 50 to the hydraulic oil chambers 401 and 501. Each of the hydrodynamic journal bearings 40 and 50 is also provided with a hydraulic medium output portion in the form of a pressure relief groove 403 and 503. The pressure relief grooves 403 and 503 extend from the hydraulic oil chambers 401 and 501 to the axially adjacent end faces of the hydrodynamic journal bearings 40 and 50, particularly the arc surfaces 405 and 505.

[0049] As Figure 1 and Figure 3 shown, the spacer 60 is formed with an annular groove 601 on its outer peripheral surface and a through hole 602 communicating the annular groove 601 and the inner peripheral surface of the spacer 60.

[0050] As Figure 1 shown, an input passage for supplying oil to the hydrodynamic journal bearing assembly is formed inside the planetary gear shaft 20. Here, the input passage of the planetary gear shaft 20 is connected to the oil inlet holes 402 and 502 of the hydrodynamic journal bearings 40 and 50 through an oil inlet hole 201. An output passage for discharging oil from the hydrodynamic journal bearing assembly is also formed inside the planetary gear shaft 20. Here, the through hole 602 of the spacer 60 leads to an oil return hole 202 of the output passage of the planetary gear shaft 20.

[0051] Thus, the oil pumped by the oil pump can enter the hydraulic oil chambers 401 and 501 successively through the input passage of the planetary gear shaft 20 and the oil inlet holes 402 and 502 of the hydrodynamic journal bearings 40 and 50. The oil can flow from the hydraulic oil chambers 401 and 501 and the oil channels 404 communicating with the hydraulic oil chambers 401 and 501 to the outer peripheral surfaces of the hydrodynamic journal bearings 40 and 50. In addition, the oil can also flow from the hydraulic oil chambers 401 and 501 and the pressure relief grooves 403 and 503 communicating with the hydraulic oil chambers 401 and 501 to the arc surfaces 405 and 505 and the axial end faces of the two adjacent hydrodynamic journal bearings 40 and 50. The oil flowing into the axial gap between the two hydrodynamic journal bearings 40 and 50 can converge into the annular groove 601 of the spacer 60 and can be further discharged through the through hole 602 into the output passage inside the planetary gear shaft 20.

[0052] Figure 4 A schematic axial cross-sectional view of a dynamic pressure sliding bearing unit according to a second embodiment is shown. The dynamic pressure sliding bearing unit according to this embodiment is constructed similarly to the dynamic pressure sliding bearing unit according to the first embodiment. Only the differences between the two embodiments are explained below.

[0053] In the dynamic pressure sliding bearing unit according to the present embodiment, the dynamic pressure sliding bearing assembly includes two dynamic pressure sliding bearings of the same configuration and arranged opposite to each other, that is, the first dynamic pressure sliding bearing 70 and the second dynamic pressure sliding bearing 80 .

[0054] Figure 5 A schematic perspective view showing a dynamic pressure sliding bearing 70 in a dynamic pressure sliding bearing unit according to a second embodiment is shown.

[0055] like Figure 4 and Figure 5 As shown, in the present embodiment, the first dynamic pressure sliding bearing 70 and the second dynamic pressure sliding bearing 80 are arranged close to each other. An annular axial protrusion 706, 806 is configured at the ends of the dynamic pressure sliding bearings 70, 80 that are close to each other, wherein the axial protrusion 706, 806 is configured in the radial inner area of ​​the dynamic pressure sliding bearings 70, 80. The axial protrusion 706 of the first dynamic pressure sliding bearing 70 is provided with a recess 707 that is recessed in the axial direction. The axial protrusion 806 of the second dynamic pressure sliding bearing 80 is provided with a recess that is recessed in the axial direction. Here, the axial protrusions 706, 806 belonging to the two dynamic pressure sliding bearings 70, 80 are combined with each other by being close to each other, thereby functionally basically replacing the spacer 60 in the first embodiment. In this case, the recesses belonging to the two axial protrusions 706, 806 can be combined into a through hole that connects to the output passage inside the planetary gear shaft 20.

[0056] Thus, the oil delivered by the oil pump can enter the hydraulic oil chambers 701 and 801 in sequence through the input passage of the planetary gear shaft 20 and the oil inlet holes 702 and 802 of the dynamic pressure sliding bearings 70 and 80. The oil can flow from the hydraulic oil chambers 701 and 801 and the oil passages connected to the hydraulic oil chambers 701 and 801 to the outer peripheral surfaces of the dynamic pressure sliding bearings 70 and 80. In addition, the oil can also flow from the hydraulic oil chambers 701 and 801 and the pressure relief grooves 703 and 803 connected to the hydraulic oil chambers 701 and 801 to the arc surfaces 705 and 805 at the axial ends close to each other of the two dynamic pressure sliding bearings 70 and 80, and then flow to the outer peripheral surfaces of the axial protrusions 706 and 806. The oil collected here is further discharged to the output passage inside the planetary gear shaft 20 through the through hole formed by the combination of the recesses of the two axial protrusions 706 and 806.

[0057] The hydrodynamic sliding bearing assembly according to the above two embodiments is configured as a multi-functional bearing assembly, which can simultaneously bear radial loads, axial loads and overturning moments. At the same time, the hydrodynamic sliding bearing assembly has a simple structure, is easy to install and has a low cost.

[0058] List of Reference Signs

[0059] 10 First member, planetary gear

[0060] 101 Boss portion

[0061] 20 Second member, planetary gear shaft

[0062] 201 Oil inlet hole

[0063] 202 Oil return hole

[0064] 203 Flange

[0065] 30 Planet carrier

[0066] 40 Hydrodynamic sliding bearing, first hydrodynamic sliding bearing

[0067] 401 Hydraulic medium chamber, hydraulic oil chamber

[0068] 402 Hydraulic medium input part, oil inlet hole

[0069] 403 Hydraulic medium output part, pressure relief groove

[0070] 404 Hydraulic medium channel, oil channel

[0071] 405 Arc surface

[0072] 50 Hydrodynamic sliding bearing, second hydrodynamic sliding bearing

[0073] 501 Hydraulic medium chamber, hydraulic oil chamber

[0074] 502 Hydraulic medium input part, oil inlet hole

[0075] 503 Hydraulic medium output part, pressure relief groove

[0076] 505 Arc surface

[0077] 60 Spacer

[0078] 601 Annular groove

[0079] 602 Through hole

[0080] 70 Hydrodynamic sliding bearing, first hydrodynamic sliding bearing

[0081] 701 Hydraulic medium chamber, hydraulic oil chamber

[0082] 702 Hydraulic medium input part, oil inlet hole

[0083] 703 Hydraulic medium output part, pressure relief groove

[0084] 704 Hydraulic medium channel, oil channel

[0085] 705 Arc surface

[0086] 706 Axial protrusion

[0087] 707 Notch

[0088] 80 Hydrodynamic sliding bearing, second hydrodynamic sliding bearing

[0089] 801 Hydraulic medium cavity, hydraulic oil cavity

[0090] 802 Hydraulic medium input part, oil inlet hole

[0091] 803 Hydraulic medium output part, pressure relief groove

[0092] 805 Arc surface

[0093] 806 Axial protrusion

Claims

1. A hydrodynamic sliding bearing assembly for a wind turbine, which is arranged radially between a first member (10) and a second member (20) that can rotate relative to each other, wherein, the first member (10) has an inner circumferential surface for surrounding the second member (20), and a boss portion (101) is formed at the inner circumferential surface. The inner circumferential surface of the first member (10) and the two axial end faces of the boss portion (101) are respectively connected and transitioned through arc surfaces. Wherein, the hydrodynamic sliding bearing assembly includes two hydrodynamic sliding bearings (40, 50; 70, 80), the hydrodynamic sliding bearings (40, 50; 70, 80) can be fixed to the second member (20) concentrically and axially arranged such that the boss portion (101) is axially received between the hydrodynamic sliding bearings (40, 50; 70, 80). Wherein, the outer circumferential surfaces of the two hydrodynamic sliding bearings (40, 50; 70, 80) are used to form a radial hydrodynamic bearing portion with the inner circumferential surface of the central hole of the first member (10), and the axially adjacent end faces of the two hydrodynamic sliding bearings (40, 50; 70, 80) are used to form an axial hydrodynamic bearing portion with the axial end faces of the boss portion (101) of the first member (10). The outer circumferential surfaces and the axially adjacent end faces of each hydrodynamic sliding bearing (40, 50; 70, 80) are respectively connected and transitioned through arc surfaces (405, 505; 705, 805). The arc surfaces of the two hydrodynamic sliding bearings (40, 50; 70, 80) are used to cooperate with the arc surface of the boss portion (101) to achieve the centering function.

2. The hydrodynamic sliding bearing assembly according to claim 1, characterized in that, the respective outer circumferential surfaces and the axially adjacent end faces of the hydrodynamic sliding bearings (40, 50; 70, 80) are provided with a hardened coating.

3. The hydrodynamic sliding bearing assembly according to claim 1 or 2, characterized in that, an axially extending hydraulic medium cavity (401, 501; 701, 801) is formed at the outer circumferential surface of the hydrodynamic sliding bearing (40, 50; 70, 80).

4. The hydrodynamic sliding bearing assembly according to claim 3, characterized in that, the hydrodynamic sliding bearing (40, 50; 70, 80) is provided with a hydraulic medium input portion (402, 502; 702, 802), and the hydraulic medium input portion (402, 502; 702, 802) communicates from the inner circumferential surface of the hydrodynamic sliding bearing (40, 50; 70, 80) to the hydraulic medium cavity (401, 501; 701, 801).

5. The hydrodynamic sliding bearing assembly according to claim 3 or 4, characterized in that, the hydrodynamic sliding bearing (40, 50; 70, 80) is provided with a hydraulic medium output portion (403, 503; 703, 803), and the hydraulic medium output portion (403, 503; 703, 803) leads out from the hydraulic medium cavity (401, 501; (701, 801) are connected to the axially adjacent end faces of the hydrodynamic journal bearings (40, 50; 70, 80).

6. The hydrodynamic journal bearing assembly according to claim 5, characterized in that a spacer ring (60) is arranged axially between the hydrodynamic journal bearings (40, 50), wherein the spacer ring (60) is configured with an annular groove (601) at the outer peripheral surface of the spacer ring and a through hole (602) connecting the annular groove (601) and the inner peripheral surface of the spacer ring (60).

7. The hydrodynamic journal bearing assembly according to claim 5, characterized in that annular axial protrusions (706, 806) are formed at the axially adjacent ends of the hydrodynamic journal bearings (70, 80), wherein the axial protrusions (706, 806) are arranged in the radially inner region of the hydrodynamic journal bearings (70, 80) and are provided with axially recessed notches (707).

8. The hydrodynamic journal bearing assembly according to any one of claims 3 to 7, characterized in that a hydromechanical medium channel (404; 704) extending circumferentially is further formed at the outer peripheral surface of the hydrodynamic journal bearings (40, 50; 70, 80), and the hydromechanical medium channel (404; 704) is connected to the hydromechanical medium chambers (401, 501; 701, 801).

9. The hydrodynamic journal bearing assembly according to any one of the above claims, characterized in that the two hydrodynamic journal bearings (40, 50; 70, 80) are identically configured.

10. A hydrodynamic journal bearing unit, comprising: - a first member (10) and a second member (20) capable of rotating relative to each other, wherein the first member (10) has an inner peripheral surface for surrounding the second member (20), and a boss portion (101) is formed at the inner peripheral surface, and - the hydrodynamic journal bearing assembly according to any one of the above claims, arranged radially between the first member (10) and the second member (20), wherein the hydrodynamic journal bearings (40, 50; 70, 80) of the hydrodynamic journal bearing assembly are fixed to the second member (20) concentrically and axially arranged such that the boss portion (101) is axially received between the hydrodynamic journal bearings (40, 50; 70, 80), wherein the inner peripheral surface of the first member (10) and the two axially end faces of the boss portion (101) are respectively connected and transitioned through arc surfaces, and the outer peripheral surfaces and the axially adjacent end faces of the respective hydrodynamic journal bearings (40, 50; 70, 80) are respectively connected and transitioned through arc surfaces (405, 505; 705, 805).

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